JP2006022847A - Thrust roller bearing cage and thrust roller bearing - Google Patents

Abstract

【Task】
A thrust roller bearing cage having excellent durability and long life and a thrust roller bearing using the same are provided.
[Solution]
A race 11 having a high rotational speed V1 is disposed on the opening side of the cage 13, and a race 12 having a low rotational speed V2 (<V1) is disposed on the opposite side. In such a state, the rotational speed V1 of the race 11 is faster than the rotational speed V2 of the race 12, and therefore the amount of lubricating oil F1 passing between the cage 13 and the race 11 is between the cage 13 and the race 12. The amount of lubricating oil F2 passing through is increased. Accordingly, the amount F3 of lubricating oil flowing along the column portion 15 of the cage 13 also increases, and the outer diameter side end surface of the roller 16 and the pocket outer diameter side end portion of the cage 13, or the outer diameter side outer periphery of the roller 16 The amount of lubricating oil supplied to the surface and the pocket inner edge (region A) of the cage 13 is increased, and wear can be effectively suppressed.
[Selection] Figure 4

Description

  BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thrust bearing retainer and a thrust bearing for supporting a thrust load of a rotating body, and more particularly to a thrust roller bearing retainer suitable for supporting a rotating part of an automobile transmission or a compressor for a car air conditioner. The present invention relates to a container and a thrust roller bearing.

  For example, as disclosed in Patent Document 1, a thrust roller bearing used in an automatic transmission (A / T), a car air conditioner compressor, or the like has a configuration shown in FIG. This thrust roller bearing has a structure in which a cage 13 is rotatably provided between two opposing thrust races (bearing discs) 11 and 12, and an outer diameter annular portion 13 a and an inner diameter annular portion of the cage 13. An annular pocket row 14 (see FIG. 2) is provided between the space 13b. The pocket row 14 is composed of a large number of pockets 15p formed in the cage 13, and needle rollers 16 are provided in the pockets 15p so as to be able to roll.

  Since the cage 13 of such a thrust roller bearing is generally composed of a thin metal plate, the needle roller 16 may jump out of the pocket 15p when the cage 13 rotates. Therefore, in order to prevent the needle roller 16 from jumping out of the pocket 15p, in the thrust roller bearing disclosed in Patent Document 2, an intermediate portion 13c (see FIG. 5) for connecting the outer diameter annular portion 13a and the inner diameter annular portion 13b of the cage 13 is shown. 2) is bent into an M shape to prevent the needle rollers 16 from popping out.

About lubrication of such a bearing, with respect to the race surface of the roller 16, the cage 13, and the races 11 and 12, the lubricating oil that has entered through the clearance between the inner ring portion 13 b and the race 11 and the race 12. It is done.
JP 2002-250347 A British Patent 1,014,307

  However, during the operation of the thrust roller bearing, the roller outer peripheral surface is in a pure rolling motion at only one central portion in the axial direction and the other portion is rolling while causing a relative slip with the race surface. The farther away from the center, the greater the relative slip, and the more severe the lubrication conditions. In addition, due to the centrifugal force, the roller contact with the roller end surface and the outer diameter end of the cage pocket, the fluctuation of the rotation speed of the roller, the oscillation of the cage itself, or the movement in the cage axial direction. An impact occurs between the cage pocket and the oil film on the roller outer circumferential surface is scraped off by the pocket column of the cage, so that the roller end surface and the cage pocket outer diameter surface, or the roller outer circumferential surface and the cage pocket It was difficult to achieve good lubrication on the inner edge. In particular, in the case of high-speed rotation, premature wear occurs on the outer diameter side end surface of the roller and the outer diameter side end portion of the cage or on the outer peripheral side surface of the roller and the inner edge of the cage pocket (region A shown in FIG. 1). There is a fear.

  Focusing on the above problems, an object of the present invention is to provide a thrust roller bearing retainer having excellent durability and a long life and a thrust roller bearing using the same.

The cage for a thrust roller bearing of the present invention is
A thrust roller made of a single plate member formed with an inner annular portion, an outer annular portion located on the radially outer side of the inner annular portion, and a plurality of column portions connecting the inner annular portion and the outer annular portion. In bearing cages,
When the cross section of the thrust roller bearing is taken in the axial direction, of the pair of races holding the thrust roller bearing retainer in the axial direction, the race with the faster rotational speed than the race with the slower rotational speed. An intermediate portion of the column portion is bent so as to be close to each other. The intermediate portion is formed so as to hold at least the center in the axial direction of the roller.

  The inventors of the present invention have noticed that there is a case where the wear is relatively high and a case where the wear is relatively low even under the same conditions, and have found that the lubrication conditions are greatly different depending on the difference in rotational speed between the race and the cage. More specifically, the principle of the present invention will be described with reference to the drawings. 3 and 4 are views showing the flow of the lubricating oil of the thrust roller bearing. In FIG. 3, the opening side of the cage 13 (the side close to one race by bending the middle part of the column part, FIG. On the left side, a race 11 having a low rotational speed V1 is arranged, and a race 12 having a high rotational speed V2 (> V1) is arranged on the opposite side. In such a state, based on the nature of the fluid viscosity, the lubricating oil adhering to the race surface moves circumferentially together with the race, and flows in the radial direction along the radial direction by the action of centrifugal force. Since the centrifugal force increases as the rotational speed of the race increases, the amount of oil flowing in the radial direction along the radial direction increases. However, in the case shown in FIG. 3, since the rotational speed V1 of the race 11 is slower than the rotational speed V2 of the race 12, if the clearance between the cage and both races is equal, the distance between the cage 13 and the race 11 The amount F1 of lubricating oil that passes through is less than the amount F2 of lubricating oil that passes between the cage 13 and the race 12. Accordingly, the amount of lubricating oil F3 flowing along the column portion 15 of the cage 13 is also reduced, and the outer diameter side end surface of the roller 16 and the pocket outer diameter side end portion of the cage 13 or the outer diameter side outer circumferential surface of the roller 16 are arranged. Therefore, the amount of lubricating oil supplied to the pocket inner edge (region A shown in FIG. 3) of the cage 13 is reduced, and wear is increased.

  On the other hand, in FIG. 4 showing the configuration of the present invention, contrary to FIG. 3, a race 11 having a high rotational speed V1 is disposed on the opening side of the cage 13, and a low rotational speed V2 (< The race 12 of V1) is arranged. In such a state, since the rotational speed V1 of the race 11 is faster than the rotational speed V2 of the race 12, if the clearance between the cage and both races is equal, the lubricating oil that passes between the cage 13 and the race 11 is used. This amount F1 is greater than the amount of lubricating oil F2 passing between the cage 13 and the race 12. Accordingly, the amount F3 of lubricating oil flowing along the column portion 15 of the cage 13 also increases, and the outer diameter side end surface of the roller 16 and the pocket outer diameter side end portion of the cage 13, or the outer diameter side outer periphery of the roller 16 The amount of lubricating oil supplied to the surface and the pocket inner edge (region A shown in FIG. 4) of the cage 13 increases, and wear can be effectively suppressed. That is, according to the present invention, even under severe lubrication conditions such as high-speed rotation, insufficient oil supply, and low lubricant viscosity, more lubricant is introduced and the most lubrication condition is achieved along the column portion 15 of the cage 13. Since it can be supplied to the severe region A and the lubrication condition there is improved, abnormal wear on the surface of the cage 13 and 16 can be avoided, and a high durability life can be realized.

  In addition, what is necessary is just to arrange | position so that the opening side of a holder | retainer may face a rotation race, when a thrust roller bearing contains a fixed race and a rotation race. Further, when both races rotate, the opening side of the cage may be directed to the race with the higher frequency of rotation speed. In addition, when the rotational speed is high, the guide type of the cage is preferably roller guide.

Further, when the average clearance between the outer annular portion is C1 and the average clearance between the inner annular portion is C3 with respect to the race in which the middle portion of the pillar portion is close, the following equation is established. Then, wear can be more effectively suppressed.
C1 <C3 (1)

Further, when the average clearance between the race where the intermediate portion of the pillar portion is close and the intermediate portion is C2, if the following formula is established, wear can be more effectively suppressed.
C1 <C2 <C3 (2)

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 5 is a cross-sectional view of a swash plate type car air conditioner compressor 1 including a thrust roller bearing according to the present embodiment. The compressor 1 for a swash plate type car air conditioner is such that a piston reciprocates through a shoe sliding on a swash plate by rotation of a swash plate fixed to a main shaft. Is supported by a radial bearing 5 so as to be freely rotatable. A plurality of cylinder bores 6 are formed in the housing 2 at equally spaced positions in the circumferential direction, and double-headed pistons 7 are slidably accommodated in the bores 6. A concave portion 8 is formed at the central portion of each piston 7 so as to straddle the outer peripheral portion of the swash plate 3. A spherical seat is formed on the axially opposed surface of the concave portion 8 to seat a spherical or hemispherical shoe 9. I'm allowed. A shoe 9 is interposed between the swash plate 3 and the piston 7 and functions to smoothly convert the rotational motion of the swash plate 3 into the reciprocating motion of the piston 7.

  The swash plate 3 is fixed to the main shaft 4 and rotates together with the main shaft 4. Since the swash plate 3 functions to reciprocate the piston 7 as described above, a thrust load is generated in the axial direction of the main shaft 4. Therefore, the thrust bearing 10 is interposed, and a thrust roller bearing is generally used as this thrust bearing.

  FIG. 6 is a cross-sectional view of one of the thrust roller bearings 10. In FIG. 6, the thrust roller bearing 10 includes a pair of races 11, 12, a plurality of rollers 16 sandwiched therebetween, and a cage 13 that holds the rollers 16. The retainer 13 is a so-called M-shaped retainer formed by bending a single plate material, and includes an inner annular portion 13b, an outer annular portion 13a located radially outside the inner annular portion 13b, and an inner annular portion. 13b and a plurality of column portions 15 connecting the outer annular portion 13a are formed, and when the cross section of the thrust roller bearing is taken in the axial direction as shown in FIG. 7, the intermediate portion 13c of the column portion 15 is bent. Is close to race 11. In this case, the side close to the race 11 is called the opening side of the cage 13.

  The thrust roller bearing 10 according to the present embodiment has substantially the same configuration as that shown in FIG. That is, the race 11 having a high rotational speed V1 is disposed on the opening side of the cage 13, and the race 12 having a low rotational speed V2 (<V1) is disposed on the opposite side. In such a state, the rotational speed V1 of the race 11 is faster than the rotational speed V2 of the race 12, so that the amount of lubricating oil passing between the cage 13 and the race 11 is between the cage 13 and the race 12. May be greater than the amount of lubricating oil that passes through. Accordingly, the amount of lubricating oil flowing along the column portion 15 of the cage 13 can also increase, so that the outer diameter side end surface of the roller 16 and the pocket outer diameter side end portion of the cage 13, or the outer diameter side of the roller 16. The amount of lubricating oil supplied to the outer peripheral surface and the pocket inner edge of the cage 13 increases, and wear can be effectively suppressed.

  Furthermore, in the present embodiment, the average clearance between the outer annular portion 13a and the clearance between the outer annular portion 13a and the clearance between the intermediate portion 13c and the race 11 where the intermediate portion 13c of the column portion 15 of the cage 13 is close. When the average clearance between C2 and the inner annular portion 13b is C3, since C2 <C3 is established, the amount of lubricating oil that passes through the inner annular portion 13b is less than that of the intermediate portion 13c. More lubricating oil passes through the clearance, and as a result, more lubricating oil flows along the column 15 of the retainer 13, thereby increasing the inner diameter side end face of the roller 16 and the pocket inner diameter end of the retainer 13, and The amount of lubricating oil supplied to the inner diameter side outer peripheral surface of the roller 16 and the pocket inner edge of the cage 13 is increased, and wear can be suppressed. Further, since C1 <C2 is established, the amount of lubricating oil that passes through the clearance of the inner annular portion 13b is larger than that of the lubricating oil that passes through the clearance of the outer annular portion 13a, as described above. As the lubricating oil flowing along the outer annular portion 13a of the cage 13 increases, the outer diameter side end surface of the roller 16 and the pocket outer diameter side end portion of the cage 13 or the outer diameter side outer circumferential surface of the roller 16 The amount of lubricating oil supplied to the pocket inner edge of the cage 13 increases, and wear can be suppressed.

  FIG. 7 is a cross-sectional view of the thrust roller bearing 10A according to the second embodiment. This embodiment differs from the embodiment of FIG. 6 only in the shapes of the races 11 and 12. More specifically, a cylindrical flange portion 11 a is formed at the outer diameter side end portion of the race 11, and a cylindrical flange portion 12 a is formed at the inner diameter side end portion of the race 12. Also in the present embodiment, since the rotational speed of the race 11 is faster than the rotational speed of the race 12, the above-described wear suppression effect can be obtained.

  FIG. 8 is a cross-sectional view of a thrust roller bearing 10B according to the third embodiment. This embodiment differs from the embodiment of FIG. 7 only in that the direction of the cage 13 is changed, that is, the opening side of the cage 13 is directed toward the race 12. Also in the present embodiment, since the rotational speed of the race 12 is faster than the rotational speed of the race 11, the above-described wear suppression effect can be obtained.

  FIG. 9 is a cross-sectional view of the thrust roller bearing 10C according to the fourth embodiment. This embodiment differs from the embodiment of FIG. 6 only in the shapes of the inner annular portion 13b and the outer annular portion 13a. More specifically, the inner annular portion 13b and the outer annular portion 13a are bent and doubled, but also in this embodiment, the rotational speed of the race 11 is higher than the rotational speed of the race 12. Therefore, the above-described wear suppression effect can be obtained.

  FIG. 10 is a cross-sectional view of a thrust roller bearing 10D according to the fifth embodiment. This embodiment is different from the embodiment of FIG. 9 only in the shapes of the races 11 and 12. More specifically, a cylindrical flange portion 11 a is formed at the outer diameter side end portion of the race 11, and a cylindrical flange portion 12 a is formed at the inner diameter side end portion of the race 12. Further, a projection (so-called anti-barre) 1b that prevents separation from the cage 13 is formed at the end of the flange portion 11a. Also in the present embodiment, since the rotational speed of the race 11 is faster than the rotational speed of the race 12, the above-described wear suppression effect can be obtained.

  The present invention has been described above with reference to the embodiments. However, the present invention is not limited to the above-described embodiments, and can of course be changed or improved within the scope of the invention. For example, the thrust roller bearing provided with the cage for a thrust roller bearing of the present invention can be used for an automatic transmission of a vehicle and the like.

It is sectional drawing of the cage for thrust roller bearings of a prior art. It is a top view of the cage for thrust roller bearings of a prior art. It is sectional drawing of the cage for thrust roller bearings for demonstrating a comparative example. It is sectional drawing of the cage for thrust roller bearings for demonstrating this invention. It is sectional drawing of the compressor for swash plate type car air conditioners containing the thrust roller bearing concerning this Embodiment. It is sectional drawing of the thrust roller bearing concerning 1st Embodiment. It is sectional drawing of the thrust roller bearing concerning 2nd Embodiment. It is sectional drawing of the thrust roller bearing concerning 3rd Embodiment. It is sectional drawing of the thrust roller bearing concerning 4th Embodiment. It is sectional drawing of the thrust roller bearing concerning 5th Embodiment.

Explanation of symbols

1 swash plate type compressor for car air conditioner 11, 12 race 13 cage 16 roller 10, 10A to 10D thrust roller bearing

Claims (4)

A thrust roller made of a single plate member formed with an inner annular portion, an outer annular portion located on the radially outer side of the inner annular portion, and a plurality of column portions connecting the inner annular portion and the outer annular portion. In bearing cages,
When the cross section of the thrust roller bearing is taken in the axial direction, of the pair of races holding the thrust roller bearing retainer in the axial direction, the race with the faster rotational speed than the race with the slower rotational speed. A thrust roller bearing cage, wherein an intermediate portion of the column portion is bent so as to be close to each other. When the average clearance between the outer annular portion is C1 and the average clearance between the inner annular portion is C3 with respect to the race in which the middle portion of the column portion is close, the following equation is established. The cage for a thrust roller bearing according to claim 1.
C1 <C3 (1) 3. The thrust roller bearing holding according to claim 2, wherein the following equation is established when an average clearance between the race in which the intermediate portion of the column portion is close and the intermediate portion is C <b> 2. vessel.
C1 <C2 <C3 (2) A thrust roller bearing comprising the thrust roller bearing retainer according to any one of claims 1 to 3, a race, and a rolling element.

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