Tapered roller bearing

A raceway surface (3a) of an outer ring (3) of a tapered roller bearing (1) includes a composite crowning surface. The composite crowning surface includes a center curve (3a1), which is formed at a center portion in a generating-line direction, and end portion curves (3a2 and 3a3), which are formed on both sides of the center curve (3a1) in the generating-line direction. The raceway surface (3a) of the outer ring (3) is entirely subjected to superfinishing. Each of a ratio (R2/R1) of a curvature radius (R2) of the end portion curve (3a2) to a curvature radius (R1) of the center curve (3a1) and a ratio (R3/R1) of a curvature radius (R3) of the end portion curve (3a3) to the curvature radius (R1) is set to 0.02 or more. Each of drop amounts of the end portion curves (3a2 and 3a3) is set to 0.07 mm or less.

The present application is a U.S. National Stage Application of International (PCT) Application No. PCT/JP2016/050147, filed on Jan. 5, 2016, which claims priority to Japanese Patent Application No. 2015-014201, filed on Jan. 28, 2015, and Japanese Patent Application No. 2015-219472, filed on Nov. 9, 2015.

TECHNICAL FIELD

The present invention relates to a tapered roller bearing.

BACKGROUND ART

Reduction in size of a transmission unit or a differential unit (hereinafter referred to as “transmission unit or the like”) of an automobile has been demanded for the purpose of reducing fuel consumption and increasing a cabin space. Along with such demands, reduction in torque and reduction in size have been demanded also for a tapered roller bearing which is to be assembled in the transmission unit or the like. In order to achieve the reduction in torque and reduction in size of the tapered roller bearing, increase in load capacity has been demanded. For example, in Patent Literature 1, there is described a tapered roller bearing having a roller coefficient (roller filling ratio) which is set to more than 0.94 to improve the load capacity.

In recent years, there has been an increasing demand for reduction in size of the transmission unit or the like, and further increase in load capacity has been demanded also for a bearing which is to be assembled in the transmission unit or the like. Further, for the purpose of reducing the size of the transmission unit or the like, employment of an aluminum housing and reduction in thickness of a housing have been considered. In this case, the stiffness of the entire unit is reduced, and a large moment load is applied to the tapered roller bearing. Consequently, a load condition of the tapered roller bearing becomes stricter. Further, when the aluminum housing is employed, the amount of thermal expansion of the housing is increased, with the result that reduction in preload (which is so-called “preload loss”) becomes more liable to occur in the tapered roller bearing. Therefore, more highly functional tapered roller bearing is demanded.

As described above, the demands on the tapered roller bearing have become stricter, and there is difficulty in meeting the demands by only increasing the roller coefficient as in Patent Literature 1.

As a method for further increasing the load capacity of the tapered roller bearing, for example, there has been known a method involving forming each of raceway surfaces of an inner ring and an outer ring into a crowning shape. For example, in Patent Literature 2, there is described a raceway surface including a so-called composite crowning surface. In the composite crowning surface, an arcuate curve having a large curvature radius (large-arc portion) is formed at a center portion of the raceway surface in a generating-line direction, and arcuate curves each having a small curvature radius (small-arc portions) are formed at both end portions of the raceway surface in the generating-line direction. As described above, with the raceway surface including the composite crowning surface, when the large-arc portion formed at the center of the raceway surface and the roller are brought into contact with each other during the normal use, a contact length between the raceway surface and the roller is increased to reduce a surface pressure, thereby being capable of preventing defects such as surface-originating separation in an early stage. Meanwhile, with the small-arc portions formed at the end portions of the raceway surface, the end portions can be recessed toward the side apart from the roller. Therefore, for example, even when a high load is applied to the tapered roller bearing, the contact between the raceway surface of the outer ring and the end portions of the tapered roller is avoided as much as possible, thereby being capable of preventing generation of an excessive edge load.

CITATION LIST

SUMMARY OF INVENTION

Technical Problem

Incidentally, in the tapered roller bearing, a contact surface pressure between the raceway surface of the inner ring and the rolling surface of the roller is typically higher than a contact surface pressure between the raceway surface of the outer ring and the rolling surface of the roller. Therefore, the above-mentioned raceway surface including the composite crowning surface has often been applied to the raceway surface of the inner ring which involves a strict load condition, but actually has almost never been applied to the raceway surface of the outer ring which involves a relatively moderate load condition.

In order to meet the demands in recent years for further increase in load capacity in the tapered roller bearing as described above, the inventor of the present invention has conducted an investigation on application of the composite crowning surface not only to the raceway surface of the inner ring but also to the raceway surface of the outer ring. As a result of the investigation, the following problem has been found. In order to avoid the excessive edge load caused by the contact between the raceway surface of the outer ring and the end portion of the tapered roller, it has been considered preferable that the curvature radius of each of the small-arc portions formed at the end portions of the raceway surface of the outer ring be set as small as possible, that is, the curvature be set as large as possible to cause the small-arc portions to be separated from the rolling surface of the tapered roller as much as possible. However, according to the investigation conducted by the inventor of the present invention, it has been found that, when the curvature of each of the small-arc portions at the end portions of the raceway surface is set excessively large, the cycle time for superfinishing applied to the raceway surface becomes longer, thereby leading to a problem of significant degradation in productivity.

The present invention has an object to improve productivity of a tapered roller bearing in which a composite crowning surface is applied to a raceway surface of an outer ring.

Solution to Problem

The raceway surfaces of the outer ring and an inner ring are typically subjected to the superfinishing after grinding. The superfinishing is performed, for example, in the manner as described in Patent Literature 2. That is, under a state in which a grinding wheel is pressed against the raceway surface of the outer ring or the inner ring being rotated, the grinding wheel is reciprocated along a generating-line direction of the raceway surface (seeFIG. 7). The inventor of the present invention performed the above-mentioned superfinishing on the raceway surface of the outer ring which is formed of the composite crowning surface. As a result, it has been found that the cycle time becomes longer as a curvature of each of end portion curves of the raceway surface is larger. The following cause is conceivable.

During the superfinishing, while the grinding wheel machines the raceway surface, the grinding wheel itself is also deformed or worn to conform to the raceway surface. As a result, a favorable contact state between the grinding wheel and the raceway surface is obtained, and a machining efficiency is improved. That is, a large-arc portion formed at the center portion of the raceway surface is polished, with the result that the grinding wheel is worn to conform to the large-arc portion. Then, small-arc portions at the end portions of the raceway surface are polished with the grinding wheel, with the result that the grinding wheel is worn to conform to each of the small-arc portions. At this time, when there is a large difference in curvature between the large-arc portion and each of the small-arc portions, it takes a long time period to cause the grinding wheel, which is worn to conform to the large-arc portion, to conform to each of the small-arc portions, with the result that the machining efficiency during this time period is degraded. Similarly, it also takes a long time period to cause the grinding wheel, which is worn to conform to each of the small-arc portions, to conform to the large-arc portion, with the result that the machining efficiency is further degraded.

Based on the findings described above, according to one embodiment of the present invention, there is provided a tapered roller bearing, comprising: an inner ring comprising a raceway surface having a tapered shape on an outer peripheral surface of the inner ring; an outer ring comprising a raceway surface having a tapered shape on an inner peripheral surface of the outer ring; a plurality of tapered rollers, which are arranged between the raceway surface of the inner ring and the raceway surface of the outer ring so as to be rollable and each comprise a rolling surface having a tapered shape on an outer peripheral surface of each of the plurality of tapered rollers; and a cage which is configured to retain the plurality of tapered rollers at predetermined intervals, wherein the raceway surface of the outer ring comprises a composite crowning surface, the composite crowning surface comprising a center curve, which is formed at a center portion in a generating-line direction and has a curvature radius R1, and end portion curves, which are formed on both sides of the center curve in the generating-line direction and each have a curvature radius R2,R3which is smaller than a curvature radius R1of the center curve, wherein the raceway surface of the outer ring is entirely subjected to superfinishing, and wherein each of a ratio R2/R1of the curvature radius R2of the end portion curve to the curvature radius R1of the center curve and a ratio R3/R1of the curvature radius R3of the end portion curve to the curvature radius R1of the center curve is set to 0.02 or more, and each of drop amounts of the end portion curves is set to 0.07 mm or less.

The center curve and the end portion curves are not limited to the arcuate curves, and may comprise non-arcuate curves (for example, logarithmic curves). In the case of the non-arcuate curves, the minimum curvature radii of the non-arcuate curves are set to curvature radii R1, R2, and R3.

As described above, in the raceway surface of the outer ring, a difference between the curvature radius R1of the center curve and each of the curvature radii R2and R3of the end portion curves is suppressed within a predetermined range, and each of drop amounts of the end portion curves is set to a predetermined amount or less. As a result, the cycle time for the superfinishing is shortened, and hence the productivity is improved.

It is preferred that, in the above-mentioned tapered roller bearing, each of the drop amounts of both end portions of the raceway surface of the outer ring be set to 0.02 mm or more. With this, the end portions (end portion curves) of the raceway surface of the outer ring can be sufficiently separated apart from the tapered roller. Therefore, the contact between each of the corner portions of the tapered roller and the raceway surface of the outer ring is avoided as much as possible, thereby being capable of reliably preventing generation of the excessive edge load.

Incidentally, when the thermal expansion occurs in the housing to which the outer ring is fixed, the preload having been applied to the tapered roller bearing may be lost, with the result that the outer ring may be moved relative to the tapered roller toward a small-diameter side in an axial direction. In this case, there is a fear in that the rolling surface of the tapered roller overhangs from the raceway surface of the outer ring toward a large-diameter side to cause generation of the excessive edge load. In particular, the aluminum housing may involve a large amount of thermal expansion. Therefore, when the outer ring is fixed to an inner peripheral surface of the aluminum housing, the above-mentioned problem is conspicuous. Also in such a case of occurrence of the thermal expansion, when the preload is increased to prevent occurrence of the preload loss, an excessively large load is applied to the bearing during the normal use, with the result that the lifetime of the bearing is shortened.

In view of the above, it is preferred that a generating-line-direction width of the raceway surface of the outer ring with respect to the roller rolling surface be set so that the rolling surface of the tapered roller (hereinafter also referred to as “roller rolling surface”) is prevented from overhanging from the raceway surface of the outer ring toward the large-diameter side even when occurrence of the preload loss in the tapered roller bearing causes the outer ring to move relative to the tapered roller in the axial direction. Specifically, it is preferred that, under a state in which the inner ring, the outer ring, and the plurality of tapered rollers are arranged at normal positions, a generating-line-direction dimension W2(seeFIG. 1) of a region of the raceway surface of the outer ring on the large-diameter side from the rolling surface of each of the tapered rollers be set in consideration of the amount of relative movement of the outer ring, which is caused by the preload loss. For example, when the generating-line-direction dimension W2of the above-mentioned region is set to 0.6 mm or more, the overhanging of the roller rolling surface from the outer ring raceway surface can be prevented even when the preload loss is liable to occur, for example, even when the outer ring is fixed to the aluminum housing. The “state in which the inner ring, the outer ring, and the tapered rollers are arranged at normal positions” corresponds to a state in which an appropriate preload in the axial direction is applied to the inner ring and the outer ring.

For example, in the tapered roller bearing configured to mainly receive the load in a radial direction among bearings configured to support a rotary shaft of a transmission which takes a horizontal posture, a downward load is applied to the inner ring. In this case, most of the load is applied to the tapered rollers on the lower half among the plurality of tapered rollers which are arranged at equal intervals in a circumferential direction, whereas the tapered rollers which are arranged near an upper end are brought into a substantially no-load state. At this time, the interval between the raceway surfaces of the inner ring and the outer ring sandwiching the tapered rollers near the upper end where substantially no load is applied is slightly increased, and the tapered rollers may be moved relative to the outer ring by the amount of the slight increase in interval toward the small-diameter side in the axial direction (see the dotted lines inFIG. 6). In such a case, in order to prevent overhanging of the roller rolling surface from the raceway surface of the outer ring toward the small-diameter side, it is necessary that the raceway surface of the outer ring be extended toward the small-diameter side from the rolling surfaces of the tapered rollers arranged at the normal positions (see the solid lines inFIG. 6). At this time, under the state in which the inner ring, the outer ring, and the plurality of tapered rollers are arranged at normal positions, a distance W3between a small-diameter-side end surface of each of the tapered rollers and a small-flange portion of the inner ring is set small. With this configuration, even when the tapered rollers are moved toward the small-diameter side, the movement of the tapered rollers can be regulated by causing the tapered rollers to be brought into abutment against the small-flange portion of the inner ring, thereby being capable of reducing the generating-line-direction width of the raceway surface of the outer ring. Specifically, it is preferred that the above-mentioned distance W3be set to 0.4 mm or less.

Incidentally, with regard to the end portion curves of the outer ring raceway surface on the small-diameter side, when the drop amounts are to be reduced without changing the curvature radii, for example, it is conceivable to move an axial position of the small-diameter-side end surface of the outer ring toward the large-diameter side, to thereby reduce the width of the end portion curves. However, the interval of the small-diameter-side end surface of the outer ring and the large-diameter-side end surface of the inner ring in the axial direction is often determined in accordance with a device in which the tapered roller bearing is to be assembled (for example, a transmission or the like). Therefore, a position of the small-diameter-side end surface of the outer ring may not be changed unreasonably. In view of the above, when an axial width W1(seeFIG. 6) of a chamfered portion formed on a small-diameter-side end portion of the inner peripheral surface of the outer ring is set large, for example, set to 0.5 mm or more, the width of the end portion curve can be reduced, thereby being capable of setting the drop amount to be small without moving the position of the small-diameter-side end surface of the outer ring.

Alternatively, also when a cylindrical surface is formed between the chamfered portion, which is formed on the small-diameter-side end portion of the inner peripheral surface of the outer ring, and the raceway surface, similarly to the above, the width of each of the end portion curves can be reduced, thereby being capable of setting the drop amount to be small without moving the position of the small-diameter-side end surface of the outer ring.

Advantageous Effects of Invention

As described above, according to the tapered roller bearing of the present invention, the cycle time for superfinishing of the raceway surface of the outer ring comprising the composite crowning surface is shortened, thereby being capable of improving the productivity.

DESCRIPTION OF EMBODIMENTS

Now, a tapered roller bearing according to one embodiment of the present invention is described with reference to the drawings.

As illustrated inFIG. 1andFIG. 2, a tapered roller bearing1of this embodiment comprises an inner ring2, an outer ring3, a plurality of tapered rollers4, and a cage5. The inner ring2comprises a raceway surface2ahaving a tapered shape on an outer peripheral surface thereof. The outer ring3comprises a raceway surface3ahaving a tapered shape on an inner peripheral surface thereof. The plurality of tapered rollers4are arranged between the raceway surface2aof the inner ring2and the raceway surface3aof the outer ring3so as to be rollable and each comprise a rolling surface4ahaving a tapered shape on an outer peripheral surface thereof. The cage5is configured to retain the tapered rollers4at equal intervals in a circumferential direction. The inner ring2, the outer ring3, and the tapered rollers4are each made of a steel material, such as bearing steel, carburized steel, or stainless steel. The cage5is integrally made of metal or resin. In the following description, a small-diameter side (left side inFIG. 1) of the tapered roller4in an axial direction (axial direction of the inner ring2and the outer ring3) is referred to as “small-diameter side”, and a large-diameter side (right side inFIG. 1) of the tapered roller4in the axial direction is referred to as “large-diameter side”.

The tapered roller bearing1is assembled in, for example, a transmission unit or a differential unit of an automobile. Specifically, as illustrated inFIG. 1, an outer peripheral surface3bof the outer ring3is press-fitted to an inner peripheral surface10aof a housing10, and an inner peripheral surface2bof the inner ring2is press-fitted to an outer peripheral surface20aof a shaft20. The housing10is made of, for example, aluminum. The shaft20is made of, for example, chrome-molybdenum steel. A shoulder surface10bof the housing10and a shoulder surface20bof the shaft20sandwich and pressurize an end surface3cof the outer ring3on the small-diameter side and an end surface2cof the inner ring2on the large-diameter side from both sides in the axial direction, to thereby apply a preload in the axial direction to the tapered roller bearing1. In the illustrated example, a shim30is interposed between the end surface3cof the outer ring3on the small-diameter side and the shoulder surface10bof the housing10. A thickness of the shim30is suitably set so that a magnitude of the preload to be applied to the tapered roller bearing1is adjusted.

The inner ring2has a small-flange portion2dand a large-flange portion2e. The small-flange portion2dis formed on the small-diameter side of the raceway surface2a. The large-flange portion2eis formed on the large-diameter side of the raceway surface2a. The raceway surface2aof the inner ring2comprises a crowning surface formed of a single curve, or a composite crowning surface formed of a center curve and end portion curves formed on both sides of the center curve. Each curve is formed of an arc or a logarithmic curve.

As illustrated inFIG. 3, the raceway surface3aof the outer ring3is formed of a center curve3a1which is formed at a center portion in a generating-line direction, an end portion curve3a2on the small-diameter side which is adjacent to the small-diameter side (left side inFIG. 3) of the center curve3a1, and an end portion curve3a3on the large-diameter side which is adjacent to the large-diameter side (right side inFIG. 3) of the center curve3a1. In this embodiment, the center curve3a1comprises an arcuate curve having a curvature radius R1. The end portion curve3a2on the small-diameter side comprises an arcuate curve having a curvature radius R2. The end portion curve3a3on the large-diameter side comprises an arcuate curve having a curvature radius R3. The center curve3a1and each of the end portion curves3a2and3a3smoothly continue so as to have common tangential lines at borders P1and P2. InFIG. 3, curvatures of the curves3a1,3a2, and3a3of the raceway surface3aare illustrated in an exaggerated manner.

In the outer raceway surface3aof the outer ring3, each of a ratio R2/R1of the curvature radius R2of the end portion curve3a2to the curvature radius R1of the center curve3a1and a ratio R3/R1of the curvature radius R3of the end portion curve3a3to the curvature radius R1of the center curve3a1is set to 0.02 or more, preferably 0.04 or more. Further, each of the ratio R2/R1and the ratio R3/R1is set to 0.3 or less, preferably 0.1 or less. Each of drop amounts D1and D2of the end portion curves3a2and3a3is set to 0.02 mm or more and 0.07 mm or less. The drop amounts D1and D2of the end portion curves3a2and3a3are widths of the end portion curves3a2and3a3in a direction orthogonal to a generating-line direction of the raceway surface3a. Specifically, the generating-line direction of the raceway surface3acorresponds to a direction of a straight line connecting ends (borders P1and P2) of the center curve3a1.

In this embodiment, an axial width W1(seeFIG. 6) of a chamfered portion3dformed on a small-diameter-side end portion of the inner peripheral surface of the outer ring3is set large so that an axial width of the end portion curve3a2on the small-diameter side of the raceway surface3ais set small. With this configuration, without changing an axial position of the small-diameter-side end surface3cof the outer ring3, the drop amount D1of the end portion curve3a2on the small-diameter side can be set small. The axial width W1of the chamfered portion3dis set to, for example, 0.5 mm or more. Further, in order to secure the drop amount D1of the end portion curve3a2on the small-diameter side to be 0.02 mm or more, the axial width W1of the chamfered portion3dis set to, for example, 1.0 mm or less.

Instead of or in addition to setting the axial width W1of the chamfered portion3dto be large, as illustrated inFIG. 4, a cylindrical surface3fmay be formed between the chamfered portion3dand the raceway surface3ato suppress the drop amount D1of the end portion curve3a2on the small-diameter side.

The rolling surface4aof the tapered roller4has a substantially linear tapered surface, a crowning surface having a single curve, or a composite crowning surface comprising a center curve and end portion curves formed on both sides of the center curve. At both ends of the outer peripheral surface of the tapered roller4, there are formed chamfered portions4band4cwhich are adjacent to the rolling surface4b.

In the tapered roller bearing1of this embodiment, for example, an inner diameter of the inner ring2is set within a range of from 15 mm to 120 mm. An outer diameter of the outer ring3is set within a range of from 30 mm to 250 mm. A combination width, which is an axial width between the small-diameter-side end surface3cof the outer ring3and the large-diameter-side end surface2cof the inner ring2, is set within a range of from 7 mm to 50 mm. Further, in the tapered roller bearing1of this embodiment, the tapered rollers4are loaded at high density. Specifically, a roller coefficient γ expressed by the following expression is set to γ>0.94.
γ=(Z·DA)/(π·PCD)

In the above-mentioned expression, Z represents the number of rollers, DA represents an average diameter of the rollers, and PCD represents a pitch circle diameter of the rollers.

The cage5comprises a small-diameter side annular portion5a, a large-diameter-side annular portion5b, and a plurality of columnar portions5cconnecting the small-diameter-side annular portion5aand the large-diameter-side annular portion5bto each other in the axial direction (seeFIG. 1andFIG. 2). The cage5is arranged on a radially outer side of centers of the tapered rollers4and at a position of not being held in contact with the outer ring3. Column surfaces5dof the columnar portions5c, which are held in contact with the tapered rollers4, are inclined so that a gap formed between the column surfaces5dopposed to each other in the circumferential direction increases as approaching the radially inner side.

The tapered roller bearing1allows the inner ring2and the outer ring3to rotate relative to each other while holding the large-diameter-side end surfaces4eof the tapered rollers4in slide contact with the large-flange portion2eof the inner ring2. At this time, when preload loss occurs due to some cause, and the outer ring3is moved relative to the tapered roller4toward the small-diameter side (seeFIG. 5), there is a fear in that the rolling surfaces4aof the tapered rollers4may overhang from the raceway surface3aof the outer ring3toward the large-diameter side to cause generation of an excessive edge load.

In view of the above, it is preferred that, under a state in which the inner ring2, the outer ring3, and the tapered rollers are arranged at normal positions (seeFIG. 1), a generating-line-direction dimension W2of a region of the raceway surface3aof the outer ring3on the large-diameter side from the rolling surfaces4aof the tapered rollers4, that is, a generating-line direction distance between the large-diameter-side end of the rolling surface4aof the tapered roller4and the large-diameter-side end of the raceway surface3aof the outer ring3be set large in consideration of the preload loss. Particularly in the case where the housing10is made of aluminum, the housing10involves a large amount of thermal expansion, and hence the preload of the tapered roller bearing1is liable to be lost. In such a case, it is preferred that the generating-line-direction dimension W2of the above-mentioned region be set to, for example, 0.6 mm or more.

In this embodiment, a distance W3(seeFIG. 6) between an end surface4dof the tapered roller4on the small-diameter side and the small-flange portion2dof the inner ring2is set small in advance. Specifically, under the state in which the inner ring2, the outer ring3, and the tapered rollers4are arranged at the normal positions, the above-mentioned distance W3is set to 0.4 mm or less. With this configuration, even when the tapered rollers4are moved toward the small-diameter side due to some cause, the tapered rollers4are brought into abutment against the small-flange portion2din an early stage (see the dotted lines inFIG. 6). With this configuration, the amount of movement of the tapered rollers4toward the small-diameter side can be suppressed. Therefore, without extension of the raceway surface3aof the outer ring3(in particular, the end portion curve3a2on the small-diameter side) toward the small-diameter side, overhanging of the roller surfaces4aof the tapered rollers4from the raceway surface3aof the outer ring3toward the small-diameter side can be prevented. When the above-mentioned distance W3is excessively small, oil is less likely to flow in through the gap formed between the end surfaces4dof the tapered rollers4on the small-diameter side and the small-flange portion2dof the inner ring2. Therefore, it is preferred that the above-mentioned distance W3be set to 0.2 mm or larger.

The raceway surface2aof the inner ring2, the raceway surface3aof the outer ring3, and the rolling surfaces4aof the tapered rollers4are subjected to grinding, and thereafter are subjected to superfinishing. The superfinishing on the raceway surface3aof the outer ring3is performed in the following manner. Under a state in which the outer ring3is rotated about a center axis thereof, as illustrated inFIG. 7, a grinding wheel6is pressed against the raceway surface3aand reciprocated along the generating-line direction of the raceway surface3a. At this time, while the grinding wheel6is reciprocated along the entire raceway surface3a, the grinding wheel6may be finely vibrated in the generating-line direction. The grinding wheel6is pressed against the center curve3a1in such a manner. As a result, the distal end surface of the grinding wheel6is deformed to conform to the center curve3a1, and the center curve3a1is polished. Then, the grinding wheel6is pressed against the end portion curves3a2and3a3, with the result that the distal end surface of the grinding wheel6is deformed to conform to the end portion curves3a2and3a3, and the end portion curves3a2and3a3are polished.

At this time, as described above, the difference between the curvature radius R1of the center curve3a1and each of the curvature radii R2and R3of the end portion curves3a2and3a3is suppressed to be relatively smaller (R2/R1≥0.02 and R3/R1≥0.02). Therefore, the amount of deformation of the distal end of the grinding wheel6is relatively smaller when the grinding wheel6moves from the center curve3a1to the end portion curves3a2and3a3or moves from the end portion curves3a2and3a3to the center curve3a1. With this, the grinding wheel6conforms to the curves3a1,3a2, and3a3in an early stage. As a result, machining is performed with high efficiency, and the cycle time for the superfinishing is shortened, thereby improving the productivity of the tapered roller bearing1.

The present invention is not limited to the above-mentioned embodiment. For example, in the above-mentioned embodiment, description is made of the case where all of the center curve3a1and the end portion curves3a2and3a3of the raceway surface3aof the outer ring3are arcuate curves. However, the present invention is not limited to this case. Any or all of those curves may be non-arcuate curves (for example, logarithmic curves). For example, the center curve3a1may be an arcuate curve, and both end portion curves3a2and3a3may be logarithmic curves. Further, the curvature radius R2of the end portion curve3a2on the small-diameter side and the curvature radius R3of the end portion curve3a3on the large-diameter side may be equal to or different from each other.

In order to verify the effect of the present invention, the following test was conducted. First, various types of tapered roller bearings having different design dimensions (in particular, factors of the outer ring raceway surface) were prepared, and were identified as Examples 1 to 8 and Comparative Examples 1 to 5. Each tapered roller bearing had the same configuration as that of the embodiment illustrated inFIG. 1toFIG. 3, and design dimensions of respective parts are shown in the following Table 1. Research was made on the following Items (1) to (3) for those tapered roller bearings.

TABLE 1Bearing functionalpropertyDesign dimensions(1)(2)(3)R2/R1CycleContactRollerABL1L2L3R1R2R3R3/R1D1D2W1W2W3timepressurepositionExample 170159.12.62.134501001000.0290.0370.0250.50.80.3∘∘∘Example 2751711.22.82.453001501500.0280.0290.0220.50.670.31∘∘∘Example 3702315.14.33.195002002000.0210.0500.0260.70.70.2∘∘∘Example 48014.88.43.22.522001001000.0450.0570.0360.50.90.25∘∘∘Example 56912.57.22.31.8130080800.0620.0390.0250.50.90.3∘∘∘Example 66612.46.32.11.7100060600.0600.0430.0290.50.80.3∘∘∘Example 76612.46.32.11.7170040400.0240.0590.0391.20.450.7∘∘xExample 870159.12.62.134503003000.0870.0150.0101.20.50.5∘xxComparative70159.12.62.1345050500.0140.0710.0471.20.50.5x∘xExample 1Comparative751711.22.82.4530050500.0090.0810.0601.50.30.6xxxExample 2Comparative702315.14.33.11430080800.0060.1180.06210.50.6x∘xExample 3Comparative8014.88.43.22.5440040400.0090.1310.0811.20.450.5xxxExample 4Comparative6912.57.22.31.8220040400.0180.0700.04310.350.5xxxExample 5A (mm): Outer diameter dimension of the outer ring 3B (mm): Axial width of the outer ring 3L1(mm): Generating-line-direction dimension of the center curve 3a1 of the raceway surface 3a of the outer ring 3L2(mm): Generating-line-direction dimension of the end portion curve 3a2 on the small-diameter side of the raceway surface 3a of the outer ring 3L3(mm): Generating-line-direction dimension of the end portion curve 3a3 on the large-diameter side of the raceway surface 3a of the outer ring 3R1(mm): Curvature radius of the center curve 3a1 of the raceway surface 3a of the outer ring 3R2(mm): Curvature radius of the end portion curve 3a2 on the small-diameter side of the raceway surface 3a of the outer ring 3R3(mm): Curvature radius of the end portion curve 3a3 on the large-diameter side of the raceway surface 3a of the outer ring 3D1(mm): Drop amount of the end portion curve 3a2 on the small-diameter side of the raceway surface 3a of the outer ring 3D2(mm): Drop amount of the end portion curve 3a3 on the large-diameter side of the raceway surface 3a of the outer ring 3W1(mm): Axial width of the chamfered portion 3d on the small-diameter side of the outer ring 3W2(mm): Generating-line-direction dimension of the region of the raceway surface 3a of the outer ring 3 on the large-diameter side from the rolling surface 4a of the tapered roller 4W3(mm): Distance between the end surface 4d of the tapered roller 4 on the small-diameter side and the small-flange portion 2d of the inner ring 2

(1) Cycle Time for Superfinishing of Outer Ring Raceway Surface

The raceway surface of the outer ring of each tapered roller bearing was subjected to the superfinishing by the method illustrated inFIG. 7, and the cycle time for the superfinishing was measured. As a determination criterion, the mark of “∘” was given when the cycle time was 30 seconds or less, and the mark of “×” was given when the cycle time exceeded 30 seconds.

The inner ring was rotated under a state in which a predetermined preload was applied to the inner ring and the outer ring of each tapered roller bearing, and the surface pressure during the rotation was measured. The measurement of the surface pressure was performed by measuring the applied load through residual stress measurement with use of an X-ray. The edge portion at which the end portions of the raceway surfaces of the inner ring and the outer ring and the rollers are held in contact was subjected to the measurement. As a determination criterion, the mark of “∘” was given when the surface pressure was 4,000 MPa or less, and the mark of “×” was given when the surface pressure exceeded 4,000 MPa.

(3) Position of Tapered Roller During Preload Loss

The inner ring was rotated under the state in which the predetermined preload was applied to the inner ring and the outer ring of the tapered roller bearing, and the presence or absence of a linear edge contact mark, which may be formed at the time of overhanging of the roller from the outer ring raceway surface large-diameter side, on the roller rolling surface radially outer side was checked. When the linear edge contact mark was formed on the roller large-diameter-side rolling surface, the mark of “×” was given.

As shown in Table 1, in Examples 1 to 8 in which each of curvature radius ratios R2/R1and R3/R1of the end portion curves to the center curve of the outer ring raceway surface was set to 0.02 or more and in which each of the drop amounts of the end portion curves was set 0.07 mm or less, the cycle time for the superfinishing of the outer ring raceway surface was 30 seconds or less. In contrast, in Examples 1 to 5 in which each of the curvature radius ratios R2/R1and R3/R1was less than 0.02 and in which each of the drop amounts of the end portion curves was more than 0.07 mm, the cycle time for the superfinishing of the outer ring raceway surface was longer than 30 seconds. Further, in Examples 4, 5, 6, and 8 in which each of the curvature radius ratios R2/R1and R3/R1was especially larger, that is, was set to 0.04 or more, the cycle time for the superfinishing was especially shorter.

Further, in Examples 1 to 6, each of the drop amounts of the end portion curves of the outer ring raceway surface was set to 0.02 mm or more. The width W2in the region of the outer ring raceway surface on the large-diameter side from the tapered roller was set to 0.6 mm or more. The distance W3between the small-flange portion of the inner ring and the end surface of the tapered roller on the small-diameter side was set to 0.4 mm or less. In Examples 1 to 6, the edge stress was not generated, and there was no abnormality in the surface pressure distribution also during the preload loss. Thus, the tapered roller bearings of Examples 1 to 6 had sufficient durability.

In contrast, in Example 8, each of the drop amounts of the end portion curves of the outer ring raceway surface was less than 0.02 mm. Consequently, the excessive edge stress was generated, and the edge portion was damaged. In Example 7 and Comparative Examples 1 to 5, each of the drop amounts of the end portion curves of the outer ring raceway surface was set to 0.02 mm or more. However, the width W2of the region of the outer ring raceway surface on the large-diameter side from the tapered roller was less than 0.6 mm, and the distance W3between the small-flange portion of the inner ring and the end surface of the tapered roller on the small-diameter side exceeded 0.4 mm. Consequently, during the preload loss, the rolling surface of the tapered roller overhung relative to the raceway surface of the outer ring, and the edge of the end portion of the raceway surface was brought into contact with the roller rolling surface. As a result, the edge portion of the roller rolling surface or the raceway surfaces of the inner ring and the outer ring were damaged.

REFERENCE SIGNS LIST