thermodynamics ii chapter 3 compressors
DESCRIPTION
Thermodynamics II Chapter 3 Compressors. Mohsin Mohd Sies Fakulti Kejuruteraan Mekanikal , Universiti Teknologi Malaysia. Coverage. Introduction Indicated Work, Mechanical Efficiency Condition for Minimum Work Isothermal Efficiency Compressors with Clearance - PowerPoint PPT PresentationTRANSCRIPT
Thermodynamics IIChapter 3
Compressors
Mohsin Mohd SiesFakulti Kejuruteraan Mekanikal, Universiti Teknologi Malaysia
Coverage
β’ Introductionβ’ Indicated Work, Mechanical Efficiencyβ’ Condition for Minimum Workβ’ Isothermal Efficiencyβ’ Compressors with Clearanceβ’ Volumetric Efficiency, Free Air Deliveryβ’ Multistage Compressionβ’ Ideal Intermediate Pressure
Introduction
β’ Compressed air is air kept under a pressure that is greater than atmospheric pressure.
β’ In industry, compressed air is so widely used that it is often regarded as the fourth utility, after electricity, natural gas and water.
Compressed air is used for many purposes, including:β’ Pneumatics, the use of pressurized gases to do work
β’ Pneumatic post, using capsules to move paper and small goods through tubes.
β’ Air toolsβ’ HVAC control systems
β’ Vehicle propulsion (compressed air vehicle)β’ Energy storage (compressed air energy storage)β’ Air brakes, including:
β’ railway braking systemsβ’ road vehicle braking systems
β’ Scuba diving, for breathing and to inflate buoyancy devicesβ’ Refrigeration using a vortex tubeβ’ Gas dusters for cleaning electronic components that cannot be
cleaned with waterβ’ Air-start systems in enginesβ’ Ammunition propulsion in:
β’ Air guns, Airsoft equipment, Paintball equipment
Usages
Compressor typesβ’ Positive Displacement Machines
(high pressure ratio, low mass flow rates)β Rotating
β’ Screw compressors (Lysholm)β’ Scroll compressorβ’ Roots blowers
β Alternating (Reciprocating Compressor)β’ Turbocompressors
(low pressure ratio, high mass flow rates)β Centrifugal compressorβ Axial compressorβ Mixed-flow compressor
Reciprocating Compressor
Single Acting
Reciprocating Compressor
Double Acting
Piston-cylinder terminologies
TDC β Top Dead CenterBDC β Bottom Dead Center
b β Bore, Diameters β Strokel β Connecting Rod Lengtha β Crank Throw = Β½ stroke
Piston-cylinder terminologies
π2
π1=Pressure Ratio=π π
Compressor Operation
β’ Process d β a : Intake or Inductionβ Piston moves from TDC to BDCβ Intake valve opens and air induced into cylinderβ Pressure P1 and temperature T1 remain constant.
β’ Process a β b : Compressionβ Intake valve closes and piston moves towards TDCβ Compression follows the polytropic process Pvn=c
until P2 is reached.
Compressor Operation
β’ Process b β c : Deliveryβ Delivery valve opensβ Compressed air exits and delivered.β Pressure P2 and temperature T2 remain constant.
β’ Process c β d : Expansionβ Both valves remain closed as the cycle returns to
the initial stateβ Constant volume if without clearanceβ Polytropic expansion if with clearance
Indicated Work- Indicated by P-v diagram, (P-v diagram = Indicator diagram)
For a cycle
π πππ ΒΏ β«1
2
πππ
ΒΏ ΒΏ ΒΏabef+bcoeβ adof ΒΏ=ΒΏ
π2π πβπ1π π
πβ1 +π2π πβπ1π πΒΏ=ΒΏ ππβ1 (π2π πβπ1ππ)ΒΏ
π2
π1=( π2
π1 )(πβ 1)π =(π£1π£2 )
(πβ1)Recall polytropic relationship between two states
Indicated WorkCan also be considered as open system
π πππ ΒΏ β«π1
π2
πππ
ΒΏ ΒΏ ΒΏ
ππβ1 (π2π πβπ1π π)ΒΏ
π πππ ΒΏπ
πβ1 (ππ π2βππ π 1 )ΒΏ ΒΏ ΒΏ
ππβ1ππ π 1(π 2
π 1β1)ΒΏ
And since PV = mRT
ΒΏπ
πβ1ππ π 1(( π2
π1 )πβ1π β1)
ΒΏπ
πβ1 π1π π((π2
π1 )πβ1π β1)
Power (and Rates)β’ Has to take into account single or double actingβ’ Wind is work per cycle of P-v diagram. β’ If single acting, one cycle per crank revolutionβ’ If double acting, two cycles per crank revolution (one cycle
each for both sides of piston face). β Mass flow rate is doubled accordingly.
οΏ½ΜοΏ½ ΒΏπ
πβ1 οΏ½ΜοΏ½π π1(( π2
π1 )πβ1π β1)
ΒΏ ΒΏ ΒΏ
οΏ½ΜοΏ½=πΓπΓπππ‘πππ
Mechanical Efficiencyβ’ The actual power input into the compressor is larger than the
indicated power, to overcome friction and other losses.
Shaft power = Indicated power + Friction power loss
Mechanical Efficiency=Indicated powershaft power
Other losses can also be taken into account accordingly
Condition for Minimum Workβ’ We aim to reduce the input workβ’ d-a is the stroke, determined by
cylinder design and measurementβ’ P2 is desired delivery pressure. As
long as P2 is reached, the compressor has done its job.
β’ Only the compression process can be adjusted by varying n, the polytropic index.
β’ Isothermal process (n=1) results in minimum work (smallest area).
β’ Compressors are cooled by water jackets or cooling fins
Isothermal Work, Isothermal Efficiency
β’ Integrating by isothermal process, Pv=c
π isothermal ΒΏ π1π π ln( π2
π1 )ΒΏ ΒΏ ΒΏ
β’ Isothermal efficiency
Ξ· isothermal=Isothermal WorkIndicated Work
Compressors with Clearanceβ’ Clearance is needed for free
movements of piston and valvesβ’ Clearance volume is Vc.β’ When delivery is completed (b-c),
there is still compressed air at P2 and T2 in the clearance volume.
β’ When intake stroke begins at Vc, no outside air can enter yet until the residual compressed air has expanded down to P1 and T1.
β’ Thus, having clearance reduces the volume of inducted air from (Va-Vc) originally to only (Va-Vd)
Compressors with Clearance
β’ Mass of air, ma = mb, and md = mc
β’ The amount of air handled, m = ma β md = mb β mc
β’ Wind = area abcd= area abef β area cefd
π πππ ΒΏπ
πβ1πππ (π 2βπ1 )β ππβ1πππ (π 2βπ1 )
ΒΏπ
πβ1 (ππβππ)π (π 2βπ 1 )
ΒΏπ
πβ1ππ (π 2βπ 1)
Even though Work depends on clearance, but work per unit mass does not depend on it.
Free Air Delivery, FAD
β’ FAD is the amount of air handled (delivered) by the compressor.
β’ FAD is given as the volumetric flow rate of air (measured at free air conditions Po and To)
FAD=οΏ½ΜοΏ½ π’=οΏ½ΜοΏ½π π π
ππ
Actually, this is easier given by the mass flow rate since it does not depend on P and T
Volumetric EfficiencyΞ·π£=
ππ’
ππ
Ξ·π£=π π’
π π
The mass of gas enteringThe mass of gas that should fill the swept volume at the same reference condition (free air condition)
The volume of gas entering measured at free air condition
The swept volume of cylinder
Volumetric Efficiency
β’ The result above is assuming that the in-cylinder condition (T1, P1) is the same as free air condition (To, Po)
Ξ·π£=π π’
π π =
(π ΒΏΒΏπβπ π)(π ΒΏΒΏ πβπ π)ΒΏ
ΒΏ
Ξ·π£=1βπ π
π π [(π2
π1 )1πβ1]
Volumetric Efficiencyβ’ The entering air is actually being heated by the hot cylinder
walls and there has to be a pressure difference (Po β P1) so that air can flow into the cylinder.
β’ We can use the unchanging mass to get the correction factor to account for these differences
π π’=(π ΒΏΒΏ πβπ π)π π
π 1
π1ππ
ΒΏ
Ξ·π£={1βπ π
π π [( π2
π1)1πβ1 ]}π π
π1
π1
ππ
Multistage Compressionβ’ For a given Vs, increasing rp willβ decrease Ξ·v.β Increase delivery temperature
β’ To achieve high pressures while avoiding those problemsβ Do Multistage Compression
β’ At some intermediate pressure Pi, the gas is sent to a smaller cylinder to be compressed further.
β’ This also allows us to cool the gas (intercooling) to reduce compression work.
Multistage Compression
Multistage Compression
β’ Complete Intercooling ifβ Intermediate temperature
Ti is cooled back to the same temperature as T1.
Optimum Intermediate Pressureβ’ The chosen Pi affects the amount of compression
work that has to be supplied.β’ An optimum Pi will give us the minimum compressor
work.β’ Letβs assume complete intercooling.Wtotal = WLow Stage + WHigh Stage
π πππ‘ππ=π
πβ1ππ π 1(( π π
π1 )πβ 1π β1)+ π
πβ1ππ π π(( π2
ππ )πβ1π β1)
π πππ‘ππ=π
πβ1ππ π 1(( π π
π1 )πβ 1π +( π2
π π )πβ 1π β2)
Since Ti = T1 ,
Optimum Intermediate Pressureβ’ For a fixed P1, T1 and P2, we can the optimum Pi that
gives us minimum Wtotal by
ππ πππ‘ππ
ππ π= ππ ππ ( π
πβ1ππ π1(( ππ
π1 )πβ1π +( π2
π π )πβ1π β2))=0
ππ πππ‘ππ
ππ π=0
ΒΏππ π π (( π π
π1 )πβ 1π +( π2
π π )πβ 1π β2)=0
π π2=π2π1
π πβπππ‘πππ’π= 2βπ2π1
π π
π1=π2
π π=π πβπππ‘πππ’π=( π2
π1)12
Optimum Intermediate Pressureβ’ So, for minimum compressor workβ Complete intercoolingβ Same pressure ratio for all stages
β’ This can be generalized to more than two stages
π πππ‘ππ=π
πβ1ππ π 1(( π π
π1 )πβ 1π β1)+ π
πβ1ππ π π(( π2
ππ )πβ1π β1)
π πππ‘ππ=2ππβ1ππ π 1(( π π
π1 )πβ 1π β1)
π πππ‘ππ=2ππβ1ππ π 1(( π2
π1 )πβ12π β1)
Optimum Intermediate Pressureβ’ This can be generalized to more than two stages (z =
number of stages, P1 = intake pressure, P2 = final pressure)
β’ For minimum compressor workβ Complete intercoolingβ Same pressure ratio for all stages ππβπππ‘πππ’π=( π2
π1 )1π§
π πππ‘ππ=π§ππβ1ππ π 1(( π2
π1 )πβ1π§π β1)