dc - dtictorque-tension relationship for selected self-locking nuts. the torque wrench and...

REPORT NO. NADC-75359-30

EFFFCT OF SELF-LOCKING NUTS ON TORQUE-TENSION RELATIONSHIP

M. J. ZurkoAir Vehicle Technology DepartmentNAVAL AIR DEVELOPMENT CENTER

Warminster, Pennsylvania 18974

-29 December 1I75

FINAL REPORTAIRTASK NO. A510-5103/001-4/3510-000-002

Work Unit A5309-59

APPROVED FOR PUBLIC RELEASE; DISTRIBUTION UNLIMITED.

DCPrepared for P

NA AL AIR SYSTEMS COMMANDDepartment of the Navy 2 1

Washington, D. C. 20361

NADC-75359-30

NOTICES

REPORT NUMBERING SYSTEM The numbering of technical project reports Issued by the Naval AirDevelopment Cnter Is arranged for tecific identification purposes. Each nuinber consists of the Centeracronym, tho clender year in which the number was assigned, the iequence .umber of the report withinthe specific calendar year, and the official 2-digit correspondence ccde of the Command Office or theFunctional Department responsible for the report. For exanple: Report No. NADC.73016-40 Indicatesthe fifteenth Center report for the year 1973, and prepared by the Crew Systems Department. Thenumerical coe- are as follows:

CODE OFFICE OR DEPARTMENT

00 Commander, Naval Air Development Center01 Technical Director, Naval Air Development Center02 Program and Finkincial Management Department03 Anti.Submarine Wart:re Program Office04 Remote Sen'ort Program Office05 Ship and Air Systems Integration Program Office06 Tactical Air Warfare Office10 Nav l Air Facility, Warminster20O Aero Electronic Technology Department30 Air Vehicle Technology Department40 Crew Systems Department50 Systems Analysis and Frgineering Department60 Naval Navigation Labr,,oatory81 Administrative and Technical Services Department85 Computer Department

PRODUCT EINDORSEMENT The discussion or instructions concerning commercial products herein donot constitute an endorsement ,y the Government nor do they convey or imply the license or right to usesuch products.

Nils ritkoe eciea 'tLU of SOWA C

STE

APPROVED BY:__ DATE: 29 December 1975P. H, STURMCoxmmdor, USNDeputy Director, AVTD

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READ INSTRUCTIONSREPORT DOCUMENTATION PAGE BEFORE COMPLETING FORM

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1 ~~NADC-75359-W~ _____________

-, '..ee~m=wmAmPmmg.7

PE~RI 0 COVERED

Effect of Self-Locking Nuts on / FinalTorque-Tension Relationship# 1

--4,.---_~~~~ ~ Ris-._t -. rrn',.; -... -'- R, NUMBER

7. AUTHOR(e) B. CONTRACT OR GRANT NUMBER(e)

M. J Aurko

9. PERFORMING ORGANIZATION NAME AND ADDRESS I T;. PROGRAM ELEMENT. PROJECv, TASK

Air Vehicle Technology Department (Code 30) A5! -5HUM3/B1-4/3510-O' -

Naval Air Development Center A00-002' Work Unit-AS309-59War minster, P A 18974 /'r-7'-

t CONTROLLING OFFICE NAME AND ADDRESS fjr -

Naval Air Systems Command 29 Dec v 7Department of the Navy -Washington, DC 20360 74 ,

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UNCLASSIFIED

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1 SUPPLEMENTARY NOTES

It KEY WORDS (Continue on reverse side 01 neceeary and Identity by block number)

Preload

Torque-Tension RelationshipNuts

Torque Wrench Method

ABSTRACT (Continue on revere aide It nece w y and identity by block number)

Testing was conducted to determine torque-tension relationship for self-

locking nuts. The test results indicated that torque wit.nch method is notaccurate for determining preload when fasteners are preloaded to 75-80

percent of their ultimate tensile strength. The accurdcy of torque wrench

method deteriorates even more if fasteners are used for more than one cycle

application. There was also significant difference in preload between all

metal nuts and ruts with nonmetallic insert. The astner preload - j /

DD , ', .. 1473 EDITION OF I N4OV 65 IS O8 LETE UNCLSIN 0C02-014I6601 _ CA__ ONO_ THS_ PAG_____ n ______ fe__

SECURITY CLACSIFICATION OF THIS PAGE (?71, Dot* Entered)

UNCLASSIFIED

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20.

variation decreased with larger fasteners.

UNCLASSIFIEDSE!CURITY CLASSIFICATION OF THIS PAGE(W(Who O. £ntead)

NhiDC-75359-30

SUMMARY

Testing was conducted by the Naval Air Development Center to determinetorque-tension relationship for selected self-locking nuts. The torque wrenchand Sidmoxe-;qilhelr bolt tension tester were used in determining torque-tension relationship.

The control of fastener preload is necessary in the design of rigidjoints for Navy aircraft, since joint strength is effected by preload as wellas by tensile strength of the fastener. The proper amount of preload willnot only extend the joint and fastener fatigue life but will also increasethe structural reliability.

The test results indicated that torque wrench method is not accurate fordetermining preload when fasteners are preloaded to 75-80 percent of theirultimate tensile strength. The accuracy of torque wrench method deteriorateseven more if fasteners are used for more than one cycle application. Therewas also significant difference in preload between all metal nuts and nutswith nonmetallic inserts. The fastener preload variation decreased withlarger fasteners.

Based on the test results it is recommended that fasteners should notbe reused when tbhy are preloaded to 75-80 percent of the fastener ultimatetensile strength by torque wrench method.

I .. . . . .. . . - -- --- -- -. .. .

PRECEDUG pA I4E

NADC- 75359-30

T AB LE O F CO0N TE NT S

Page No.

SUMMARY. ..............................

LSOFTABLES .. ............................ 3

LSOFFIGURES. ..........................

INTRODUCTION.................................7

DESCRIPTION OF TEST SAMPLES.......................8

DESRIPIONOF TEST AND SETUP......................

SUMMARY OF RESULTS .. .......................... 8

DISCUSSION................................11

CONCLUSIONS...............................12

RECOMMENDATIONS............................12

L IS T OF T AB LE

Table No. Title Page No.

I Torque-Tension Variation for No. 10 Size Nut. ....... 14

II Torque-Tension Variation for No. 1/4 Size Nut .. ...... 15

III Torque-Tension Variation fLor No. 5/16 Size Nut.......16

IV Torque-Tension Variation for No. 3/8 Size Nut .. ...... 17

V Torque-Tension Variation for No. 1/2 Size Nut .. ...... 18

VI Friction Factor for MS21042 Nuts...............19

VII Friction Factor for MS21044 Nuts .............. 20

VIII Friction Factor for MS21045 Nuts...............21

Ix Friction Factor for MS21245 Nuts .............. 22

3

NADC-75359-30

LIST OF FIGURES

Figure No. Title Page No.

1 MS21042 Nut, Self-Locking, 4500 F, ReducedHexagon and Height ....... .................. ... 23

2 MS21044 Nut, Self-Locking, 250 F, RegularHexagon and Height ....... ................. ... 24

3 MS21044 Nut, Self-Locking, 4500 F, RegularHexagon and Height ....... .................. ... 25

4 MS21245 Nut, Self-Locking, 450 F, RegularHexagon, Reduced Height ..... ............... ... 26

5 Torque-Tension Relationship for MS21042L3 ......... .. 27

6 Torque-Tension Relationship for MS21042L4 .......... .. 28



9 Torque-Tension Relationship for MS21042-3 .......... .. 31

10 Torque-Tension Relationship for MS21042-4 .......... .. 32

11 Torque-Tension Relationship for MS21042-5 .... ........ 33

12 Torque-Tension Relationship for MS21042-6 ........ ... 34

13 Torque-Tension Relationship for MS2104413. ......... . 35

14 Torque-Tension Relationship for MS21044N4 .......... .. 36


16 Torque-Tension Relationship for MS21044N6(Red Nylon) ....... ..................... ... 38

17 Torque-Tension Relationship for MS21044N6(Green Nylon) ....... .................... . 39



20 Torque-Tension Relationship for MS21045.4 .......... . 42


4

NADC-75359-30

LIST OF FIGURES (Cont.)

Figure No. Title Page No.

22 Torque-Tension Relationship for MS21045L6 .......... ... 44

23 Torque-Tension Relationship for MS21045L8 .. .. ...... 45

24 Torque-Tension Relationship for MS21045-3.. ........ 4




28 Torque-Tension Relationship for MS21045-8 ........... . .950

29 Torque-Tension Relationship for MS21245L8 .... ........ 51


31 Comparative Torque-Tension Relationship forNo. 10 Size Nuts Torqued to 50 in.-lbs .......... ... 53

32 Comparative Torque-Tension Relationship forNo. 10 Size Nuts Torqued to 75 in.-lbs .. .. ...... 54

33 Comparative Torque-Tension Relationship forNo. 10 Size Nuts Torqued to 100 in.-lbs. ...... 55

34 Comparative Torque-Tension Relationship for1/4 Size Nuts Torqued to 100 in.-'lbs .. .. ....... 56

35 Comparative Torque-Tension Relationship for1/4 Size Nuts Torqued to 200 in.-lbs ........... ... 57

36 Comparative Torque-Tension Relationship for1/4 Size Nuts Torque-I to 250 in. -lbs. .. ........

37 Comparative Torque-Tension Relationship for5/16 Size Nuts Torqued to 200 in.-lbs .......... ... 59

38 Comparative Torque-Tension Relationship for5/16 Size Nuts Torqued to 300 in.-lbs. .. ....... 60

39 Comparative Torque-Tension Relationship for5/16 Size Nuts Torqued to 400 in.-]bs .......... ... 61

40 Comparative Torque-Tension Relationship for3/8 Size Nuts Tczyued to 200 in.-lbs ........... ... 62

5

NADC-75359-30

L I S T 0 F F I G U R E S (Cont.)

Figure Title Page No.

41 Comparative Torque-Tension Relationship for

3/8 Size Nuts Torqued to 300 in.-lbs ........... ... 63

42 Comparative Torque-Tension Relationship for3/8 Size Nuts Torqued to 400 in.-lbs ........... ... 64

43 Comparative Torque-Tension Relationship for3/8 Size Nuts Torqued to 500 in.-lbs ............ ... 65

44 Comparative Torque-Tension Relationship for1/2 Size Nuts Torqued to 50 ft.-lbs .. ......... ... 66

45 Comparative Torque-Tension Relationship for1/2 Size Nuts Torqued to 75 ft.-lbs .. ......... ... 67

46 Comparative Torque-Tension Relationship for1/2 Size Nuts Torqued to 100 ft.-lbs .......... ... 68

47 Comparative Torque-Tension Relationship for1/2 Size Nuts Torqued to 125 ft.-lbs ... ........ ... 69

48 Calculated Torque-Tension Relationship forNo. 10 Size Nuts with Varied Friction Factor ....... 70

49 Calculated Torque-Tension Relationship for1/4 Size Nuts with Varied Friction Factor ........ . 71

50 Calculated Torque-Tenslrn Relationship for5/16 Size Nuts with Varied Friction Factor ........ ... 72

51 Calculated Torque-Tension Relationship for3/8 Size Nuts with Varied Friction Factor ....... . 73

52 Calculated Torque-Tension Relationship for1/2 Size Nuts with Varied Friction Factor ........ . 74

6

NADC-7 5359-30

INTRODUCTION

The testing program to determine torque-tension relationship forselected threaded fasteners was conducted by the Naval Air Development Center(NAVAIRDEVCEN) under AIRTASK A510-5103/001-4/3510-000-002, Work UnitA5303-59.

Due to the continual naval aircraft service problems created by the lackof realistic torque values for threaded fasteners the Naval Air SystemsCommand requested that a study be made and testing conducted by this Centerto determine torque-tension relationship that could provide realistic torquevalues for selected threaded fasteners.

The control of fastener preload is necessary in the design of rigid jointsfor Navy aircraft, since joint strength is effected by preload as well astensile strength of the fastener. The proper amount of preload will extend thejoint and fastener fatigue life thereby inzreasing the structural reliabilityof the system. Exact preload is difficult to obtain due to variables such as;bolt and nut friction, bearing area friction, bolt and nut dissimilar materialshaving diiferent anti-seize properties, thread tolerances, hardness, alignment,type of finish, coating, lubricant and age of lubricant. There are a number ofdifferent methods that can be used to control preload of threaded fasteners,some of them are listed below in order of increasing accuracy:

1. Feel method - preload is determined by feel.

2. Torque wrench method - the nut or bolt is turned to a predeterminedtorque.

3. Turn-of-nut method - the nut or bolt is turned a predeterminednumber of degrees after all play has been removed from the joint.

4. Preload indicating washer method - utilizes compression of an innerring between two flat washers with an outer indicating washer for control.As the load increases, the inner ring (which is higher than the outer indicatingwasher) is sqeezed down and is enlarged in diameter; the predetermined preloadis obtained when the outer indicating washer binds against the two flat washers.The other type of indicating washer utilized collapse of washer's precisioncollar when predetermined preload has been reached.

5. Frangible nut (collar shear-off) method - utilizes collar on the nutthat shears-off at a predetermined preload.

6. Pull method - the pin is stretched to a predetermined load with a toolwhile the collar is swaged into the groove of the pin or threaded on to thepin.

7. Bolt elongation method - preload is determined by measuring theacutal change in the length of the bolt.

7

NAnC-75359-30

8. Strain gage method - preload is determined by use of strain gages.

NAVAIRDEVCEN evaluated method 2 (torque wrench method), and used the preloadof 80 percent of the fastener ultimate tensile strength in this evaluation,since this is an optimum preload for torque wrench method. This method isvery inexpensive and has been widely accepted by the aircraft industry. ASnap-on torque wrench was used to determine the torque and Skidmore-Wilhelmbolt tension tester was used to determine the tension.

DESCRIPTION OF TEST SAMPLES

The alloy steel self-locking nuts used in test program were MS21042,MS21044, MS21045 and MS21245. Half of the nuts from each military standardhad a dry film lubricant and the other half a soluble lubricant, and wereobtained from the Defense Industrial Supply Center (DISC).

The MS21042 nuts were of designs A and B and aze shown in figure 1, theirlocking element zonsisted of upper threaded section bing ellipticallyoffset. The MS21044 nuts were of design C and are shown in fiaure 2, theirlocking element consisted of nonmetallic insert. The MS21045 nuts wereof designs G, H, E and F and are shown in figure 3. The locking element ofdesigns G and H consisted of upper threaded section being divided into sixequal segments which were upset or closed in. The locking element of designsE and F consisted of upper threaded section being elliptically offset. TheMS21245 nuts were of design K and are shown in figure 4, their locking elementconsisted of upper threaded section being divided Jnto six equal segments whichwere upset or closed in. The nuts of designs D and J are shown in figures 3and 4 but were not used in this evaluation. The nuts were tested on MS21250,MS20004, MS20005, MS20006 and MS20008 bolts, with exception of MS21250 the boltswere of 160 KSI Ftu strength level. The MS21250 bolts were of 180 KSI Ftustrength lev! and were used for No. 10 size, since this size is not availablein 160 MSI Ftu strength level. The MS20002 countersunk washers were used underbolts and nuts bearing areas.

DESCRIPTION OF TEST AND SETUP

The bolts and nuts with countersunk washer6 under the bearing areas were

installed in 30,000 pounds Skidmore-Wilhelm boit tension tester, whichhad two gages, one of 10,000 pounds and the other 30,00r pounds. The nutwas then turned while the bolt was held stationary. This procedure wasrepeated for 5 cycles. The nuts were preloaded to approximately 80 percentof the nut minimum ultimate tensile strength. The torque needed to obtainthis preload was established by tests on initial samples and was not variedfor the nuts of the same size and strength level, regardless of the nutdesign or preload. The torque readings were obtained by using 300 in.-lbs.,600 in.-lbs. and 250 ft.-lbs. Snap-on torque wrench and preload readingswere obtained from gages on Skidmore-Wilhelm bolt tension tester.

SUMMARY OF RESULTS

The torque-tension relationship (figures 5 through 30) betw:een variousself-locking element designs, lubricants and even between samples of the same

NADC-75359-30

design and size exhibited marked differences. The comparative torque-tension relationship, preload spread and variation between samples ofdifferent designs and lubricants are shown in figures 31 through 47and in tables I through V. The effect of friction factor (coefficientof friction) on torque-tension relationship are shown in figures 48through 52. Due to wide preload spread obtained on the fifth cycle,see tables I through V, results beyond first cycle could not be evaluatedin detail. The differences in the preload among the samples for the firstcycle (at the torque which was initially determined by test to be 80 percentof the nut minimum ultimate axial strength) are detailed below:

1. MS21042 (first cycle with dry film lubricant).

Sizes No. 10, 1/4, 5/16 and 3/8 inch were of design B, B, A and Arespectively, see figure 1. The preload spreads on five samples of each sizewere: 36, 19, 8 and 17 percent for sizes No. 10, 1/4, 5/16 and 3/8 inchrespectively. Sample nuts of sizes No. 10 and 1/4 inch were from 32 percentbelow to 21 percent above the 80 percent preload, see tables I and II. Samplenuts of sizes 5/16 and 3/8 inch were 51 to 11 percent below the 80 percentpreload, see tables III and IV.

2. MS21042 (first cycle with soluble lubricant).

Sizes No. 10, 1/4, 5/16 and 3/8 inch were of design B, see figure 1.The preload spreads on five samples of each size were: 29, 53, 13 and 18percent for sizes No. 10, 1/4, 5/16 and 3/8 inch respectively. Sample nutsof size 1/4 inch were from 24 percent below to 29 percent above the 80 percentprcload, see table II. Sample nuts of sizes No. 10, 5/16 and 3/9 inch were68 to 6 percent below the 80 percent preload, see tables I, III and IV.

Based on sample average of sizes No. 10, 1/4, 5/16 and 3/8 inchthe average friction factor (coefficient of friLtion) for nuts with dryfilm lubricant was 0.21 and for nuts with soluble lubricant was 0.25,see table VI.

3. MS21044 (first cycle with soluble lubricant and nonmetallic insert).

Sizes No. 10, 1/4, 5/16, 3/8 and 1/2 inch were of design C, seefigure 2. The preload spread on five samples of each size were: 80, 54, 39,25 and 39 percent for sizes No. 10, 1/4, 5/16, 3/8 and 1/2 inch respectively.Sample nuts of sizes No. 10 and 1/4 inch were from 63 percent below to17 percent above the 80 percent preload, see tables I and II. Sample nutsof sizes 5/16, 3/8 and 1/2 inch were 62 to 4 percent below the 80 percentpreload, see tables III, IV and V.

Based on sample average of 3izes No. 10, 1/4, 5/16, 3/8 and 1/2 theaverage friction factor (coefficient of friction) for nuts was 0.30, seetable VII.

9

NADC-75359-30

4. MS21045 (first cycle with dry film lubricant).

Sizes No. 10, 1/4, 5/16, 3/8 and 1/2 inch were of design E, G, F,H and H respectively, see figure 3. The preload spreads on 5 samples of eachsize were: 23, 23, 25, 18 and 40 percent for sizes No. 10, 1,'4, 5/16, 3/8and 1/2 inch respectively. Sample nuts of sizes No. 10 and 3/8 inch were from17 percent below to 9 percent above the 80 percent preload, sr tables I and

~IV. Sample nuts of size 1/4 inch were 24 to I percent below the 80 percentpreload, see table II. Sample nuts of sizes 5/16 and 1/2 inch were 13 to 53

percent above the 80 percent preload, see tables III and V.

5. MS21045 (first cycle with soluble lubricant).

Sizes No. 10, 1/4, 5/16, 3/8 and 1/2 inch were of desi.gn E, E, G,E and F respectively, see figure 3. The preload spreads on five samples of

each size were: 46, 38, 58, 8 and 23 percent for sizes No. 10, 1/4, 5/16 3/8and 1/2 inch respectively. Sample nuts of sizes No. 10 and 1/2 inch were from9 percent below to 37 percent above the 80 percent preload, see tables I andV. Sample nuts of size 3/8 inch were 36 to 28 percent below the 80 percentpreload, see table IV. Sample nuts of size 1/4 and 5/16 were 19 to 65 percentabove the 80 percent preload, see tables II and Yii.

Based on sample average of sizes No. 1u, 1/4, 5/16, 3/8 and 1/2inch the average friction factor (coefficient of friction) for nuts withdry film lubricant was 0.20 and for nuts with soluble lubricant wes 9.18,see table VIII.

6. MS21245 (first cycle).

Nuts with dry film and nuts with soluble lubricant were of 1/2 inchsize and of design K, see figure 4. The preload spread on five samples with

dry film lubricant was 28 percent and for samples with noluble lubricant was34 percent. The preload spread on sample nuts with dry film lubricanc variedfrom 2 to 30 percent above, and on samples with soluble lubricant from15 percent below to 19 percent above the 80 percent preload, see table V.

Based on sample average of one size the average friction factor(coefficient of friction) for nuts with dry film lubricant was 0.14 andfor nuts with soluble lubricant was 0.16, see table IX.

Preload for the fifth cycle varied widely and the extreme variations arelisted below:

1. MS21042 (fifth cycle with dry film lubricant).

a. Size No. 10, 1900 to 2900 pounds for the first cycle and 700 to3400 pounds for the fifth cycle.

b. Size 3/8, 6000 to 10800 pounds for the first cycle and 3850 to10,000 pounds for the fifth cycle.

10

NADC-75359-30

2. MS21042 (fifth cycle with soluble lubricant).

a. Size No. 10, 1800-2600 pounds for the first cycle and3800 pounds for the fifth cycle for one sample only because bolts broke onother four samples before required torque was reached.

b. Size 5/16, 2500 to 3500 pounds for the first cycle and 2100

to 6750 pounds for the fifth cycle.

3. MS21044 (fifth cycle with soluble lubricant and nonmetallic insert).

a. Size 3/8, green insert, 3125 to 4750 pounds for the first cycleind 11625 to 12750 pounds for the fifth cycle.

b. Size 3/8, red insert, 3055 to 5800 pounds for the first cycleand 11375 pounds for the fifth cycle for one sample only. because nut threadstrip?ed on other four samples before required torque was reached.


a. Size 1/4, 4375 to 5750 pounds for the first cycle and 2375 to2750 for the fifth cycle.

b. Size 3/8, 5875 to 7500 pounds for the first cycle and 4750 to12375 for the fifth cycle.

5. MS21045 (fifth cycle with dry film lubricant).

a. Size 1/4, 2800 to 3625 pounds for the first cycle and 1750 to2375 for the fifth cycle.

b. Size 3/8, 7600 to 9250 Eounds for the first cycle and 9250 to11250 pounds for the fifth cycle.


a. Size 1/2, 9375 to 13125 pounds for the first cycle and 3000 to3750 pounds for the fifth cycle.

DISCUSSION

In this test program no attempt was made to determine what effectlubricant age or various locking elements have on preload. The militarystandards leave the shape of the upper part of the nut and the lockingelement design optional, therefore, different manufacturers make nutswith various upper shapes and locking elements which meet the same militarystandard. The self-locking nuts used in this test program were obtainedfrom Defense Industrial Supply Center (DISC) by specifying federal stocknumber, therefore, they are representative samples as to what is used in thefield. The tested nuts had various upper shapes and locking elements, see

Ii

_ . .. m= .== --- m -- "11

NADC-75359-30

figures 1, 2, 3 and 4, and because they were obtained out of stock and lackidentification markings, determination could not be made when or who manu-factured them.

During torque-tension tests the MS21042-3 all metal nuts and MS21044N6 nutswith red and green nonmetallic inserts had appreciably higher preload on thefifth cycle than on the first cycle, which is contrary to data obtained forthe other samples, see figures 9, 16 and 17. The trend of the test dataindicates that with each reuse of the fastener, higher torque is needed toobtain the same preload. No explanation can be ade for opposing resul-s onMS21042-3 and MS21044N6.

C 0 N C L U S I 0 N S

1. Based on the test results the torque wrench method for determining pre-load is not accurate.

2. Fasteners that have been preloaded to 75-80 percent of the ultimate tensile

strength should not be used beyond first cycle application.

3. The fastener preload becomes more uniform with larger size fasteners.

4. The variation of the friction factor (coefficient of friction) betweenall metal dry film lubricated nuts and all aetal nuts with soluble lubricantwas not aignificant. The friction factors, for the first cycle only, wereas follows:

a. Friction factor 0.21 for MS21042 with dry film lubricant.b. Friction factor 0.25 for MS21042 with soluble lubricant.

c. Friction factor 0.21 for MS21045 with dry film lubricant.d. Friction factor 0.18 for MS21045 with soluble lubricant.

e. Friction factor 0.14 for MS21245 with dry film lubricant.f. Friction factor 0.16 for MS21245 with soluble lubricant.

If sizes No. 10 and 1/4 inch were not included in calculating average frictionfactor for MS 21045, the friction factor for nuts with and without dry filmlubricant would be 0.15.

5. There is a significant difference in friction factor between all metalnuts and nuts with nonmetallic insert. The friction factor tor nuts with non-metallic insert was 0.30.

RECOMMENDATIONS

1. Based on the test results it is recommended that fasteners should notbe reused when they were preloaded to 75-80 percent of the fasteners ultimatetensile strength by torque wrench method.

2. It is recommended that when fasteners are preloaded to 75-80 percent

12

NADC-75359-30

of the fastener ultimate tensile strength the torque wrench method should notbe used in application where failure of one fastener would result infailure of the system.

3. lased on the test results it is recommended that friction factor of0.30 be used for MS21044 self-locking nuts with nonmetallic insert for sizesNo. 10 ,hrough 1/2 inch and 0.15 Zor MS21045 self-locking nuts made from alloysteel for sizes 5/16 through 1/2 inch.

4. Additional tests should be conducted to determine accuracy of othermethods to control preload of threaded fasteners such as preload indicatingwashers and frangible nut (collar shear-off nut).

13

NADC-75359-30

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"D.I S T R I B U T 1 0 N L I S T

AIRTASK NO. A510-5103/001-4/3510-000-002Work Unit No. A5305-59

No. of Copies

NAVAIR (AIR-954) ...... ..................... . . . . 28(2 for retention) (2 for AIR-53031)(2 for AIR-5102B) (2 foAIR-530321)(2 for AIR-5203) (2 for AIR-539323)(2 for AIR-520C) (2 for AIR-5304)(2 for AIR-52021D) (2 for AIR-340)(2 for AIR-530215) (2 for AIR-4111)(2 for AIR-5303) (2 for AIR-41111C)

COMNAVAIRPAC .......... . . . ...... . . . . . . 1AFSD ASD (ENFSS) . . . . . . .. .. .. .. .. .. .. .. . .3

ASO (TEC and PGB-21) . . .... . . . . . . . . . . . . . . 2

DISC (PGB, SCB and M) ... . . . . . . . ..... . 3NAVAIRENGCEN, ESSD (X-22) .1...............ARMY AVNSYSCOM (AMSAV-ESP . ................... 2

DDC . .2 .

NAVAIRDEVCEN, Warminster, Pennsylvania 18974 . . . . . 21(3 for 813) (1 for 50)(2 for 30023) (1 for 60)(1 for 03) (1 for 30P4)(1 for 20) (1 for 30P6)(1 for 30) (i1 for 30P7)(1 for 40) (1 for 301)

(1 for 302)(1 for 303)(1 for 304)(1 for 305)(1 for 3053)(1 for 3053: M. Zurko)

'I

dc - dtictorque-tension relationship for selected self-locking nuts. the torque wrench and...

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