TIGHTENING TORQUES AND THE TORQUE-TENSION …

1 62 TIGHTENING TORQUES AND THE TORQUE-TENSION RELATIONSHIPAll of the analysis and design work done in advance willhave little meaning if the proper preload is not discussions in this technical section stress theimportance of preload to maintaining joint are many methods for measuring preload (seeTable 12). However, one of the least expensive tech-niques that provides a reasonable level of accuracyversus cost is by measuring torque . The fundamentalcharacteristic required is to know the relationshipbetween torque and tension for any particular boltedjoint. Once the desired design preload must be identifiedand specified first, then the torque required to inducethat preload is the elastic range, before permanent stretch is induced, the relationship between torque and tensionis essentially linear (see figure 13). Some studies havefound up to 75 variables have an effect on this relation-ship: materials, temperature, rate of installation, threadhelix angle, coefficients of friction, etc.

2 One way that hasbeen developed to reduce the complexity is to dependon empirical test results. That is, to perform experimentsunder the application conditions by measuring theinduced torque and recording the resulting tension . Thiscan be done with relatively simple, calibrated hydraulicpressure sensors, electric strain gages, or piezoelectricload cells. Once the data is gathered and plotted on achart, the slope of the curve can be used to calculate acorrelation factor. This technique has created an acceptedformula for relating torque to = K 2D 2PT = torque , = fastener nominal diameter, inchesP = preload, = nut factor, TIGHTENING factor, or k-value If the preload and fastener diameter are selected inthe design process, and the K-value for the applicationconditions is known, then the necessary torque can becalculated. It is noted that even with a specified torque ,actual conditions at the time of installation can result invariations in the actual preload achieved (see Table 12).

3 One of the most critical criteria is the selection of theK-value. Accepted nominal values for many industrialapplications are:K = for as-received steel bolts into steel holes K = steel bolts with cadmium plating, which acts likea lubricant,K = steel bolts with zinc K-value is not the coefficient of the friction ( ); it isan empirically derived correlation is readily apparent that if the torque intended for azinc plated fastener is used for cadmium plated fastener,the preload will be almost two times that intended; itmay actually cause the bolt to influence is where friction occurs. For steelbolts holes, approximately 50% of the installation torqueis consumed by friction under the head, 35% by threadfriction, and only the remaining 15% inducing preloadtension. Therefore, if lubricant is applied just on thefastener underhead, full friction reduction will not beachieved.

4 Similarly, if the material against which thefastener is bearing, aluminum, is different than theinternal thread material, cast iron, the effectivefriction may be difficult to predict, These examples illustrate the importance and the value of identifying the TORQUE-TENSION relationship . It is a recommendpractice too contact the lubricant manufacturer for K-value information if a lubricant will be recommended seating TORQUES for Unbrakoheaded socket screws are based on inducing preloadsreasonably expected in practice for each type. The values for Unbrako metric fasteners are calculated using VDI2230, a complex method utilized extensivelyin Europe. All values assume use in the received con-dition in steel holes. It is understandable the designermay need preloads higher than those listed. The following discussion is presented for those YIELD AND TENSIONCAPABILITY AFTER TORQUINGOnce a headed fastener has been seated against a bear-ing surface, the inducement of torque will be translatedinto both torsion and tension stresses.

5 These stressescombine to induce twist. If torque continues to be induced,the stress along the angle of twist will be the largeststress while the bolt is being , thestress along the bolt axis (axial tension ) will be somethingless. This is why a bolt can fail at a lower tensile stressduring installationthan when it is pulled in straight tensionalone, eg . a tensile test. Research has indicated the axialtension can range from 135,000 to 145,000 PSI for industrysocket head cap screws at torsion- tension yield, depend-ing on diameter. Including the preload variation that canoccur with various installation techniques, eg. up to 25%,it can be understood why some recommended torquesinduce preload reasonably lower than the yield 13 also illustrates the effect of straight tensionapplied after installation has stopped. Immediately afterstopping the installation procedure there will be somerelaxation, and the torsion component will drop towardzero.

6 This leaves only the axial tension , which keeps the joint clamped together. Once the torsion is relieved,the axial tension yield value and ultimate value for thefastener will be MeasuringAccuracyRelativeMethodPercentCo stFeel (operator s judgement) 351 torque wrench of the nut 153 Load-indicating washers 107 Fastener elongation 3 to 515 Strain gages 120 Table 12 Industrial Fasteners Institute s torque -Measuring Method63 THE TORQUE-TENSION RELATIONSHIPFig. 14 Elongation (in.)Bolt tension (lb.) torque -inducedtensionStraight tensionafter torquingto preloadStraight tensionFig. 13 torque / tension Relationshipmild steel Rb 87brass Rb 72aluminum Rb 72cast iron Rb 83 note 1note 2(2024-T4) note 3 UNCUNFUNCUNFUNCUNF screwsizeplainplainplainplainplainplain# 0 * * * #1* * * * * * #2* * * * * * #3* * * * * * #4* * * * * * #5*20*21*20*21*20*21#6*25*28*25*28*25*28 #8*46*48*46*48*46*48#10*67*76*67*76 *67*761/4*158*1801361361131135/16*326*36 02282281901903/8*5806354764763973977/16* 930*1,0406806805705701/2*1,420*1,5901,23 01,2301,0301,0309/16*2,0402,2501,6901,69 01,4101,4105/8*2,8203,1202,3402,3401,950 1,9503/4*5,0005,3404,0004,0003,3403,3407 /8*8,0608,3706,2806,2805,2305,2301*12,10 012,8009,6009,6008,0008,0001 1/8*13,800*15,40013,70013,70011,40011,40 01 1/4*19,200*21,60018,90018,90015,80015,80 01 3/8*25,200*28,80024,20024,20020,10020,10 01 1/2*33,600*36,10032,90032,90027,40027,40 0 NOTES:1.

7 TORQUES based on 80,000 psi bearing stress under head of TORQUES based on 60,000 psi bearing stress under head of TORQUES based on 50,000 psi bearing stress under head of screw.*Denotes TORQUES based on 100,000 psi tensile stress in screwthreads up to 1" dia., and 80,000 psi for sizes 1 1/8" dia. and convert inch-pounds to inch-ounces multiply by convert inch-pounds to foot-pounds divide by 15 Recommended Seating TORQUES (Inch-Lb.) for Application in Various MaterialsUNBRAKO pHd (1960 Series) Socket Head Cap ScrewsTORQUE VS. INDUCED LOADUNBRAKO SOCKET HEAD CAP SCREWTYPICAL