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Long Piping

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Introduction................................................................................................................. Introduction-1

Objective .................................................................................................................... Introduction-2

Section 1:Section 1:Section 1:Section 1:Section 1: Long Piping Limita Long Piping Limita Long Piping Limita Long Piping Limita Long Piping Limitationtiontiontiontion

1.1 Capacity Loss ........................................................................................................... 1-1

1.2 Oil Return Problem ................................................................................................... 1-3

1.3 Compressor Failure .................................................................................................. 1-4

1.4 High Installation Cost................................................................................................ 1-5

1.5 Unit Orientation ........................................................................................................ 1-6

1.6 Piping Length Limit .................................................................................................. 1-12

Section 2:Section 2:Section 2:Section 2:Section 2: Pr Pr Pr Pr Precautions on Long Piping Installaecautions on Long Piping Installaecautions on Long Piping Installaecautions on Long Piping Installaecautions on Long Piping Installationstionstionstionstions

2.1 Additional Oil ............................................................................................................ 2-2

2.2 Additional Refrigerant ............................................................................................... 2-3

2.3 Oil Trap .................................................................................................................... 2-5

2.4 Suction Accumulator ................................................................................................ 2-7

2.5 Oil Separator ............................................................................................................ 2-7

2.6 Pipe Sizing ............................................................................................................... 2-8

2.7 Crankcase Heater ................................................................................................... 2-19

2.8 Pump Down Cycle ................................................................................................... 2-21

2.9 Minimize Bends ....................................................................................................... 2-22

2.10 Minimize Excessive Height ...................................................................................... 2-23

Section 3:Section 3:Section 3:Section 3:Section 3: Ca Ca Ca Ca Capacity Efpacity Efpacity Efpacity Efpacity Effffffectectectectect

3.1 Pressure Drop Charts ............................................................................................... 3-4

Section 4:Section 4:Section 4:Section 4:Section 4: Piping Installa Piping Installa Piping Installa Piping Installa Piping Installationtiontiontiontion

4.1 Pipe Material ............................................................................................................ 4-1

4.2 Pipe Insulation .......................................................................................................... 4-1

The data and suggestions in this manual are believed current and accurate at the time of publication, but they arenot a substitute for trained, experienced professional service. Individual applications and site variations cansignificantly affect the results and effectiveness of any information. The reader must satisfy him/herself regardingthe applicability of any article and seek professional evaluation of all materials. MCQUAY International disclaim anyresponsibility for actions based on this manual.

Copyright © 2005 by MCQUAY International. All rights reserved. This publication is strictly confidential and ismeant for DISTRIBUTORS of MCQUAY International only. No part of this publication may be reproduced or distributedin any form or by any means, or stored in a database or retrieval system, without the prior written permission ofMCQUAY International.

4.3 Horizontal Runs ........................................................................................................ 4-2

4.4 Vertical Runs ............................................................................................................ 4-4

4.5 Pipe Bends ............................................................................................................... 4-7

4.6 Vibration and Noise in Piping .................................................................................... 4-8

AAAAAppendix ppendix ppendix ppendix ppendix A :A :A :A :A : Common Compr Common Compr Common Compr Common Compr Common Compressor Fessor Fessor Fessor Fessor Failurailurailurailurailureeeee

A.1 Liquid Flood Back ..................................................................................................... A-2

A.2 Flooded Starts .......................................................................................................... A-3

A.3 Liquid Slugging ......................................................................................................... A-4

A.4 Loss of Lubrication ................................................................................................... A-5

A.5 Overheating .............................................................................................................. A-7

A.6 Contamination .......................................................................................................... A-9

A.6 Refrigerant Migration ............................................................................................... A-12

AAAAAppendix B :ppendix B :ppendix B :ppendix B :ppendix B : Suction Suction Suction Suction Suction AccumAccumAccumAccumAccumulaulaulaulaulatortortortortor

B.1 Applications .............................................................................................................. B-3

B.2 Installation ................................................................................................................ B-4

B.3 Sizing and Selecting an Accumulator ....................................................................... B-4

AAAAAppendix C :ppendix C :ppendix C :ppendix C :ppendix C : Oil Se Oil Se Oil Se Oil Se Oil Separparparparparaaaaatortortortortor

C.1 Introduction .............................................................................................................. C-1

C.2 Function ................................................................................................................... C-3

C.3 Installation ................................................................................................................ C-3C.3 Maintenance ............................................................................................................. C-4

AAAAAppendix D :ppendix D :ppendix D :ppendix D :ppendix D : Useful Useful Useful Useful Useful TTTTTaaaaabbbbble and Charle and Charle and Charle and Charle and Chartststststs

IntroductionSplit type air-conditioner units consist of an evaporator unit and condensing unit which are both joined togetherby two lengths of copper piping. Generally, one of them will be in the indoor room while the other will be locatedoutdoors.

The performance specifications of the air-conditioner unit have been given based upon a specified pipe length.Deviations from this standard length will cause variations to the unit performance. There is also a maximumpipe length allowed for these units, whereby if exceeded, the unit may not give reliable performance. Mostmanufacturers will publish these longest distances in both the vertical and horizontal directions where theirevaporator and condenser can be installed apart. Most of the time, installers are not aware of these limitations.As a result, they encounter problems when the units are not performing as specified.

It is important that during installation, these pipe length limits are not exceeded. It is recommended that thepipe lengths be as close to the standard lengths as possible. The relative location of both evaporator andcondensing units are also very crucial to ensure an effective and reliable system.

However, this will not be so easily achievable in practice. The building architectural and structural design maynot allow such straight forward installations. It is very common for these pipe lengths to be longer than thestandard lengths, if not exceeding them. Therefore, it is vital to understand what the failure mechanisms of theair-conditioner unit are when this happens. With this in mind, we can then take the necessary precautions toprevent damage to the units.

Introduction - 1

Intr Intr Intr Intr Introductionoductionoductionoductionoduction

ObjectiObjectiObjectiObjectiObjectivvvvveeeee

The purpose of this Application Manual is to give guidelines into long piping installations of split type airconditioner units. It gives recommendations on the necessary precautions and modifications which are neededto be carried out to maintain the life span of the system. Information is also given on some of the commoncompressor failures encountered with such installations and what are the counter-measures which can beused to prevent them.

The topics covered in this manual are as follows:

a) Long piping limitations.b) Precautions on installation.c) Changes in capacity performance due to long piping.d) Practical piping installation.

Introduction - 2

Section 1Long Piping Limitations

There are a few points that an installer and contractor need to consider when dealing with long piping

installations. These points are:

a) Capacity loss of the system.

b) Problem of oil return to the compressor.

c) Compressor failure.

d) High installation cost.

1.1 Ca1.1 Ca1.1 Ca1.1 Ca1.1 Capacity Losspacity Losspacity Losspacity Losspacity LossCapacity loss is due to pressure loss which is caused by friction in pipe and elevation. Consider the Darcy-

Weisbach equation:

∆∆∆∆∆p = f (L/D) (ρρρρρV2/2) ............ (1.1)where,

∆p = Pressure drop, Pa.

f = Friction factor, dimensionless.

L = Length of pipe, m.

D = Internal diameter of pipe, m.

ρ = Fluid density at mean temperature, kg/m3.

V = Average velocity, m/s.

Therefore:

∆∆∆∆∆p ∝∝∝∝∝ L and V2

∆∆∆∆∆p ∝∝∝∝∝ 1/D

This equation can also be expressed in the form of specific energy:

∆∆∆∆∆h = ∆∆∆∆∆p/ρρρρρg = f (L/D) (V2/2g) ............ (1.2)where,

∆h = Energy loss, m.

g = Gravity acceleration, m/s2.

And:

∆∆∆∆∆h ∝∝∝∝∝ L and V2

∆∆∆∆∆h ∝∝∝∝∝ 1/D

1 - 1

The remaining terms are the same as mentioned in equation (1.1).

By considering equation (1.1), it is known that L is directly proportional to ∆∆∆∆∆p. When L increases (with otherterms remaining constant); ∆∆∆∆∆p will increase proportionally as well. In other words, when the piping lengthincreases, the pressure drop encountered will be increasing proportionally as well.Again, considering equation (1.1), it is known that D is indirectly proportional to ∆∆∆∆∆p.When D decreases (other terms remaining constant), ∆∆∆∆∆p will also increase proportionally as well. Therefore,when the piping diameter decreases, the pressure drop encountered will be increasing proportionally as well.

The pressure drop and capacity drop are directly related to each other. If the pressure drop decreases,the capacity drop will be also do the same. If the piping length is long, the flow will encounter a higher pressuredrop. Therefore, the capacity for longer piping will decrease as well. Same for decreasing pipe diameter,the pressure drop will be large and hence, the capacity will drop as well.

Why will the pressure drop cause a reduction in capacity? Basically, there are three reasons:a) Suction line pressure drop due to friction loss will force the compressor to operate at a lower suction pressure with a resultant reduction of refrigerant mass flow.

b) Pressure drop due to friction loss in discharge lines causes the compressor to operate at a higher pressure resulting in reduced refrigerant mass flow and increased power consumption.

c) Liquid line pressure drop due to friction loss and liquid static head may cause flash gas. This flash gas will reduce the performance of the expansion device as the liquid column cannot be maintained.

1 - 2

1.2 Oil R1.2 Oil R1.2 Oil R1.2 Oil R1.2 Oil Returetureturetureturn Prn Prn Prn Prn Proboboboboblemlemlemlemlem

The functions of oil in refrigeration systems are:a) Minimize mechanical wearb) Reduce frictionc) Lubricate moving partsd) Seal clearancese) Deaden noise, andf) Assist to transfer heat.

In the compressor, oil and refrigerant will mix continuously. Refrigeration oils are soluble in liquid refrigerantand mix completely at normal room temperatures. Since oil must pass through the compressor cylinders toprovide lubrication, a small amount of oil is always in circulation with the refrigerant. Oil and refrigerant vapourdo not mix readily and the oil can be properly circulated through the system if gas velocities are high enoughto sweep the oil along.

If refrigerant velocities are not sufficiently high, oil will tend to lie at the bottom of the evaporatortubing which, decreases heat transfer efficiency and possibly causing a shortage of oil in thecompressor. The problem arises when the piping is longer than the standard testing length of 7.6m. More oilwill tend to be trapped along the longer piping and only a lesser amount will be returned to the compressor.This damages the compressor internal moving parts due to lack of lubrication.

As evaporative temperatures are lowered, this problem becomes more critical since the viscosity of the oilincreases with a decrease in temperature. Since the longer piping will cause a lower evaporating pressuredue to the higher pressure drop, the oil becomes more viscous and more difficult to be swept along with therefrigerant. For these reasons, a proper design of tubing is essential for satisfactory oil return in a refrigerationcycle.

One of the basic characteristics of a refrigerant and oil mixture in a sealed system is the fact that refrigerantwill migrate through the system into the oil in the compressor. On reaching the compressor, the refrigerant is‘absorbed’ into the oil and this migration will continue until the oil is saturated with liquid refrigerant. Theamount of refrigerant the oil will attract is primarily dependent on the temperature differential between the oiland refrigerant.

When the pressure of a saturated mixture of refrigerant and oil is suddenly reduced, as happens in a compressoron start up, the amount of liquid refrigerant required to saturate the oil is drastically reduced, and the remainderof liquid refrigerant flashes into vapour, causing violent boiling of the refrigerant and oil mixture. This causesthe typical foaming often observed in the compressor on start up, which can move all of the oil out of thecompressor in less than a minute.

With longer piping run, more refrigerant charge is required, thus causing more refrigerant to migrate into theoil. Foaming will be prolonged during start-up causing higher probability of the compressor failure.

The introduction of excessive liquid refrigerant into the compressor can also cause a loss of oil pressure or oildelivery to the bearings even though the level of the refrigerant and oil mixture in the compressor is high. Thehigh percentage of liquid refrigerant entering the compressor not only reduces the lubricating quality of theoil but on entering the oil pump the intake may flash into vapour, restricting the entrance of adequate oil tomaintain proper lubrication of the compressor bearings. Should this oil dilution effect continue, compressorfailure will occur.

1 - 3

1.3 Compr1.3 Compr1.3 Compr1.3 Compr1.3 Compressor Fessor Fessor Fessor Fessor Failurailurailurailurailureeeee

With longer piping installations, the chances for compressor failure to occur becomes higher. The following arethe common causes of mechanical failure due to long piping applications:

a) Refrigerant flood back.

In long piping application, the system will need to have a higher refrigerant charge level in order to obtainreasonable capacity. Therefore, the system will accumulate more liquid refrigerant. Refrigerant flood backoccurs when liquid refrigerant flows through the suction line into the compressor during the running cycle.The liquid refrigerant will wash away the oil off the bearing surface and result in excessive wear.

b) Flooded start.

Liquid migration happens when the compressor is off for long periods. Refrigerant migrates to the compressorand mixes with oil. During start-ups, refrigerant foaming will wash the oil away from the bearings. Withlonger pipe length, more refrigerant gets to migrate into the oil and the foaming becomes more violentduring start-ups. The moving parts get ‘starved’ of lubrication during this period of time, and this will causefailure.

c) Slugging.

Slugging is the result of significant quantity of liquid refrigerant entering into the cylinder of the compressor.The hydraulic force from liquid refrigerant, oil or a mixture of both will damage the compressor cylinder. Inshort, slugging results from severe flooded starts where some of the foam gets sucked into the compressionchamber, resulting in liquid compression. The risk of slugging is higher with long piping installationsbecause of the higher refrigerant charge required by the system.

d) Loss of oil.

With long piping applications, there is a higher risk of the compressor oil flowing through the system andbeing trapped within the system (evaporator, condenser, piping, accumulator and other components) andreturning only a little oil to the compressor. Lack of lubrication will lead to:

i. Oil not reaching the bearings.ii. Oil dilution.iii. Oil thinning by overheating.

A symptom of this problem is the compressor gets overheated due to the friction in moving parts.

1 - 4

1.41.41.41.41.4 High InstallaHigh InstallaHigh InstallaHigh InstallaHigh Installation Costtion Costtion Costtion Costtion Cost

Consider the equation below:

Q = AV ............ (1.3)

where,Q = Flow rate, m3/s.A = Cross-sectional area of pipe (based on Inside Diameter), m2.V = Average velocity, m/s.

When a smaller diameter pipe is used, high velocity is required to convey the necessary quantity of fluid. Butbased on equation (1.1), high velocity causes larger pressure drop and hence, the capacity will be reduceddrastically. It will also increase the operating cost due to the compressor having to do more work.

When larger pipes are used, a lower velocity is required to give the desired quantity of flow. Low velocity willcreate less pressure drop. However, from the stand point of initial cost, the larger pipes are more costly thanthe smaller pipes.

When applying long piping, the following should be noted by end users (which will increase the cost ofinstallation):

a) Longer pipe used.b) Bigger pipe used – to reduce the pressure drop.c) More refrigerant charge.d) More installation work.e) More potential problems encountered (flood back, slugging, oil return and etc).

1 - 5

1.51.51.51.51.5 Unit OrientaUnit OrientaUnit OrientaUnit OrientaUnit Orientationtiontiontiontion

The location of both indoor unit and outdoor unit are very important. Different types of orientation in differentoperating mode will have different effects on oil return, refrigerant migration, and liquid refrigerant enteringthe compressor. The following section will show what could happen if :

a) The indoor unit is below the outdoor unit, orb) The indoor unit is above the outdoor unit.

Cooling mode oil return case.

Consider when the indoor unit is below the outdoor unit. When the system is operating, the oil will have to goback upwards to the compressor against gravitational forces. The amount of oil return may be very little andwill directly harm the compressor internal moving parts. If both the ambient temperature for both indoor andoutdoor are low (e.g. 19 ° C or lower), the oil viscosity will increase and this makes the amount of oil returningback to the compressor much lesser. This is a very critical condition with the outdoor unit locatedabove the indoor unit. With long piping lengths, this phenomenon becomes more severe. See Figure 1.1.

Figure 1.1 : Oil return - cooling mode

1 - 6

[evap] 19ºC

[cond] 19ºC

O/D

I/D

oil return up

low fan

Cooling mode cold start case

For the refrigerant migration case, the vapor refrigerant will tend to move to the compressor when it is off forlong periods. This phenomenon is explained in Section 1.1.2. Note that this condition becomes more apparentwhen there is a larger ambient temperature difference between the indoor and outdoor units. When theindoor unit is above the outdoor unit, the migration of refrigerant becomes easier as the downwardflow of refrigerant is helped by gravity. See Figure 1.2. With longer pipes, the degree of migration increasesdue to the higher refrigerant charge.

Figure 1.2 : Cold start – cooling mode

Cooling mode liquid flood back case

When the system is operating in cooling mode, any unvaporized liquid refrigerant will flow out from theevaporator unit and flood into the compressor. Generally, a compressor cannot tolerate any liquid flow into itas liquid compression will occur. This will damage the compressor moving parts. This phenomenon is morecritical when the indoor unit is higher due to the gravitational forces making the liquid easier to flow downwards.Figure 1.3 represents this case. This situation is aggravated with long piping installations due to the extrarefrigerant charge required.

I/D

O/D

[off] 19ºC or lower

[off] 35ºC

refrigerant migration

I/D

O/D

[cond] 46ºC or 19ºC

[evap] 27ºC or 19ºC

liquid easier to flow down to compressor

low fan

Figure 1.3 : Liquid flood back - cooling mode

1 - 7

Heating mode oil return case

When running under the heating mode, the connecting pipes become the refrigerant discharge lines. By havingthe indoor unit (condenser) on a higher elevation with respect to the outdoor unit, oil will be pumped upwardsby the compressor. Figure 1.4 represents this case. With long pipe installation, the oil velocity may becomelower and gets accumulated inside the indoor heat exchanger.

I/D

O/D

[evap] 8ºC or lower

[cond] 20ºC

oil pumped up

1 - 8

Figure 1.4 : Oil return - heating mode

Heating mode cold start case

For the refrigerant migration case, the same phenomenon as explained in Section 1.1.2 will occur. When theindoor unit is above the outdoor unit, the migration of refrigerant takes place much easier due to gravitationaleffects. This case is more critical than the Cooling Mode (section 1.5.2) as the outdoor unit ambient temperatureis much lower, causing a higher temperature differential between the two indoor and outdoor units. Figure 1.5represents this case. The longer the pipe is, the higher will be the migration rate due to the higher refrigerantcharge.

Figure 1.5 : Cold start – heating mode

I/D

O/D

[off] 8ºC or lower

[off] 20ºC

refrigerant migration

Heating mode liquid flood back case

When the indoor unit (condenser) is higher than the outdoor unit (evaporator), and the system is runningunder the heating mode, the liquid refrigerant from the condenser is able to flow down to the outdoor unitmore easily with the help of gravitational pull. With a high refrigerant charge, there is a higher risk of havingliquid compression. Therefore, due to this type of unit orientation, and also because of the defrost cycle (seeSection 1.5.7), it is considered as a critical condition for heating cycle. The longer the pipe is the higherwill be the risks due to the higher refrigerant charge.

Figure 1.6 : Liquid flood back – heating mode

I/D

O/D

[evap] 24ºC

[cond] 27ºC

liquid easier to flow down to compressor

1 - 9

Defrosting cycle

The defrosting cycle occurs when the system is running under the heating mode. The purpose of this cycle isto help melt any ice build-up on the outdoor coil which has been operating as an evaporator. If the ice is notremoved, the heating performance of the system will deteriorate as the ice will act as an insulation on the coilsurface, preventing heat transfer.

To defrost, the system will momentarily switch back to the cooling mode (when the operation of the 4-wayvalve reverses the refrigerant flow) where the outdoor coil becomes the hot condenser to melt the ice. Whenthe defrost is completed, the system will then resume back to heating mode. During this defrost period, theindoor unit fan will stop. As a result, this may cause the liquid refrigerant entering the indoor coil to not be ableto evaporate fast enough. The excess liquid refrigerant will then flow to the compressor. By having the indoorin a higher elevation and with long pipe length (hence, higher refrigerant charge), this becomes more evidentas the liquid flowing down is assisted by gravity. Liquid flood back and slugging may occur. This in turn willlead to compressor failures.

See following diagrams.

1 - 10

Indoor coil (condenser)

Outdoor coil (evaporator)

Compressor

4-way valve

Expansion device

Ice build-up on coil surface

Figure 1.7 : Refrigerant flow during normal heating cycle

Indoor coil (evaporator)

Outdoor coil (condenser)

Compressor

4-way valve

Expansion device

Fan stopped

Incomplete evaporation, liquid floodback to compressor

Figure 1.8 : Refrigerant flow during DEFROST cycle

1.61.61.61.61.6 Piping Length LimitsPiping Length LimitsPiping Length LimitsPiping Length LimitsPiping Length Limits

In summary, compressor failure is the main consideration with long piping applications. See Appendix A formore detailed explanation on compressor failures. Piping length should be as short as possible to prevent thecompressors from breaking down. In view of the importance of unit orientation, care must be taken to keep tothe allowable maximum height difference.

Special precautions must be taken when there is no choice but to use longer pipe lengths. Understandably, theextent of these precautions must be balanced with the increased cost of installation.

The following table shows the recommended piping length limits for different condensing units:

Note* : Applicable to model with built-in accumulator for long piping application only. Please refer to distributor for further details.

Table 1.1: Pipe lengths for different condensing units

The standard pipe length, where the units are rated at is 7.6 meters (25 feet). A more thorough explanationon precautions needed with longer pipe installations are given in the next chapter. Pipe lengths longer thanthose specified in Table 1.1 is not recommended.

It is also not necessary to change the recommended pipe sizes for these units, as long as these limits are notexceeded. In general, the outdoor unit pipe size connections should always be used as the reference. Table1.2 shows the pipe sizes for different condensing units.

1 - 11

Model Maximum Length (m)

Maximum Height (m)

Maximum number of bends allowed

SL10B/BR/10C/CR 12 5 10SL15B/BR/15C/CR 12 5 10SL20B/BR/20C/CR* 25 15 10SL25B/BR/25C/CR* 25 15 10SL30/40/50C/CR* 45 25 10SL60/61C/CR* 35 15 10VCU25A 15 8 10VCU30/35/40/50A 20 10 10MSS60C/CR/75C/CR* 45 25 10MSS100/125/150B/BR/C/CR/D/DR/E/ER* 45 25 10MSS200/250/300D2/DR2* 45 25 10

Suction (“) Liquid (“)SL10B/BR/C/CR 3/8 1/4SL15B/BR/C/CR 1/2 1/4SL20B/BR/C/CR 5/8 1/4SL25B/BR/C/CR 5/8 3/8

VCU25/30A 5/8 3/8SL30C/CR 5/8 3/8

SL40/50C/CR 3/4 3/8VCU35/40/50A 3/4 3/8SL60/61C/CR 3/4 1/2

VCU60A 7/8 1/2MSS60C/CR 3/4 1/2MSS75D/DR 1 1/2

MSS100B/BR/C/CR/D/DR/E/ER 1-1/8 5/8MSS125/150B/BR/C/CR/D/DR/E/ER 1-3/8 5/8

MSS200D2/DR2 1-1/8 5/8MSS250/300D2/DR2 1-3/8 5/8

Pipe size**Model

Note**: Subject to change without prior notice. For updated information, please refer to Technical Manuals.

Table 1.2 : Pipe sizes for different condensing units

1 - 12

Section 2Precautions On Long Piping InstallationsThere are several considerations when dealing with long piping installations. These include:

a) Additional oil.b) Additional refrigerant.c) Oil traps.d) Suction accumulator.e) Oil separator.f) Pipe sizing.g) Crankcase heater.h) Pump down cycle.i) Minimise bends.j) Minimise excessive heights.

2 - 1

2.12.12.12.12.1 AdAdAdAdAdditional Oilditional Oilditional Oilditional Oilditional Oil

Each compressor has a rated oil holding capacity. It is important to check with the compressorspecifications on these oil charges as each compressor comes pre-charged with oil. This specifiedcompressor oil holding charge is sufficient for a standard piping installation of 7.6m (24.9 feet).

With longer pipe lengths, it is important to add in additional oil into the system. This is necessarybecause some of the oil will be pumped out of the compressor and stick to the internal pipe surfaces.Additional oil is needed to maintain a safe oil level in the compressor sump.

As a guideline, from the actual pipe run, for every 10ft of extra length from standard testinglength, 3 fl.oz of oil (1 fl.oz ≈≈≈≈≈ 30cm3 ≈≈≈≈≈ 0.03l) should be added into the system.

Sample calculation 01:a) Standard factory testing length = 7.6m / 24.9 ftb) Actual pipe length = 10.0m / 32.8ftc) Compressor specifications:

Oil charge = 38fl.oz.

Extra length = 32.8ft – 24.9ft = 7.9 ft

With 10ft = 3fl.oz. , the extra oil charge for the extra length of 7.9ft = 2.37fl.oz.

Therefore, an additional 2.37fl.oz of oil should be added into the compressor in this example, giving atotal charge of 38 + 2.37 = 40.37 fl. oz.

2 - 2

2.22.22.22.22.2 AdAdAdAdAdditional Rditional Rditional Rditional Rditional Refrigefrigefrigefrigefrigerererererantantantantant

Similar to the additional oil case, each compressor has a rated refrigerant maximum holding capacity. As ageneral practice, do not exceed these limits in order to prevent the compressor from breakdown. It is importantto double check with the compressor specifications on the refrigerant charge limits.

With the longer pipe lengths, more refrigerant is needed to fill the extra volume. The refrigerant charge in thedelivered unit is sufficient for the standard pipe length of 7.6 meters.

It is also important to understand the difference between having the expansion device located in theindoor unit or the outdoor unit. If the expansion device is located at the indoor unit, the entire liquid line willbe filled with liquid refrigerant before expanding at the indoor unit. This will be considered as a singlephase flow in the liquid line. The refrigerant amount required will be significantly higher.

When the expansion device is in the outdoor unit, the refrigerant will begin to expand along the liquid line.This will be considered as a two phase flow in the liquid line. As a result, the refrigerant amount requiredis lower.

The additional amount of refrigerant required can be calculated once the density of the refrigerant alongthese pipes is known. As a guideline, this value should not be more than the maximum refrigerant charge ofthe compressor.

Sample calculation 02:a) 1st option pipe length = 40ft = 12.2mb) 2nd option pipe length = 75ft = 22.9mc) Standard pipe length = 7.6md) L type hard copper tube with OD size = ½”e) Density of refrigerant R-22, ρR22 at 40oC = 1129kg/m3 (saturated temperature of liquid at condenser outlet).f) Standard factory charge = 2.50kgg) Compressor maximum refrigerant charge = 3.60kgh) Given that total charge must not be greater than the compressor maximum charge.i) The expansion device located at the indoor unit.

From Table D.5, we look at L type hard copper tube with OD = ½”, ID = 0.430in (≈0.011m). Also fromthe R22 Thermo Physical Properties, ρR22 at 40oC = 1129kg/m3.

It is known that:Mass = Volume x Density

Hence,∆m = ∆V x ρR22 ……………… (2.1)

Where, ∆m is the additional refrigerant mass required for the additional pipe length∆V is the additional refrigerant volume due to the additional pipe length

If d is the pipe internal diameterL is the pipe length which is equal to the on site pipe length minus the standard pipe lengthThen,

∆m = 0.25 x π x d2 x L x ρR22

∆mL=12.2m = 0.49kg (for 1st option pipe length)∆mL=22.9m = 1.64kg (for 2nd option pipe length)

For 1st option case; Total charge = Extra charge + Standard factory charge = 0.49 + 2.50 = 2.99kg ! 2.99kg < 3.6kg

For 2nd option case; Total charge = Extra charge + Standard factory charge = 1.64 + 2.50 = 4.14kg ! 4.14kg > 3.6kgThus, the second option pipe length is not recommended.

2 - 3

Sample calculation 03:

Continuing from sample calculation 02, but this time with an outdoor expansion device. As explained earlierthis will be considered as a two phase flow in the liquid line. The refrigerant amount required would now belower. It is difficult to exactly quantify the refrigerant charge in this situation as the actual expansion processthat occurs in the expansion device is not known.

However, it is estimated that the refrigerant required is 40% less compared to the amount needed when theexpansion device is at the indoor unit.

Hence,

∆mL=12.2m = 0.49/1.4 = 0.35kg (for 1st option pipe length)

∆mL=22.9m = 1.64/1.4 = 1.17kg (for 2nd option pipe length)

For 1st option, the total charge = Extra charge + Standard factory charge

= 0.35+ 2.50

= 2.85kg ( < 3.6kg )

For 2nd option, the total charge = Extra charge + Standard factory charge

= 1.17 + 2.50

= 3.67kg ( > 3.6kg )

The second option pipe length is still not recommended in this situation.

2 - 4

In normal installation cases, oil traps are not required. However, when piping is long, oil traps are requiredto be installed at fixed intervals along the vertical suction pipe. This is especially so when the outdoorunit is located on a higher elevation than the indoor unit. These oil traps help to get any accumulated oilto move upwards, as shown in Figure 2.1. The design of the traps will forcibly cause the gaseous refrigerantto pass through the oil thus, carrying it upwards back to the compressor.

As a guideline, an oil trap is required at every 10 to 15ft (3 – 4.6m) intervals.

Figure 2.2 illustrates how oil traps are installed.

However, the high pressure drop across such traps may cause high capacity reduction.

Figure 2.1: Internal refrigerant flow inside an oil trap

2 - 5

2.32.32.32.32.3 Oil Oil Oil Oil Oil TTTTTrrrrraaaaappppp

EVAPORATOR

EVAPORATOR

TO COMPRESSOR

TO COMPRESSOR

30’

15’

15’

15’

45’

Figure 2.2: Oil traps installations

2.4 Suction 2.4 Suction 2.4 Suction 2.4 Suction 2.4 Suction AccumAccumAccumAccumAccumulaulaulaulaulatortortortortor

A suction accumulator serves as a vessel to store any liquid refrigerant which may return back alongthe suction line to the compressor. It will protect the compressor from liquid floodback and slugging.All OYL heat pump units have a built-in suction accumulator in the outdoor unit, but not for thecooling only units.

Nevertheless, it is not recommended to have an additional suction accumulator installed in theunits as long as the maximum pipe length limits defined in Section 1.6 are not exceeded. The existingaccumulator in the unit is able to provide sufficient protection to the compressor within the specifiedpipe length limits.

A more thorough explanation and study on suction accumulator is given in Appendix B.

2.5 Oil Se2.5 Oil Se2.5 Oil Se2.5 Oil Se2.5 Oil Separparparparparaaaaatortortortortor

The oil separator has been designed to remove compressor oil along the discharge line. It is usefulto ensure sufficient oil return back to the compressor. However, it is not recommended that anadditional oil separator be installed in the units as long as the maximum pipe length limits are notexceeded.

The unit will be able to function properly within the specified limits, provided that care is taken to haveoil traps along the pipe line (see Section 2.3) and that the refrigerant velocity in the pipes are sufficientlyhigh to carry the oil back to the compressor (see Section 2.6).

Appendix C gives a more detailed study and explanation of the oil separator.

2 - 6

2.62.62.62.62.6 Pipe SizingPipe SizingPipe SizingPipe SizingPipe Sizing

Refrigerant pipe lines must be selected for optimum size with respect to:

a) Initial cost.b) Pressure drop.c) Oil return.

It is desirable to have line sizes as small as possible from the standpoint of low initial cost. However,the overall system performance must be evaluated and the following recognised:

a) Suction and discharge line pressure drop due to friction losses reduces compressorcapacity and increases power consumption.

b) Liquid line pressure drop due to friction loss and liquid static head may cause flash gas(Flash gas is the refrigerant gas which results from the vaporisation of liquid refrigerantto cool the remaining liquid refrigerant to a lower pressure level).

c) Suction and discharge lines must be sized for proper gas velocity to assure oil return tothe compressor.

The design considerations with long refrigerant piping installations are:

a) Assure positive and continuous return of oil to the compressor crankcase.b) Refrigerant pressure losses are inevitable with long piping. This should not be

remedied at the expense of retarding oil return to the compressor.c) Prevent liquid refrigerant from entering the compressor during running, off cycles and

start up.d) Avoid trapping of oil in the evaporator or suction line which may subsequently return to

the compressor as large slug with possible damage to the compressor.

In view of the above mentioned considerations, it is recommended that the refrigerant pipe size bemaintained as specified on the indoor and outdoor units. It is not necessary to resize the pipe aslong as the refrigerant pipe length limits are not exceeded.

2 - 7

2.6.1 Suction lineThe suction line should have the following characteristics:

a) A total pressure drop of not more than 2oF change in saturation temperature (which isequivalent to 3 psi for R-22 refrigerant @ 40ºF evaporating temperature). Of course, forlong piping installations, this value will be much higher.

b) Sufficient velocity (>1500fpm for vertical riser, >750 fpm for horizontal runs) for oil returnto the compressor (greater refrigerant velocities are obtained by decreasing the size ofthe suction line. However this will create a higher pressure drop).

Note: (Criteria (b) has higher priority over (a)).

c) Prevention of liquid refrigerant from draining into the compressor during “OFF” cycle.

When installing the evaporator below the compressor, using a “trap” at the bottom of the pipe riseris necessary. The purpose of the trap is to drain oil and liquid refrigerant out of the line to which theexpansion valve bulb is strapped. See following diagram:

Figure 2.3: Evaporator located below the compressor.

Figure 2.4: Evaporator located above the compressor.

The trap should be as small as possible to prevent large slugs of oil being returned to the compressor whenthe trap clears. When a suction riser is 30 feet or more in length, an oil trap should be installed every 15 feetof vertical rise. This trap aids in oil return and provides a drainage point for oil, which is en route up the riserwhen the compressor stops. When the unit starts again, the oil is returned to the compressor quickly and ina relatively small slugs. See Section 2.3.

Evaporator

Trap To

compressor

2 - 8

When installing the evaporator above the compressor, using an inverted “Loop” can prevent refrigerantfrom draining into the compressor during “OFF” cycle. However, the loop will not prevent refrigerant migrationdue to temperature of the evaporator being higher than the compressor.

Evaporator To compressor

2.6.2 Discharge linePressure drop due to friction loss in discharge lines causes the compressor to operate in higher pressureresulting in reduced capacity and increased power consumption.

Discharge lines should have:

a) A total pressure drop of 1oF to 2oF change in saturation temperature (equivalent to 3.5 psi forR-22 refrigerant @ 120ºF condensing temperature). Long piping will give higher readings.

b) Sufficient velocity (>1500fpm) for oil return to the compressor.

Note: (Criteria (b) has higher priority over criteria (a))

c) A means to prevent refrigerant from draining back to compressor head during the “OFF”cycle.

2 - 9

Long discharge pipe lines are only encountered during the reversed cycle heating mode. The same pipe isthe suction line during the cooling mode. Therefore, the main consideration with long discharge pipe installationsis the discharge oil line trap, which is actually the same as the suction line oil traps. The same rule applies,i.e. a trap should be installed every 15 feet of vertical rise. These traps will aid in oil return and provide adrainage point for oil that is en route up the riser when the compressor stops, as well as for liquid refrigerantwhich may condense during the “OFF” cycle.

2.6.3 Liquid line

When the refrigerant is in liquid state, the oil in the liquid line is readily carried along by the refrigerant to theevaporator. There is no problem with oil return in liquid lines. Thus, the design of the liquid piping is lesscritical than that of the suction lines and the discharge lines.

The problem encountered in the liquid line is mainly one of preventing the liquid from flashing before itreaches the refrigerant control (capillary tube or thermal expansion valve).

The problem of flash gas in the liquid line is that:

a) It reduces the capacity of the refrigerant control.b) It causes erosion of the valve pin and seat.c) It often results in erratic control of the liquid refrigerant to the evaporator.

To avoid flashing of the liquid in the liquid line, sufficient liquid subcooling is required along the pipe line.

The liquid line should be designed with a maximum gas velocity of 360 fpm.

2.6.4 Refrigerant piping checking method

This section provides a general guide on how to check the refrigerant piping.

Procedure:1) Select indoor and outdoor models:

a) Capacity (Btu/hr or tons)b) Original gas and liquid line size.c) Standard factory length.

2) Obtain the following parameters:a) Horizontal pipe length. Check if pipe limits have been exceeded.b) Vertical pipe length. Check if pipe limits have been exceeded.c) Number of bends.d) List of fittings installed, e.g.: filter drier, valves, sight glass.

3) Based on the information from 1(a) and 1(b), use the pressure drop charts (Figure D.4) andvelocity charts (Figure D.3) for the following:a) Pressure drop for current pipe size and pipe size at least 2 sizes bigger than current size.b) Velocity in pipe for current pipe size and for pipe size at least 2 sizes bigger than current size.

Note: The charts are applicable only for refrigerant R-22.

4) Based on the information from 2(a) and 2(b), calculate the actual pressure loss for the pipesizes.

5) Based on the information from 2(c) and 2(d), find from Table D.1 to Table D.6 for the equivalentlengths of the fittings such as elbows and valves.

6) Check the values against the design criteria set for pressure drop and velocity in gas line. Thedesign criteria are listed as below:a) Gas line criteria:

i) Minimum horizontal line gas velocity = 750fpmii)Minimum vertical risers gas velocity = 1500fpm

2 - 10

7) Check the refrigerant velocity of the standard pipe size. Check also the refrigerant pipe pressuredrop. Determine the performance of the standard pipe size. Compare the values with thosepipes which are 2 sizes larger as reference.

8) Get factory standard length; calculate the additional oil from the actual pipe run. For every 10ft ofextra length from standard testing length, add 3 fl.oz. of oil (1 fl.oz. ≈ 30cc).

9) Refer to Table D.5. Based on the length and inner diameter of the pipe, find theamount of refrigerant to be added in.

Sample calculation 06:Capacity = 50000Btu/hr (Note: 1ton = 12000Btu/hr).Suction line size = ¾” (OD). L type hard copper pipe.Liquid line size = 3/8" (OD). L type hard copper pipe.40oF (4.4ºC) evaporation temperature.120oF (48.9ºC) condensing temperature. (Refrigerant density = 1087 kg/m3)Standard testing length = 7.6m.Compressor maximum R22 holding capacity = 4.5kg.Standard R22 charge = 2.5kg.System is utilizing expansion valve (indoor).Cooling mode system.

2 - 11

6’

2’

5’

5’

4’

15

4’

7’

10

10

Evaporator

Condenser NOTE : Dimensions are not to scale

Figure 2.5 : Schematic diagram for sample problem

Capacity = 4.17 tons (5 hp)Total pipe length = 68 ft (20.7 meters)Elevation = 15 ft (4.6 meters)

With reference to the specifications in Secton 1 for a 5 hp unit (50 meters maximum length, 15 meters maximumheight), the total pipe length and elevation are still within the limits.

We can thus build the following tabulation:

Table 2.1: Tabulated values for various parameters.

For this calculation example, it is necessary to perform an interpolation to obtain the equivalent length le (7/8)and le (5/8) of the bends from the available data in Table D.1 and D.2.

Formula used to obtain these values is:

li = li-1 + [(φi – φi-1) /(φi+1 – φi-1)] x (li+1 – li-1)

Where: li = Equivalent length to be determine.li-1 = 1 step smaller equivalent length .li+1 = 1 step bigger equivalent length.φi = Diameter of li.φi-1 = 1 step smaller diameter.φi+1 = 1 step bigger diameter.

Equivalent length for 90o long radius bend for 7/8", le le (7/8) = le (3/4) + [(OD7/8 – OD3/4)/(OD1 – OD3/4)] x (le (1) – le(3/4)) = 1.40 + [(7/8 – 3/4)/(1 – 3/4)] x (1.70 – 1.40) = 1.55

Equivalent length for 90o long radius bend for 5/8", le le (5/8) = le (1/2) + [(OD5/8 – OD1/2)/(OD3/4 – OD1/2)] x (le (3/4) – le(1/2)) = 1.00 + [(5/8 – 1/2)/(3/4 – 1/2)] x (1.40 – 1.00) = 1.20

With these answers, the pressure drop across the pipes can be calculated, as shown in Table 2.1.As expected, the pressure drop across the larger pipes is found to be much lower.

With this installation, the extra pipe length = 68ft – (7.6m / (0.3048m/ft))= 43.1ft

Therefore, the extra lubricant oil required = Extra length x (0.3fl.oz/ft)= 12.92fl.oz.

2 - 12

Sect

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OD

Siz

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ch)

Vel

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(fpm

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e 2.

6.

Num

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.

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D.2

.

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c =

a x

b

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t), d

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D.3

, D.4

& D

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Tota

l len

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(ft),

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h (f

t) f =

c +

d +

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Pres

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(psi

), g.

Ref

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Fi

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2.7

Cal

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pres

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p (p

si)

h =

f x (g

/100

)

3/4 4000 1.40 12.60 0.00 80.60 15 12.1 7/8 2700 1.55 14.00 0.00 82.00 6.5 5.3 Suction 1 2100

9 1.70 15.30 0.00

68 83.30 3.2 2.7

3/8 340 0.90 8.10 0.00 76.10 25 19.0 1/2 190 1.00 9.00 0.00 77.00 5.5 4.2 Liquid 5/8 120

9 1.20 10.80 0.00

68 78.80 1.8 1.4

Refer to Table D.5 to determine the internal pipe diameter. The extra refrigerant required is calculated asfollows :

OD =3/8" case (ID = 0.305").Extra R22 = ρV = 0.25πd2Lρ = 0.25(3.142)(0.305in x (0.0254mm/in))2(68ft x (0.3048m/ft) – 7.6m)(1087kg/m3) = 0.67kg Total charge = 2.5 + 0.67 = 3.17kg (OK)

OD = ½” case (ID = 0.43").Extra R22 = ρV = 0.25πd2Lρ = 0.25(3.142)(0.430in x (0.0254m/in))2(68ft x (0.3048m/ft) – 7.6m)(1087kg/m3) = 1.34kg Total charge = 2.5 + 1.34 = 3.84kg (OK)

OD = 5/8" case (ID = 0.545").Extra R22 = ρV = 0.25πd2Lρ = 0.25(3.142)(0.545in x (0.0254mm/in))2(68ft x (0.3048m/ft) – 7.6m)(1087kg/m3) = 2.15kg Total charge = 2.5 + 2.15 = 4.65kg (NG)

Because the pipe length limit is not exceeded, the original pipe size is still recommended to be used in thissystem. The calculations reveal that the system will be safe to operate, but additional oil of 12.9 fl. oz. andadditional refrigerant R22 charge of 0.7kg must be added.

In this example, R-22 is used as the refrigerant. When other refrigerants are used, the corresponding refrigerantproperties must be applied. For example, properties of refrigerant R407C and R410A are available in theAppendix section. The corresponding pipe charts must also be used in the computation.

2 - 13

Figure 2.6: R-22 refrigerant velocity chart

2 - 14

190 120 340 2100

2700

4000

1”

Figure 2.7: R-22 refrigerant pressure drop chart

2 - 15

6.5 3.2 15

1.8 5.5 25

1”

2.72.72.72.72.7 CrCrCrCrCrankcase Heaankcase Heaankcase Heaankcase Heaankcase Heaterterterterter

Crankcase heater is a sealed heater installed with close contact to the outer circumference at the bottom ofthe compressor. Examples of crankcase heater and how crankcase heater is installed onto a compressor isshown in Figure 2.8, Figure 2.9, and Figure 2.10.

Figure 2.18: Example of crankcase heater.

Figure 2.19: Crankcase heater installed onto a rotary compressor.

2 - 16

Figure 2.10: Crankcase heater installed onto a reciprocating compressor.

The purpose of installing crankcase heater is to protect the compressor from the negative effects of the liquidrefrigerant in the compressor and in the lubricating oil. In simple words, crankcase heaters are frequentlyused to retard migration. It removes the refrigerant by heating from the outside. Refrigerant entering thecompressor will be vaporized and driven back into the suction line. Crankcase heater should be installedduring long piping installations where the risk of liquid refrigerant migration is much higher.

The crankcase heater size differs according to the capacity and the application of the compressor. A heaterof about 40W to 80W should be used.

When the compressor is inactive for a long period, the crankcase heater should be energized for at least 6 to12 hours before operation of the compressor is started. Please note that burning might occur if oil gets on tothe crankcase heater.

Deterioration due to water condensation and acoustic insulation materials (such as “pheuol products”) canlead to defective insulation.

2 - 17

2.82.82.82.82.8 Pump DoPump DoPump DoPump DoPump Down Cywn Cywn Cywn Cywn Cyccccclelelelele

The most positive dependable means of properly controlling the liquid refrigerant, particularly if the charge islarge, is by means of a pump down cycle. By closing a liquid line valve, the refrigerant can be pumped into thecondenser and receiver, and the compressor operation controlled by means of a low-pressure control. Therefrigerant can thus, be isolated during periods when the compressor is not in operation. Migration to thecompressor and crankcase is prevented.

Although the pump down cycle is one of the protection method against migration, it will not protect againstliquid flooding during operation.

2.92.92.92.92.9 MinimizMinimizMinimizMinimizMinimize Bendse Bendse Bendse Bendse Bends

Piping between the condenser and evaporator units shall not have too many bends. Bends should be avoidedas much as possible.

When the number of bends (bending angle) is large, the internal pipe resistance increases, and the refrigerantflow is impaired. These bends tend to retard oil return. The compressor capacity is also reduced and thereare higher risks of compressor failures. Refer Section 1.6 for the recommended maximum number ofbends.

Figure 2.11: Too many bends

2 - 18

2.102.102.102.102.10 MinimizMinimizMinimizMinimizMinimize Exe Exe Exe Exe Excessicessicessicessicessivvvvve Heightse Heightse Heightse Heightse Heights

The system does not perform correctly when both the condenser and evaporator units are too far away fromeach other (either vertically or horizontally). The required refrigerant quantity increases and the products’guaranteed range is exceeded. Also, the circulation of refrigerant and lubrication oil malfunctions, the capacitydrops, and compressor trouble may occur.

The piping length should be as short as possible because the capacity and the reliability decreases as pipinglength increases. Select the shortest length possible. Refer Section 1.6 for the recomended maximumheights and lengths.

Figure 2.12: Too long horizontal length.

2 - 19

Figure 2.13: Excessive height different.

Section 3Capacity EffectOne of the most frequently asked question with long piping installations is “How much is the effect to thecooling or heating capacities when operating with long piping?” It has been mentioned that with longerpiping, the capacity will be lower due to pressure losses along the pipe lines. However, to determine themagnitude of the capacity reduction is not just a simple matter of calculating the pressure drops along thepipe line.

The cooling or heating capacity of a system is very much dependent on the operating suction and dischargepressures of the compressor. It is also dependent on the amount of superheat at the suction, and subcoolat the condenser outlet. All of these boil down to the refrigerant mass flow rate pumped by the compressor.When the pipe lines become longer, and the refrigerant charge is increased, the values of both the superheatand subcool will also change. This will affect the mass flow rate. In other words, in order to accuratelydetermine the capacity, we will need to measure the pressures, superheat, and subcooling.

Another consideration is that with the longer pipe lines, there will be higher heat losses due to conductionalong the pipe length. Of course, this can be overcome by ensuring good pipe insulation on the pipes.Generally, a suitable pipe insulation of sufficient thickness (e.g. Superlon/Armaflex, ½” thick) will be effectivein giving good thermal insulation.

In view of the above, it is difficult to determine accurately the capacity reductions due to long pipe installation.It is not practical to directly measure both the compressor suction and discharge pressures as there are nopressure taps at these locations in the air-conditioning unit. A table or graph of the compressor performanceis also required to determine this value.

Nevertheless, it is possible to roughly estimate the capacity by using the calculated pressure drop alongthe suction and discharge pipe lines in relation to the original rated capacity of the system with the standardpipe length. It is assumed that the rated evaporating and condensing temperatures of the system remainthe same. Note 1.

Note 1: Strictly speaking, this is not true, as a reduction in suction pressure will also reduce the discharge pressure (and vice-versa). The system balancing will be affected. However, this assumption has been made to simplify the estimation process.

3 - 1

Cooling Capacity

The cooling capacity of the unit has been rated with a standard pipe length at a specific evaporating temperatureand condensing temperature.

Figure 3.1: Cooling cycle

With a longer pipe length, the compressor suction pressure must become lower in order to maintain thesame evaporating temperature at the coil, i.e. Te. As a result, the refrigerant mass flow rate of the compressorreduces, giving a lower cooling capacity. The longer the pipe the lower the suction pressure.

The pressure drop along the pipe can be expressed as equivalent temperature reading because of thegeneral acceptance of this method of pipe sizing. The corresponding pressure drop in psi (or kPa) may bedetermined by referring to the saturated refrigerant properties. Different refrigerants will give different valuesof pressure drop.

The following general capacity trend has been extracted from CARRIER Handbook:

Table 3.1: Suction line pressure drop against compressor capacity

3 - 2

Std. pipe length

Suction pipe

Liquid pipe (2-phase) P

P

Evap. temp.

(sat.), Te

Cond. temp.

(sat.), Tc

Ps

Suction pressure

)))) ))))

Suction pipe line Pressure Drop Compressor Capacity, %

No Line Loss 100

2ºF (1.1ºC) Line Loss 95.7


Heating Capacity

With the action of the 4-way reversing valve, the suction pipe will now become the discharge pipe. Becauseof the expansion device configuration, the liquid pipe will maintain the same 2-phase flow.

Figure 3.2: Heating cycle

As before, the heating capacity has been rated at specific evaporating and condensing temperatures, withthe standard pipe length. With a longer pipe installation, there will be no change in the suction pipe linepressure drop, but rather the effect comes from the discharge pipe.Due to the additional discharge pipe pressure drop, the compressor discharge pressure has to be increasedin order to maintain the same condensing temperature at the coil.

As a result of this higher discharge pressure, the compressor capacity will decrease, increasing the powerinput. The following table illustrates this situation:

Notice that the amount of capacity loss due to the discharge pipe line pressure drop is lower than theequivalent pressure drop along the suction line.

Table 3.2: Discharge line pressure drop against compressor capacity.

3 - 3

Cond. temp.

(sat.), Tc

Evap. temp.

(sat.), Te

))))

Std. pipe length

Discharge pipe

Liquid pipe (2-phase)

P

P

Indoor unit

Outdoor unit

Pd

Discharge pressure

))))

Discharge pipe line Pressure Drop Compressor Capacity, %

No Line Loss 100



3.1 Pr3.1 Pr3.1 Pr3.1 Pr3.1 Pressuressuressuressuressure Dre Dre Dre Dre Drop Charop Charop Charop Charop Chartststststs

The following explains the refrigerant pipe line pressure drop chart which has been describedunder the topic Pipe sizing in Section 2.

Figure 3.3: Pressure drop chart for R-22

3 - 4

A

B

C

Figure 3.3 shows the pressure drop chart for R-22

This chart gives the pressure drop along 3 different types of refrigerant pipe lines, i.e.a) suction pipe [A]b) liquid pipe [B]c) discharge pipe [C]

The differentiations can be found on the right hand side of the chart.

Note that for each of the liquid and discharge pipe, there is only one representative line irrespective of thepipe size. But there are several lines for the suction pipe, corresponding to different evaporating temperatures.

Figure 3.3 is applicable only for R-22 refrigerant. Other types of refrigerant will require different charts. Thechart for R-407C refrigerant has also been included in the Appendix section.

The following explains how the pressure drop chart is used. Refer to Figure 3.3:

1. Determine the cooling capacity of the system in Refrigerant Tons.2. Project downwards from the capacity scale at the top. Intersect the three types of pipe lines

[A], [B], and [C].3. Determine the evaporating temperature and condensing temperature of the system.4. Project horizontally to the left at the point of intersection with the suction line (at the

corresponding evaporating temperature), discharge line, and liquid line.5. Intersect the projected lines with the left section of the chart at the corresponding pipe

sizes.6. Then, project downwards to the pressure drop scale at the bottom of the chart.7. Follow the slope lines to read from the bottom scale for the desired condensing temperature.

Note that the pressure drop values are given in the unit ‘psi/100 Feet’.

3 - 5

The next step is to estimate the capacity changes. The approach used in this manual is by referring to thecapacity changes on the actual compressor performance curves. The focus will be on three different typesof compressors:

a) Matsushita rotary compressorb) Bristol reciprocating compressorc) Copeland scroll compressor

Table 3.3 shows the average percentage of capacity loss per degree of pressure drop along the suctionline for each of these compressors. This is done for cooling mode at a specific evaporating temperaturerange of 40 – 45ºF (4.4 – 7.2ºC) and condensing temperature range of 120 – 125ºF (48.9 – 51.7ºC).

Table 3.3: Average percentage capacity loss per degree pressure drop in cooling mode

3 - 6

Matsushita rotary % capacity loss per ºF

(R-22)

% capacity loss per ºF

(R-407C)

1 h.p. -2.1% -2.1%

1.5 h.p. -1.9% -2.0%

2 h.p. -1.8% -1.9%

2.5 h.p. -1.3% -1.9%

Bristol reciprocating % capacity loss per ºF

(R-22)

3 h.p. -2.0%

4 h.p. -2.3%

5 h.p. -2.2%

6 h.p. -1.9%

Copeland scroll % capacity loss per ºF

(R-22)


(R-407C)

3 h.p. -1.9% -2.0%

4 h.p. -2.1% -2.2%

5 h.p. -1.9% -2.1%

6 h.p. -1.9% -2.0%

7.5 h.p. -1.9% -2.0%

10 h.p. -1.8% -2.0%

12.5 h.p. -1.8% -1.9%

3 - 7

Table 3.4 shows the average capacity losses during heating mode for every degree of pressure drop along the hot gas discharge pipe line. This is applicable for evaporating temperature range of 26 – 30ºF (-3 – -1ºC) and condensing temperature range of 111 – 114ºF (43.9 – 45.6ºC).

Matsushita rotary % capacity loss per ºF

(R-22)


(R-407C)

1 h.p. -0.7% -0.8%

1.5 h.p. -0.6% -0.6%

2 h.p. -0.6% -0.7%

2.5 h.p. -1.1% -0.7%

Bristol reciprocating % capacity loss per ºF

(R-22)

3 h.p. -0.7%

4 h.p. -0.8%

5 h.p. -0.8%

6 h.p. -0.7%

Copeland scroll % capacity loss per ºF

(R-22)


(R-407C)

3 h.p. -0.6% -0.7%

4 h.p. -0.7% -0.8%

5 h.p. -0.6% -0.7%

6 h.p. -0.6% -0.7%

7.5 h.p. -0.6% -0.7%

10 h.p. -0.5% -0.7%

12.5 h.p. -0.6% -0.7%

Table 3.4: Average percentage capacity loss per degree pressure drop in heating mode

By knowing the additional pressure drop along the long pipe line, the change of cooling or heating capacitycan be estimated.

Referring to Sample Calculation 06, from Figure 2.7 it was determined for the 5 hp unit, that the pressuredrop for the ¾” suction pipe is 15 ft. per 100 ft., and for the 3/8" liquid pipe is 25 ft. per 100 ft. The unit hasbeen rated with a standard pipe length of 25 ft (7.6 m). Thus, if the unit is installed with a total pipe length(inclusive of bends) of 68 ft, the pressure drop along the additional pipe length can be calculated as follows:

Additional suction pressure drop = (68 – 25) ft *15/100 = 6.45 psi.Additional liquid pressure drop = (68 – 25) ft * 25/100 = 10.75 psi.Within the scope of this manual, the effect of the liquid line pressure drop is assumed negligible.

a) For refrigerant R-22, every ºF of suction pressure drop is equivalent to about 1.5 psi. Refer to R-22 saturated tables at 40 – 45ºF. Hence, the additional suction pressure drop of 6.45 psi is equivalentto 6.45/1.5 = 4.3ºF.

If the unit is using a Copeland scroll compressor, the capacity reduction will be about 4.3 * 1.9 = 8.2%, i.e.giving a rated capacity of 0.918 * 50,000 = 45,900 Btu/hr.If a Bristol reciprocating compressor is used instead, the capacity reduction will be about 4.3 * 2.2 = 9.5%.

b) Recalculating the above example by using refrigerant R-407C, every ºF of suction pressure drop isalso equivalent to about 1.5 psi. Note that R-407C is an azeotropic refrigerant, and the refrigerantdew saturated temperature is used in the calculation. Refer Tables D.30 to D.33 for the refrigerantproperties. The calculation of the suction line pressure drop is done using the R-407C PressureDrop chart as in Figure 3.4. From the chart, the pressure drop of the ¾” suction pipe is 13 psi per100 feet. Therefore, the total equivalent pipe length of 68 ft. will now give a total pressure drop of(68 – 25) ft * 13/100 = 5.59 psi. This is equivalent to 5.59/1.5 = 3.7ºF.

With a Copeland scroll compressor (R-407C), the capacity reduction will be 3.7 * 2.1 = 7.8%, i.e. giving arated capacity of 0.922 * 50,000 = 46,100 Btu/hr.

The same can be done with other refrigerants using the saturated properties of the refrigerant.

3 - 8

Figure 3.4 : Example on using pressure drop chart fro R-22

3 - 9

10

During heating mode, both the pipes will now be under high pressure, with the suction pipe becoming thedischarge pipe. The same example will be used to work out the pressure drop along this discharge line.This example assumes the capillary tube is found in the outdoor unit with a condensing temperature of100ºF.

Again, the effect of the liquid line pressure drop is assumed negligible. Looking at the pressure drop chart,we find that the pressure drop along this is about 10 psi /100 ft. Refer to Figure 3.4.This translates to an additional discharge line pressure drop of (68 – 25)ft * 10 /100 = 4.3 psi

a) For R-22 refrigerant at 110 – 114ºF, every ºF of discharge pipe pressure drop is equivalent to3.3psi. Therefore, the additional pressure drop of 4.3 psi is equivalent to 4.3/3.3 = 1.3ºF.With a Copeland scroll compressor, this will give a capacity reduction of 1.3 * 0.6% =0.78%.

If the heating capacity of the unit is rated at 53,000 Btu/hr, the unit will thus, have a rating of 0.9922 * 53,000= 52,586 Btu/hr.

b) For R-407C refrigerant, every ºF of discharge pipe pressure drop is equivalent to 3.5 psi. FromFigure 3.5, a pressure drop of about 7 psi per 100 feet is obtained when this example is recalculatedusing R-407C. Thus, the additional discharge line pressure drop is (68 – 25) ft * 7/100 = 3 psi.

Hence, the long piping will give an equivalent pressure drop of 3/3.5 = 0.85ºF. The capacity reduction isthen 0.85 * 0.8% = 0.68% for a Bristol compressor.

3 - 10

Figure 3.5: Pressure drop chart for R-407C

3 - 11

13 7

Section 4Piping InstallationThe following section will provide some guidelines for refrigerant copper pipe installation, especially in relationto long piping jobs. Since the copper pipe is a flexible material, care must be taken to ensure proper installation.

4.1 Pipe Ma4.1 Pipe Ma4.1 Pipe Ma4.1 Pipe Ma4.1 Pipe Materialterialterialterialterial

It is recommended that Type L or Type M hard copper pipes be used to install the split type air-conditioningunits. See Table D.5 for the physical properties of the pipe. Alternatively, refrigeration tubing with thinner wallthickness, may be used. The wall thickness must be sufficient to withstand a burst pressure of at least 1700psig (11730 kPa) when used with R-22 and R-407C refrigerant.

However, working with R-410A refrigerant will require a stronger pipe material to withstand the higher workingpressure. Burst strength of at least 2400 psig will be required. In view of this, do not use the softer refrigerationtubing and Type M pipes. It is recommended that Type L be used for R-410A.

Joining of two pipes can be done easily by brazing with a copper filler rod. For better quality joint, a filler rodwith 2% silver may be used. It may also be necessary to braze the copper pipe to a brass or steel fitting. Insuch instances, brazing with 34% silver filler rods must be used (together with brazing flux).

4.2 Pipe Insula4.2 Pipe Insula4.2 Pipe Insula4.2 Pipe Insula4.2 Pipe Insulationtiontiontiontion

It is only necessary to insulate the cold suction pipe. Do not insulate the hot liquid pipe. If the expansiondevice is located in the outdoor unit, the liquid pipe will have a 2-phase flow inside which is cold. This mustalso be insulated. Generally, this is for the smaller units (1 to 2.5 hp).

However, for heat pump units, it is important for both pipes to be insulated. This is because of the coldambient temperatures when the unit is running in heat mode. The insulation will prevent heat loss to theambient along the hot pipe line.

Insulation can be done easily by inserting the copper pipes into elastomeric insulation pipes. Examples areArmaflex and Superlon. Use the correct insulation sizes to the corresponding copper pipe size. Do not usea larger insulation as this will create an air space which will then create condensation (sweating). Cut sectionsof the insulation must be glued or taped together over the pipes, e.g. at bends and joints.

Recommended insulation: k-value of 0.034 – 0.037 W/m.KMinimum insulation thickness: ½” (12.7 mm)

Do not insert two copper pipes into a single large pipe insulation. Such practice will cause the system to loseperformance due to heat gain or heat loss because the pipe surfaces are not in good contact with theinsulation. Cross heat transfer between a cold and hot pipe can occur due to the close proximity of the twopipes. Potential sweating problems may also occur due to the created air space within.

4 - 1

4.3 Horiz4.3 Horiz4.3 Horiz4.3 Horiz4.3 Horizontal Rontal Rontal Rontal Rontal Runsunsunsunsuns

Normally, refrigerant pipes are run above the ceiling space. In order to do such horizontal runs, it is necessaryto have supports at certain intervals so that the pipes do not sag. Supports in the form of saddles or anglebrackets may be used. Multiple pipes can share the same support.

copper pipes

saddle bar

hanger rods (threaded)

nuts

ceiling

hanger rods embedded into ceiling with wall

plugs

SADDLE SUPPORT

Figure 4.1: Pipe support using saddle

4 - 2

copper pipes

bracket

wall

Figure 4.2: Pipe support using angle bracket

ANGLE BRACKET

It is not recommended to run the pipes on the floor, for the simple reason that people may just step on thepipes and damage them. However, should there be a need to do so; some kind of protection must be given.An example is to place the pipes into a GI trunking box which is mounted (screwed) onto the floor.

Floor level

Trunking box

Figure 4.3: Pipe support using trunking box

The following table gives recommendation for the support spacing of the copper pipes:

4 - 3

Pipe diameter, OD (“) Distance between spacing, (ft) Up to 5/8” 6

7/8” to 1-1/8” 8 1-3/8” to 2-1/8” 10

support spacing

Pipe sagging due to spacing too far apart

Figure 4.4: Effect of improper support spacing

Table 4.1 : Recommneded support spacing of copper pipes

4.4 4.4 4.4 4.4 4.4 VVVVVererererertical Rtical Rtical Rtical Rtical Runsunsunsunsuns

Vertical pipe runs (of small sizes up to 5/8") are usually mounted on walls by nailing them with wall clips. Thisis an easy and quick method of installation.

An alternative method is by using pipe brackets. Simple saddle brackets made with angle iron are mountedwith wall plugs onto the wall. The pipes are then clamped onto these brackets. This method is especiallygood for heavier and larger pipe sizes.

copper pipe

bracket

TOP VIEW

Figure 4.5: Vertical pipe installation on saddle brackets

4 - 4

4 - 5

Another method of running these pipes is by using electrical cable trays. These pre-fabricated trays are mounted onto the wall by using saddle brackets. The copper pipes are then clamped onto the trays. The main advantage of using these trays is a very neat, organized, and clean installation.

Figure 4.6: Vertical pipe installation on cable tray Another similar method is by using trunking boxes. The trunking can be mounted straight onto the wall with wall plugs or on brackets. Copper pipes are then inserted into the trunking. The main advantage is that the pipes will be covered and protected from damage.

Figure 4.7: Trunking box

In some instances, the pipes are required to go through a floor slab. A suitably sized hole must be madein the floor (e.g. by coring method) to accommodate all the pipes going through. Suitable brackets maythen be fabricated to hold the pipes together.

floor slab

core hole

brackets

Figure 4.8: Pipe run through floor slab

4 - 6

4.5 Pipe Bends4.5 Pipe Bends4.5 Pipe Bends4.5 Pipe Bends4.5 Pipe Bends

Copper pipes MUST NOT be bent with bare hands. This will cause the pipe to dent or collapse at the bentarea. Use the proper pipe bending tool and the correct tool size corresponding to the required pipe diameter.

Pipes up to ¾” can be bent by using the pipe bending tool. Generally, larger pipes are not bent but rathercopper elbows are used instead. The elbows are brazed onto straight lengths of pipe.

An application example will be making an oil trap. The pipe bending tool is used to bend the two U-shape ofthe trap. For the larger pipe size, braze together 4 elbows to form the trap.

4 - 7

Figure 4.11 : Example of how elbows can be used to create U-traps.

Figure 4.9: Pipe bender

Figure 4.10 : Copper elbow

It is very common to find refrigerant pipe runs having to go over obstacles, e.g. concrete beams and columns,existing pipe works, and electrical conduits. To do this, many elbows and bends are used along the way. Asmuch as this is necessary, it is important to keep within the specified maximum quantity of bends for thesystem. Refer to Table 1.1.

4.6 4.6 4.6 4.6 4.6 VVVVVibribribribribraaaaation and Noise in Pipingtion and Noise in Pipingtion and Noise in Pipingtion and Noise in Pipingtion and Noise in Piping

Improper pipe installation may create undesirable vibration and noise. The effect of such vibrations are:a) Physical damage to the piping, mainly due to fatigue failure along the brazed

joints. This lead to loss of refrigerant and subsequent compressor damage.b) Transmission of noise along the pipe into occupied spaces.

The vibrations along the pipes are generated by the rigid connection of the piping to the compressor. It isimpossible to eliminate vibration in piping, it is only possible to mitigate its effect. The indoor and outdoor airconditioning units have the internal piping designed to give minimal vibrations at the point of pipe connection.Thus, it is vital that the external piping must be designed and run properly to prevent unnecessary excessivevibrations.

Several points for consideration:1) In general, pipe vibration can be reduced by having flexibility in the piping and using isolation type

hangers. Do not clamp the pipe too near to the outdoor unit (which houses the compressor) as thiswill increase the pipe rigidity at the connection. Allow sufficient length before putting in the first clampor pipe support.

2) Vibration and noise radiation from a piping system may also be caused by gas pulsations due tothe compressor action or from turbulence of high velocity refrigerant flow in the pipes. This ismore apparent along the hot discharge line, e.g. during heating mode.

Noise resulting from gas pulsations is usually objectionable only when the piping characteristics ofthe system result in amplification of the pulsation due to resonance. Such problems may be reducedby changing the size and length of the resonating pipe. Mufflers may also be added. Turbulencenoises may be overcome by using a larger pipe to reduce the refrigerant velocities.

3) When the pipes penetrate through walls or floors, provide sufficient clearance to prevent vibrationcontact of the pipe surface with the hole.

4) Flexible metal hose may be used to absorb vibration transmitted along smaller pipe lines. Theseshould be installed at right angles to the direction of vibration for best effect. However, such metalhose is not suitable for larger pipes because it is not actually flexible unless the ratio of length to thediameter is relatively great. Since, in practice, the length which can be used is often limited, it followsthat flexibility is reduced with larger pipe size.

4 - 8

Appendix ACommon Compressor FailureThere are a few possibilities of compressor failure due to long piping installation. These are:

a) Liquid flood back.b) Flooded starts.c) Liquid slugging.d) Loss of lubrication.e) Over heating.f) Contamination.g) Presence of moisture.h) Refrigerant migration.i) Liquid compression mechanism.

A - 1

A.1A.1A.1A.1A.1 Liquid FLiquid FLiquid FLiquid FLiquid Floodbacloodbacloodbacloodbacloodbackkkkk

Liquid floodback can be termed as the continuous return of liquid refrigerant (instead of vapour) to thecompressor during the running cycle.

Typical common causes of liquid floodback are:

a) Over-charge of refrigerant.b) Return air filter dirty.c) Dirty coil.d) Return air duct too small.e) Evaporator blower dirty.f) Evaporator blower motor faulty.g) TXV or capillary tube oversized.h) Superheat setting is too low.

With long piping installations, the main contributing factor is the extra refrigerant charged to the system,which causes this liquid floodback phenomenon.

Liquid floodback will cause dilution of the compressor oil and also will ‘wash’ oil from the moving partssurfaces. This in turn will lead to overheating of the mechanical bearing surfaces as the lubricatingproperties of the oil deteriorate and friction builds-up.

Due to such causes, common compressor components affected are:a) Broken valves (suction and discharge).b) Seized bearings (main and cage).c) Seized connecting rods and pistons.d) Burnt motor due to mechanical fragments or high current draw.

To prevent such undesirable situation, there are several ways to prevent it:a) Adequately sized accumulator.b) Ensure sufficient superheat at the suction.c) Correct size of expansion valve.d) Proper air flow/distribution.e) Proper refrigerant charge.

A.2A.2A.2A.2A.2 FFFFFlooded Starlooded Starlooded Starlooded Starlooded Startststststs

Flooded starts are the result of refrigerant migration into the oil in the crankcase. This mixture causesfoaming of the oil during start-ups. The foaming mixture gets sucked into the compression chamber andcauses damage to the moving parts. Furthermore, during this period the oil level in the crankcase mayreduce below the safety limit, causing insufficient lubrication. This phenomenon is more serious at loweroutdoor temperatures as the refrigerant migration rate is higher. Generally, this absorption takes placeduring shutdown of the system.

With such phenomenon, the affected compressor components are:a) Broken valves (suction and discharge – IMMEDIATE).b) Blown gaskets – IMMEDIATE.c) Loss of lubrication – GRADUAL.

With long piping installations, because of the higher refrigerant charge, the migration rate into the oilbecomes higher. Therefore, during start-ups the foaming becomes more violent, subjecting the compressorto higher operating stresses.

There are ways to minimise such undesirable situation. They are:a) Proper refrigerant charge.b) Correct amount of oil in the crankcase (refer to manufacturer specifications and data sheets).c) Install crankcase heater.d) Pump down cycle.

A - 2

A.3A.3A.3A.3A.3 Liquid SlugLiquid SlugLiquid SlugLiquid SlugLiquid Slugginggingginggingging

This is a term to describe a compressor pumping liquid refrigerant, oil, or both. In other words, it is liquidcompression. This is characterised by a loud metallic clatter within the compressor, accompanied by extremevibrations. Liquid slugging is a severe form of liquid floodback.

Slugging normally appears at start up when liquid refrigerant has migrated to the sump.Liquid slugging occurs due to:

a) No crankcase heater fitted.b) Defective crankcase heater or not connected.c) Compressor experiencing liquid floodback (see Section A.1: Liquid floodback).d) Overcharge of refrigerant.e) Overcharge of oil in crankcase.

Again the main contributing factor with long piping installations is the extra refrigerant charge required by thesystem. If not careful, this may cause large amount of liquid refrigerant flooding into the compressor.

Typical failures related to this phenomenon are:a) Damaged piston, connecting rod, crankshaft and scroll orbits.b) Suction or discharge reed broken.c) Motor damaged due to broken internal components.

There are several ways to prevent liquid slugging:a) Pump down control system.b) Crankcase heater must be energised at least 24 hours before the initial start-up.c) Adequate accumulator sizing.d) Proper superheat setting on the expansion valve.e) Correct size of expansion valve.f) Proper refrigerant charge.

A.4A.4A.4A.4A.4 Loss ofLoss ofLoss ofLoss ofLoss of Lubrica Lubrica Lubrica Lubrica Lubricationtiontiontiontion

Introduction

In any refrigeration system, oil and refrigerant are always present. The main purpose of oil is to lubricate themechanical moving parts of the compressor. Liquid refrigerant and oil are miscible in one another and theirmagnitude of miscibility will depend on the type of refrigerant, the temperature, and the pressure which bothare exposed to. It is because of this miscibility that a certain amount of oil will always leave the compressor’scrankcase and be circulated with the refrigerant.

Although oil is always treated as a lubricant to reduce mechanical wear and friction, oil actually accomplishesmany more purposes. The other functions of oil are:

a) Act as a seal between the discharge and suction sides of the compressor.b) Act as a noise dampener by reducing internal mechanical noise within a compressor.c) Performs heat transfer task by sweeping away any heat from internal rotating and stationary parts.

Causes and prevention

Loss of lubrication is defined as the absence or lack of oil in the crankcase. Generally, this will occur when therate of oil return is lower than the rate it is pumped out of the compressor. The system must allow oil to returnto the compressor at the rate it leaves; else it can cause overheating problems.

The common causes of loss of lubrication are:

a) Low refrigerant velocity (e.g. due to wrong pipe sizing).b) Insufficient or no oil traps.c) Very frequent ON/OFF cycling of the compressor.d) Low loads which reduces the refrigerant flow rate.e) Liquid flood back.f) Oil trapped in the system.g) Loss of refrigerant charge.

With long piping installations, there are several points to be aware of:

1) The higher refrigerant charge required in the system may dilute the oil in the compressor, causing deterioration of the lubricating properties. See Section 2.1: Additional oil.2) The long piping may cause the velocity of the refrigerant in the pipe to reduce, due to friction

forces. As a result, the oil becomes more difficult to be carried along by the refrigerant. Hence, therate of oil return to the compressor reduces.

To prevent oil loss, the following choices of solutions can be considered:

a) Apply compressor minimum run time setting to ensure oil return after start up.This will allow time for the compressor to return the oil from the system. Too frequent start-stopcycles will reduce this run time and can cause oil return problems.

b) Correctly size the pipe diameter length, and reduce the number of bends. Where necessary installproper oil traps on the vertical pipe lines.

c) Do not overcharge the system to prevent oil dilution.

A - 3

A.5A.5A.5A.5A.5 OvOvOvOvOverheaerheaerheaerheaerheatingtingtingtingting

Compressors generate heat through compression, motor windings, and friction at load bearing surfaces. It isthis heat that causes the compressor external shell and discharge port to be hot. Compressors are designedto withstand this high temperature up to a specified limit.

In most common applications, the highest operating temperature allowed at the discharge line is 135oC(275oF) for reciprocating compressors and 115oC for rotary compressors. At temperatures higher than thislimit, the lubricating properties of the oil will deteriorate. The motor winding insulation will also begin tobreakdown, causing damage to the compressor. In some instances, some of the moving parts may alsoseize together.

The causes of over heating can be categorized into three broad areas:

a) Refrigerationi) Improper setting of controls (TXV, pressure regulators, hot gas bypass, pressure

control switches, etc) – causing insufficient refrigerant flow through the compressor,reducing the motor cooling

ii) Lack of proper suction line insulation – causing a higher return gas temperature tothe compressor

iii) Low suction pressure due to undersized evaporator and loss of refrigerant – whichcauses a lower refrigerant flow rate and reducing the motor cooling

iv) High discharge pressure due to blocked condenser, insufficient air circulation, re-circulation of hot discharge air, undersized discharge line, condenser fan motor failureand refrigerant overcharge.

v) Highly superheated return gas temperature

b) High compression ratioCompression ratio is defined as the ratio of the compressor discharge pressure to thesuction pressure. High ratios generally occur when the outdoor ambient temperaturebecomes very high while trying to maintain a cool indoor temperature. It is important thatthe system operates within the specified operating temperature limits to prevent suchhigh ratios.

c) Electricali) Voltage unbalance between phases, causing excessive winding temperature.ii) Current unbalance between phases, causing excessive winding temperature.iii) Single phasing of the power supply, causing high winding temperature.iv) Supply voltage too high (e.g. > 15% of nominal voltage).v) Faulty capacitors and contactors.vi) Rapid ON/OFF cycling of the compressor.

With the long piping installation, the main contributing factor which may lead to compressor overheating is dueto insufficient oil return and oil dilution. This lack of lubrication will cause friction to build up in the moving partsand cause the temperature to rise.

To prevent overheating:

a) Maintain the suction and discharge pressure at safe levels.b) Control the return gas temperature by

i) Insulating the suction line.ii) Setting adequate superheat.

c) Ensure sufficient lubrication (See Section A.4: Loss of lubriation).

A - 4

A.6A.6A.6A.6A.6 ContaminaContaminaContaminaContaminaContaminationtiontiontiontion

Contamination is the presence of foreign substances in the refrigerant system. Some foreign matter can causechemical reaction or change the chemical composition of material within the system.

There are several types of contamination:

a) Acid in system from previous compressor change.b) Flux from solder joints.c) Copper shavings.d) Water.e) Dirt.f) Air.

The effects of contamination are:

a) Blocked oil passages – leads to bearing failure.b) Motor failures due to solid shorting windings.c) High head pressure due non condensable gases.d) Moisture in the system - forms acid in the system which attacks the metal and windings.

Moisture will also cause the expansion device to freeze-up internally.

The longer the piping, the higher the chances that contamination will get into the system.

There are several ways to eliminate such undesirable situations:

a) Air – Evacuate the system thoroughly before charging.b) Moisture – Evacuate the system thoroughly before charging.c) Foreign matter – Apply care to workmanship. Use filter-driers.

A - 5

Presence of Moisture

Of all the contaminants, moisture in a HVAC system is the most harmful. Moisture will reduce the life span ofthe HVAC system. The possible causes for moisture to be present are:

a) Open system – exposed to air and moisture.b) Compressor tubes left open.c) Leak in system (particularly on the low side).d) Wet rags or water to cool poor solder joints.e) Wet refrigerant.f) Lack of knowledge with the use of hygroscopic oils.g) Incorrect evacuation process.

Again, with long piping installations, the chances are higher that moisture may enter into the refrigerationsystem. This is due to the extra brazing/welding of the long pipe sections.

Figure A.1 shows the progression of compressor failure due to the contamination of foreign substances,while Figure A.2 shows the same when the contamination is due to air and moisture.

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Figure A.1: Causes and effects of foreign substances entry into refigerantion system.

A - 6

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Figure A.2 : Causes and effects of air and moisture entry to refrigerant system.

A - 7

A.7A.7A.7A.7A.7 RRRRRefrigefrigefrigefrigefrigerererererant Migant Migant Migant Migant Migrrrrraaaaationtiontiontiontion

Refrigerant migration is described as the ‘absorption’ of liquid refrigerant into the compressor oil duringperiods when the compressor is not operating for a long period. It occurs when the compressor sump becomescolder than the indoor coil. As a result of this temperature differential, there will be partial pressure differentialof the refrigerant between these two locations. This will force the refrigerant to migrate to the compressorwhere it is absorbed into the oil. Although this type of migration is most pronounced in colder weather, it canalso occur at relatively high ambient temperatures with remote type condensing units for air conditioning andheat pump applications.

When the compressor is started in this condition, the following negative effects occur:

a) During starting, the rapid pressure drop inside the compressor causes the refrigerant in the lubricatingoil to ‘explode’ out, thereby creating foaming in the sump. The foam, which contains lubricating oil isthen sucked into the cylinder causing liquid compression.

b) Liquid compression occurs because the liquid refrigerant and lubricating oil in the cylinder arecompressed. This will damage the valve parts and bearings.

c) As the foam gets pumped out of the compressor, the amount of lubricating oil inside the compressoris reduced. Thus, the bearings will not be lubricated sufficiently and seizure might occur.

Long piping will require more refrigerant charge, therefore causing the migration rate to increase. The oildilution also becomes more severe. All this gives potential problems to the compressor if care is not takenduring installation and operation.

The dangers of refrigerant migration can be prevented by having proper control of the refrigerant chargeamount and by installing a crankcase heater. See Section A.2: Flooded starts and Section A.3: Liquid slugging.

A - 8

Appendix BSuction AccumulatorAs mentioned in Section 2.4: Suction Accumulator, it is not recommended to install an additional suctionaccumulator in the long piping system as long as the maximum pipe length limits are not exceeded. Allheat pump products have built in suction accumulator. Nevertheless, the following provides someinformation on the function and construction of an accumulator.

The accumulator is a vessel which serves as a storage container for liquid refrigerant which has floodedthrough the system. It has a provision for metering the return of oil and liquid to the compressor at a ratein which the compressor can safely operate.

Each accumulator features an inlet deflector that bends refrigerant flow to prevent internal splashing andaid in the collection of refrigerant oil in the bottom of the unit. A U-tube is connected to the outlet connectionof the accumulator. As refrigerant gas leaves the accumulator, oil is pulled through an oil return orificeand returned to the compressor. Solid copper fittings allow for easy installation.

Suction accumulator assures only the return of refrigerant vapour and prevents compressor failure dueto liquid refrigerant entering the compressor.

Figure B.1: Refrigerant flow inside accumulator.

B - 1

Figure B.2: Internal layout of suction accumulator.

B - 2

Oil return orifice

BBBBB.1.1.1.1.1 AAAAApplicapplicapplicapplicapplicationstionstionstionstions

Refrigerant flood back in a system is one of the most common causes of compressor failure. Excessiveliquid refrigerant dilutes the oil in the compressor crankcase causing wear and tear to the moving parts.Complete loss of oil in the compressor can result in broken rods and crankshafts.

In heat pump systems, an accumulator can act as a receiver during the heating cycle, when the systemload imbalance results in excessive liquid refrigerant in the system. Flooding can occur in a heat pumpsystem whenever the cycle is switched between cooling and heating as there may be liquid that has notvaporized. The liquid is then pumped back to the compressor.

This may also occur during the defrost cycle, where the liquid has not cleared the evaporator on start upor termination of the defrost cycle, or during low ambient heating cycle when there is insufficient airtemperature to vaporize the liquid.

All the above mentioned problems will be compounded with long piping installations due to the additionalrefrigerant charge.

The accumulator should be located in the compressor’s common suction line between :a) The reversing valve and compressor in heat pump units, andb) The evaporator and compressor in cooling only units.

It must also have provisions for a positive return of oil to the compressor so that oil does not becometrapped in the accumulator. The liquid refrigerant and oil must be metered back to the compressor at acontrolled rate to avoid damage to the compressor. Therefore, proper sizing of the oil orifice is required.The actual refrigerant holding capacity needed for an accumulator is also determined by the particularapplication and should be selected to hold the maximum liquid refrigerant flood back anticipated.

B - 3

BBBBB.2.2.2.2.2 InstallaInstallaInstallaInstallaInstallationtiontiontiontion

Install the accumulator in the common suction line as close to the compressor as possible. Be sure thatthe inlet connection is connected to the common suction line and the outlet connection goes to thecompressor. Always install accumulators in the vertical position.

When the compressor-condensing unit is located indoors, there may be a problem of suction accumulatorsthat sweat and drip. It is necessary to completely insulate the accumulator to be vapour sealed to preventcondensation forming under the insulation.

A rusting problem may occur if the accumulator is exposed to moisture for long periods of time. Caremust be taken to prevent the paint from being burnt off during the welding process to avoid the metalfrom being exposed. When the compressor is being changed due to severe compressor burnout, thesuction accumulator should also be changed. The contaminants and particles that are caught in theaccumulator during the burnout can return to the new compressor and cause damage. It is also possiblethat oil from the first compressor may be stored in the accumulator and the excess oil return may causefailure.

BBBBB.3.3.3.3.3 Sizing and Selecting an Sizing and Selecting an Sizing and Selecting an Sizing and Selecting an Sizing and Selecting an AccumAccumAccumAccumAccumulaulaulaulaulatortortortortor

Suction accumulators should never be selected based on connection sizes only. It is more important toselect an accumulator based on the minimum pressure drop, proper oil return, and the amount of refrigerantit is required to hold.

Suction accumulators are meant to assist with momentary flooding and migration. However, under severeconditions the accumulator must have sufficient volume to prevent over flowing and causing damage tothe compressor. As a guideline, the accumulator must have adequate liquid holding capacity of not lessthan 50% of the entire system charge. The accumulator should not add excessive pressure drop to thesystem. A properly sized oil return orifice ensures positive oil return to the compressor. The recommendedorifice size is 1 mm.

B - 4

Appendix COil Seperator

There is no requirement to install additional oil separators in the system if the pipe length limits are notexceeded, as described in Section 2.5 : Oil Separator. The following provides some additional informationabout the function, construction, and installation of commercially available oil separators.

CCCCC.1 Intr.1 Intr.1 Intr.1 Intr.1 Introductionoductionoductionoductionoduction

Refrigeration compressors are lubricated by refrigerant oil that circulates from the crankcase or housing.When the compressor operates, refrigerant oil will leave the compressor in a mixture with the hot compressedrefrigerant gas. Small amounts of oil circulating through the system will not affect the system’s performance.However, too much circulating oil interferes with the operation of flow controls, evaporator, condenser, andfilter driers.

At low temperature installations, refrigerant oil thickens and becomes difficult to move out of the evaporator.Accumulation of refrigerant oil in the evaporator would affect evaporator efficiency leading to compressorfailure.

No matter what type of oil separator, they are not 100% efficient; some small quantities of oil will continue tobe transported with the discharge gas and refrigerant through the system.

Placing an oil separator between the compressor discharge and the condenser will protect the refrigerationsystem. The oil separator will maintain correct oil level in the compressor, reduce oil trapping, and improve onsystem reliability.

C - 1

Figure C.1: Oil sperator within a cooling system circuit.

Figure C.2 : Internal layout of oil seperator

C - 2

CCCCC.2 Function.2 Function.2 Function.2 Function.2 Function

A mixture of refrigerant and oil from compressor enters into the inlet of the oil separator. This mixture flowsthrough a screen and baffle arrangement to cause the fine particles of oil to gather and drop to the bottom ofthe oil separator. The refrigerant gas passes through the outlet screen to trap residual oil particles, andpasses “oil free” to the condenser.

The refrigerant oil gathers in the bottom of the oil separator unit, where a float operated needle valve opensto allow the return of oil to the compressor. Oil returns quickly to the compressor because of the higherpressure in the oil separator than in the crankcase. When the oil level has lowered, the needle valve willreseat to allow oil to build-up again in the separator.

CCCCC.3 Installa.3 Installa.3 Installa.3 Installa.3 Installationtiontiontiontion

The oil separator must be primed with the correct type and grade of compressor oil. It must be mountedsecurely in a vertical position. If space permits, the separator can be installed inside the unit, else, it can beinstalled externally.

The oil separator should be installed in the discharge line as close as possible to the compressor. An initialcharge of refrigerant oil must be added to the oil separator to actuate the float mechanism to return oil to thecompressor. Use the same type of oil that is in the crankcase of the compressor.

The discharge line from the compressor is assembled to the inlet connection of the oil separator and a line isconnected from the outlet connection of the oil separator to the inlet of the condenser. The smallest connectionon the oil separator is the oil return connection and a line is run from this to the compressor crankcase orsuction pipe line. To do this, it may be necessary to cut the existing internal piping of the unit and modify it.

The pipe line from the separator to the condenser should be carried about 50mm higher than the condenserand pitched with a downward slope into the condenser inlet connection. In this way, should any condensationoccur in this line at the condenser connection, it will drain forward into the condenser.

C - 3

The body of the oil separator should be insulated so that it retains some heat during the compressor idleperiods. Otherwise, it may act as a primary condenser on start up. If this should occur, the separator will feedcondensed liquid refrigerant back to the compressor crankcase, causing liquid hammering, oil dilution, andrisk of more mechanical damage. This situation can easily and safely be eliminated by the addition of anelectrical off cycle heater cable of low wattage, applied to the separator body below the insulation.

CCCCC.4 Maintenance.4 Maintenance.4 Maintenance.4 Maintenance.4 Maintenance

When the float valve jams, oil stops flowing to the compressor preventing sufficient oil return. A periodicinspection will help prevent such undesired situation.

Oil separators stop working when solid materials such as oxide scale and carbon jam the float mechanismand block the orifice to the compressor.

The high discharge temperatures of the compressor may cause solid particles to be formed in the oil. Theseparticles will end up in the bottom of the separator, jamming the float mechanism and blocking the valve seat.

If the oil return is continually hot, the oil float valve may be leaking, or it is being held open by sludge or foreignmatter. The backpressure will be affected, reducing system capacity. A compressor that is pumping excessiveoil will also cause the return line to be continually hot.

If the oil return line is continually cold, there may be condensation of liquid refrigerant in the oil separator. Thisliquid, when entering the compressor crankcase could cause lubrication failure within the compressor. Thisshould not be allowed to happen.

When piping up long discharge lines, vertical runs of piping should include oil traps every 3 meters of rise toprevent excess oil in the discharge line from returning to the oil separator during the off cycle.

During long off-cycles or long manual shutdowns, liquid refrigerant may collect in the oil separator. The returnof liquid refrigerant to the compressor through the oil return line may cause slugging and possible damage tothe compressor. A check valve installed on the outlet line of the oil separator will help prevent the liquidrefrigerant from returning to the compressor. Insulating the oil separator will prevent it from acting as acondenser and passing heat to the surrounding air. The addition of a filter in the oil return line will help keepthe oil clean.

Appendix DUseful Tables and Charts

No Reduction

Reduced 1/4

Reduced 1/2

3/8 1.4 0.9 2.3 0.7 1.1 2.3 2.7 0.9 1.2 1.41/2 1.6 1.0 2.5 0.8 1.3 2.5 3.0 1.0 1.4 1.63/4 2.0 1.4 3.2 0.9 1.6 3.2 4.0 1.4 1.9 2.01 2.6 1.7 4.1 1.3 2.1 4.1 5.0 1.7 2.3 2.6

1 1/4 3.3 2.3 5.6 1.7 3.0 5.6 7.0 2.3 3.1 3.31 1/2 4.0 2.6 6.3 2.1 3.4 6.3 8.0 2.6 3.7 4.0

2 5.0 3.3 8.2 2.6 4.5 8.2 10 3.3 4.7 5.02 1/2 6.0 4.1 10 3.2 5.2 10 12 4.1 5.6 6.0

3 7.5 5.0 12 4.0 6.4 12 15 5.0 7.0 7.53 1/2 9.0 5.9 15 4.7 7.3 15 18 5.9 8.0 9.0

4 10 6.7 17 5.2 8.5 17 21 6.7 9.0 105 13 8.2 21 6.5 11 21 25 8.2 12 136 16 10 25 7.9 13 25 30 10 14 168 20 13 NIL 10 NIL 33 40 13 18 2010 25 16 NIL 13 NIL 42 50 16 23 2512 30 19 NIL 16 NIL 50 60 19 26 3014 34 23 NIL 18 NIL 55 68 23 30 3416 38 26 NIL 20 NIL 62 78 26 35 3818 42 29 NIL 23 NIL 70 85 29 40 4220 50 33 NIL 26 NIL 81 100 33 44 5024 60 40 NIL 30 NIL 94 115 40 50 60

90o Std1Straight-Thru Flow

Smooth Bend Tees

Nominal pipe or

tube size (in.)

Smooth bend elbowsFlow-Thru

Branch

180o

Std145o

Street145o Std190o

Street1

90o

Long Radius2

Note : 1) R/D approximately equal to 1.2) R/D approximately equal to 1.5.

Table D.1: Various bends losses equivalent length

D - 1

90o Ell 60o Ell 45o Ell 30o Ell

3/8 2.7 1.1 0.6 0.31/2 3.0 1.3 0.7 0.43/4 4.0 1.6 0.9 0.51 5.0 2.1 1.0 0.7

1 1/4 7.0 3.0 1.5 0.91 1/2 8.0 3.4 1.8 1.1

2 10 4.5 2.3 1.32 1/2 12 5.2 2.8 1.7

3 15 6.4 3.2 2.03 1/2 18 7.3 4.0 2.4

4 21 8.5 4.5 2.75 25 11 6.0 3.26 30 13 7.0 4.08 40 17 9.0 5.110 50 21 12 7.212 60 25 13 8.014 68 29 15 9.016 78 31 17 1018 85 37 19 1120 100 41 22 1324 115 49 25 16

Nominal Pipe or

Tube Size (in.)

Mitre Elbows

Table D.2: Various elbow losses equivalent length

D - 2

D - 3

Globe2 60o - Y 45o - Y Angle2 Gate5 Swing Check3

Lift Check

Flanged End

Screwed End

3/8 17 8 6 6 0.6 5 NIL NIL1/2 18 9 7 7 0.7 6 NIL 33/4 22 11 9 9 0.9 8 NIL 41 29 15 12 12 1 10 NIL 5

1 1/4 38 20 15 15 1.5 14 NIL 91 1/2 43 24 18 18 1.8 16 NIL 10

2 55 30 24 24 2.3 20 27 142 1/2 69 35 29 29 2.8 25 28 20

3 84 43 35 35 3.2 30 42 403 1/2 100 50 41 41 4 35 48 NIL

4 120 58 47 47 4.5 40 60 NIL5 140 71 58 58 6 50 80 NIL6 170 88 70 70 7 60 110 NIL8 220 115 85 85 9 80 150 NIL10 280 145 105 105 12 100 190 NIL12 320 165 130 130 13 120 250 NIL14 360 185 155 155 15 135 NIL NIL16 410 210 180 180 17 150 NIL NIL18 460 240 200 200 19 165 NIL NIL20 520 275 235 235 22 200 NIL NIL24 610 320 265 265 25 240 NIL NIL

Globe & Vertical

Lift Same as Globe

Valve4

Angle Lift Same as

Angle Valve

Valve Losses in Equivalent feet of pipe1

Y - Type Strainer6

Nominal pipe or

tube size (in.)

Note : 1) Losses are for all valves in fully open position and strainers clean.2) These losses do not apply to valves with needle point type seats.3) Losses also apply to the in line ball type check valve.4) For “Y” pattern globe lift check valve with seat approximately equal to the nominal pipe diameter, use values of 60o “Y” valve for loss.5) Regular and short pattern plug cock valves, when fully open, have same loss as gate valve. For valve losses of shoty pattern plug cocks above 6 inches check manufacturer.6) For 0.045 thru 3/16 inch perforations with screen 50% clogged, loss is double.

Table D.3: Valve losses equivalent length

D - 4

1/4 1/2 3/4 1/4 1/2 3/4 Entrance Exit Entrance Exit

3/8 1.4 0.8 0.3 0.7 0.5 0.3 1.5 0.8 1.5 1.11/2 1.8 1.1 0.4 0.9 0.7 0.4 1.8 1.0 1.8 1.53/4 2.5 1.5 0.5 1.2 1.0 0.5 2.8 1.4 2.8 2.21 3.2 2.0 0.7 1.6 1.2 0.7 3.7 1.8 3.7 2.7

1 1/4 4.7 3.0 1.0 2.3 1.8 1.0 5.3 2.6 5.3 4.21 1/2 5.8 3.6 1.2 2.9 2.2 1.2 6.6 3.3 6.6 5.0

2 8.0 4.8 1.6 4.0 3.0 1.6 9.0 4.4 9.0 6.82 1/2 10 6.1 2.0 5.0 3.8 2.0 12 5.6 12 8.7

3 13 8.0 2.6 6.5 4.9 2.6 14 7.2 14 113 1/2 15 9.2 3.0 7.7 6.0 3.0 17 8.5 17 13

4 17 11 3.8 9.0 6.8 3.8 20 10 20 165 24 15 5.0 12 9.0 5.0 27 14 27 206 29 22 6.0 15 11 6.0 33 19 33 258 NIL 25 8.5 NIL 15 8.5 47 24 47 35

10 NIL 32 11 NIL 20 11 60 29 60 4612 NIL 41 13 NIL 25 13 73 37 73 5714 NIL NIL 16 NIL NIL 16 86 45 86 6616 NIL NIL 18 NIL NIL 18 96 50 96 7718 NIL NIL 20 NIL NIL 20 115 58 115 9020 NIL NIL NIL NIL NIL NIL 142 70 142 10824 NIL NIL NIL NIL NIL NIL 163 83 163 130

Pipe Projection*

Nominal pipe or

tube size (in.)

Sudden Enlargement* d/D Sudden Contraction* d/D Sharp Edge*

* Enter table for losses at smallest diameter “d.”

Table D.4: Special fitting losses equivalent length

D - 5

ClassificationNom. Tube

Size (in.)OD (in.) Stubbs

Gagetw (in.) ID (in.)

Transverse area (sq

in.)

Minimum Test

Pressure (psi)

Weight of Tube (lb/ft)

WT of Water in

Tube* (lb/ft)

Outside Surface (sq ft/ft)

HARD 1/4 3/8 23 0.025 0.325 0.083 1000 0.106 0.036 0.0983/8 1/2 23 0.025 0.450 0.159 1000 0.144 0.069 0.1311/2 5/8 22 0.028 0.569 0.254 890 0.203 0.110 0.1643/4 7/8 21 0.032 0.811 0.516 710 0.328 0.224 0.2291 1 1/8 20 0.035 1.055 0.874 600 0.464 0.379 0.295

1 1/4 1 3/8 19 0.042 1.291 1.309 590 0.681 0.566 0.3601 1/2 1 5/8 18 0.049 1.527 1.831 580 0.940 0.793 0.425

2 2 1/8 17 0.058 2.009 3.170 520 1.460 1.372 0.5562 1/2 2 5/8 16 0.065 2.495 4.890 470 2.030 2.120 0.687

3 3 1/8 15 0.072 2.981 6.980 440 2.680 3.020 0.8183 1/2 3 5/8 14 0.083 3.459 9.400 430 3.580 4.060 0.949

4 4 1/8 13 0.095 3.935 12.160 430 4.660 5.262 1.0805 5 1/8 12 0.109 4.907 18.910 400 6.660 8.180 1.3406 6 1/8 NIL 0.122 5.881 27.160 375 8.910 11.750 1.6008 8 1/8 NIL 0.170 7.785 47.600 375 16.460 20.600 2.130

HARD 3/8 1/2 19 0.035 0.430 0.146 1000 0.198 0.063 0.1311/2 5/8 NIL 0.040 0.545 0.233 1000 0.284 0.101 0.1643/4 7/8 NIL 0.045 0.785 0.484 1000 0.454 0.209 0.2291 1 1/8 NIL 0.050 1.025 0.825 880 0.653 0.358 0.295

1 1/4 1 3/8 NIL 0.055 1.265 1.256 780 0.882 0.554 0.3601 1/2 1 5/8 NIL 0.060 1.505 1.780 720 1.140 0.770 0.425

2 2 1/8 NIL 0.070 1.985 3.094 640 1.750 1.338 0.5562 1/2 2 5/8 NIL 0.080 2.465 4.770 580 2.480 2.070 0.687

3 3 1/8 NIL 0.090 2.945 6.812 550 3.330 2.975 0.8183 1/2 3 5/8 NIL 0.100 3.425 9.213 530 4.290 4.000 0.949

4 4 1/8 NIL 0.110 3.905 11.970 510 5.380 5.180 1.0805 5 1/8 NIL 0.125 4.875 18.670 460 7.610 8.090 1.3406 6 1/8 NIL 0.140 5.845 26.830 430 10.200 11.610 1.600

HARD 1/4 3/8 21 0.032 0.311 0.076 1000 0.133 0.033 0.0983/8 1/2 18 0.049 0.402 0.127 1000 0.269 0.055 0.1311/2 5/8 18 0.049 0.527 0.218 1000 0.344 0.094 0.1643/4 7/8 16 0.065 0.745 0.436 1000 0.641 0.189 0.2291 1 1/8 16 0.065 0.995 0.778 780 0.839 0.336 0.295

1 1/4 1 3/8 16 0.065 1.245 1.217 630 1.040 0.526 0.3601 1/2 1 5/8 15 0.072 1.481 1.722 580 1.360 0.745 0.425

2 2 1/8 14 0.083 1.959 3.014 510 2.060 1.300 0.5562 1/2 2 5/8 13 0.095 2.435 4.656 470 2.920 2.015 0.687

3 3 1/8 12 0.109 2.907 6.637 450 4.000 2.870 0.8183 1/2 3 5/8 11 0.120 3.385 8.999 430 5.120 3.890 0.949

4 4 1/8 10 0.134 3.857 11.680 420 6.510 5.050 1.0805 5 1/8 NIL 0.160 4.805 18.130 400 9.670 7.800 1.3406 6 1/8 NIL 0.192 5.741 25.880 400 13.870 11.200 1.600

SOFT 1/4 3/8 21 0.032 0.311 0.076 1000 0.133 0.033 0.0983/8 1/2 18 0.049 0.402 0.127 1000 0.269 0.055 0.1311/2 5/8 18 0.049 0.527 0.218 1000 0.344 0.094 0.1643/4 7/8 16 0.065 0.745 0.436 1000 0.641 0.189 0.2291 1 1/8 16 0.065 0.995 0.778 780 0.839 0.336 0.295

1 1/4 1 3/8 16 0.065 1.245 1.217 630 1.040 0.526 0.3601 1/2 1 5/8 15 0.072 1.481 1.722 580 1.360 0.745 0.425

2 2 1/8 14 0.083 1.959 3.014 510 2.060 1.300 0.5562 1/2 2 5/8 13 0.095 2.435 4.656 470 2.920 2.015 0.687

3 3 1/8 12 0.109 2.907 6.637 450 4.000 2.870 0.8183 1/2 3 5/8 11 0.120 3.385 8.999 430 5.120 3.890 0.949

4 4 1/8 10 0.134 3.857 11.680 420 6.510 5.050 1.0805 5 1/8 NIL 0.160 4.805 18.130 400 9.670 7.800 1.3406 6 1/8 NIL 0.192 5.741 25.880 400 13.870 11.200 1.600

Govt. Type "M" 250 lb Working

Pressure

Govt. Type "L" 250 lb Working

Pressure

Govt. Type "K" 400 lb Working

Pressure

* To change “Wt of Water in Tube (lb/ft)” to Gallons of Water (gal/ft),” divide values in tableby 8.34.

Table D.5: Properties of Copper tube

D - 6

Pipe Fittings

Hard copper tubing, Type L* Wrought copper, wrought brass or tinned cast brass.

Steel pipe, standard wall

Lap welded or seamless for sizes larger than 2" IPS.


Steel pipe

Extra strong wall for sizes 1 1/2" IPS and smaller. Standard wall for sizes larger than 1 1/2" IPS. Lap welded or seamless for larger than 2" IPS.


Steel pipe, standard wall Lap welded or seamless for larger than 2" IPS.

Black or galvanized steel pipe** Welding, galvanized, cast, malleable or black iron. ***

Hard copper tubing** Cast brass, wrought copper or wrought brass.

Galvanized steel pipe** Welding, galvanized, cast, malleable or iron. ***


Galvanized steel pipe** Galvanized, drainage, cast or malleable iron.***


Black steel pipe** Welding or cast iron.***


Black steel pipe Welding or cast iron.***


Service

Suction Line

Liquid Line

Hot Gas Line

R12, R22 AND R500

Hot Water

Chilled Water

Condenser or Make Up

Water

Drain or Condensate

Lines

Steam or Condensate

150lb welding or threaded malleable iron.



* Except for sizes 1/4" and 3/8" OD where wall thicknesses of 0.30 and 0.32 inch are required. Soft copper refrigerantion tubing may be used for sizes 1 3/8" OD and smaller. Mechanical joints must not be used with soft copper tubing in sizes larger than 7/8" OD.

** Normally standard wall steel pipe or Type M hard copper tubing is satisfactory for air conditioning applications. However, the piping material selected should be checked for the design temperature-pressure ratings.

*** Normally 125lb cast iron and 150lb malleable iron fittings are satisfactory for the usual air conditioning applications. However, the fitting material selected should be checked for the design temperature-pressure ratings.

Table D.6: Pipe type recommendations

D - 7

Copeland’s Summit Series Compressor Specification

7070

ZR72KCE-TFD-501 7065.874.0

7.210.010.0

82.0

17.17.2

48.0

48.065.574.0

10.010.016.4

70707070ZR36K3E-PFJ-501

ZR47KCE-TFD-501

382

150150150150150150150

ZR42K3-PFJ-501ZR47KC-TFD-501ZR61KC-TFD-501ZR72KC-TFD-501

ZR36K3-PFJ-501

Model

ZR61KCE-TFD-501

Tmax (oC)

382382382382382382

Pmax (psig)Operating Conditions

382382

150150

Current (A)CCH (W)

7070

82.0 16.4LRA RLA

97.0

Table D.7: Compressor’s operating specifications

ZR36K3-PFJ-501ZR42K3-PFJ-501

Initial RefillModel

N/A11201240

Initial Refill1240

White Oil Charge (CC)

MMMA Oil Charge (CC)

Refrigerant charge

kg lbN/AN/A

1120 N/A 81120 8

ZR72KCE-TFD-501

ZR72KC-TFD-501ZR36K3E-PFJ-501ZR47KCE-TFD-501ZR61KCE-TFD-501

N/A

ZR47KC-TFD-501ZR61KC-TFD-501

16601950 1830 N/A1240

17701240

N/A

N/A

3.6N/A N/A

N/AN/A N/AN/A 1240

177019501360

10

11204.53.6

4.5N/AN/A

8

4.54.5

8

10

1010

8N/A

3.63.63.6

N/A

16601830

Table D.8: Compressor’s charging specifications

D - 8

Matsushita’s Compressor Specification

2PS164D2BC02

Model

4PS132DAA4JS350PAA54JS435PAA54JS435DAC4JS350DAC4KS225DAA4PS164DAA

2J35S236AB72KS28S236A6F72KS206D3AB042JS438D3JA022JS324D3AB072PV164N7BB0265PS132DPSM3715PS102DPSM3705RS080DRSM3292JS464D3BC022JS438D3BA022JS350D3BA022KS210D3BB02

5RS092XAB2RS127D5BB02

5CS102XEB2JS438D3AA02 2JS350D3BB022KS224D3AC022JS356P3AA0152JS442P3AA0152J44C3R225A4

2JS35C225ASA42JS464D3AA022KS340D3AA02 A

A

Current (A) Operating ConditionsLRA RLA Pmax (MPa) Tmax (

oC)

2.82.6

N / A

115115115

13.9 / 14.79.1 / 9.44.1 / 3.9

60 / 6635.5 / 38.7

18 / 20TypeInitial

Oil Charge (cc) Refrigerant Charge (kg)

1.1001.1002.100

700 A 2.100

A350430

1130

700 A 2.100700 A 2.100700 A 2.100410 A 1.100700 A 2.100

1130 A 2.100360 B 1.250290 A 0.800320 B 1.100410 A 0.750700 A 1.350700 A 1.350

1130 A 1.350300 B 0.800350 B 0.800350 B 0.800450 A 1.100

1000 A 2.1001130 A 2.100410 A 1.000670 A 1.800

1130 A 2.100350 B 1.100410 B 1.100700 B 2.100700 B 2.100700 B 2.100700 B 2.100

115115

115

115

4.1N / AN / A

1152.810.1 / 10.650 / 551152.65.45 / 5.30

115N / A12.6 / 13.151 / 57115N / A10.0 / 10.552 / 56115N / A6.00 / 5.9023 / 25115N / A3.921.4115N / A4.824.9115N / A1354115N / A10.247

27 / 29.51154.1N / AN / A

2.63.10 / 2.9511.3 / 12.3

115N / A7.4N / A1154.15.30 / 5.3020.2 / 22.01154.13.75 / 3.5515.8 / 17.2

4.13.10 / 3.0011.3 / 12.41152.813.5 / 14.460 / 66

2.812.5 / 13.058 / 62

1152.812.2 / 12.563.0 / 67.01153.210.3 / 9.8042.0 / 47.0

N / AN / AN / AN / A1152.610.667.01152.68.4049.01152.65.30 / 5.2525.0 / 27.0

N / A N / A N / A N / A

N / A N / AN / A N / A N / A N / AN / A N / A

1152.83.55 / 3.4014.0 / 15.0 350 B 1.1002.84.1021.0

1152.85.0026.0115

Note: 1) Oil Type A - ATMOS M60 or SUNISO 4GDID.2) Oil Type B - RB68A or FREOL ALPHA 68M.3) All current is based on 220V /240V respectively unless stated otherwise.4) 240V supply voltage.5) 380V supply voltage.6) 110V supply voltage.7) 230V supply voltage.8) Pa = PSI x 6900.


D - 9

Toshiba’s Compressor Specification

115 400 A 0.850PH135X1C - 4DZ2 19.8 / 21.6 3.40 / 3.20 2.6115 400 A 0.850PH160X1C - 4DZ2 21.7 / 23.7 4.10 / 4.00 2.6115 400 A 0.850PH165X1C - 4DH2 21.7 / 23.7 4.20 / 4.00 2.6115 350 A 0.850PH120X1C - 4DH2 17.6 / 19.0 3.10 / 2.90 2.6

Refrigerant Charge (kg)LRA RLA Pmax (MPa) Tmax (

oC) Initial TypeModelCurrent (A) Operating Conditions Oil Charge (cc)

Note: 1) Oil Type A - SUNISO 4GSD.2) Pa = PSI x 6900.3) All current is based on 220V /240V respectively unless stated otherwise.4) kg = lb x 0.454.


D - 10

Bristol’s Compressor Specification

10.096 80 C 65H25G124DBE7 130 17.0 N / A

10.0H25G104DBE7 115 14.6 N / A 96 80 C 65 10.0

96 80 C 65H25G094DBE2 95 12.7 N / A

20.0H25G294DPD2 400 82.4 N / A 224 208 C 100 20.0

224 208 C 100H25G244DPD2 360 66.6 N / A

20.0H25G204DPD2 282 62.8 N / A 224 208 C 100 20.0

224 208 C 100H25G184DPD2 234 51.4 N / A96 80 C 70H25G104DBD2 228 29.0 N / A

224 208 B 95H2NG294DPE6 200 43.9 N / A224 208 B 95H2NG294DPE3 215 44.0 N / A224 208 B 95H2NG244DRE6 180 36.6 N / A224 208 B 95H2NG244DRE3 190 36.5 N / A224 208 B 95H2NG204DRE6 141 30.0 N / A224 208 B 95H2NG204DRE3 150 30.0 N / A

10.0H25G144DBD2 & 5 252 43.1 N / A 96 80 C 70

96 80 C 70H25G124DBD2 & 5 264 33.5 N / A

15.0H25G094DBD4 & 5 190 25.4 N / A 96 80 C 70 10.0

65 62 A 40H25A62QDBL5 157 14.9 400 - 500

15.0H25A62QDBL4 150 16.0 400 - 500 65 62 A 40 15.0

65 62 A 40H25A62QCBC2 147 24.6 400 - 50055 52 A 30H23A463ABK1 100 18.8 400 - 50050 47 A 30H23A383ABC2 97.0 17.0 400 - 50040 37 A 30H23B35QABK1 95.0 15.2 450 - 55040 37 A 30H23B32QABK1 91.0 14.0 450 - 550

H2NG204DRE3 20.0H2NG294DPE3 215 44.0 N / A 224 208 B 95

450 - 550 40 37 AH23A623DBE3

H23B24QABK1 55.0

H23A463DBE3 A

5.539.0 5.20 400 - 500 47 A 30 5.550

55 52

82.0 15.5 47H23A383DBE3

45.0 6.30 400 - 500

H23A353DBE3 35.0 5.00 400 - 500 50 47 AA 30

H23B30QABK1

CCH (W)

H23B26QABC2

400 - 500 50H23A383ABK1

ALRA RLA

30 5.5

20.020.020.010.0

20.06.06.05.55.5

Initial Refill Type

Oil Charge (fl .oz)Current (A)

6.0Pmax (PSIG)450 - 55012.4

Operating Conditions

40 37 30

Refrigerant Charge (l b)Model

6.030A3740450 - 55012.270.068.0

30 5.562.0 8.20 400 - 500 55 52 A 30 5.5

30 6.0150 30.0 N / A 224 208 B 95

9.80

10.020.020.020.0

Note: 1) 220V / 240V / 50Hz supply voltage.2) 230V / 208V / 60Hz supply voltage.3) 380V / 415V / 50Hz supply voltage.4) 230V / 200V / 60Hz supply voltage.5) 220V / 200V / 50Hz supply voltage.6) 460V / 60Hz supply voltage.7) 380V / 460V / 60Hz supply voltage.8) Oil Type A - Specification 581003.9) Oil Type B - Zerol 150T.10) Oil Type C - Specification 581006.11) Pa = PSI x 69000.12) L = fl.oz x 0.02957.13) kg = lb x 0.454.


ModelCurrent (A) Operating

Conditions Oil Charge (fl .oz) CCH (W) Refrigerant Charge (l b)

LRA RLA Pmax (PSIG) Initial Refill TypeH25G144DBE6 126 21.6 N / A 96 80 C 70 10.0H25G184DPE6 117 25.7 N / A 224 208 C 95 20.0H25G204DPE6 141 31.4 N / A 224 208 C 95 20.0H25G244DPE6 180 33.3 N / A 224 208 C 95 20.0H25G294DPE6 200 41.2 N / A 224 208 C 95 20.0H23B30QABC2 82 14.0 450 - 550 40 37 A 30 6.0H26A72QDBE6 79 9.2 400 - 500 65 62 A 40 15.0H26A72QDBL4 158 18.3 400 - 500 65 62 A 40 15.0H2NG184DPE3 125 26.0 N / A 224 208 B 95 20.0H2NG184DPD5 265 53.5 N / A 224 208 B 100 20.0H23B20QABC2 57 9.0 450 - 550

6.040 37 A 30 6.0

H23B24QABK1 55 9.8 450 - 550 40 37 A 30

Note: 1) 220V / 240V / 50Hz supply voltage.2) 230V / 208V / 60Hz supply voltage.3) 380V / 415V / 50Hz supply voltage.4) 230V / 200V / 60Hz supply voltage.5) 220V / 200V / 50Hz supply voltage.6) 460V / 60Hz supply voltage.7) 380V / 460V / 60Hz supply voltage.8) Oil Type A - Specification 581003.9) Oil Type B - Zerol 150T.10) Oil Type C - Specification 581006.11) Pa = PSI x 6900.12) L = fl.oz x 0.02957.13) kg = lb x 0.454.

Table D.12: Compressor�s operating specifications

D - 11

D - 12

Oil Dilution RatioAs discuss at Section 2.1, liquid flood back will cause dilution of the compressor oil. This dilutionprocess will deteriote the lubricating properties of oil.

The formula shown below is to help end users to select a proper refrigerant charge and oil charge:

Where: 1) R is a dilution ratio and must be greater than 22%. 2) Volume for oil in centimeter cube (cc).

3) ρoil is assume to be 0.9g/cc.

Sample calculation A-01:

a) Standard factory testing length = 7.6m / 24.9 ftb) Actual pipe length = 10.0m / 32.8ftc) Compressor specifications: i) Initial oil charge = 38fl.oz. (Brand new compressor) ii) Refill oil charge = 34fl.oz. (Not brand new compressor)d) Standard factory charge = 2.50kg

Extra length = 32.8ft – 24.9ft = 7.9 ft

With 10ft = 3fl.oz. , therefore extra oil charge for extra length of: 7.9ft = 2.37fl.oz.

1 fl.oz » 30cm 3 » 0.03l

Total volume of oil = 38.00fl.oz + 2.37fl.oz = 40.37fl.oz = 1211.1cm3

Substitute values to equattion A.3 :

=

=

R is greater than 22%, therefore criteria met.

0.9 x 1211.1 x 100%0.9 x 1211.1 + 250030.36%

R = 0.9*oil(cc) x 100%0.9*oil(cc) + R22 Weight(g)

x 100%

……...(A.1)

……...(A.2)

……...(A.3)

x 100%

R = (ρV)oil

(ρV)oil + mrefrigerant

R = 0.9*oil(cc) + R22 Weight(g)0.9*oil(cc) x 100%

moil + mrefrigerant

moil=R

Flanged Sealed -40oF +40oF -40oF +40oF -40oF +40oF -40oF +40oFA-F5882 4 A-W5582 4 1.00 1.50 1.50 2.00 1.50 2.00 1.00 1.75A-F5885 5 A-W5585 5 3.00 4.00 4.50 5.50 4.75 5.75 3.75 4.50A-F5887 7 A-W5587 7 4.50 5.50 7.00 8.00 7.50 8.50 4.80 6.40A-F5888 9 A-W5588 9 6.00 7.50 9.00 10.50 9.50 11.50 6.38 8.50A-F5890 11 A-W5590 11 7.50 10.00 11.50 13.50 12.00 14.50 8.00 11.50A-F5892 13 A-W5592 13 9.00 11.50 14.00 17.50 16.00 17.50 9.50 13.25

NIL A-W5690 11 9.00 12.00 13.00 14.00 15.00 20.00 9.50 13.75A-F5792 13 A-W5692 13 11.00 14.00 16.00 18.00 20.00 24.00 11.75 16.00A-F5794 17 A-W5694 17 17.00 22.00 25.00 30.00 30.00 35.00 18.00 25.25

ALCO Oil Separator Capacity Ratings in TONS

Model Number R12 R22 R502 R134AAt Evaporator Temperature

Table D.13: Oil separator capacity ratings in TONS

Flanged Sealed -40oC +40oC -40oC +40oC -40oC +40oC -40oC +40oCA-F5882 4 A-W5582 4 3.52 5.27 5.27 7.03 5.27 7.03 3.52 6.15A-F5885 5 A-W5585 5 10.55 14.06 15.82 19.34 16.70 20.22 13.19 15.82A-F5887 7 A-W5587 7 15.82 19.34 24.61 28.13 26.37 29.89 16.88 22.50A-F5888 9 A-W5588 9 21.10 26.37 31.64 36.92 33.40 40.43 22.43 29.89A-F5890 11 A-W5590 11 26.37 35.16 40.43 47.47 42.19 50.98 28.13 40.43A-F5892 13 A-W5592 13 31.64 40.43 49.22 61.53 56.26 61.53 33.40 46.59

NIL A-W5690 11 31.64 42.19 45.71 49.22 52.74 70.32 33.40 48.35A-F5792 13 A-W5692 13 38.68 49.22 56.26 63.29 70.32 84.38 41.31 56.26A-F5794 17 A-W5694 17 59.77 77.35 87.90 105.48 105.48 123.06 63.29 88.78

ALCO Oil Separator Capacity Ratings in KWS

Model Number At Evaporator TemperatureR12 R22 R502 R134A

Table D.14: Oil separator capacity ratings in KWS

D - 13

in mmA-W5582 4 1 1/2 12A-W5585 5 1 5/8 16A-W5587 7 1 7/8 22A-W5588 9 1 1 1/8 28A-W5590 11 1 1 3/8 35A-W5592 13 1 1 5/8 42A-W5690 11 1 1 3/8 35A-W5692 13 1 1 5/8 42A-W5694 17 1 2 1/8 54

Model No. Style No. Ain mm

Connection Size Dimensions

mmB

in

21.0021.25

10.25444

100100100

14.2517.75

4

66

397

100100100152

21.6344

647448719.18

152152

ALCO Oil Separator Dimensional DataSealed Type (Style No. 1)

15.6318.63

260362451533540549

Table D.15: Oil separator dimensions for style 1

in mmA-W5582 4 2 1 5/8 42A-W5585 5 2 2 1/8 54 1155166 152

20.2520.31 4.50

mm6 514 4.25 108

mm in mm in152


Model No. Style No. Connection Size DimensionsA B C

in


in mmA-F5882 4 3 1/2 12A-F5885 5 3 5/8 16A-F5887 7 3 7/8 22A-F5888 9 3 1 1/8 28A-F5890 11 3 1 3/8 35A-F5892 13 3 1 5/8 42A-F5792 13 2 1 5/8 42A-F5794 17 2 2 1/8 54 516

4 14.25 362

66 152

4 100 21.63

5.50 1425.50 1424 100

in mm in mm

100

4.50 115152 20.25 514 4.25 108

20.31

4 100 21.25 54021.00

549

5.50 142

5.50 1425.50

4 100 17.75 451


Model No. Style No. Connection Size DimensionsA B

in mmC

533

10.25 260

142

5.50 1424 100


D - 14

Figure D.1 : Different styles of oil separator

inch mm inch mm inch mm1/4 -- -- -- S5580 8.25 20.95 -- -- --3/8 -- -- -- S5581 8.25 20.95 -- -- --1/2 A-W5582 4 10.75 27.30 S5582 10.25 26.03 601 10.25 26.035/8 A-W5585 5 13.19 33.50 S5585 14.25 36.19 602 12.75 32.387/8 A-W5587 7 15.00 38.10 S5587 17.75 48.08 603 14.50 36.83

1 1/8 A-W5588 9 16.25 41.27 S5588 21.00 53.34 604 15.38 39.051 3/8 A-W5590 11 19.50 44.53 S5590 21.25 53.97 605 19.00 48.261 5/8 A-W5592 13 19.88 50.47 -- -- -- -- -- --7/8 -- -- -- S5687 11.13 28.25 -- -- --1/8 -- -- -- S5688 15.38 39.04 -- -- --

1 3/8 A-W5690 11 -- -- S5690 15.63 39.69 -- -- --5/8 A-W5692 13 -- -- S5692 18.63 47.30 -- -- --

2 5/8 A-W5694 17 -- -- S5694 19.13 48.57 -- -- --

Fitting Size

Shell Diameter Model Length

ALCO

Oil Separator Cross Reference ChartSealed Type - Float Valve

4"

6"

AC & R

Model LengthTEMPRITE

Model Length

Table D.18: Oil separator (sealed type) cross reference chart

inch mm inch mm inch mm1/2 A-F5882 4 10.50 26.67 S5882 10.25 26.03 501 10.13 25.725/8 A-F5885 5 15.00 38.10 S5885 14.25 36.19 502 12.63 32.067/8 A-F5887 7 18.00 45.72 S5887 17.75 44.96 503 14.25 36.19

1 1/8 A-F5888 9 21.25 53.97 S5888 21.00 53.34 504 15.25 38.741 3/8 A-F5890 11 21.38 54.29 S5890 21.25 53.97 505 18.75 47.621 5/8 A-F5892 13 21.75 55.24 -- -- -- -- -- --1 5/8 A-F5792 13 20.13* 51.11 S5792 20.25 51.43 506 20.25 51.432 1/8 A-F5794 17 20.31* 51.59 S5794 20.31 51.59 507 21.25 53.971 5/8 -- -- -- S1901 21.00 53.34 -- -- --2 1/8 -- -- -- S1902 21.00 53.34 -- -- -- 2 1/5 -- -- -- -- -- -- 508 24.88 63.182 5/8 -- -- -- S1903 21.50 54.61 -- -- --3 1/8 -- -- -- -- -- -- 509 36.25 92.67 3 1/8 -- -- -- S1904 25.75 63.41 -- -- --3 5/8 -- -- -- -- -- -- -- -- --3 5/8 14" -- -- -- -- -- -- 510 51.25 130.17

12"

4"

6"

8"

10"

Model Length Model Length

Oil Separator Cross Reference ChartFlanged Type - Float Valve

Fitting Size

Shell Diameter

ALCO AC & R TEMPRITE

Model Length

Table D.19: Oil separator (float type) cross reference chart

D - 15

-40oF -20oF 0oF +20oF +40oF -40oF -20oF 0oF +20oF +40oFA-AS 3 84 0.22 0.34 0.60 0.80 1.20 0.23 0.40 0.80 1.00 1.30

A-AS 3 105 0.31 0.48 0.80 1.20 1.70 0.40 0.60 1.20 1.60 2.00A-AS 3 125 0.31 0.48 0.80 1.20 1.70 0.40 0.60 1.20 1.60 2.00A-AS 3 126 0.41 0.64 1.00 1.60 2.30 0.40 0.70 1.50 2.00 2.60A-AS 3 145 0.31 0.48 0.80 1.20 1.70 0.40 0.60 1.20 1.60 2.00A-AS 3 146 0.41 0.64 1.00 1.60 2.30 0.40 0.70 1.50 2.00 2.60A-AS 4 64 0.22 0.34 0.60 0.80 1.20 0.23 0.40 0.80 1.00 1.30A-AS 4 65 0.31 0.48 0.80 1.20 1.70 0.40 0.60 1.20 1.60 2.00

A-AS 4 105 0.31 0.48 0.80 1.20 1.70 0.40 0.60 1.20 1.60 2.00A-AS 4 106 0.41 0.64 1.00 1.60 2.30 0.40 0.70 1.50 2.00 2.60A-AS 5 96 0.41 0.64 1.00 1.60 2.30 0.40 0.70 1.50 2.00 2.60 A-AS 5 97 0.72 1.10 1.80 2.80 4.00 0.80 1.30 2.70 3.60 1.30A-AS 5 126 0.41 0.64 1.00 1.60 2.30 0.40 0.70 1.50 2.00 2.60A-AS 5 127 0.72 1.10 1.80 2.80 4.00 0.80 1.30 2.70 3.60 4.60A-AS 5 137 0.72 1.10 1.80 2.80 4.00 0.80 1.30 2.70 3.60 4.60A-AS 5 139 1.30 2.00 3.10 5.00 7.20 1.40 2.10 4.40 5.90 7.60A-AS 5 179 1.90 3.00 3.10 5.00 7.20 1.40 2.10 4.40 2.90 1.60

A-AS 5 1711 1.90 3.00 4.60 7.30 10.70 2.20 3.40 7.20 9.60 12.20A-AS 6 117 0.72 1.10 1.80 2.80 4.00 0.80 1.30 2.70 3.60 4.60A-AS 6 137 0.72 1.10 1.80 2.80 4.00 0.80 1.30 2.70 3.60 4.60A-AS 6 139 1.30 2.00 3.10 5.00 7.20 1.40 2.10 4.40 5.90 7.60

A-AS 6 1411 1.90 3.00 4.60 7.30 10.70 2.20 3.40 7.20 9.60 12.20A-AS 6 1713 3.00 1.80 7.30 11.70 17.00 3.30 5.10 10.70 14.20 18.20A-AS 6 2013 3.00 4.80 7.30 11.70 17.00 3.30 5.10 10.70 14.20 18.20A-AS 6 2513 3.00 4.80 7.30 11.70 17.00 3.30 5.10 10.70 14.20 18.20

Capacity in Tons of RefrigerationModel Number R134A R404A/R507

Table D.20: Suction accumulator capacity selection chart

-40oF -20oF 0oF +20oF +40oF -40oF -20oF 0oF +20oF +40oFA-AS 3 84 0.40 0.60 0.90 1.40 2.00 0.30 0.50 0.80 1.30 1.80

A-AS 3 105 0.50 0.80 1.40 2.10 3.00 0.50 0.76 1.20 1.90 2.70A-AS 3 125 0.50 0.80 1.40 2.10 3.00 0.50 0.76 1.20 1.90 2.70A-AS 3 126 0.72 1.10 1.80 2.80 4.00 0.60 1.00 1.60 2.50 3.50A-AS 3 145 0.50 0.80 1.40 2.10 3.00 0.60 0.76 1.20 1.90 2.70A-AS 3 146 0.72 1.10 1.80 2.80 4.00 0.60 1.00 1.60 2.50 3.50A-AS 4 64 0.40 0.60 0.90 1.40 2.00 0.30 0.50 0.80 1.30 1.80A-AS 4 65 0.50 0.80 1.40 2.10 3.00 0.50 0.76 1.20 1.90 2.70

A-AS 4 105 0.50 0.80 1.40 2.10 3.00 0.50 0.76 1.20 1.90 2.70A-AS 4 106 0.72 1.10 1.80 2.80 4.00 0.60 1.00 1.60 2.50 3.50A-AS 5 96 0.72 1.10 1.80 2.80 4.00 0.60 1.00 1.60 2.50 3.50 A-AS 5 97 1.30 2.00 3.30 5.10 7.30 1.10 1.70 2.80 4.30 6.20A-AS 5 126 0.72 1.10 1.80 2.80 4.00 0.60 1.00 1.60 2.50 3.50A-AS 5 127 1.30 2.00 3.30 5.10 7.30 1.10 1.70 2.80 4.30 6.20A-AS 5 137 1.30 2.00 3.30 5.10 7.30 1.10 1.70 2.80 4.30 6.20A-AS 5 139 2.10 3.30 5.30 8.30 11.80 1.90 2.90 4.60 7.10 10.20A-AS 5 179 2.10 3.30 5.30 8.30 11.80 1.90 2.90 4.60 7.10 10.20

A-AS 5 1711 3.40 5.30 8.50 13.20 18.80 3.00 4.60 7.40 11.60 16.50A-AS 6 117 1.30 2.00 3.30 5.10 7.30 1.10 1.70 2.80 4.30 6.20A-AS 6 137 1.30 2.00 3.30 5.10 7.30 1.10 1.70 2.80 4.30 6.20A-AS 6 139 2.10 3.30 5.30 8.30 11.80 1.90 2.90 4.60 7.10 10.20

A-AS 6 1411 3.40 5.30 8.50 13.20 18.80 3.00 4.60 7.40 11.60 16.50A-AS 6 1713 5.10 8.00 12.80 20.00 28.50 4.40 6.90 11.00 17.20 24.50A-AS 6 2013 5.10 8.00 12.80 20.00 28.50 4.40 6.90 11.00 17.20 24.50A-AS 6 2513 -- -- 12.80 20.80 28.50 4.40 6.90 11.00 17.20 24.50

Capacity in Tons of Refrigeration

Model Number R22 R502

Table D.21: Suction accumulator capacity selection chart

D - 16

A B C D

Fitting Size

(Nominal)

Diameter (in)

Length (in)

Fitting Separation

(in)

40oF Liquid R404A /R507

40oF Liquid

R502/R22/R134A

A-AS 3 84 1/2 2.0 3 8 1.63 2.0 1.5 1.5A-AS 3 105 5/8 2.4 3 10 1.63 3.0 2.0 2.0A-AS 3 125 5/8 2.9 3 12 1.63 3.0 2.5 3.0A-AS 3 126 3/4 2.9 3 12 1.63 4.0 2.5 3.0A-AS 3 145 5/8 3.3 3 15 1.63 3.0 3.3 3.5A-AS 3 146 3/4 3.3 3 14 1.63 4.0 2.8 3.5A-AS 4 64 1/2 2.8 4 6 2.50 2.0 2.0 2.5A-AS 4 65 5/8 2.8 4 6 2.50 3.0 2.0 2.5A-AS 4 105 5/8 4.6 4 10 2.50 3.0 3.5 4.0A-AS 4 106 3/4 4.6 4 10 2.50 4.0 3.5 4.0A-AS 5 96 3/4 5.1 5 9 2.75 4.0 5.5 6.0 A-AS 5 97 7/8 5.1 5 9 2.75 7.3 5.5 6.0A-AS 5 126 3/4 6.6 5 12 2.75 4.0 7.5 8.0A-AS 5 127 7/8 6.6 5 12 2.75 7.3 7.5 8.0A-AS 5 137 7/8 7.1 5 13 2.75 7.3 8.0 8.5A-AS 5 139 1 1/8 7.1 5 13 2.75 11.8 8.0 8.5A-AS 5 179 1 1/8 8.4 5 17 2.75 11.8 10.0 12.0

A-AS 5 1711 1 3/8 8.4 5 17 2.75 18.8 10.0 12.0A-AS 6 117 7/8 10.0 6 11 2.94 7.3 9.0 10.0A-AS 6 137 7/8 11.7 6 13 2.94 7.3 11.0 12.0A-AS 6 139 1 1/8 11.7 6 13 2.94 11.8 11.0 12.0

A-AS 6 1411 1 3/8 12.1 6 14 2.94 18.8 12.0 15.0A-AS 6 1713 1 5/8 15.4 6 17 2.94 28.5 15.0 16.0A-AS 6 2013 1 5/8 18.1 6 20 2.94 28.5 16.0 20.0A-AS 6 2513 1 5/8 22.6 6 25 2.94 28.5 20.0 25.0

ALCO Accumulator Dimensional Data

Model Number

Holding Capacity

Tons R22 (+40oF)

Unit Weight (LBS)

Table D.22: Suction accumulator holding capacity selection chart

Figure D.2: Accumulator cross-section

D - 17

Mod

el

OD

Tub

e

Fitti

ng

Nom

inal

Len

gth

(Cap

to C

ap)

Tons

R22

(+40

oF)

Hol

ding

cap

acity

(LB

S)1

Mod

el

Fitti

ng

Nom

inal

Len

gth

(Cap

to C

ap)

Tons

R22

(+40

oF)

Hol

ding

cap

acity

(LB

S)1

Mod

el

Fitti

ng

Ove

rall

Leng

th

Tons

R22

(+40

oF)

Hol

ding

cap

acity

(LB

S)3

A-AS 3 84 3 1/2 8 2.0 2.0 VA-30-4S 1/2 8 2.0 2.0 -- -- -- -- --A-AS 3 105 3 5/8 10 3.0 2.5 VA-31-5S 5/8 10 3.0 2.5 PA3060-10-5 5/8 10.35 2.0 2.2A-AS 3 125 3 5/8 12 3.0 3.0 VA-32-5S 5/8 12 3.0 3.0 -- -- -- -- --A-AS 3 126 3 3/4 12 4.0 3.0 VA-32-6S 3/4 12 4.0 3.0 -- -- -- -- --A-AS 3 145 3 5/8 15 3.0 3.5 VA-35-5S 5/8 15 3.0 3.5 PA3060-15-5 5/8 15.05 2.1 3.4A-AS 3 146 3 3/4 14 4.0 3.5 VA-35-6S 3/4 14 4.0 3.5 PA3060-15-6 3/4 15.05 2.3 3.4A-AS 4 64 4 1/2 6 2.0 3.0 -- -- -- -- -- -- -- -- -- --A-AS 4 65 4 5/8 6 3.0 3.0 -- -- -- -- -- -- -- -- -- --A-AS 4 75 4 5/8 6 5/8 3.0 3.5 -- -- -- -- -- -- -- -- -- --

A-AS 4 105 4 5/8 10 3.0 5.0 VA-44-5SRD 5/8 10 3.0 5.0 PA4065-9-5C 5/8 9.62 3.0 3.8A-AS 4 106 4 3/4 10 4.0 5.0 VA-44-6SRD 3/4 10 4.0 5.0 PA4065-9-6C 3/4 9.62 3.0 3.6A-AS 5 96 5 3/4 9 4.0 6.0 VA-54-6SRD 3/4 9 4.0 6.0 PA5083-9-6C 3/4 9.62 3.8 5.6 A-AS 5 97 5 7/8 9 7.3 6.0 VA-54-7SRD 7/8 9 7.3 6.0 PA5083-9-7C 7/8 9.62 3.9 5.5A-AS 5 126 5 3/4 12 4.0 9.0 VA-56-6SRD 3/4 12 4.0 9.9 PA5083-11-6 3/4 11.33 3.9 6.9A-AS 5 127 5 7/8 12 7.3 9.0 VA-56-7SRD 7/8 12 7.3 9.0 PA5083-11-7 7/8 11.33 4.4 6.8A-AS 5 137 5 7/8 13 7.3 9.5 VA-57-7SRD 7/8 13 7.3 9.5 PA5083-12-7 7/8 12.88 5.4 7.8A-AS 5 139 5 1 1/8 13 11.8 9.5 VA-57-9SRD 1 1/8 13 11.8 9.5 -- -- -- -- --A-AS 5 179 5 1 1/8 17 11.8 12.0 VA-59-9SRD 1 1/8 17 11.8 12.0 -- -- -- -- --A-AS 5 1711 5 1 3/8 17 18.8 12.0 VA-59-11SRD 1 3/8 17 18.8 12.0 -- -- -- -- --A-AS 6 117 6 7/8 11 7.3 10.0 -- -- -- -- -- -- -- -- -- --A-AS 6 137 6 7/8 13 7.3 12.0 VA-610-7SRD 7/8 13 7.3 12.0 -- -- -- -- --A-AS 6 139 6 1 1/8 13 11.8 12.0 VA-610-9SRD 1 1/8 13 11.8 12.0 -- -- -- -- --A-AS 6 1411 6 1 3/8 14 18.8 13.0 VA-611-11SRD 1 3/8 14 18.8 13.0 -- -- -- -- --A-AS 6 1713 6 1 5/8 17 28.5 16.0 -- -- -- -- -- -- -- -- -- --A-AS 6 2013 6 1 5/8 20 28.5 20.0 VA-616-13SRD 1 5/8 20 28.5 20.0 -- -- -- -- --A-AS 6 2513 6 1 5/8 25 28.5 25.0 -- -- -- -- -- -- -- -- -- --

Suction Accumulator Cross ReferenceALCO VKMP PARKER

Notes: 1) R22 at 40oF evaporator.2) R22.3) R22 at 40oF divided by 0.7.4) R22 at 0oF saturation.

Table D.23: Suction accumulator cross reference chart

D - 18

Mod

el

OD

Tub

e

Fitti

ng

Nom

inal

Len

gth

(Cap

to C

ap)

Tons

R22

(+40

oF)

Hol

ding

cap

acity

(LB

S)1

Mod

el

Fitti

ng

Ove

rall

Leng

th

Tons

R22

(+40

oF)

Hol

ding

cap

acity

(LB

S)4

Mod

el

Fitti

ng

Ove

rall

Leng

th

Tons

R22

(+40

oF)

Hol

ding

cap

acity

(LB

S)2

A-AS 3 84 3 1/2 8 2.0 2.0 -- -- -- -- -- 3680 1/2 7.69 0.9 1.5A-AS 3 105 3 5/8 10 3.0 2.5 -- -- -- -- -- -- -- -- -- --A-AS 3 125 3 5/8 12 3.0 3.0 -- -- -- -- -- 3685 5/8 12.00 2.0 2.5A-AS 3 126 3 3/4 12 4.0 3.0 -- -- -- -- -- -- -- -- -- --A-AS 3 145 3 5/8 15 3.0 3.5 -- -- -- -- -- -- -- -- -- --A-AS 3 146 3 3/4 14 4.0 3.5 -- -- -- -- -- -- -- -- -- --A-AS 4 64 4 1/2 6 2.0 3.0 -- -- -- -- -- 3816 1/2 6.50 0.9 2.1A-AS 4 65 4 5/8 6 3.0 3.0 S-7043 5/8 6 3/8 1.81 2.1 3701 5/8 6.63 2.0 2.1A-AS 4 75 4 5/8 6 5/8 3.0 3.5 -- -- -- -- -- -- -- -- -- --A-AS 4 105 4 5/8 10 3.0 5.0 S-7045 5/8 10 3/8 1.81 4.1 3702 5/8 10.63 2.0 4.0A-AS 4 106 4 3/4 10 4.0 5.0 S-7046 3/4 10 3/8 2.51 4.1 3703 3/4 10.63 3.0 4.0A-AS 5 96 5 3/4 9 4.0 6.0 -- -- -- -- -- -- -- -- -- -- A-AS 5 97 5 7/8 9 7.3 6.0 -- -- -- -- -- -- -- -- -- --A-AS 5 126 5 3/4 12 4.0 9.0 -- -- -- -- -- -- -- -- -- --A-AS 5 127 5 7/8 12 7.3 9.0 S-7057 7/8 13 4.32 8.5 -- -- -- -- --A-AS 5 137 5 7/8 13 7.3 9.5 -- -- -- -- -- 3738 7/8 13.00 4.0 7.0A-AS 5 139 5 1 1/8 13 11.8 9.5 -- -- -- -- -- -- -- -- -- --A-AS 5 179 5 1 1/8 17 11.8 12.0 -- -- -- -- -- -- -- -- -- --

A-AS 5 1711 5 1 3/8 17 18.8 12.0 -- -- -- -- -- -- -- -- -- --A-AS 6 117 6 7/8 11 7.3 10.0 -- -- -- -- -- 3827 7/8 13.00 4.0 7.0A-AS 6 137 6 7/8 13 7.3 12.0 -- -- -- -- -- -- -- -- -- --A-AS 6 139 6 1 1/8 13 11.8 12.0 S-7061 1 1/8 15 9.09 11.8 3700 1 1/8 15.00 9.0 11.4

A-AS 6 1411 6 1 3/8 14 18.8 13.0 -- -- -- -- -- 3837 1 3/8 13.50 17.0 9.5A-AS 6 1713 6 1 5/8 17 28.5 16.0 -- -- -- -- -- 3698 1 5/8 17.13 28.0 13.0A-AS 6 2013 6 1 5/8 20 28.5 20.0 -- -- -- -- -- -- -- -- -- --A-AS 6 2513 6 1 5/8 25 28.5 25.0 S-7065 1 5/8 24 3/4 27.50 20.1 3704 1 5/8 24.75 28.0 20.5

Suction Accumulator Cross ReferenceALCO AC&R Refrigeration Research

Notes: 1) R22 at 40oF evaporator.2) R22.3) R22 at 40oF divided by 0.7.4) R22 at 0oF saturation.

D - 19

Table D.24: Suction accumulator cross reference chart

Figure D.3 : R-22 refrigerant velocity chart

D - 20

D - 21

Figure D.4 : R-22 refrigerant pressure drop chart

D - 22

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

r-1

00.0

00.

0020

115

71.3

8.26

6090

.71

358.

970.

5050

2.05

431.

061

0.49

71.

243

1127

143.

684

5.8

7.25

143.

14.

46-1

00.0

0-9

5.00

0.00

341

1558

.15.

9554

96.0

236

1.41

0.53

482.

0262

1.06

10.

505

1.24

011

0414

5.3

772.

67.

4614

0.5

4.65

-95.

00-9

0.00

0.00

481

1544

.93.

6448

101.

3236

3.85

0.56

461.

9980

1.06

10.

512

1.23

710

8014

7.0

699.

47.

6713

7.8

4.84

-90.

00-8

5.00

0.00

759

1531

.62.

7115

106.

6336

6.31

0.59

281.

9744

1.06

20.

520

1.23

510

5714

8.7

645.

27.

8813

5.2

5.05

-85.

00-8

0.00

0.01

037

1518

.21.

7782

111.

9436

8.77

0.62

101.

9508

1.06

20.

528

1.23

310

3315

0.3

591.

08.

0913

2.6

5.25

-80.

00-7

5.00

0.01

542

1504

.71.

3608

111

7.26

371.

240.

6479

1.93

081.

064

0.53

71.

232

1010

151.

854

9.3

8.31

130.

15.

47-7

5.00

-70.

000.

0204

714

91.2

0.94

3412

2.58

373.

700.

6747

1.91

081.

065

0.54

51.

231

986

153.

350

7.6

8.52

127.

65.

68-7

0.00

-65.

000.

0289

914

77.5

0.74

011

127.

9337

6.15

0.70

041.

8939

1.06

80.

555

1.23

196

315

4.7

474.

58.

7312

5.1

5.90

-65.

00-6

0.00

0.03

750

1463

.70.

5368

133.

2737

8.59

0.72

601.

8770

1.07

10.

564

1.23

094

015

6.0

441.

48.

9412

2.6

6.12

-60.

00-5

5.00

0.05

102

1449

.70.

4303

313

8.65

381.

010.

7506

1.86

251.

075

0.57

51.

231

917

157.

241

4.5

9.15

120.

26.

36-5

5.00

-50.

000.

0645

314

35.6

0.32

3914

4.03

383.

420.

7752

1.84

801.

079

0.58

51.

232

893

158.

338

7.5

9.36

117.

86.

59-5

0.00

-49.

000.

0679

914

32.8

0.30

9214

5.11

383.

900.

7801

1.84

541.

080

0.58

71.

233

889

158.

538

2.7

9.41

117.

46.

64-4

9.00

-48.

000.

0714

514

29.9

0.29

4514

6.19

384.

370.

7849

1.84

281.

081

0.58

91.

233

884

158.

737

7.8

9.45

116.

96.

69-4

8.00

-47.

000.

0752

014

27.1

0.28

1514

7.28

384.

850.

7897

1.84

021.

082

0.59

21.

234

880

158.

937

3.2

9.49

116.

46.

74-4

7.00

-46.

000.

0789

414

24.2

0.26

8414

8.36

385.

320.

7944

1.83

761.

083

0.59

41.

234

875

159.

136

8.6

9.53

115.

96.

79-4

6.00

-45.

000.

0830

014

21.3

0.25

6714

9.45

385.

790.

7992

1.83

521.

085

0.59

71.

235

870

159.

336

4.1

9.58

115.

56.

84-4

5.00

-44.

000.

0870

514

18.4

0.24

5015

0.53

386.

260.

8039

1.83

271.

086

0.59

91.

235

865

159.

535

9.6

9.62

115.

06.

89-4

4.00

-43.

000.

0914

314

15.5

0.23

4515

1.62

386.

730.

8087

1.83

031.

087

0.60

11.

236

861

159.

735

5.3

9.66

114.

56.

94-4

3.00

-42.

000.

0958

014

12.6

0.22

4015

2.70

387.

200.

8134

1.82

781.

088

0.60

31.

236

856

159.

935

1.0

9.70

114.

06.

99-4

2.00

-41.

000.

1004

414

09.7

0.21

4415

3.79

387.

660.

8180

1.82

541.

090

0.60

61.

236

852

160.

134

6.8

9.74

113.

67.

04-4

1.00

-40.

81

0.10

132

1409

.20.

2126

154.

0038

7.75

0.81

891.

8250

1.09

00.

606

1.23

685

116

0.1

346.

09.

7511

3.5

7.05

-40.

81 b

-40.

500.

1028

214

08.3

0.20

9815

4.34

387.

900.

8204

1.82

431.

090

0.60

71.

236

849

160.

234

4.7

9.77

113.

37.

07-4

0.50

-40.

000.

1052

314

06.8

0.20

5215

4.89

388.

130.

8227

1.82

311.

091

0.60

81.

237

847

160.

334

2.6

9.79

113.

17.

09-4

0.00

-39.

000.

1103

114

03.9

0.19

6815

5.98

388.

600.

8274

1.82

091.

092

0.61

11.

238

843

160.

533

8.6

9.83

112.

77.

14-3

9.00

-38.

000.

1153

814

01.0

0.18

8315

7.07

389.

060.

8320

1.81

861.

093

0.61

31.

238

838

160.

633

4.5

9.87

112.

27.

19-3

8.00

-37.

000.

1208

313

98.1

0.18

0715

8.17

389.

520.

8367

1.81

641.

095

0.61

61.

239

833

160.

833

0.6

9.92

111.

77.

24-3

7.00

-36.

000.

1262

813

95.1

0.17

3015

9.27

389.

970.

8413

1.81

411.

096

0.61

91.

239

828

160.

932

6.7

9.96

111.

27.

29-3

6.00

-35.

000.

1321

313

92.1

0.16

6216

0.37

390.

430.

8459

1.81

201.

098

0.62

21.

240

824

161.

132

2.9

10.0

011

0.8

7.35

-35.

00-3

4.00

0.13

797

1389

.10.

1593

161.

4739

0.89

0.85

051.

8098

1.09

90.

624

1.24

181

916

1.2

319.

110

.04

110.

37.

40-3

4.00

-33.

000.

1442

413

86.2

0.15

3016

2.57

391.

340.

8551

1.80

771.

101

0.62

71.

242

815

161.

431

5.4

10.0

810

9.9

7.46

-33.

00-3

2.00

0.15

050

1383

.20.

1468

163.

6739

1.79

0.85

961.

8056

1.10

20.

629

1.24

281

016

1.5

311.

710

.12

109.

47.

51-3

2.00

-31.

000.

1572

013

80.2

0.14

1216

4.78

392.

240.

8642

1.80

361.

104

0.63

21.

243

805

161.

730

8.2

10.1

710

9.0

7.56

-31.

00-3

0.00

0.16

389

1377

.20.

1355

165.

8839

2.69

0.86

871.

8015

1.10

50.

635

1.24

480

016

1.8

304.

610

.21

108.

57.

61-3

0.00

Not

e :

b =

Nor

mal

boi

ling

poin

t.c

= cr

itica

l poi

nt.

16.3

4

R22

The

rmop

hysi

cal P

rope

rtie

s.P

rope

rties

of S

atur

ated

Liq

uid

and

Sat

urat

ed V

apor

.

17.6

2

17.3

0

16.9

8

16.6

6

17.9

4

18.5

9

18.2

7

22.9

2

27.2

4

19.2

5

18.9

2

Tem

p.

(o C)

28.1

2

26.3

6

24.6

3

Tem

p.

(o C)

Pres

. (M

Pa)

Surf

ace

tens

ion

(mN

/m)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)So

und

velo

city

(m

/s)

Visc

osity

(mPa

s)Th

erm

al C

ond.

(m

W/m

K)

16.5

0

16.8

2

17.1

4

17.4

6

17.7

8

18.0

3

18.1

1

18.4

3

18.0

8

Tabl

e D

.25:

R-2

2 Th

erm

ophy

sica

l pro

pert

ies

22.0

8

23.7

8

25.5

0

18.7

6

19.0

9

19.4

2

20.4

121

.24

19.5

8

D - 23

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

r-2

9.00

0.17

104

1374

.20.

1304

166.

9939

3.14

0.87

331.

7995

1.10

70.

638

1.24

579

616

1.9

301.

210

.25

108.

07.

67-2

9.00

-28.

000.

1781

913

71.1

0.12

5316

8.10

393.

580.

8778

1.79

751.

108

0.64

11.

246

791

162.

029

7.7

10.2

910

7.5

7.72

-28.

00-2

7.00

0.18

582

1368

.10.

1206

169.

2239

4.03

0.88

231.

7956

1.11

00.

644

1.24

778

716

2.2

294.

410

.34

107.

17.

78-2

7.00

-26.

000.

1934

413

65.0

0.11

6017

0.33

394.

470.

8868

1.79

371.

112

0.64

61.

248

782

162.

329

1.0

10.3

810

6.6

7.83

-26.

00-2

5.00

0.20

156

1362

.00.

1117

171.

4539

4.91

0.89

131.

7918

1.11

40.

650

1.24

977

716

2.4

287.

710

.42

106.

27.

89-2

5.00

-24.

000.

2096

813

58.9

0.10

7517

2.56

395.

340.

8957

1.78

991.

115

0.65

31.

250

772

162.

528

4.4

10.4

610

5.7

7.94

-24.

00-2

3.00

0.21

832

1355

.80.

1036

173.

6839

5.78

0.90

021.

7881

1.11

70.

656

1.25

276

816

2.6

281.

310

.51

105.

38.

00-2

3.00

-22.

000.

2269

613

52.7

0.09

9817

4.80

396.

210.

9046

1.78

621.

119

0.65

91.

253

763

162.

727

8.1

10.5

510

4.8

8.06

-22.

00-2

1.00

0.23

614

1349

.60.

0962

175.

9239

6.64

0.90

911.

7844

1.12

10.

662

1.25

475

916

2.8

275.

010

.59

104.

48.

12-2

1.00

-20.

000.

2453

113

46.5

0.09

2717

7.04

397.

060.

9135

1.78

261.

123

0.66

51.

255

754

162.

827

1.9

10.6

310

3.9

8.17

-20.

00-1

9.00

0.25

505

1343

.40.

0894

178.

1739

7.49

0.91

791.

7809

1.12

50.

669

1.25

774

916

2.9

268.

910

.68

103.

58.

23-1

9.00

-18.

000.

2647

913

40.3

0.08

6217

9.30

397.

910.

9223

1.77

911.

127

0.67

21.

258

744

163.

026

5.9

10.7

210

3.0

8.29

-18.

00-1

7.00

0.27

511

1337

.20.

0833

180.

4339

8.33

0.92

671.

7774

1.12

90.

675

1.26

074

016

3.1

263.

010

.76

102.

68.

35-1

7.00

-16.

000.

2854

313

34.0

0.08

0318

1.56

398.

750.

9311

1.77

571.

131

0.67

81.

261

735

163.

126

0.1

10.8

010

2.1

8.40

-16.

00-1

5.00

0.29

636

1330

.80.

0776

182.

7039

9.16

0.93

551.

7740

1.13

30.

682

1.26

373

116

3.2

257.

310

.85

101.

68.

46-1

5.00

-14.

000.

3072

813

27.6

0.07

4918

3.83

399.

570.

9398

1.77

231.

135

0.68

51.

264

726

163.

225

4.4

10.8

910

1.1

8.52

-14.

00-1

3.00

0.31

883

1324

.40.

0724

184.

9739

9.98

0.94

421.

7707

1.13

70.

689

1.26

672

116

3.3

251.

610

.94

100.

78.

59-1

3.00

-12.

000.

3303

813

21.2

0.06

9918

6.11

400.

390.

9485

1.76

901.

139

0.69

21.

267

716

163.

324

8.8

10.9

810

0.2

8.65

-12.

00-1

1.00

0.34

259

1318

.00.

0676

187.

2640

0.80

0.95

291.

7674

1.14

20.

696

1.26

971

216

3.3

246.

111

.02

99.8

8.71

-11.

00-1

0.00

0.35

479

1314

.70.

0653

188.

4040

1.20

0.95

721.

7658

1.14

40.

699

1.27

070

716

3.3

243.

411

.06

99.3

8.77

-10.

00-9

.00

0.36

767

1311

.50.

0632

189.

5540

1.60

0.96

151.

7643

1.14

70.

703

1.27

270

216

3.4

240.

811

.11

98.9

8.83

-9.0

0-8

.00

0.38

054

1308

.20.

0610

190.

7040

1.99

0.96

581.

7627

1.14

90.

707

1.27

469

716

3.4

238.

111

.15

98.4

8.89

-8.0

0-7

.00

0.39

412

1304

.90.

0591

191.

8640

2.38

0.97

011.

7612

1.15

20.

711

1.27

669

316

3.4

235.

611

.20

98.0

8.96

-7.0

0-6

.00

0.40

769

1301

.60.

0571

193.

0140

2.77

0.97

441.

7596

1.15

40.

715

1.27

868

816

3.4

233.

011

.24

97.5

9.02

-6.0

0-5

.00

0.42

199

1298

.30.

0553

194.

1740

3.16

0.97

871.

7581

1.15

70.

719

1.28

068

416

3.4

230.

511

.28

97.1

9.09

-5.0

0-4

.00

0.43

628

1295

.00.

0535

195.

3340

3.55

0.98

301.

7566

1.15

90.

722

1.28

267

916

3.4

227.

911

.32

96.6

9.15

-4.0

0-3

.00

0.45

132

1291

.70.

0519

196.

5040

3.93

0.98

731.

7551

1.16

20.

727

1.28

567

416

3.4

225.

511

.37

96.2

9.22

-3.0

0-2

.00

0.46

636

1288

.30.

0502

197.

6640

4.30

0.99

151.

7536

1.16

40.

731

1.28

766

916

3.4

223.

011

.41

95.7

9.28

-2.0

0-1

.00

0.48

218

1284

.90.

0486

198.

8340

4.68

0.99

581.

7522

1.16

70.

735

1.28

966

516

3.4

220.

611

.46

95.3

9.35

-1.0

00.

000.

4979

912

81.5

0.04

7120

0.00

405.

051.

0000

1.75

071.

169

0.73

91.

291

660

163.

321

8.2

11.5

094

.89.

420.

001.

000.

5146

012

78.1

0.04

5720

1.18

405.

421.

0043

1.74

931.

172

0.74

41.

294

655

163.

321

5.9

11.5

594

.49.

491.

002.

000.

5312

012

74.7

0.04

4220

2.35

405.

781.

0085

1.74

781.

175

0.74

81.

296

650

163.

221

3.5

11.5

993

.99.

562.

003.

000.

5486

312

71.3

0.04

2920

3.53

406.

141.

0127

1.74

641.

178

0.75

31.

299

646

163.

221

1.2

11.6

493

.59.

633.

00

Not

e :

b =

Nor

mal

boi

ling

poin

t.c

= cr

itica

l poi

nt.

11.2

5

12.4

5

Tem

p.

(o C)

14.6

1

11.4

011

.55

11.8

511

.70

13.0

6

13.3

7

R22

The

rmop

hysi

cal P

rope

rtie

s.P

rope

rties

of S

atur

ated

Liq

uid

and

Sat

urat

ed V

apor

.

12.3

0

12.0

012

.15

13.8

3

13.5

2

13.2

1

12.9

112

.76

13.6

8

12.6

0

15.7

0

15.3

915

.55

14.4

5

15.8

6

14.1

4

Tem

p.

(o C)

Pres

. (M

Pa)

Surf

ace

tens

ion

(mN

/m)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)So

und

velo

city

(m

/s)

Visc

osity

(mPa

s)Th

erm

al C

ond.

(m

W/m

K)

16.0

216

.18

Tabl

e D

.26:

R-2

2 Th

erm

ophy

sica

l pro

pert

ies

13.9

9

14.3

0

14.9

2

15.2

315

.07

14.7

6

D - 24

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

r4.

000.

5660

512

67.8

0.04

1620

4.71

406.

501.

0169

1.74

501.

181

0.75

71.

301

641

163.

120

8.9

11.6

893

.19.

704.

005.

000.

5843

212

64.3

0.04

0420

5.90

406.

851.

0212

1.74

361.

184

0.76

21.

304

637

163.

120

6.7

11.7

392

.79.

775.

006.

000.

6025

912

60.8

0.03

9120

7.09

407.

201.

0254

1.74

221.

187

0.76

61.

307

632

163.

020

4.4

11.7

792

.29.

846.

007.

000.

6217

412

57.3

0.03

8020

8.28

407.

551.

0296

1.74

091.

190

0.77

11.

310

627

162.

920

2.2

11.8

291

.89.

927.

008.

000.

6408

812

53.8

0.03

6820

9.47

407.

891.

0338

1.73

951.

193

0.77

51.

313

622

162.

820

0.0

11.8

691

.39.

998.

009.

000.

6609

212

50.3

0.03

5821

0.67

408.

231.

0380

1.73

821.

196

0.78

01.

316

618

162.

719

7.9

11.9

190

.910

.07

9.00

10.0

00.

6809

512

46.7

0.03

4721

1.87

408.

561.

0422

1.73

681.

199

0.78

51.

319

613

162.

619

5.7

11.9

690

.410

.14

10.0

011

.00

0.70

191

1243

.10.

0337

213.

0840

8.89

1.04

641.

7355

1.20

30.

790

1.32

360

816

2.5

193.

612

.01

90.0

10.2

211

.00

12.0

00.

7228

612

39.5

0.03

2721

4.28

409.

211.

0505

1.73

411.

206

0.79

51.

326

603

162.

419

1.5

12.0

589

.510

.29

12.0

013

.00

0.74

477

1235

.90.

0318

215.

4940

9.53

1.05

471.

7328

1.21

00.

801

1.33

059

916

2.3

189.

412

.10

89.1

10.3

713

.00

14.0

00.

7666

812

32.2

0.03

0921

6.70

409.

851.

0589

1.73

151.

213

0.80

61.

333

594

162.

218

7.3

12.1

488

.610

.45

14.0

015

.00

0.78

956

1228

.60.

0300

217.

9241

0.16

1.06

311.

7302

1.21

70.

812

1.33

758

916

2.1

185.

312

.19

88.2

10.5

315

.00

16.0

00.

8124

412

24.9

0.02

9121

9.14

410.

471.

0672

1.72

891.

220

0.81

71.

340

584

161.

918

3.2

12.2

487

.710

.61

16.0

017

.00

0.83

632

1221

.20.

0283

220.

3741

0.77

1.07

141.

7276

1.22

40.

823

1.34

458

016

1.8

181.

212

.29

87.3

10.6

917

.00

18.0

00.

8602

012

17.4

0.02

7522

1.59

411.

071.

0755

1.72

631.

228

0.82

81.

348

575

161.

617

9.2

12.3

386

.810

.77

18.0

019

.00

0.88

511

1213

.70.

0267

222.

8341

1.37

1.07

971.

7251

1.23

20.

834

1.35

357

016

1.5

177.

312

.38

86.4

10.8

619

.00

20.0

00.

9100

212

09.9

0.02

6022

4.06

411.

661.

0838

1.72

381.

236

0.84

01.

357

565

161.

317

5.3

12.4

385

.910

.95

20.0

021

.00

0.93

599

1206

.10.

0253

225.

3041

1.94

1.08

801.

7225

1.24

00.

847

1.36

256

016

1.2

173.

412

.48

85.5

11.0

421

.00

22.0

00.

9619

512

02.3

0.02

4622

6.54

412.

221.

0921

1.72

121.

244

0.85

31.

366

555

161.

017

1.5

12.5

385

.011

.12

22.0

023

.00

0.98

898

1198

.50.

0239

227.

7941

2.50

1.09

631.

7200

1.24

80.

860

1.37

155

116

0.8

169.

612

.58

84.6

11.2

123

.00

24.0

01.

0160

1194

.60.

0232

229.

0441

2.77

1.10

041.

7187

1.25

20.

866

1.37

554

616

0.6

167.

712

.63

84.1

11.3

024

.00

25.0

01.

0442

1190

.70.

0226

230.

3041

3.03

1.10

451.

7175

1.25

650.

8725

1.38

0054

116

0.4

165.

812

.69

83.7

11.4

025

.00

26.0

01.

0724

1186

.70.

0220

231.

5541

3.29

1.10

861.

7162

1.26

10.

879

1.38

553

616

0.2

163.

912

.74

83.2

11.4

926

.00

27.0

01.

1017

1182

.80.

0214

232.

8241

3.54

1.11

281.

7149

1.26

60.

886

1.39

153

216

0.0

162.

112

.79

82.8

11.5

927

.00

28.0

01.

1309

1178

.80.

0208

234.

0841

3.79

1.11

691.

7136

1.27

10.

893

1.39

652

715

9.7

160.

312

.84

82.3

11.6

928

.00

29.0

01.

1614

1174

.80.

0203

235.

3541

4.03

1.12

111.

7124

1.27

60.

901

1.40

252

215

9.5

158.

512

.90

81.9

11.7

929

.00

30.0

01.

1919

1170

.70.

0197

236.

6241

4.26

1.12

521.

7111

1.28

10.

908

1.40

851

715

9.2

156.

712

.95

81.4

11.8

930

.00

31.0

01.

2236

1166

.70.

0192

237.

9141

4.49

1.12

931.

7099

1.28

60.

916

1.41

451

215

9.0

154.

913

.01

81.0

12.0

031

.00

32.0

01.

2552

1162

.60.

0187

239.

1941

4.71

1.13

341.

7086

1.29

10.

924

1.42

050

715

8.7

153.

113

.06

80.5

12.1

032

.00

33.0

01.

2881

1158

.50.

0182

240.

4841

4.93

1.13

761.

7074

1.29

70.

932

1.42

750

215

8.5

151.

413

.12

80.1

12.2

133

.00

34.0

01.

3210

1154

.30.

0177

241.

7741

5.14

1.14

171.

7061

1.30

20.

940

1.43

449

715

8.2

149.

613

.17

79.6

12.3

134

.00

35.0

01.

3551

1150

.10.

0173

243.

0841

5.34

1.14

581.

7049

1.30

80.

949

1.44

149

215

7.9

147.

913

.23

79.2

12.4

335

.00

36.0

01.

3892

1145

.80.

0168

244.

3841

5.54

1.14

991.

7036

1.31

40.

957

1.44

848

715

7.6

146.

113

.28

78.7

12.5

436

.00

Not

e :

b =

Nor

mal

boi

ling

poin

t.c

= cr

itica

l poi

nt.

R22

The

rmop

hysi

cal P

rope

rtie

s.P

rope

rties

of S

atur

ated

Liq

uid

and

Sat

urat

ed V

apor

.

9.06

9.35

9.21

9.50

9.79

10.0

8

10.3

710

.22

8.22

8.36

8.64

Tem

p.

(o C)

9.93

9.64

8.78

8.50

11.1

0

8.92

8.08

Tem

p.

(o C)

Pres

. (M

Pa)

Surf

ace

tens

ion

(mN

/m)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)So

und

velo

city

(m

/s)

Visc

osity

(mPa

s)Th

erm

al C

ond.

(m

W/m

K)

7.94

7.66

7.38

7.11

Tabl

e D

.27:

R-2

2 Th

erm

ophy

sica

l pro

pert

ies

6.71

6.84

6.57

6.98

7.25

7.52

7.80

10.6

6

10.9

610

.81

10.5

1

D - 25

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

r37

.00

1.42

4711

41.6

0.01

6424

5.69

415.

731.

1541

1.70

231.

320

0.96

71.

456

483

157.

314

4.4

13.3

478

.312

.66

37.0

038

.00

1.46

0111

37.3

0.01

5924

7.00

415.

911.

1582

1.70

101.

326

0.97

61.

463

478

157.

014

2.7

13.4

077

.812

.77

38.0

039

.00

1.49

6911

32.9

0.01

5524

8.33

416.

081.

1624

1.69

981.

333

0.98

61.

472

473

156.

714

1.1

13.4

677

.412

.90

39.0

040

.00

1.53

3611

28.5

0.01

5124

9.65

416.

251.

1665

1.69

851.

339

0.99

51.

480

468

156.

413

9.4

13.5

276

.913

.02

40.0

041

.00

1.57

1711

24.1

0.01

4725

0.99

416.

401.

1706

1.69

721.

346

1.00

51.

489

463

156.

113

7.8

13.5

876

.513

.15

41.0

042

.00

1.60

9811

19.6

0.01

4325

2.32

416.

551.

1747

1.69

591.

353

1.01

51.

498

458

155.

713

6.1

13.6

476

.013

.28

42.0

043

.00

1.64

9311

15.1

0.01

4025

3.67

416.

691.

1789

1.69

461.

361

1.02

61.

508

453

155.

413

4.5

13.7

175

.613

.42

43.0

044

.00

1.68

8711

10.6

0.01

3625

5.01

416.

831.

1830

1.69

331.

368

1.03

71.

517

448

155.

013

2.8

13.7

775

.113

.55

44.0

045

.00

1.72

9611

06.0

0.01

3325

6.37

416.

951.

1872

1.69

201.

376

1.04

91.

528

443

154.

613

1.2

13.8

474

.613

.69

45.0

046

.00

1.77

0411

01.4

0.01

2925

7.73

417.

071.

1913

1.69

061.

384

1.06

11.

538

437

154.

212

9.5

13.9

074

.113

.83

46.0

047

.00

1.81

2810

96.7

0.01

2625

9.10

417.

171.

1955

1.68

931.

393

1.07

41.

550

432

153.

812

7.9

13.9

773

.713

.98

47.0

048

.00

1.85

5110

91.9

0.01

2326

0.47

417.

271.

1997

1.68

791.

401

1.08

61.

561

427

153.

412

6.3

14.0

473

.214

.13

48.0

049

.00

1.89

8910

87.1

0.01

1926

1.86

417.

361.

2039

1.68

661.

410

1.10

01.

574

422

153.

012

4.7

14.1

172

.814

.29

49.0

050

.00

1.94

2710

82.3

0.01

1626

3.25

417.

441.

2080

1.68

521.

419

1.11

31.

586

417

152.

612

3.1

14.1

872

.314

.45

50.0

051

.00

1.98

8010

77.4

0.01

1326

4.65

417.

501.

2122

1.68

381.

429

1.12

81.

600

412

152.

212

1.6

14.2

571

.914

.62

51.0

052

.00

2.03

3310

72.4

0.01

1026

6.05

417.

561.

2164

1.68

241.

439

1.14

21.

614

407

151.

712

0.0

14.3

271

.414

.78

52.0

053

.00

2.08

0210

67.4

0.01

0826

7.47

417.

601.

2206

1.68

101.

450

1.15

81.

629

402

151.

311

8.5

14.4

070

.914

.96

53.0

054

.00

2.12

7010

62.3

0.01

0526

8.89

417.

631.

2248

1.67

951.

461

1.17

31.

644

396

150.

811

6.9

14.4

770

.415

.14

54.0

055

.00

2.17

5510

57.2

0.01

0227

0.33

417.

651.

2291

1.67

811.

473

1.19

11.

661

391

150.

311

5.4

14.5

570

.015

.33

55.0

056

.00

2.22

3910

52.0

0.01

0027

1.76

417.

661.

2333

1.67

661.

485

1.20

81.

677

386

149.

811

3.8

14.6

369

.515

.52

56.0

057

.00

2.27

4010

46.7

0.00

9727

3.21

417.

651.

2376

1.67

511.

498

1.22

71.

696

381

149.

311

2.3

14.7

269

.115

.72

57.0

058

.00

2.32

4010

41.3

0.00

9427

4.66

417.

631.

2418

1.67

361.

511

1.24

61.

714

375

148.

811

0.7

14.8

068

.615

.92

58.0

059

.00

2.37

5810

35.9

0.00

9227

6.14

417.

591.

2461

1.67

211.

525

1.26

71.

735

370

148.

310

9.2

14.8

968

.116

.14

59.0

060

.00

2.42

7510

30.4

0.00

9027

7.61

417.

551.

2504

1.67

051.

539

1.28

71.

755

364

147.

710

7.6

14.9

867

.616

.36

60.0

062

.50

2.56

4410

15.9

0.00

8428

1.40

417.

311.

2613

1.66

641.

583

1.35

01.

818

351

146.

310

3.8

15.2

266

.516

.99

62.5

065

.00

2.70

1210

01.4

0.00

7928

5.18

417.

061.

2722

1.66

221.

626

1.41

31.

881

337

144.

910

0.0

15.4

665

.317

.61

65.0

067

.50

2.84

9398

5.6

0.00

7428

9.14

416.

581.

2834

1.65

761.

685

1.49

91.

969

323

143.

396

.215

.74

64.1

18.3

967

.50

70.0

02.

9974

969.

70.

0069

293.

1041

6.09

1.29

451.

6529

1.74

31.

584

2.05

630

914

1.7

92.4

16.0

262

.919

.16

70.0

072

.50

3.15

7695

2.1

0.00

6429

7.28

415.

291.

3061

1.64

771.

828

1.70

82.

186

295

139.

988

.516

.36

61.8

20.1

672

.50

75.0

03.

3177

934.

40.

0060

301.

4641

4.49

1.31

771.

6424

1.91

31.

832

2.31

528

013

8.1

84.6

16.7

060

.621

.16

75.0

077

.50

3.49

0891

4.1

0.00

5530

5.95

413.

251.

3300

1.63

622.

047

2.03

22.

525

265

136.

280

.617

.13

59.6

22.5

277

.50

80.0

03.

6638

893.

70.

0051

310.

4441

2.01

1.34

231.

6299

2.18

12.

231

2.73

524

913

4.2

76.6

17.5

558

.623

.87

80.0

082

.50

3.85

0886

9.3

0.00

4731

5.41

410.

101.

3557

1.62

212.

432

2.60

83.

134

232

132.

072

.418

.13

58.0

25.8

582

.50

Not

e :

b =

Nor

mal

boi

ling

poin

t.c

= cr

itica

l poi

nt.

R22

The

rmop

hysi

cal P

rope

rtie

s.P

rope

rties

of S

atur

ated

Liq

uid

and

Sat

urat

ed V

apor

.

1.56

3.75

3.51

2.92

2.36

3.63

2.09

3.22

1.82

1.30

4.24

2.64

4.00

Tem

p.

(o C)

5.51

5.38

5.72

5.62

5.88

6.17

Visc

osity

(mPa

s)Th

erm

al C

ond.

(m

W/m

K)

5.25

5.00

4.62

4.87

5.13

Tem

p.

(o C)

Pres

. (M

Pa)

Surf

ace

tens

ion

(mN

/m)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)So

und

velo

city

(m

/s)

6.44

6.04

6.30

Tabl

e D

.28:

R-2

2 Th

erm

ophy

sica

l pro

pert

ies

4.74

4.49

1.07

3.88

4.12

4.37

D - 26

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

rLi

quid

Vapo

r85

.00

4.03

7884

4.8

0.00

4332

0.38

408.

191.

3690

1.61

422.

682

2.98

43.

532

215

129.

768

.118

.71

57.4

27.8

285

.00

87.5

04.

2401

812.

50.

0040

326.

2440

5.03

1.38

461.

6032

3.33

23.

980

4.57

919

612

7.2

63.2

19.6

058

.431

.19

87.5

090

.00

4.44

2378

0.1

0.00

3633

2.09

401.

871.

4001

1.59

223.

981

4.97

55.

626

177

124.

658

.320

.48

59.3

34.5

590

.00

92.5

04.

6624

721.

50.

0031

340.

8339

4.58

1.42

321.

5704

10.6

4615

.133

16.0

2815

312

1.3

51.4

22.6

271

.446

.85

92.5

095

.00

4.88

2466

2.9

0.00

2634

9.56

387.

281.

4462

1.54

8617

.310

25.2

9026

.430

128

118.

044

.424

.76

83.5

59.1

595

.00

95.6

04.

9385

590.

30.

0022

358.

6137

6.65

1.47

051.

5194

6156

.43

95.6

096

.15

4.99

0052

3.8

0.00

1936

6.90

366.

901.

4927

1.49

27∞

∞∞

00.

0N

ILN

IL∞

∞96

.15

c

Not

e :

b =

Nor

mal

boi

ling

poin

t.c

= cr

itica

l poi

nt.

Spec

. Hea

t, c p

(kJ/

kgK

)So

und

velo

city

(m

/s)

Visc

osity

(mPa

s)

Tabl

e D

.29:

R-2

2 Th

erm

ophy

sica

l pro

pert

ies

0.02

0.23

0.62

0.05

0.00

0.40

R22

The

rmop

hysi

cal P

rope

rtie

s.P

rope

rties

of S

atur

ated

Liq

uid

and

Sat

urat

ed V

apor

.

Tem

p.

(o C)

0.83

Ther

mal

Con

d.

(mW

/mK

)Te

mp.

(o C

)Pr

es.

(MPa

)

Surf

ace

tens

ion

(mN

/m)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)

D - 27

Figure D.5 : R-22 p-h diagram

D - 28

S uva 407C R E F R IG E R A NTV E L OC IT Y IN L INE S (65°F E vap. Outlet)

Figure D.6 : R-407C refrigerant velocity chart

D - 29

S uva 407C R E F R IG E R A NTP R E S S UR E DR OP IN L INE S (65°F E vap. Outlet)

Figure D.7 : R-407C refrigerant pressure drop chart

D - 30

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r0.

0100

0-8

2.79

-74.

9514

96.9

1.89

7091

.30

365.

970.

5293

1.94

421.

245

0.66

21.

180

1025

149.

10.

0100

00.

0150

0-7

7.79

-70.

0514

82.7

1.44

3997

.56

369.

000.

5614

1.92

601.

251

0.67

41.

180

997

150.

50.

0150

00.

0200

0-7

2.79

-65.

1414

68.5

0.99

0710

3.81

372.

020.

5934

1.90

781.

257

0.68

51.

179

968

151.

90.

0200

00.

0300

0-6

7.14

-59.

6014

52.1

0.75

4211

0.96

375.

430.

6281

1.89

091.

264

0.70

01.

180

938

153.

30.

0300

00.

0400

0-6

1.48

-54.

0614

35.6

0.51

7611

8.11

378.

830.

6627

1.87

391.

271

0.71

41.

180

908

154.

60.

0400

00.

0500

0-5

7.82

-50.

4714

24.7

0.43

575

122.

8038

1.02

0.68

441.

8646

1.27

70.

724

1.18

188

915

5.4

0.05

000

0.06

000

-54.

16-4

6.88

1413

.80.

3539

127.

4838

3.20

0.70

611.

8553

1.28

20.

734

1.18

286

915

6.2

0.06

000

0.07

000

-51.

38-4

4.15

1405

.50.

3120

013

1.06

384.

840.

7223

1.84

901.

287

0.74

31.

183

855

156.

70.

0700

00.

0800

0-4

8.59

-41.

4213

97.1

0.27

0113

4.64

386.

480.

7384

1.84

271.

291

0.75

11.

184

841

157.

20.

0800

00.

0900

0-4

6.32

-39.

2013

90.2

0.24

455

137.

5938

7.81

0.75

141.

8380

1.29

50.

758

1.18

683

015

7.6

0.09

000

0.10

000

-44.

04-3

6.97

1383

.20.

2190

140.

5338

9.13

0.76

431.

8333

1.29

80.

765

1.18

781

815

7.9

0.10

000

0.10

100

-43.

84-3

6.77

1382

.50.

2170

140.

8038

9.25

0.76

541.

8329

1.29

90.

766

1.18

781

615

7.9

0.10

100

0.10

132

-43.

77-3

6.70

1382

.30.

2163

140.

8938

9.29

0.76

581.

8328

1.29

90.

766

1.18

781

615

7.9

0.10

132

b 0.

1100

0-4

2.10

-35.

0613

77.1

0.20

1514

3.07

390.

250.

7752

1.82

951.

302

0.77

21.

188

808

158.

10.

1100

00.

1200

0-4

0.17

-33.

1813

71.2

0.18

4414

5.58

391.

350.

7861

1.82

581.

305

0.77

81.

189

798

158.

40.

1200

00.

1300

0-3

8.48

-31.

5213

65.9

0.17

1914

7.81

392.

320.

7956

1.82

271.

309

0.78

41.

191

790

158.

60.

1300

00.

1400

0-3

6.78

-29.

8513

60.6

0.15

9415

0.03

393.

280.

8050

1.81

961.

312

0.79

01.

192

781

158.

80.

1400

00.

1500

0-3

5.27

-28.

3713

55.9

0.15

0015

2.03

394.

140.

8134

1.81

701.

315

0.79

61.

194

774

159.

00.

1500

00.

1600

0-3

3.75

-26.

8913

51.1

0.14

0515

4.02

394.

990.

8217

1.81

431.

318

0.80

11.

195

766

159.

10.

1600

00.

1700

0-3

2.38

-25.

5513

46.7

0.13

3115

5.84

395.

750.

8292

1.81

211.

321

0.80

61.

196

759

159.

30.

1700

00.

1800

0-3

1.00

-24.

2013

42.3

0.12

5615

7.65

396.

510.

8367

1.80

981.

324

0.81

11.

197

752

159.

40.

1800

00.

1900

0-2

9.74

-22.

9713

38.3

0.11

9715

9.33

397.

210.

8436

1.80

781.

327

0.81

61.

199

746

159.

50.

1900

00.

2000

0-2

8.48

-21.

7313

34.2

0.11

3716

1.00

397.

900.

8504

1.80

581.

329

0.82

11.

200

740

159.

50.

2000

00.

2100

0-2

7.32

-20.

5913

30.5

0.10

8816

2.56

398.

530.

8567

1.80

401.

332

0.82

61.

202

734

159.

60.

2100

00.

2200

0-2

6.15

-19.

4513

26.7

0.10

3816

4.11

399.

160.

8630

1.80

221.

335

0.83

01.

203

728

159.

70.

2200

00.

2300

0-2

5.07

-18.

3913

23.2

0.09

966

165.

5739

9.75

0.86

881.

8006

1.33

80.

835

1.20

572

315

9.8

0.23

000

0.24

000

-23.

98-1

7.33

1319

.60.

0955

216

7.02

400.

330.

8746

1.79

891.

340

0.83

91.

206

717

159.

80.

2400

00.

2500

0-2

2.97

-16.

3413

16.3

0.09

200

168.

3940

0.87

0.88

011.

7975

1.34

30.

843

1.20

771

215

9.8

0.25

000

0.26

000

-21.

95-1

5.34

1312

.90.

0884

716

9.75

401.

410.

8855

1.79

601.

345

0.84

71.

208

707

159.

80.

2600

00.

2700

0-2

0.99

-14.

4013

09.7

0.08

544

171.

0540

1.92

0.89

061.

7947

1.34

70.

851

1.21

070

215

9.9

0.27

000

0.28

000

-20.

03-1

3.46

1306

.50.

0824

017

2.34

402.

420.

8957

1.79

331.

349

0.85

51.

211

697

159.

90.

2800

00.

2900

0-1

9.13

-12.

5813

03.5

0.07

976

173.

5740

2.89

0.90

051.

7921

1.35

20.

859

1.21

369

315

9.9

0.29

000

0.30

000

-18.

22-1

1.69

1300

.50.

0771

217

4.80

403.

360.

9053

1.79

081.

354

0.86

31.

214

688

159.

90.

3000

0

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

Tabl

e D

.30:

R-4

07C

The

rmop

hysi

cal p

rope

rtie

s

R40

7C T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 31

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r0.

3100

0-1

7.36

-10.

8512

97.6

0.07

4817

5.97

403.

810.

9099

1.78

971.

357

0.86

71.

216

684

159.

90.

3100

00.

3200

0-1

6.49

-10.

0012

94.7

0.07

2517

7.14

404.

250.

9144

1.78

851.

359

0.87

11.

217

680

159.

90.

3200

00.

3300

0-1

5.67

-9.2

012

91.9

0.07

0417

8.26

404.

670.

9188

1.78

741.

361

0.87

51.

219

676

159.

90.

3300

00.

3400

0-1

4.85

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912

89.1

0.06

8417

9.38

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090.

9231

1.78

631.

363

0.87

91.

220

672

159.

90.

3400

00.

3500

0-1

4.07

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312

86.5

0.06

6518

0.46

405.

490.

9272

1.78

531.

366

0.88

31.

221

668

159.

90.

3500

00.

3600

0-1

3.28

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612

83.8

0.06

467

181.

5340

5.88

0.93

131.

7843

1.36

80.

886

1.22

266

415

9.8

0.36

000

0.37

000

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53-6

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1281

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0630

182.

5640

6.26

0.93

531.

7834

1.37

00.

890

1.22

466

015

9.8

0.37

000

0.38

000

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78-5

.39

1278

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0613

718

3.59

406.

630.

9392

1.78

241.

372

0.89

31.

225

656

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80.

3800

00.

3900

0-1

1.06

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912

76.1

0.05

9918

4.59

406.

990.

9430

1.78

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374

0.89

71.

227

653

159.

80.

3900

00.

4000

0-1

0.33

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812

73.6

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838

185.

5840

7.34

0.94

671.

7806

1.37

60.

900

1.22

864

915

9.7

0.40

000

0.41

000

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4-3

.30

1271

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0570

186.

5440

7.68

0.95

031.

7798

1.37

80.

904

1.23

064

615

9.7

0.41

000

0.42

000

-8.9

4-2

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1268

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0557

187.

5040

8.02

0.95

391.

7789

1.38

00.

907

1.23

164

215

9.6

0.42

000

0.43

000

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7-1

.97

1266

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0544

188.

4340

8.35

0.95

741.

7781

1.38

30.

911

1.23

363

915

9.6

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000

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000

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0-1

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1264

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0532

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3640

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0.96

091.

7772

1.38

50.

914

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463

615

9.5

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000

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000

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1261

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0521

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2640

8.98

0.96

431.

7765

1.38

70.

918

1.23

663

315

9.5

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000

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000

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0-0

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1259

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0509

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1640

9.29

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7757

1.38

90.

921

1.23

762

915

9.4

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000

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000

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80.

5712

57.3

0.04

9919

2.04

409.

590.

9709

1.77

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391

0.92

51.

239

626

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40.

4700

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4800

0-5

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1.18

1255

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9140

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411.

7742

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30.

928

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315

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0.48

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000

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51.

7712

52.9

0.04

7919

3.76

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170.

9772

1.77

351.

395

0.93

11.

241

620

159.

30.

4900

00.

5000

0-3

.84

2.36

1250

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6141

0.45

0.98

031.

7728

1.39

70.

934

1.24

261

715

9.2

0.50

000

0.52

500

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03.

7712

45.5

0.04

4819

6.63

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110.

9877

1.77

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402

0.94

21.

246

610

159.

10.

5250

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5500

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0427

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6541

1.77

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511.

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70.

950

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060

315

8.9

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0.57

500

0.39

6.49

1235

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0410

200.

5641

2.37

1.00

201.

7680

1.41

20.

958

1.25

459

615

8.8

0.57

500

0.60

000

1.74

7.80

1230

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0392

202.

4641

2.97

1.00

891.

7665

1.41

60.

966

1.25

758

915

8.6

0.60

000

0.62

500

3.00

9.03

1225

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0377

204.

2641

3.52

1.01

531.

7651

1.42

10.

974

1.26

158

315

8.4

0.62

500

0.65

000

4.26

10.2

612

21.0

0.03

618

206.

0541

4.07

1.02

171.

7637

1.42

60.

981

1.26

557

715

8.2

0.65

000

0.67

500

5.45

11.4

212

16.5

0.03

489

207.

7641

4.57

1.02

781.

7624

1.43

10.

989

1.26

957

115

8.0

0.67

500

0.70

000

6.64

12.5

812

12.0

0.03

359

209.

4741

5.07

1.03

391.

7611

1.43

60.

997

1.27

356

515

7.8

0.70

000

0.72

500

7.77

13.6

812

07.7

0.03

246

211.

1041

5.54

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961.

7599

1.44

11.

005

1.27

755

915

7.6

0.72

500

0.75

000

8.90

14.7

812

03.4

0.03

133

212.

7241

6.00

1.04

531.

7587

1.44

51.

012

1.28

055

315

7.4

0.75

000

0.77

500

9.98

15.8

311

99.2

0.03

034

214.

2841

6.43

1.05

081.

7576

1.45

01.

020

1.28

454

815

7.2

0.77

500

0.80

000

11.0

516

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1195

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0293

421

5.84

416.

851.

0562

1.75

641.

455

1.02

71.

288

543

157.

00.

8000

00.

8250

012

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17.8

711

91.0

0.02

846

217.

3441

7.25

1.06

141.

7553

1.46

01.

035

1.29

353

815

6.8

0.82

500

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

Tabl

e D

.31:

R-4

07C

The

rmop

hysi

cal p

rope

rtie

s

R40

7C T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 32

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r0.

8500

013

.10

18.8

611

87.0

0.02

7621

8.83

417.

651.

0665

1.75

421.

464

1.04

21.

297

532

156.

50.

8500

00.

8750

014

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19.8

211

83.1

0.02

6822

0.27

418.

021.

0715

1.75

321.

469

1.04

91.

301

527

156.

30.

8750

00.

9000

015

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20.7

711

79.1

0.02

6022

1.71

418.

381.

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1.75

221.

474

1.05

61.

305

522

156.

10.

9000

00.

9250

016

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21.6

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75.3

0.02

5322

3.10

418.

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0811

1.75

121.

479

1.06

41.

310

518

155.

90.

9250

00.

9500

016

.94

22.5

911

71.5

0.02

4622

4.49

419.

061.

0858

1.75

021.

483

1.07

11.

314

513

155.

60.

9500

00.

9750

017

.85

23.4

711

67.8

0.02

397

225.

8441

9.38

1.09

041.

7493

1.48

81.

079

1.31

850

915

5.4

0.97

500

1.00

000

18.7

524

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1164

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0233

227.

1841

9.69

1.09

491.

7483

1.49

31.

086

1.32

250

415

5.1

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000

1.05

000

20.4

626

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1157

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222

9.75

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261.

1035

1.74

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503

1.10

11.

331

496

154.

61.

0500

01.

1000

022

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27.6

711

49.8

0.02

1123

2.31

420.

831.

1121

1.74

461.

512

1.11

61.

340

487

154.

11.

1000

01.

1500

023

.77

29.2

211

42.9

0.02

018

234.

7442

1.32

1.12

011.

7429

1.52

21.

132

1.35

047

915

3.6

1.15

000

1.20

000

25.3

730

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1136

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0193

237.

1642

1.81

1.12

811.

7412

1.53

21.

147

1.35

947

015

3.1

1.20

000

1.25

000

26.8

732

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1129

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0185

239.

4742

2.24

1.13

571.

7396

1.54

21.

163

1.36

946

315

2.6

1.25

000

1.30

000

28.3

733

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1122

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0177

241.

7742

2.66

1.14

321.

7380

1.55

21.

178

1.37

945

515

2.0

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000

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000

29.7

935

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1116

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0170

243.

9742

3.02

1.15

041.

7364

1.56

31.

194

1.39

044

815

1.5

1.35

000

1.40

000

31.2

136

.41

1109

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0163

246.

1742

3.38

1.15

751.

7348

1.57

31.

210

1.40

044

015

1.0

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000

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000

32.5

637

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1103

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0157

248.

2942

3.69

1.16

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7333

1.58

41.

227

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0.5

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000

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000

33.9

039

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1097

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0151

250.

4042

4.00

1.17

101.

7318

1.59

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243

1.42

342

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9.9

1.50

000

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000

35.1

840

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0146

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4342

4.27

1.17

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7303

1.60

51.

260

1.43

542

014

9.3

1.55

000

1.60

000

36.4

641

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1085

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0141

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4.53

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1079

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011.

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3942

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7258

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313

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7.6

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000

40.0

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1067

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2942

5.13

1.20

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1.65

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332

1.48

639

514

7.1

1.75

000

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000

41.2

446

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0123

262.

1942

5.30

1.20

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7229

1.66

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350

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000

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000

42.3

747

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1055

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264.

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5.43

1.21

381.

7215

1.67

71.

370

1.51

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314

5.9

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000

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000

43.4

948

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1049

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8942

5.56

1.21

951.

7200

1.68

91.

389

1.52

837

714

5.3

1.90

000

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000

44.5

749

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1044

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0112

126

7.69

425.

661.

2250

1.71

861.

703

1.41

01.

544

371

144.

71.

9500

02.

0000

045

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50.2

910

38.3

0.01

087

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4842

5.75

1.23

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7172

1.71

61.

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1.55

936

514

4.1

2.00

000

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000

46.6

951

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1032

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0105

627

1.24

425.

811.

2358

1.71

571.

730

1.45

31.

576

360

143.

62.

0500

02.

1000

047

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52.2

710

26.9

0.01

025

272.

9942

5.87

1.24

111.

7142

1.74

41.

475

1.59

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3.0

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000

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000

48.7

353

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1021

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727

4.71

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891.

2463

1.71

281.

759

1.49

91.

610

349

142.

42.

1500

02.

2000

049

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54.1

910

15.6

0.00

969

276.

4242

5.91

1.25

151.

7113

1.77

41.

522

1.62

834

414

1.8

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000

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000

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055

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1010

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327

8.10

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901.

2566

1.70

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790

1.54

71.

647

339

141.

22.

2500

02.

3000

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56.0

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04.3

0.00

917

279.

7842

5.88

1.26

161.

7084

1.80

51.

572

1.66

633

314

0.6

2.30

000

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

Tabl

e D

.32:

R-4

07C

The

rmop

hysi

cal p

rope

rtie

s

R40

7C T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 33

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r2.

3500

052

.61

56.9

399

8.7

0.00

8928

1.43

425.

841.

2665

1.70

691.

823

1.59

91.

688

328

140.

02.

3500

02.

4000

053

.55

57.8

299

3.0

0.00

8728

3.08

425.

791.

2714

1.70

541.

840

1.62

51.

709

323

139.

42.

4000

02.

4500

054

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58.6

898

7.4

0.00

8528

4.70

425.

711.

2762

1.70

391.

858

1.65

41.

732

318

138.

82.

4500

02.

5000

055

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59.5

498

1.8

0.00

8328

6.32

425.

621.

2810

1.70

231.

876

1.68

31.

755

313

138.

22.

5000

02.

5500

056

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60.3

897

6.2

0.00

8028

7.92

425.

511.

2857

1.70

081.

896

1.71

51.

780

308

137.

62.

5500

02.

6000

057

.14

61.2

297

0.5

0.00

783

289.

5142

5.39

1.29

031.

6992

1.91

61.

746

1.80

530

313

6.9

2.60

000

2.65

000

58.0

062

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964.

90.

0076

291.

0942

5.24

1.29

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6977

1.93

81.

781

1.83

329

813

6.3

2.65

000

2.70

000

58.8

662

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959.

20.

0074

529

2.66

425.

091.

2995

1.69

611.

959

1.81

51.

860

293

135.

72.

7000

02.

7500

059

.70

63.6

295

3.5

0.00

7329

4.22

424.

911.

3041

1.69

451.

983

1.85

31.

891

289

135.

12.

7500

02.

8000

060

.53

64.4

194

7.8

0.00

709

295.

7742

4.72

1.30

861.

6928

2.00

61.

890

1.92

128

413

4.5

2.80

000

2.85

000

61.3

565

.17

942.

10.

0069

297.

3142

4.50

1.31

311.

6911

2.03

21.

932

1.95

527

913

3.9

2.85

000

2.90

000

62.1

665

.93

936.

30.

0068

298.

8542

4.28

1.31

751.

6894

2.05

81.

973

1.98

827

413

3.2

2.90

000

2.95

000

62.9

566

.67

930.

50.

0066

300.

3842

4.02

1.32

191.

6877

2.08

72.

019

2.02

627

013

2.6

2.95

000

3.00

000

63.7

467

.41

924.

70.

0064

301.

9142

3.76

1.32

621.

6860

2.11

52.

065

2.06

426

513

2.0

3.00

000

3.10

000

65.2

768

.83

912.

80.

0061

304.

9442

3.12

1.33

491.

6824

2.18

32.

174

2.15

425

613

0.7

3.10

000

3.20

000

66.8

070

.25

900.

90.

0059

307.

9742

2.48

1.34

351.

6787

2.25

12.

283

2.24

424

612

9.4

3.20

000

3.30

000

68.2

671

.60

888.

50.

0056

310.

9942

1.67

1.35

201.

6747

2.33

92.

424

2.36

223

712

8.1

3.30

000

3.40

000

69.7

172

.94

876.

00.

0053

314.

0142

0.85

1.36

051.

6707

2.42

72.

565

2.47

922

812

6.8

3.40

000

3.50

000

71.1

174

.22

862.

80.

0051

317.

0641

9.82

1.36

901.

6663

2.54

62.

755

2.63

921

912

5.5

3.50

000

3.60

000

72.5

075

.49

849.

60.

0048

320.

1041

8.79

1.37

751.

6618

2.66

52.

945

2.79

821

012

4.1

3.60

000

3.70

000

73.8

476

.70

835.

30.

0046

323.

2141

7.50

1.38

621.

6568

2.83

73.

218

3.02

720

112

2.7

3.70

000

3.80

000

75.1

877

.91

821.

00.

0044

326.

3241

6.20

1.39

481.

6518

3.00

93.

490

3.25

619

112

1.3

3.80

000

3.90

000

76.4

779

.05

805.

10.

0042

329.

5741

4.55

1.40

371.

6459

3.28

33.

916

3.61

418

211

9.9

3.90

000

4.00

000

77.7

580

.19

789.

10.

0039

332.

8141

2.89

1.41

261.

6400

3.55

64.

342

3.97

217

311

8.4

4.00

000

4.10

000

79.0

081

.26

770.

30.

0037

336.

3441

0.66

1.42

231.

6327

4.06

35.

108

4.61

616

411

6.9

4.10

000

4.20

000

80.2

482

.33

751.

50.

0035

033

9.86

408.

431.

4319

1.62

544.

570

5.87

45.

259

154

115.

34.

2000

04.

3000

081

.46

83.3

272

6.8

0.00

327

344.

0240

5.09

1.44

331.

6151

5.84

77.

686

6.77

214

411

3.5

4.30

000

4.40

000

82.6

784

.30

702.

10.

0030

334

8.17

401.

741.

4546

1.60

487.

125

9.49

88.

286

134

111.

74.

4000

04.

5000

084

.02

85.0

062

4.5

0.00

261

358.

9939

1.37

1.48

431.

5751

8167

.54.

5000

04.

6528

086

.08

86.0

850

6.0

0.00

198

375.

5237

5.52

1.52

981.

5298

∞∞

∞0

0.0

4.65

28 c

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

Tabl

e D

.33:

R-4

07C

The

rmop

hysi

cal p

rope

rtie

s

R40

7C T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 34

Figure D.8 : R407C p-h diagram

D - 35

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r0.

0100

0-8

8.54

-88.

4914

62.6

2.09

8877

.49

377.

550.

4628

2.08

801.

311

0.65

21.

225

1102

159.

70.

0100

00.

0150

0-8

3.80

-83.

7514

48.8

1.59

8383

.74

380.

400.

4958

2.06

371.

316

0.66

21.

225

1070

161.

30.

0150

00.

0200

0-7

9.05

-79.

0014

35.0

1.09

7789

.99

383.

240.

5288

2.03

941.

321

0.67

21.

225

1038

162.

90.

0200

00.

0300

0-7

3.69

-73.

6414

19.0

0.83

6097

.10

386.

400.

5644

2.01

621.

327

0.68

51.

226

1006

164.

50.

0300

00.

0400

0-6

8.33

-68.

2814

03.0

0.57

430

104.

2138

9.55

0.60

001.

9930

1.33

20.

697

1.22

797

316

6.0

0.04

000

0.05

000

-64.

86-6

4.81

1392

.50.

4836

610

8.85

391.

550.

6223

1.97

991.

336

0.70

71.

229

953

166.

90.

0500

00.

0600

0-6

1.39

-61.

3413

81.9

0.39

302

113.

4939

3.54

0.64

451.

9668

1.34

00.

716

1.23

093

316

7.8

0.06

000

0.07

000

-58.

76-5

8.71

1373

.80.

3465

911

7.04

395.

020.

6610

1.95

781.

344

0.72

41.

232

918

168.

40.

0700

00.

0800

0-5

6.12

-56.

0713

65.6

0.30

016

120.

5839

6.50

0.67

751.

9487

1.34

80.

732

1.23

390

316

9.0

0.08

000

0.09

000

-53.

97-5

3.92

1358

.90.

2718

012

3.49

397.

690.

6908

1.94

181.

351

0.73

91.

235

891

169.

40.

0900

00.

1000

0-5

1.82

-51.

7613

52.1

0.24

343

126.

4039

8.87

0.70

401.

9349

1.35

40.

745

1.23

687

816

9.8

0.10

000

0.10

100

-51.

62-5

1.56

1351

.50.

2411

612

6.67

398.

980.

7052

1.93

431.

355

0.74

61.

236

877

169.

90.

1010

00.

1013

2-5

1.56

-51.

5013

51.3

0.24

044

126.

7539

9.01

0.70

561.

9341

1.35

50.

746

1.23

687

716

9.9

0.10

132

b 0.

1100

0-4

9.98

-49.

9213

46.3

0.22

400

128.

9039

9.86

0.71

521.

9293

1.35

70.

752

1.23

886

817

0.2

0.11

000

0.12

000

-48.

16-4

8.10

1340

.50.

2050

613

1.38

400.

840.

7262

1.92

381.

360

0.75

81.

240

858

170.

50.

1200

00.

1300

0-4

6.56

-46.

5013

35.4

0.19

120

133.

5740

1.69

0.73

591.

9192

1.36

30.

764

1.24

284

917

0.8

0.13

000

0.14

000

-44.

95-4

4.89

1330

.30.

1773

313

5.75

402.

540.

7455

1.91

451.

366

0.76

91.

243

840

171.

00.

1400

00.

1500

0-4

3.52

-43.

4613

25.7

0.16

682

137.

7240

3.29

0.75

401.

9105

1.36

90.

775

1.24

583

217

1.2

0.15

000

0.16

000

-42.

09-4

2.02

1321

.00.

1563

113

9.68

404.

030.

7625

1.90

651.

372

0.78

01.

246

824

171.

40.

1600

00.

1700

0-4

0.80

-40.

7313

16.8

0.14

806

141.

4740

4.70

0.77

021.

9030

1.37

50.

785

1.24

881

717

1.6

0.17

000

0.18

000

-39.

50-3

9.43

1312

.50.

1398

114

3.25

405.

360.

7778

1.89

951.

377

0.79

01.

250

810

171.

70.

1800

00.

1900

0-3

8.31

-38.

2413

08.6

0.13

316

144.

9040

5.95

0.78

481.

8964

1.38

00.

795

1.25

280

417

1.8

0.19

000

0.20

000

-37.

12-3

7.05

1304

.70.

1265

114

6.54

406.

540.

7918

1.89

321.

383

0.79

91.

253

797

171.

90.

2000

00.

2100

0-3

6.02

-35.

9513

01.1

0.12

103

148.

0740

7.09

0.79

821.

8904

1.38

60.

804

1.25

579

117

2.0

0.21

000

0.22

000

-34.

92-3

4.85

1297

.40.

1155

514

9.59

407.

640.

8046

1.88

761.

388

0.80

81.

257

785

172.

10.

2200

00.

2300

0-3

3.90

-33.

8312

94.0

0.11

095

151.

0240

8.14

0.81

051.

8851

1.39

10.

813

1.25

978

017

2.2

0.23

000

0.24

000

-32.

87-3

2.80

1290

.50.

1063

515

2.44

408.

640.

8164

1.88

251.

393

0.81

71.

260

774

172.

20.

2400

00.

2500

0-3

1.91

-31.

8412

87.3

0.10

244

153.

7940

9.10

0.82

201.

8802

1.39

50.

822

1.26

276

917

2.3

0.25

000

0.26

000

-30.

95-3

0.88

1284

.10.

0985

215

5.13

409.

560.

8275

1.87

781.

397

0.82

61.

264

763

172.

40.

2600

00.

2700

0-3

0.05

-29.

9812

81.0

0.09

515

156.

4040

9.99

0.83

271.

8757

1.40

00.

830

1.26

675

817

2.4

0.27

000

0.28

000

-29.

15-2

9.07

1277

.90.

0917

715

7.66

410.

410.

8378

1.87

351.

402

0.83

41.

267

753

172.

40.

2800

00.

2900

0-2

8.30

-28.

2212

75.0

0.08

883

158.

8741

0.81

0.84

271.

8715

1.40

50.

838

1.26

974

917

2.5

0.29

000

0.30

000

-27.

44-2

7.36

1272

.10.

0858

916

0.07

411.

200.

8476

1.86

951.

407

0.84

21.

271

744

172.

50.

3000

0

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

R41

0A T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Tabl

e D

.34:

R-4

10A

Ther

mop

hysi

cal p

rope

rtie

s

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 36

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r0.

3100

0-2

6.63

-26.

5512

69.3

0.08

3316

1.22

411.

570.

8522

1.86

761.

409

0.84

61.

273

740

172.

50.

3100

00.

3200

0-2

5.81

-25.

7312

66.5

0.08

0716

2.36

411.

940.

8568

1.86

571.

411

0.85

01.

274

735

172.

50.

3200

00.

3300

0-2

5.04

-24.

9612

63.8

0.07

8416

3.46

412.

290.

8612

1.86

401.

414

0.85

41.

276

731

172.

50.

3300

00.

3400

0-2

4.27

-24.

1812

61.1

0.07

6116

4.55

412.

630.

8656

1.86

221.

416

0.85

81.

277

726

172.

50.

3400

00.

3500

0-2

3.53

-23.

4412

58.5

0.07

410

165.

6041

2.96

0.86

981.

8606

1.41

80.

862

1.27

972

217

2.5

0.35

000

0.36

000

-22.

79-2

2.70

1255

.90.

0720

516

6.65

413.

290.

8740

1.85

891.

420

0.86

51.

281

718

172.

50.

3600

00.

3700

0-2

2.08

-22.

0012

53.4

0.07

022

167.

6641

3.60

0.87

801.

8574

1.42

20.

869

1.28

371

417

2.5

0.37

000

0.38

000

-21.

37-2

1.29

1250

.90.

0683

816

8.67

413.

900.

8819

1.85

581.

424

0.87

31.

284

710

172.

50.

3800

00.

3900

0-2

0.69

-20.

6112

48.5

0.06

672

169.

6541

4.19

0.88

581.

8543

1.42

70.

877

1.28

670

717

2.5

0.39

000

0.40

000

-20.

01-1

9.92

1246

.10.

0650

617

0.62

414.

480.

8896

1.85

281.

429

0.88

01.

288

703

172.

50.

4000

00.

4100

0-1

9.36

-19.

2712

43.8

0.06

355

171.

5641

4.76

0.89

331.

8514

1.43

10.

884

1.29

069

917

2.5

0.41

000

0.42

000

-18.

70-1

8.61

1241

.40.

0620

417

2.49

415.

030.

8969

1.84

991.

433

0.88

71.

291

695

172.

50.

4200

00.

4300

0-1

8.07

-17.

9812

39.2

0.06

067

173.

4041

5.29

0.90

051.

8486

1.43

50.

891

1.29

369

217

2.5

0.43

000

0.44

000

-17.

44-1

7.35

1236

.90.

0592

917

4.31

415.

550.

9040

1.84

721.

437

0.89

41.

295

688

172.

40.

4400

00.

4500

0-1

6.83

-16.

7412

34.7

0.05

803

175.

1941

5.80

0.90

741.

8460

1.43

90.

898

1.29

768

517

2.4

0.45

000

0.46

000

-16.

22-1

6.13

1232

.50.

0567

717

6.07

416.

050.

9107

1.84

471.

441

0.90

11.

298

682

172.

30.

4600

00.

4700

0-1

5.63

-15.

5412

30.4

0.05

561

176.

9241

6.29

0.91

401.

8435

1.44

30.

905

1.30

067

917

2.3

0.47

000

0.48

000

-15.

04-1

4.95

1228

.20.

0544

517

7.77

416.

520.

9173

1.84

221.

445

0.90

81.

302

675

172.

30.

4800

00.

4900

0-1

4.47

-14.

3812

26.1

0.05

339

178.

6041

6.75

0.92

051.

8410

1.44

80.

912

1.30

467

217

2.3

0.49

000

0.50

000

-13.

90-1

3.81

1224

.00.

0523

217

9.43

416.

970.

9236

1.83

981.

450

0.91

51.

306

669

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20.

5000

00.

5250

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2.55

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4612

19.0

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998

181.

4041

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8370

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924

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314

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90.

5500

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566

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8317

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941

1.31

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0436

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9526

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470

0.94

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324

640

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70.

6000

00.

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.49

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202

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8341

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957

1.32

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317

1.5

0.62

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000

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0-6

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1195

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1.82

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480

0.96

51.

333

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30.

6500

00.

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811

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0.03

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2442

0.15

0.97

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8221

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973

1.33

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1.2

0.67

500

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000

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6-3

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1186

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3.90

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1.81

991.

490

0.98

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342

614

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00.

7000

00.

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.00

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011

82.8

0.03

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4942

0.87

0.98

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50.

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0.9

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0.75

000

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1178

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0349

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7.07

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9894

1.81

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500

0.99

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352

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70.

7500

00.

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411

74.6

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1.52

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8137

1.50

51.

005

1.35

759

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0.5

0.77

500

0.80

000

0.07

0.17

1170

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320

0.10

421.

821.

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1.81

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509

1.01

31.

361

591

170.

30.

8000

00.

8250

01.

031.

1311

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0.03

175

201.

5642

2.10

1.00

561.

8099

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41.

021

1.36

658

617

0.1

0.82

500

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

R41

0A T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Tabl

e D

.35:

R-4

10A

Ther

mop

hysi

cal p

rope

rtie

s

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 37

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r0.

8500

01.

992.

0911

62.9

0.03

0820

3.01

422.

381.

0108

1.80

801.

519

1.02

91.

371

580

169.

90.

8500

00.

8750

02.

913.

0111

59.2

0.02

9920

4.41

422.

641.

0158

1.80

621.

524

1.03

71.

376

575

169.

70.

8750

00.

9000

03.

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9311

55.4

0.02

9020

5.81

422.

891.

0208

1.80

441.

529

1.04

51.

381

569

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50.

9000

00.

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704.

8111

51.8

0.02

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1.80

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534

1.05

31.

387

564

169.

30.

9250

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585.

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48.1

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208.

5042

3.35

1.03

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1.53

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1.39

255

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000

0.97

500

6.43

6.54

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80.

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277.

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1142

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7977

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016

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000

1.05

000

8.87

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3.60

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559

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413

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01.

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356

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4.49

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7915

1.56

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110

1.42

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216

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1.15

000

11.9

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1120

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8.44

424.

791.

0649

1.78

861.

580

1.12

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436

524

167.

31.

1500

01.

2000

013

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13.5

711

14.3

0.02

149

220.

7942

5.08

1.07

301.

7857

1.59

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143

1.44

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516

6.8

1.20

000

1.25

000

14.8

614

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1108

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0206

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3.02

425.

311.

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1.78

291.

601

1.16

01.

459

507

166.

31.

2500

01.

3000

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16.3

811

01.7

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973

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2542

5.54

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821.

7801

1.61

11.

177

1.47

149

916

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17.5

817

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484

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3500

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89.5

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820

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5142

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7749

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285

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3.16

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31.

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510

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244.

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6.45

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7554

1.72

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365

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000

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000

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0133

324

6.77

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21.

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310

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248.

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131

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61.

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0000

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000

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733

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62.

0500

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1000

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11.5

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255.

3842

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1.72

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415

7.5

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000

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000

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635

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1006

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425.

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1.73

971.

828

1.52

81.

743

389

157.

02.

1500

02.

2000

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36.2

110

01.0

0.01

085

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6842

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7374

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553

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338

315

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000

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000

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2021

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860

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11.

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155.

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2500

02.

3000

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0.6

0.01

027

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711.

7330

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61.

608

1.80

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215

5.3

2.30

000

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

R41

0A T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Tabl

e D

.36:

R-4

10A

Ther

mop

hysi

cal p

rope

rtie

s

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 38

Den

sity

(k

g/m

3 ) Vo

lum

e (m

3 /kg)

c p

/cv

Bub

ble

Dew

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Liqu

idVa

por

Vapo

rLi

quid

Vapo

r2.

3500

038

.75

38.8

798

5.4

0.01

0026

3.48

425.

331.

2120

1.73

081.

894

1.63

71.

833

367

154.

82.

3500

02.

4000

039

.62

39.7

398

0.2

0.00

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5.06

425.

141.

2169

1.72

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911

1.66

61.

857

361

154.

22.

4000

02.

4500

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797

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884

356

153.

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4500

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5000

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41.4

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91.

910

351

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12.

5000

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5500

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42.2

396

4.7

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269.

7042

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7220

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000

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631.

2450

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7000

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45.3

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7142

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7.19

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2539

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078

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099

322

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8000

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3.6

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778

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47.5

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186

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260

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461

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13.

2000

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6141

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4000

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480

196

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14.

2000

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3000

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178

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94.

4000

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5000

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∞∞

∞0

0.0

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239

c

Not

e :

b =

one

stan

dard

atm

osph

ere.

c =

criti

cal p

oint

.

R41

0A T

herm

ophy

sica

l Pro

pert

ies.

Pro

perti

es o

f Sat

urat

ed L

iqui

d an

d S

atur

ated

Vap

or.

Abso

lute

Pr

essu

re

(MPa

)

Tabl

e D

.37:

R-4

10A

Ther

mop

hysi

cal p

rope

rtie

s

Soun

d ve

loci

ty

(m/s

)Te

mpe

ratu

re (o C

)Ab

solu

te

Pres

sure

(M

Pa)

Enth

alpy

(kJ/

kg)

Entr

opy

(kJ/

kgK

)Sp

ec. H

eat,

c p

(kJ/

kgK

)

D - 39

Figure D.9: R410A p-h diagram

D - 40

Conversion Table

Capacity Pressure

Btu/hr x 0.252 = kCal/hr psi x 0.07 = kg/cm2

Btu/hr x 0.293 = WATTS (W) psi x 27.7 = W.G.(in.)BHP x 0.746 = KILOWATTS (kW) psi x 2.309 = W.G.(ft.)Btu/hr x 0.001 = MBH psi x 0.69 x 104 = Pascal (Pa)

psi x 14.5038 = barVolume bar x 1 x 105 = Pascal (Pa)

L x 0.001 = m3

L x 0.264 = US GPM TemperatureL x 0.0353 = ft3 oF = (1.8 x oC) + 32in3 x 16.386 = cm3 oC = (oF - 32) / 1.8fl.oz x 0.02957 = L oK = 273.15 + oCft3 x 0.02831 = m3

MassPounds x 0.454 = KILOGRAMS (kg)Grams x 0.035 = fl.oz.

Flow RateL/s x 3.6 = m3/hrL/s x 0.001 = m3/sL/s x 15.85 = US GPML/s x 2.119 = CFM

Areain2 x 6.94 x 10-3 = ft2

in2 x 6.452 x 10- = m2

in2 x 6.452 = cm2

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