US20040177509A1 - Process for setting bearings and verifying force preload - Google Patents
Process for setting bearings and verifying force preload Download PDFInfo
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- US20040177509A1 US20040177509A1 US10/389,305 US38930503A US2004177509A1 US 20040177509 A1 US20040177509 A1 US 20040177509A1 US 38930503 A US38930503 A US 38930503A US 2004177509 A1 US2004177509 A1 US 2004177509A1
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- bearings
- bearing
- gauge
- tapered
- preload
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- 230000036316 preload Effects 0.000 title claims abstract description 65
- 238000000034 method Methods 0.000 title claims description 24
- 125000006850 spacer group Chemical group 0.000 claims abstract description 23
- 238000005096 rolling process Methods 0.000 claims abstract description 7
- 230000000694 effects Effects 0.000 claims description 4
- 230000000712 assembly Effects 0.000 description 4
- 238000000429 assembly Methods 0.000 description 4
- 238000005259 measurement Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/50—Positive connections
- F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2229/00—Setting preload
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
- F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
- F16H57/022—Adjustment of gear shafts or bearings
- F16H2057/0221—Axial adjustment
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49636—Process for making bearing or component thereof
- Y10T29/49643—Rotary bearing
- Y10T29/49679—Anti-friction bearing or component thereof
- Y10T29/49682—Assembling of race and rolling anti-friction members
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49636—Process for making bearing or component thereof
- Y10T29/49696—Mounting
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49636—Process for making bearing or component thereof
- Y10T29/497—Pre-usage process, e.g., preloading, aligning
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49764—Method of mechanical manufacture with testing or indicating
- Y10T29/49766—Method of mechanical manufacture with testing or indicating torquing threaded assemblage or determining torque herein
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49764—Method of mechanical manufacture with testing or indicating
- Y10T29/49771—Quantitative measuring or gauging
- Y10T29/49776—Pressure, force, or weight determining
Definitions
- This invention relates in general to opposed antifriction bearings and more particularly to a process for setting such bearings in preload and for verifying the force preload.
- the bearings that support the rotating components should operate in a condition of preload, which is characterized by an absence of clearances, both axial and radial, in the bearings.
- preload like end play where clearance exist, is considered in the context of an axial dimension (e.g. 0.002 in. preload), but the real and more meaningful measure of preload is in the context of the internal forces captured by the opposed bearings.
- several pairs of bearings identical in size and configuration, all set to the same dimensional preload could well lock in different internal forces, that is to say, different force preloads.
- Pinion assemblies for automotive differentials illustrate the problems and uncertainties one encounters in connection with setting the bearings.
- the typical pinion assembly has a carrier, a pinion shaft provided with a pinion at its one end, and a pair of tapered roller bearings which support the shaft in the carrier.
- the carrier is attached to the main housing of a differential, the pinion meshes with a ring gear, and to insure that the mesh is proper, the bearings must be set to preload.
- the procedure for adjusting the bearings in a pinion assembly involves fitting the shaft to the carrier with one of the tapered rollers of the bearing seated along the raceways for that bearing. Thereupon, measurements are taken from the other bearing to determine the size of a spacer, which, when installed, will impart the proper preload to the two bearings. The assembly procedure is then completed using the spacer. Thereafter, the torque required to rotate the shaft is measured to see if it falls within acceptable limits. But torque does not provide a very good measure of preload, because in identical pinion assemblies set to the same force preload, torque can vary as much as ⁇ 20%. In view of this variance, some pinion assemblies which exhibit torque outside the accepted range may actually have an acceptable force preload.
- the present invention resides in a process for setting opposed antifriction bearings with a desired dimensional preload and verifying that the force preload is acceptable.
- machine components are assembled with one of the bearings in place between them.
- the other bearing has a gauge interposed in it and the gauge provides measurement for determining the size of a spacer which will give the bearings a desired dimensional preload.
- the gauge also exerts a known axial force of the bearings, and while that force is exerted the torque required by the bearings is measured. This provides a torque signature.
- the other bearing is assembled without the gauge and with the spacer installed to provide the desired dimensional preload, the torque is again measured, and from this new torque and the torque signature, one can determine the load, that is the force preload, in the bearings.
- FIG. 1 is a sectional view of a pinion assembly, the bearings of which have been set and verified in accordance with the present invention
- FIG. 2 is an exploded sectional view of the pinion assembly with the gauge interposed between components of one of the bearings of the assembly;
- FIG. 3 is a perspective view, partially broken away and in section, of the pinion assembly, with the gauge fitted to one of its bearings;
- FIG. 4 is an enlarged sectional view of the gauge and the bearing to which it is fitted.
- the pinion assembly A includes (FIG. 1) a carrier 2 , a pinion shaft 4 that extends through the carrier 2 , head and tail bearings 6 and 8 , respectively, which support the pinion shaft 4 in the carrier 2 , a yoke 10 fitted to the tail end of the pinion shaft 4 , and a nut 12 threaded over the end of the pinion shaft 4 to retain the yoke 10 firmly on the shaft 4 .
- the bearings 6 and 8 enable the shaft 4 to rotate about an axis X and are set to a condition of preload, so that the axis X remains perfectly stable with respect to the carrier 2 .
- the bearings 6 and 8 are mounted in opposition in the indirect configuration, with the preload setting being controlled by a sleeve 14 and a spacer 16 that are located around the shaft 4 , with the spacer 16 being against a reference surface 18 on the end of the sleeve 14 .
- the carrier 2 is actually a subhousing which is bolted to the main housing of the differential. It has two bearing seats 20 and 22 , the former for the head bearing 6 and the latter for the tail bearing 8 .
- the shaft 4 extends through the carrier 2 where the bearing seats 20 and 22 of the carrier 2 surround it.
- the shaft 4 projects out of the head end of the carrier 2 , and here it is provided with a pinion 30 .
- the back of the pinion 30 forms a shoulder 32 at the head end of the shaft 4 , with the shoulder 32 being squared off with respect to the axis X.
- the shaft 4 also projects out of the tail end of the carrier 2 , and here it is provided with a spline 34 and beyond the spline 34 with a reduced end 36 which is threaded.
- Each bearing 6 and 8 includes (FIGS. 1 & 2) an inner race in the form of a cone 40 , and outer race in the form of a cup 42 , rolling elements in the form of tapered rollers 44 , and a cage 46 .
- the rollers 44 lie in a single row between the cone 40 and the cup 44 , while the cage 46 maintains the correct spacing between the rollers 44 and further holds the rollers 44 around the cone 40 when the cone 40 is removed from the cup 42 , so that the cone 40 , rollers 44 , and cage 46 form a cone assembly.
- the cone 40 has a tapered raceway 50 , which is presented outwardly away from the axis X, and a thrust rib 52 at the large end of the raceway 50 .
- the cone 40 On the end of the thrust rib 52 the cone 40 has a back face 54 , and at its opposite end, beyond the small end of the raceway 50 , the cone 40 has a front face 56 . Both the back face 54 and front face 56 are squared off with respect to the axis X.
- the cup 42 has a tapered raceway 58 , which is presented inwardly toward the axis X, and a back face 60 at the small end of the raceway 58 .
- the back face 60 is also squared off with respect to the axis X.
- the tapered rollers 44 fit between the cone 40 and cup 42 with their tapered side faces against the raceways 50 and 58 and their large end faces against the thrust rib 52 . Indeed, the thrust rib 52 prevents the rollers 44 from moving up the raceways 50 and 58 and out of the space between the cone 40 and cup 42 .
- the rollers 44 are on apex, meaning that the conical envelopes formed by their tapered side faces have their apices at a common point along the axes X.
- the conical envelopes formed by the raceways 50 and 58 have their apices at the same point.
- the cones 40 of the two bearings 6 and 8 fit over the pinion shaft 4 , each with an interference fit.
- the back face 54 for the cone 40 of the head bearing 6 bears against the shoulder 32 on the pinion 30
- the back face 54 for the cone 40 of the tail bearing 8 bears against the yoke 10 which is held firmly against it by the nut 12 .
- the sleeve 14 and spacer 16 also fit around the shaft 4 when they lie between the two cones 40 . Indeed, the sleeve 14 and spacer 16 are clamped snugly between the front faces 56 on the two cones 40 .
- the cup 42 for the head bearing 6 fits into the bearing seat 20 in the carrier 2
- the cup 42 for the tail bearing 8 fits into the other bearing seat 22 , there being interference fits between the cups 42 and their respective bearing seats 20 and 22 .
- the back faces 60 of the two cups 42 bear firmly against the ends of their respective bearing seats 20 and 22 .
- the rollers 44 for the two bearings 6 and 8 lie between the raceways 50 and 58 on the cones 40 and cups 42 of those bearings 6 and 8 .
- their tapered side faces contact the raceways 50 and 58
- their large end faces bear against the thrust ribs 52 . Since the bearings 6 and 8 are in preload, no clearances exists between any of the rollers 44 and the raceways 50 and 58 between which they are located.
- the thickness of the spacer 16 controls the magnitude of the preload in the bearings 6 and 8 , and to determine the thickness required to provide the proper preload, one must know the distance that the front face 56 for the cone 40 of the tail bearing 6 will locate from the reference surface 18 at the end of the sleeve 14 when the bearings 6 and 8 are in a condition of zero end play, that is to say, when there is neither end play nor preload in the bearings 6 and 8 . This distance cannot be measured when the cone 40 of the tail bearing 8 is around the shaft 4 in its operating position, since its front face 56 is too obscured for such a measurement. Instead a gauge B (FIGS. 2-4), which in effect projects the raceway 58 of the cup 42 for the tail bearing 8 and the reference surface 18 of the sleeve 14 out of the carrier 2 , is utilized.
- the gauge B is employed with the pinion assembly A partially assembled, that is to say, assembled to the extent that the pinion shaft 4 extends through the carrier 2 with is head bearing 6 in place and the rollers 44 of that bearing seated against the raceways 50 and 58 of it cone 40 and cup 42 (FIG. 3).
- the partial assembly further includes installation of the cup 42 for the tail bearing 8 in its seat 22 in the carrier 2 and placement of the sleeve 14 over the pinion shaft 4 and against the front face 56 for the cone 40 of the head bearing 6 .
- the gauge B basically includes (FIG. 4) a male element 66 and a female element 68 which are located essentially end to end and in addition an intervening element 70 which extends between the male and female elements 66 and 68 .
- the gauge B also has a spring 72 which urges the male and female elements 66 and 68 apart.
- Both the male element 66 and the female element 68 fit over the intervening element 70 where they are capable of shifting axially with respect to it and to each other.
- the male element 66 has a tapered surface 76 which is presented outwardly away from the axes X.
- the taper of the surface 76 conforms to the taper of the raceway 58 on the cup 42 of the tail bearing 8 and is further of a diameter small enough to enable the male element 66 to fit into the cup 42 of the bearing 8 .
- the tapered surface 76 seats perfectly against the raceway 58 , which provides one of two conical envelopes employed by the gauge B.
- the female member 68 lies axially beyond the male member 66 .
- the intervening element 70 fits within the male and female elements 66 and 68 such that the two elements 66 and 68 can slide over it.
- the male and female elements 66 and 68 may each assume infinite positions with respect to the intervening element 70 and with respect to each other as well.
- the intervening element 70 has an inner end 80 which is configured to seat against the reference surface 18 on the sleeve 14 and an outer end 82 which is configured to fit against the front face 56 of the cone 40 for the tail bearing 8 .
- the two ends 80 and 82 lie a fixed and known distance a apart.
- the spring 72 fits around the intervening element 70 and between the male and female elements 66 and 68 and urges them apart. It may take the form of a Belleville spring or even a coil spring. Irrespective of its configuration, it carries a strain sensor 84 which senses the strain in the spring 72 and produces a signal that reflects that strain. The signal is monitored by instruments which basically convert the strain into the distance between the male and female elements 66 and 68 , and further into the force exerted by the spring 72 on the two elements 66 and 68 .
- the male element 66 and the female element 68 possess equivalent diameters d along their respective tapered surfaces 76 and 78 (FIGS. 2 & 4).
- the equivalent diameters d are separated by an axial distance b and that distance varies, although slightly, between different pairs of bearings 6 and 8 .
- the gauge B installed over the tail end of the partially assembled pinion assembly A (FIGS. 3 & 4).
- the gauge B is lowered over the pinion shaft 4 at the tail end of the assembly A far enough to enable the tapered surface 76 on its male element 66 to seat against the tapered raceway 58 for the tail cup 42 and also far enough to enable the inner end 80 of the intervening element 70 to seat against the reference surface 18 on the sleeve 14 .
- the male element 66 and intervening element 70 thus assume fixed positions with respect to the head bearing 6 .
- the cone assembly for the tail bearing 8 that is its cone 40 together with its tapered rollers 44 and cage 46 , is inserted into the female element 68 .
- the rollers 44 seat against the raceway 50 of the cone 40 and also against the tapered surface 78 of the female element 68 .
- the front face 56 of the cone 40 is presented opposite the outer end 82 of the intervening element 70 , it remains separated from the outer end 82 at this juncture.
- the cone 40 of the tail bearing 6 thus becomes a positional race, the axial position of which along the shaft 4 determines the setting for the bearings 6 and 8 .
- the assembly nut 92 is tightened far enough to clamp the cone 40 of the head bearing 6 , the sleeve 14 , the intervening element 70 of the gauge B, and the cone 40 of the tail bearing 8 all tightly together between the pinion 30 and the assembly yoke 90 .
- the spring 72 compresses, and the sensor 84 applied to it produces a signal reflecting the distance the female element 68 moves toward the male element 66 . This determines the distance b between the like diameters d on the male and female elements 66 and 68 .
- the pinion shaft 4 should rotate relative to the carrier 2 . This insures that the rollers 44 of the head bearing 6 seat properly against the raceways 56 and 58 and thrust rib 52 of that bearing, and that the rollers 44 of the tail bearing 8 seat properly against the raceway 50 and the thrust rib 52 of the tail cone 40 and also against the tapered surface 78 of the female element 68 on the gauge B. The rotation is imparted to the pinion shaft 4 at the assembly yoke 90 which is temporarily on it.
- the instrument that is attached to the sensor 84 register the distance b between the diameters d on the tapered surfaces 76 and 78 of the male and female elements 66 and 68 , respectively, but it also determines the force exerted by the spring 72 .
- the torque required to maintain the rotation is also measured.
- the force represents a temporary or assembly load in the bearings 6 and 8 with the gauge B interposed between the cup 42 and the cone assembly of the tail bearing 8 .
- the formula takes into account the change i in the axial dimension owning to the interference fit of the cone 40 for the tail bearing 8 .
- the preload imparted by the gauge B produces a torque signature s for the two bearings 6 and 8 . That signature then becomes the basis for ascertaining the force preload in the fully assembled pinion assembly A and verifying that it falls within acceptable limits.
- the torque signature s remains the same for the bearings 6 and 8 irrespective of preload.
- the torque t varies with preload.
- the procedure for setting bearings and verifying force preload may be used for bearings mounted in the direct configuration as well, that is to say, with bearings having the large ends of the rollers in the two rows presented toward each other.
- the procedure irrespective of the location of the tapered surfaces 76 and 78 and the ends 80 and 82 , uses the difference between a measured distance and a fixed distance to determine the size of a spacer which will provide opposed bearings with the proper setting.
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Abstract
Description
- Not Applicable
- This invention relates in general to opposed antifriction bearings and more particularly to a process for setting such bearings in preload and for verifying the force preload.
- One can find rotating shafts in a wide variety of machinery, and when such shafts carry heavy loads or must rotate with a good measure of precision, they are often supported on antifriction bearings. Usually the antifriction bearings arranged in a pair, with the bearings of the pair being adjusted against each other to a desired setting. Typical of the bearings are single row tapered roller bearings. When positioned with the large ends of the tapered rollers in the two bearings presented away from each other (indirect mounting) or the large ends of the rollers presented toward each other (direct mounting), displacement of one race of one of the bearing axially will change the setting for the two bearings.
- Where the axis of rotation must remain perfectly stable, such as in the pinion assemblies for automotive differentials or in machine tool spindles, the bearings that support the rotating components should operate in a condition of preload, which is characterized by an absence of clearances, both axial and radial, in the bearings. Typically, preload, like end play where clearance exist, is considered in the context of an axial dimension (e.g. 0.002 in. preload), but the real and more meaningful measure of preload is in the context of the internal forces captured by the opposed bearings. In this regard, several pairs of bearings identical in size and configuration, all set to the same dimensional preload could well lock in different internal forces, that is to say, different force preloads. Pinion assemblies for automotive differentials illustrate the problems and uncertainties one encounters in connection with setting the bearings. The typical pinion assembly has a carrier, a pinion shaft provided with a pinion at its one end, and a pair of tapered roller bearings which support the shaft in the carrier. When the carrier is attached to the main housing of a differential, the pinion meshes with a ring gear, and to insure that the mesh is proper, the bearings must be set to preload.
- Typically, the procedure for adjusting the bearings in a pinion assembly involves fitting the shaft to the carrier with one of the tapered rollers of the bearing seated along the raceways for that bearing. Thereupon, measurements are taken from the other bearing to determine the size of a spacer, which, when installed, will impart the proper preload to the two bearings. The assembly procedure is then completed using the spacer. Thereafter, the torque required to rotate the shaft is measured to see if it falls within acceptable limits. But torque does not provide a very good measure of preload, because in identical pinion assemblies set to the same force preload, torque can vary as much as ±20%. In view of this variance, some pinion assemblies which exhibit torque outside the accepted range may actually have an acceptable force preload. This can lead to expensive disassembly and reassembly. Then again, some that exhibit a torque within the acceptable range may actually have an unacceptable force preload. And too much force preload can lead to early failure of the bearings. On the other hand, too little force preload may permit excursions into end play owing to differential thermal expansions between the carrier and shaft during operation. End play detracts for the stability of the pinion shaft and may allow the pinion to assume positions which lead to wear and create annoying noise.
- The present invention resides in a process for setting opposed antifriction bearings with a desired dimensional preload and verifying that the force preload is acceptable. To this end, machine components are assembled with one of the bearings in place between them. The other bearing has a gauge interposed in it and the gauge provides measurement for determining the size of a spacer which will give the bearings a desired dimensional preload. The gauge also exerts a known axial force of the bearings, and while that force is exerted the torque required by the bearings is measured. This provides a torque signature. When the other bearing is assembled without the gauge and with the spacer installed to provide the desired dimensional preload, the torque is again measured, and from this new torque and the torque signature, one can determine the load, that is the force preload, in the bearings.
- FIG. 1 is a sectional view of a pinion assembly, the bearings of which have been set and verified in accordance with the present invention;
- FIG. 2 is an exploded sectional view of the pinion assembly with the gauge interposed between components of one of the bearings of the assembly;
- FIG. 3 is a perspective view, partially broken away and in section, of the pinion assembly, with the gauge fitted to one of its bearings; and
- FIG. 4 is an enlarged sectional view of the gauge and the bearing to which it is fitted.
- The process for setting bearings in preload and verifying that preload in terms of force finds utility in connection with a wide variety of machinery employing shafts mounted on opposed tapered roller bearings. Actually, its utility extends to opposed bearings that enable a machine component to rotate relative to another machine component with a good measure of stability, and this requires that the bearings be in preload. Typical of such an arrangement is a pinion assembly A which is bolted to the housing of an automotive differential to engage and rotate the ring gear in the differential.
- The pinion assembly A includes (FIG. 1) a
carrier 2, apinion shaft 4 that extends through thecarrier 2, head andtail bearings pinion shaft 4 in thecarrier 2, ayoke 10 fitted to the tail end of thepinion shaft 4, and anut 12 threaded over the end of thepinion shaft 4 to retain theyoke 10 firmly on theshaft 4. Thebearings shaft 4 to rotate about an axis X and are set to a condition of preload, so that the axis X remains perfectly stable with respect to thecarrier 2. To this end, thebearings sleeve 14 and aspacer 16 that are located around theshaft 4, with thespacer 16 being against areference surface 18 on the end of thesleeve 14. - The
carrier 2 is actually a subhousing which is bolted to the main housing of the differential. It has two bearingseats - The
shaft 4 extends through thecarrier 2 where thebearing seats carrier 2 surround it. Theshaft 4 projects out of the head end of thecarrier 2, and here it is provided with apinion 30. The back of thepinion 30 forms ashoulder 32 at the head end of theshaft 4, with theshoulder 32 being squared off with respect to the axis X. Theshaft 4 also projects out of the tail end of thecarrier 2, and here it is provided with aspline 34 and beyond thespline 34 with a reducedend 36 which is threaded. - Each bearing6 and 8 includes (FIGS. 1 & 2) an inner race in the form of a
cone 40, and outer race in the form of acup 42, rolling elements in the form oftapered rollers 44, and acage 46. Therollers 44 lie in a single row between thecone 40 and thecup 44, while thecage 46 maintains the correct spacing between therollers 44 and further holds therollers 44 around thecone 40 when thecone 40 is removed from thecup 42, so that thecone 40,rollers 44, andcage 46 form a cone assembly. - The
cone 40 has atapered raceway 50, which is presented outwardly away from the axis X, and athrust rib 52 at the large end of theraceway 50. On the end of thethrust rib 52 thecone 40 has aback face 54, and at its opposite end, beyond the small end of theraceway 50, thecone 40 has afront face 56. Both theback face 54 andfront face 56 are squared off with respect to the axis X. - The
cup 42 has atapered raceway 58, which is presented inwardly toward the axis X, and aback face 60 at the small end of theraceway 58. Theback face 60 is also squared off with respect to the axis X. - The
tapered rollers 44 fit between thecone 40 andcup 42 with their tapered side faces against theraceways thrust rib 52. Indeed, thethrust rib 52 prevents therollers 44 from moving up theraceways cone 40 andcup 42. Therollers 44 are on apex, meaning that the conical envelopes formed by their tapered side faces have their apices at a common point along the axes X. The conical envelopes formed by theraceways - The
cones 40 of the twobearings pinion shaft 4, each with an interference fit. Theback face 54 for thecone 40 of the head bearing 6 bears against theshoulder 32 on thepinion 30, whereas theback face 54 for thecone 40 of the tail bearing 8 bears against theyoke 10 which is held firmly against it by thenut 12. Thesleeve 14 andspacer 16 also fit around theshaft 4 when they lie between the twocones 40. Indeed, thesleeve 14 andspacer 16 are clamped snugly between the front faces 56 on the twocones 40. Thecup 42 for the head bearing 6 fits into the bearingseat 20 in thecarrier 2, whereas thecup 42 for thetail bearing 8 fits into the other bearingseat 22, there being interference fits between thecups 42 and theirrespective bearing seats cups 42 bear firmly against the ends of theirrespective bearing seats rollers 44 for the twobearings raceways cones 40 and cups 42 of thosebearings raceways thrust ribs 52. Since thebearings rollers 44 and theraceways - The thickness of the
spacer 16 controls the magnitude of the preload in thebearings front face 56 for thecone 40 of thetail bearing 6 will locate from thereference surface 18 at the end of thesleeve 14 when thebearings bearings cone 40 of thetail bearing 8 is around theshaft 4 in its operating position, since itsfront face 56 is too obscured for such a measurement. Instead a gauge B (FIGS. 2-4), which in effect projects theraceway 58 of thecup 42 for thetail bearing 8 and thereference surface 18 of thesleeve 14 out of thecarrier 2, is utilized. - The gauge B is employed with the pinion assembly A partially assembled, that is to say, assembled to the extent that the
pinion shaft 4 extends through thecarrier 2 with ishead bearing 6 in place and therollers 44 of that bearing seated against theraceways cone 40 and cup 42 (FIG. 3). The partial assembly further includes installation of thecup 42 for thetail bearing 8 in itsseat 22 in thecarrier 2 and placement of thesleeve 14 over thepinion shaft 4 and against thefront face 56 for thecone 40 of thehead bearing 6. - The gauge B basically includes (FIG. 4) a
male element 66 and afemale element 68 which are located essentially end to end and in addition an interveningelement 70 which extends between the male andfemale elements spring 72 which urges the male andfemale elements - Both the
male element 66 and thefemale element 68 fit over the interveningelement 70 where they are capable of shifting axially with respect to it and to each other. Themale element 66 has a taperedsurface 76 which is presented outwardly away from the axes X. The taper of thesurface 76 conforms to the taper of theraceway 58 on thecup 42 of thetail bearing 8 and is further of a diameter small enough to enable themale element 66 to fit into thecup 42 of thebearing 8. When so fitted, the taperedsurface 76 seats perfectly against theraceway 58, which provides one of two conical envelopes employed by the gauge B. Essentially thefemale member 68 lies axially beyond themale member 66. It has a taperedsurface 78 which is presented inwardly toward the axis X. Its taper and size conform to the other conical envelope employed by the gauge B, that is the envelope formed by the outwardly presented faces of therollers 44 for thetail bearing 8. After all, when thetail bearing 8 is assembled in its operating condition, the taperedrollers 44 that surround itscone 40 seat against the taperedrace raceway 58 of itscup 42—or in other words the two conical envelopes are then coincident. The interveningelement 70 fits within the male andfemale elements elements female elements element 70 and with respect to each other as well. The interveningelement 70 has aninner end 80 which is configured to seat against thereference surface 18 on thesleeve 14 and anouter end 82 which is configured to fit against thefront face 56 of thecone 40 for thetail bearing 8. The two ends 80 and 82 lie a fixed and known distance a apart. - The
spring 72 fits around the interveningelement 70 and between the male andfemale elements strain sensor 84 which senses the strain in thespring 72 and produces a signal that reflects that strain. The signal is monitored by instruments which basically convert the strain into the distance between the male andfemale elements spring 72 on the twoelements - The
male element 66 and thefemale element 68 possess equivalent diameters d along their respective taperedsurfaces 76 and 78 (FIGS. 2 & 4). The equivalent diameters d are separated by an axial distance b and that distance varies, although slightly, between different pairs ofbearings - In order to ascertain the axial dimension c (FIG. 1) for the
spacer 16 required to provide thebearings pinion shaft 4 at the tail end of the assembly A far enough to enable the taperedsurface 76 on itsmale element 66 to seat against the taperedraceway 58 for thetail cup 42 and also far enough to enable theinner end 80 of the interveningelement 70 to seat against thereference surface 18 on thesleeve 14. Themale element 66 and interveningelement 70 thus assume fixed positions with respect to thehead bearing 6. Thereupon, the cone assembly for thetail bearing 8, that is itscone 40 together with itstapered rollers 44 andcage 46, is inserted into thefemale element 68. Therollers 44 seat against theraceway 50 of thecone 40 and also against the taperedsurface 78 of thefemale element 68. While thefront face 56 of thecone 40 is presented opposite theouter end 82 of the interveningelement 70, it remains separated from theouter end 82 at this juncture. Thecone 40 of thetail bearing 6 thus becomes a positional race, the axial position of which along theshaft 4 determines the setting for thebearings - The reduced
end 36 of thepinion shaft 4 projects out of the gauge B, and anassembly yoke 90 is fitted over it, so that theyoke 90 bears against theback face 54 of thetail cone 40. Finally, the threads on thereduced end 36 of theshaft 4 are engaged with anassembly nut 92 which is turned down against theyoke 90. Indeed, thenut 92 forces thefemale element 68 downwardly against the bias of thespring 72 until thefront face 56 of the cone 40 (FIG. 3) comes against theouter end 82 of the interveningelement 70 of the gauge B. In other words, theassembly nut 92 is tightened far enough to clamp thecone 40 of thehead bearing 6, thesleeve 14, the interveningelement 70 of the gauge B, and thecone 40 of thetail bearing 8 all tightly together between thepinion 30 and theassembly yoke 90. Thespring 72 compresses, and thesensor 84 applied to it produces a signal reflecting the distance thefemale element 68 moves toward themale element 66. This determines the distance b between the like diameters d on the male andfemale elements - When the instrument registers the measured distance b, the
pinion shaft 4 should rotate relative to thecarrier 2. This insures that therollers 44 of the head bearing 6 seat properly against theraceways rib 52 of that bearing, and that therollers 44 of thetail bearing 8 seat properly against theraceway 50 and thethrust rib 52 of thetail cone 40 and also against the taperedsurface 78 of thefemale element 68 on the gauge B. The rotation is imparted to thepinion shaft 4 at theassembly yoke 90 which is temporarily on it. Not only does the instrument that is attached to thesensor 84 register the distance b between the diameters d on the tapered surfaces 76 and 78 of the male andfemale elements spring 72. The torque required to maintain the rotation is also measured. The force represents a temporary or assembly load in thebearings cup 42 and the cone assembly of thetail bearing 8. - From the distance b measured by the gauge B and the fixed distance a that the intervening
element 70 spaces thetail cone 40 from thereference surface 18 on thesleeve 14, one can calculate the axial dimension c for thespacer 16 which will provide the desired dimensional preload p to the twobearings - c=a−b+p−i
- The formula takes into account the change i in the axial dimension owning to the interference fit of the
cone 40 for thetail bearing 8. - From the force f registered by the instrument to which the
sensor 84 is connected and the torque t applied to theassembly yoke 90, one can obtain a torque signature s for the twobearings - s=t/f
- Once the torque signature s is known, one can calculate the force preload in the bearing simply by measuring the torque required to rotate its
pinion shaft 4, that is to say: - f=t/s
- And indeed, once the pinion assembly A is fully assembled (FIG. 1) with the
rollers 44 of itstail bearing 8 seated against not only theraceway 50 of itscone 40, but also against theraceway 58 of itscup 42, and further withspacer 16 and the the operatingyoke 10 andnut 12 in place, the force preload in thebearings spring 72 of the gauge B applies some preload to thebearings tail bearing 8 is concerned being transferred between thecone 40 andcup 42 through the gauge B androllers 44 instead of directly through therollers 44. The preload imparted by the gauge B produces a torque signature s for the twobearings bearings - f=t/s
- The procedure for setting bearings and verifying force preload may be used for bearings mounted in the direct configuration as well, that is to say, with bearings having the large ends of the rollers in the two rows presented toward each other. Moreover, for some measurements it may be desirable to have the tapered surfaces76 and 78 on a single gauge element where they are a fixed distance apart and the
ends spring 72 between those elements, so that the distance between theends ends
Claims (13)
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US10/389,305 US6796031B1 (en) | 2003-03-14 | 2003-03-14 | Process for setting bearings and verifying force preload |
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US10/389,305 US6796031B1 (en) | 2003-03-14 | 2003-03-14 | Process for setting bearings and verifying force preload |
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US20040177509A1 true US20040177509A1 (en) | 2004-09-16 |
US6796031B1 US6796031B1 (en) | 2004-09-28 |
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US10/389,305 Expired - Fee Related US6796031B1 (en) | 2003-03-14 | 2003-03-14 | Process for setting bearings and verifying force preload |
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DE102008004604A1 (en) * | 2008-01-16 | 2009-07-23 | Daimler Ag | Method for determining thickness of axial spacer of bevel pinion, involves mounting bevel pinion in axle housing of rear axle drive, where bevel pinion is mounted by mount |
DE102010029208A1 (en) * | 2010-05-21 | 2011-11-24 | Bayerische Motoren Werke Aktiengesellschaft | Method for determining spring pre-stress at spring-bearing-arrangement for balancing thermal conditioned position changes in motor car-axle drive, involves measuring spring force after arrangement is rotatable in housing |
US20160245385A1 (en) * | 2015-02-24 | 2016-08-25 | American Axle & Manufacturing, Inc. | Power transmitting component with pinion flange fixed to pinion |
US20170146069A1 (en) * | 2015-05-22 | 2017-05-25 | The Timken Company | Bearing package and installation tool |
US20170175872A1 (en) * | 2015-12-22 | 2017-06-22 | Ge Avio Srl | Assembling process for mounting a rolling bearing on a gear shaft, and gear assembly obtainable by such a process |
WO2020108791A1 (en) * | 2018-11-28 | 2020-06-04 | Sew-Eurodrive Gmbh & Co. Kg | System and method for adjusting a preload force value in a system comprising a shaft, a housing part, two bearings and a fixing element |
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US6993852B2 (en) * | 2001-02-06 | 2006-02-07 | The Timken Company | Gauge and process for adjusting bearings |
US7090609B2 (en) * | 2003-08-08 | 2006-08-15 | Dana Corporation | Pinion support for a differential assembly |
US7155827B2 (en) * | 2003-10-30 | 2007-01-02 | Torque-Traction Technologies, Llc. | Method for verifying predetermined bearing preload of differential assembly module |
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DE102008004604A1 (en) * | 2008-01-16 | 2009-07-23 | Daimler Ag | Method for determining thickness of axial spacer of bevel pinion, involves mounting bevel pinion in axle housing of rear axle drive, where bevel pinion is mounted by mount |
DE102010029208A1 (en) * | 2010-05-21 | 2011-11-24 | Bayerische Motoren Werke Aktiengesellschaft | Method for determining spring pre-stress at spring-bearing-arrangement for balancing thermal conditioned position changes in motor car-axle drive, involves measuring spring force after arrangement is rotatable in housing |
DE102010029208B4 (en) | 2010-05-21 | 2019-03-28 | Bayerische Motoren Werke Aktiengesellschaft | Method and device for determining the spring preload |
US20160245385A1 (en) * | 2015-02-24 | 2016-08-25 | American Axle & Manufacturing, Inc. | Power transmitting component with pinion flange fixed to pinion |
US9695923B2 (en) * | 2015-02-24 | 2017-07-04 | American Axle & Manufacturing, Inc. | Power transmitting component with pinion flange fixed to pinion |
US20170146069A1 (en) * | 2015-05-22 | 2017-05-25 | The Timken Company | Bearing package and installation tool |
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US20170175872A1 (en) * | 2015-12-22 | 2017-06-22 | Ge Avio Srl | Assembling process for mounting a rolling bearing on a gear shaft, and gear assembly obtainable by such a process |
WO2020108791A1 (en) * | 2018-11-28 | 2020-06-04 | Sew-Eurodrive Gmbh & Co. Kg | System and method for adjusting a preload force value in a system comprising a shaft, a housing part, two bearings and a fixing element |
WO2020179670A1 (en) * | 2019-03-04 | 2020-09-10 | Ntn株式会社 | Preload inspection method and assembly method for wheel bearing device |
JP2020143919A (en) * | 2019-03-04 | 2020-09-10 | Ntn株式会社 | Preload inspection method and assembly method for wheel bearing device |
CN113366292A (en) * | 2019-03-04 | 2021-09-07 | Ntn株式会社 | Method for inspecting preload of wheel bearing device and method for assembling wheel bearing device |
US11959519B2 (en) | 2019-03-04 | 2024-04-16 | Ntn Corporation | Preload inspection method and assembly method for bearing device for vehicle wheel |
JP2021051054A (en) * | 2019-09-26 | 2021-04-01 | Ntn株式会社 | Preload inspection method for wheel bearing device |
WO2021059865A1 (en) * | 2019-09-26 | 2021-04-01 | Ntn株式会社 | Preload inspection method for wheel bearing device |
JP7049297B2 (en) | 2019-09-26 | 2022-04-06 | Ntn株式会社 | Preload inspection method for wheel bearing devices |
US11874195B2 (en) | 2019-09-26 | 2024-01-16 | Ntn Corporation | Preload inspection method for bearing device for vehicle wheel |
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