JP2009162360A - Thrust roller bearing and its retainer - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust roller bearing capable of avoiding effect of eccentric rotation and securing oil passing properties and cooling performance of a roller contact part, and its retainer. <P>SOLUTION: The retainer 10 is composed of at least first/second retainer composing plates 11, 12, and a roller 4 is held by a pocket 13 aligned in the circumferential direction. The first retainer composing plate 11 has a cross section comprising flat parts 11a, 11b on inner/outer diameter sides, a center flat part 11c slanting from the respective flat parts 11a, 11b to the axial direction, and continuing parts 11d, 11e continuing from the respective flat parts 11a, 11b to the center flat part 11c. The second retainer composing plate 12 comprises a flat plate part 12a overlapping the respective flat parts 11a, 11b and folded-back parts 12b, 12c folded back from the inner/outer diameter sides. The flat parts 11a, 11b of the first retainer composing plate 11 are inserted between the folded-back parts 12b, 12c and the flat plate part 12a. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a thrust roller bearing used in an automobile transmission, a torque converter, a car air conditioner compressor, and the like, and a retainer thereof.

Thrust roller bearings used in torque converters are susceptible to eccentric rotation between the engine and transmission. Further, in thrust roller bearings for transmissions, misalignment occurs in the bearing mounting portion due to accumulation of tolerances of peripheral parts. For example, Patent Document 1 has a description that a conventional thrust roller bearing which is a two-piece type (box-shaped) cage has insufficient prevention of slippage, and Patent Document 3 has a conventional W There is a description that a short roller is dropped in a thrust roller bearing as a shape cage (M-type cage).
Specifically, a three-position integrated thrust roller bearing used in a torque converter or transmission, that is, two L-shaped hooked race rings 32 and 33 and rollers with cages (cage as shown in FIGS. 11 and 12). & Roller) cannot absorb an eccentricity larger than the radial clearance inside the bearing. Therefore, the cages 40 and 40A may be sandwiched between the flanges 32b and 33b of the both race rings 32 and 33, and the cages 40 and 40A may have a short life.

Also, as thrust roller bearings for transmissions, there are many types with only a cage and roller that do not require a race ring with the other part as a direct rolling surface in addition to those with a race ring as shown in FIGS. Although used, these bearings are required to have oil permeability in order to supply lubricating oil to the peripheral parts through the bearings.
Furthermore, since thrust roller bearings used in car air conditioner compressors are used under lean lubrication, there is a need for improved wear resistance and lubrication conditions. As a specific example, in order to obtain oil permeability for feeding lubricating oil to peripheral parts and cooling performance of roller contact portions (roller rolling surface, roller pair cage), the roller surface is exposed more from the cage. Is required. The reason why the roller contact portion needs to have a cooling performance is that when the roller contact portion generates heat, the viscosity of the lubricating oil is lowered, which results in poor oil film formation and poor lubrication.
If there is no countermeasure against such a problem, the following problems occur. For example, Patent Document 7 describes an example of damage in a thrust roller bearing used as a conventional two-piece type (tuftride treated product) cage, and Patent Document 11 describes a conventional two-piece type (box Type) Thrust roller bearings used as cages have a description of poor lubricity.

Various thrust roller bearings listed below have been proposed as countermeasures for solving the two problems of avoiding the influence of the eccentric rotation described above and ensuring the oil permeability and cooling performance of the roller contact portion (Patent Literature). 2, 4-6, 8, 9).
Patent Document 2: A structure in which a cage is prevented from being pinched against eccentricity.
Patent Document 4: A structure that absorbs a radial load with an elastic ring against eccentricity. Patent Document 5: A structure in which the guide surface with the raceway of the cage is a convex curved surface to improve lubricity. Patent Document 6: A structure that prevents the roller chamfered portion from entering the end face of the cage pocket. Patent Document 8: A measure for improving the lubricity of the pocket removal surface.
Patent Document 9: Structure having improved lubricity by using a W-shaped cage as a rolling element guide.
Japanese Patent No. 3900843 Japanese Patent No. 3692585 Japanese Patent No. 3661133 Japanese Patent No. 3632262 JP 2007-187207 A JP 2007-1000077 A JP 2006-189133 A JP 2005-83449 A JP 2003-106336 A JP 2002-339984 A JP 2002-70872 A

In conventional thrust roller bearings with three-way rings, which are bearings with bearing rings, the cage is caught between the rings of both bearing rings due to the fact that it cannot absorb the eccentricity larger than the radial clearance inside the bearing. As measures against the problems that occur, the structures disclosed in Patent Document 2 and Patent Document 4 have been proposed as described above.
However, these structures have an unavoidable increase in the size of the bearing, and if the size cannot be increased, the roller length is reduced (and the load capacity is reduced), thereby creating a space for establishing the structure. It is necessary to reduce the rated life.
Therefore, instead of reducing the roller length, it is required to increase the thickness of the cage, optimize the shape, or perform hardening treatment within the conventional dimensions to make a reinforced cage. It has been.

As described above, the thrust roller bearing retainer includes a two-piece (box-shaped) retainer 40 as shown in FIG. 11 and a W-shaped retainer 40A as shown in FIG. Since it is difficult to incorporate the rollers 34 by elastically deforming the conventional two-sheet type (box-type) cage 40, processing is performed in the order of heat treatment of the steel plate → roller assembly → bending (caulking). It is. 12 has a structure in which the rollers 34 are more exposed from the cage 40A than the box-type cage 40 of FIG. 11, and thus has a high cooling effect. However, with respect to the problems roughly divided into the above two, the conventional two-piece type (box type) cage 40 and W-type cage 40A have advantages and disadvantages as listed below. Balancing the advantages is extremely difficult.
Two-sheet type (box type) cage 40
(Advantages)
・ Since the cross-sectional shape is approximately square, it is strong against radial loads (clamped by cages 32 and 33).
-Since the cross-sectional shape is approximately square, even short rollers can be held.
(Cons)
-Since the rolls are crimped after heat treatment, cracks are likely to occur and the prevention of loosening is insufficient. (In Patent Document 1, there is a description that raw materials before quenching are easier to bend)
-For this reason, it is not suitable for improving wear resistance by carburizing and hardening and increasing the number of hardened layers.
-Since the rollers 34 are sandwiched and the rolls are crimped, it is necessary to strictly manage the parts and assembly accuracy in order to secure an appropriate gap, resulting in an increase in cost.
-The oil permeability is poor because the cross-sectional shape is approximately square.
W type cage (M type cage) 40A
(Advantages)
-The oil permeability is good (described in Patent Document 10), and the roller surface can be exposed more from the cage 40A, so the roller contact portion has a great cooling effect.
-Since heat treatment can be performed after foam molding, and subsequent plastic processing such as roll caulking is not required, carburizing and quenching, increasing the hardened layer, and surface treatment can be easily performed.
-Since high assembly accuracy is not required, it is also low in terms of roller assembly.
(Cons)
-Since a single plate is bent several times by pressing, the plate thickness decreases with respect to the original plate thickness.
・ The strength is low because the stress concentrates on the bent part with respect to the radial load (sandwiched).・ Roller 34 is easy to tilt and cannot hold short roller.

  An object of the present invention is to provide a thrust roller bearing that can avoid the influence of eccentric rotation and that is oil-permeable and can secure the cooling performance of a contact portion, and a cage for the same.

In the thrust roller bearing according to the present invention, the rollers are held in pockets provided at a plurality of locations in the circumferential direction in a cage including at least a first cage component plate and a second cage component plate that are axially overlapped with each other. The first cage component plate is a flat plate-shaped portion that is positioned on the inner diameter side and the outer diameter side and facing each other in the axial direction, and the outer diameter side flat portion and the outer diameter side flat portion, respectively. A central flat portion that is in the middle in the radial direction with respect to the inner diameter side flat portion and the outer diameter side flat portion and is axially offset, and an inner diameter side continuous from the outer peripheral edge of the inner diameter side flat portion to the inner peripheral edge of the central flat portion And the second retainer component plate is a first retainer component plate having a cross-sectional shape having an outer diameter side continuous portion continuing from the inner periphery of the outer diameter side flat portion to the outer periphery of the central flat portion. The first surface on the side opposite to the direction of bias of the central flat portion of A flat plate portion that overlaps the inner diameter side flat portion and the outer diameter side flat portion of the cage component plate, and an inner diameter side folded portion and an outer diameter side folded portion that are folded from the inner and outer peripheral edges of the flat plate portion, respectively. The inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate are respectively disposed between the inner diameter side folded portion and the flat plate portion and between the outer diameter side folded portion and the flat plate portion. It is characterized by being sandwiched.
According to this configuration, the second cage component plate is formed in a flat shape, and the first cage component plate is held by the inner diameter side folded portion and the outer diameter side folded portion. On the other hand, stress on the bent first retainer component plate is reduced. That is, since the second cage component plate does not have a bent portion like the first cage component plate, the second cage component plate is strong against a radial force. Because of the strong second cage component plate, the stress on the bent portion of the first cage component plate can be reduced, thereby avoiding a short life of the cage.
In particular, in a so-called three-piece integral type thrust roller bearing having two L-shaped raceways, the cage is held between inner and outer rings under rotational conditions with a unit eccentricity larger than the radial clearance inside the bearing. Although a radial load acts on the cage, as described above, the stress on the bent portion of the cage can be reduced without increasing the size of the bearing, so that the cage can be prevented from being damaged.
Further, the bent portion of the first cage component plate is not a complicated shape like the W-type cage in the conventional example, and the bending process by the press does not require a plurality of steps and only needs to be performed once. Therefore, the thickness of the bent portion hardly decreases with respect to the original plate thickness, and the stress on the bent portion can be further reduced.
In addition, the box-type cage and the W-type cage in the conventional thrust roller bearing have a substantially rectangular cross section, whereas the cross section of the cage in the thrust roller bearing has a substantially triangular shape. It is also possible to ensure a good oil permeability.
In addition, since the inner diameter side folded portion and the outer diameter side folded portion of the second cage component plate can be formed into an arcuate curved surface, when a three-position integral type thrust roller bearing is constructed, the cage and the inner and outer rings The inflow property of the lubricant to the contact surface is improved. Even when the thrust roller bearing is configured only by the cage that holds the roller, the inflow of the lubricant to the contact surface of the guide portion of the mating member that becomes the cage and the rolling surface is improved.
In addition, when a three-piece integrated thrust roller bearing, which is a bearing with two bearing rings, is configured by making the inner diameter side folded portion and the outer diameter side folded portion of the second cage component plate into an arcuate curved surface. The frictional resistance is reduced by reducing the contact area between the inner and outer diameter surfaces of the cage and the inner and outer rings, and the torque can be reduced. Even when a thrust roller bearing is configured with only a cage that holds the roller, the contact area between the cage and the guide portion of the mating member that becomes the rolling surface is reduced, so that frictional resistance is reduced and low torque is achieved. can do.
In addition, the structure of the cage can expose most of the surface of the roller from the cage as compared with the conventional box-type cage, so that the cooling effect of the roller contact portion is increased. As described above, the oil permeability and the lubrication performance such as the cooling effect of the contact portion can also prevent the life from being reduced due to wear or heat generation even under severe conditions such as lean lubrication.
By the above effects, the influence of eccentric rotation can be avoided, and the oil permeability can be ensured for the cooling performance of the contact portion.

In this invention, the first cage component plate and the second cage component plate are heat-treated products of steel plates, and the inner diameter side folded portion and the outer diameter side folded portion are subjected to crimping in an unheat treated state. The formed part may be sufficient.
In the case of this configuration, it is easy to perform the caulking process, and a large tightening force can be obtained. In addition, since heat treatment is performed after caulking, a wide range of wear resistance technologies such as carburizing and quenching, hardening layer upgrade, and surface treatment can be adopted as heat treatment, expanding the range of functions, costs, and productivity. . In addition, since the crimping process (plastic processing) can be performed before the hardening process by the heat treatment, it is not necessary to perform the roll crimping, and the processing time by the press crimping can be shortened.

  In the present invention, the first cage component plate and the second cage component plate are heat-treated products of steel plates, and each roller is incorporated into the heat-treated cage. good. That is, the cage is heat-treated before assembling the rollers. With this configuration, it is not necessary to crimp the cage while securing the appropriate gap between the rollers and the cage pocket while holding the rollers, so that high parts accuracy and assembly accuracy are not required, and assembly costs Can be prevented.

  In this invention, the pocket of the cage is formed by a pocket hole punched and formed in the first cage component plate by pressing and a pocket hole punched and formed in the second cage component plate by pressing. Thus, in the pocket holes of the first and second cage component plates, the return portions generated by the punching may be on the non-overlapping surface side. In the case of this configuration, it is possible to obtain a certain pocket gap without being affected by the return portion due to punching, and to stabilize the behavior of the cage.

  In this invention, the width dimension in the cage radial direction of the pocket hole of the second cage component plate is longer than the width dimension in the cage radial direction of the pocket hole of the first cage component plate constituting the pocket. You may do it. In the case of this configuration, a large amount of lubrication to the end face of the roller can be ensured. In this case, since the cage is structured to receive the end surface of the roller at the end surface along the circumferential direction of the cage of the pocket hole of the first cage component plate located near the roller axis, the inclination of the roller Therefore, even short rollers can be held.

  In this invention, the width dimension in the cage circumferential direction of the pocket hole of the first cage component plate is larger than the width dimension in the cage circumferential direction of the pocket hole of the second cage component plate constituting the pocket. May be lengthened.

  In this invention, the oil passage opening which is a part where the width dimension of the pocket hole in the circumferential direction of the pocket hole is locally increased at the edge portion along the radial direction of the pocket hole of the pocket hole of the second cage component plate May be provided. Thus, oil permeability can be improved by providing an oil passage port at the edge portion along the cage radial direction of the pocket hole of the second cage component plate.

In this invention, a flat raceway plate portion and an inner ring having a cylindrical portion extending from the inner peripheral edge of the raceway plate portion, a flat raceway plate portion facing the raceway plate portion of the inner race, and an outer peripheral edge of the raceway plate portion An outer ring having a cylindrical portion extending from the inner ring to the inner ring side, the retainer, and the rollers, and each roller held by the retainer is interposed between the inner ring and the raceway plate portion of the outer ring, and is eccentric with each other. A thrust roller bearing in which the inner ring and the outer ring are supported by a pair of rotating bearing ring support members, respectively, an outer diameter side gap that is a gap between the outer peripheral surface of the cage and the cylindrical portion of the outer ring, and At least one of the inner diameter side gaps, which are gaps between the inner peripheral surface of the cage and the cylindrical portion of the inner ring, may be larger than the eccentric amount of the pair of bearing ring support members.
In a three-piece integral type thrust roller bearing having two L-shaped raceways in a radial direction, the cage is held in the radial direction by being sandwiched between inner and outer rings under rotational conditions with a unit eccentricity larger than the radial clearance inside the bearing. Load acts. In the case of the above configuration, since the radial clearance in the bearing is larger than the unit eccentricity (the eccentricity of the pair of bearing ring support members), the cage is not sandwiched between the inner and outer rings, and is caused by the eccentricity. Generation of a radial load on the cage can be prevented.

The thrust roller bearing retainer according to the present invention includes at least a first retainer constituting plate and a second retainer constituting plate that are axially overlapped with each other, and a plurality of pockets in which a plurality of rollers are respectively held in a circumferential direction. The first roller constituting plate is provided on the inner diameter side and the outer diameter side of each of the first retainer constituting plates, and each of the inner diameter side flat portion is a flat plate portion facing the axial direction. An outer diameter side flat portion, a central flat portion that is radially intermediate to the inner diameter side flat portion and the outer diameter side flat portion, and is offset in the axial direction, and continues from the outer peripheral edge of the inner diameter side flat portion to the central flat portion. The second cage component plate has a cross-sectional shape having an inner diameter side continuous portion and an outer diameter side continuous portion continuing from the inner periphery of the outer diameter side flat portion to the outer periphery of the central flat portion. Surface opposite to the direction of bias of the central flat part of the plate A flat plate portion that overlaps the inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate, and an inner diameter side folded portion and an outer diameter side folded portion that are folded from the inner and outer peripheral edges of the flat plate portion, respectively. Between the inner diameter side folded portion and the flat plate portion and between the outer diameter side folded portion and the flat plate portion, the inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate It is characterized by sandwiching each part.
According to this configuration, the influence of eccentric rotation can be avoided, and the oil permeability can be ensured for the cooling performance of the contact portion.

In the thrust roller bearing according to the present invention, the rollers are held in pockets provided at a plurality of locations in the circumferential direction in a cage including at least a first cage component plate and a second cage component plate that are axially overlapped with each other. The first cage component plate is a flat plate-shaped portion that is positioned on the inner diameter side and the outer diameter side and facing each other in the axial direction, and the outer diameter side flat portion and the outer diameter side flat portion, respectively. A central flat portion that is in the middle in the radial direction with respect to the inner diameter side flat portion and the outer diameter side flat portion and is axially offset, and an inner diameter side continuous from the outer peripheral edge of the inner diameter side flat portion to the inner peripheral edge of the central flat portion And the second retainer component plate is a first retainer component plate having a cross-sectional shape having an outer diameter side continuous portion continuing from the inner periphery of the outer diameter side flat portion to the outer periphery of the central flat portion. The first surface on the side opposite to the direction of bias of the central flat portion of A flat plate portion that overlaps the inner diameter side flat portion and the outer diameter side flat portion of the cage component plate, and an inner diameter side folded portion and an outer diameter side folded portion that are folded from the inner and outer peripheral edges of the flat plate portion, respectively. The inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate are respectively disposed between the inner diameter side folded portion and the flat plate portion and between the outer diameter side folded portion and the flat plate portion. Since the cage has been sandwiched, the rigidity of the cage is increased, the strength can be secured against the cage being pinched by the inner and outer ring ridges at the time of eccentric rotation, and the oil-permeable property can ensure the cooling performance of the contact portion.
Since the thrust roller bearing retainer of the present invention sandwiches the inner diameter side flat portion and the outer diameter side flat portion of the first retainer constituting plate in the same manner as the thrust roller bearing of the present invention, it is affected by the eccentric rotation. Can be avoided, and the oil permeability is sufficient to ensure the cooling performance of the contact portion.

An embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a cross-sectional view of the thrust roller bearing of this embodiment. The thrust roller bearing 1 includes an annular inner ring 2 that is one of the race rings, an annular outer ring 3 that is the other race ring disposed concentrically with the inner ring 2, an annular cage 10, and rollers 4. Is provided. The inner ring 2 has an L-shaped cross section having a flat track plate portion 2a and a cylindrical portion 2b extending from the inner periphery of the track plate portion 2a. The outer ring 3 has an inverted L-shaped cross section having a flat track plate portion 3a facing the track plate portion 2a of the inner ring 2 and a cylindrical portion 3b extending from the outer peripheral edge of the track plate portion 3a to the inner ring 2 side. ing. Between the raceway plate portions 2 a and 3 a of the inner ring 2 and the outer ring 3, the rollers 4 held by the cage 10 are interposed.
The roller 4 is prevented from falling off the cage 10 as will be described later, and the cage 10 and each roller 4 constitute a roller 20 with a cage. The inner ring 2 and the outer ring 3 are provided with engaging projections 2ba and 3ba projecting toward the roller arrangement portion at the tips of the cylindrical portions 2b and 3b at a plurality of positions in the circumferential direction. By engaging 2ba and 3ba with the cage 10, the three-way integral thrust bearing 1 in which the roller with cage 20 and the inner and outer rings 2 and 3 are not separated is formed.
The thrust bearing in FIG. 10 is supported by the inner ring 2 and the outer ring 3 being in contact with the opposing surfaces of a pair of bearing ring support members 5 and 6 that rotate eccentrically with each other. For example, one bearing ring support member 5 is fixed, and the other bearing ring support member 6 performs an eccentric rotation in which the center O2 is eccentric by an eccentric amount e with respect to the rotation center O1. Examples of such bearing ring support members 5 and 6 include a fixed scroll member and an eccentric rotation scroll member in a scroll pump.

  FIG. 2 is an enlarged cross-sectional view of a portion where the pocket 13 is formed in the cage 10, and FIG. 3 is a cross-sectional view of the cage 10 holding the rollers 4. The cage 10 is composed of at least an annular first cage component plate 11 and a second cage component plate 12 that are axially overlapped with each other, and each roller 13 is inserted into each pocket 13 provided at a plurality of locations in the circumferential direction. Is retained.

  The first cage component plate 11 has a cross-sectional shape including an inner diameter side flat portion 11a, an outer diameter side flat portion 11b, a central flat portion 11c, an inner diameter side continuous portion 11d, and an outer diameter side continuous portion 11e. Has been. The inner diameter side flat portion 11a and the outer diameter side flat portion 11b are flat plate portions that are located on the inner diameter side and the outer diameter side, respectively, and that face in the axial direction. The central flat part 11c is a flat plate-like part located in the middle of the radial direction with respect to the inner diameter side flat part 11a and the outer diameter side flat part 11b and being offset in the axial direction. The inner diameter side continuous portion 11d is an inclined portion that continues from the outer peripheral edge of the inner diameter side flat portion 11a to the inner peripheral edge of the central flat portion 11c. The outer diameter side continuous portion 11e is an inclined portion that continues from the outer peripheral edge of the central flat portion 11c to the inner peripheral edge of the outer flat side portion 11b.

  The second cage component plate 12 has a cross-sectional shape including a flat plate portion 12a, an inner diameter side folded portion 12b, and an outer diameter side folded portion 12c. The flat plate portion 12a is a surface opposite to the biasing direction of the central flat portion 11c of the first retainer constituting plate 11, and extends over the inner diameter side flat portion 11a and the outer diameter side flat portion 11b of the first retainer constituting plate 11. It is an overlapping part. The inner diameter side folded portion 12b is a portion having a shape folded from the inner peripheral edge of the flat plate portion 12a. The outer diameter side folded portion 12c is a portion having a shape folded from the outer peripheral edge of the flat plate portion 12a. The inner diameter side flat portion 11a of the first cage constituting plate 11 is sandwiched between the inner diameter side folded portion 12b and the flat plate portion 12a. Further, the outer diameter side flat portion 11b of the first cage constituting plate 11 is sandwiched between the outer diameter side folded portion 12c and the flat plate portion 12a. Here, the corners of the inner diameter side folded portion 12b and the outer diameter side folded portion 12c are arcuate, but the entire inner diameter side folded portion 12b and outer diameter side folded portion 12c are semicircular as shown in FIG. 7, for example. You may make it become.

  The first cage component plate 11 and the second cage component plate 12 are heat-treated products of steel plates, and the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 are not yet formed. It is a portion formed by caulking in a heat treatment state. The rollers 4 are incorporated into the cage 10 that has been heat-treated in this manner. FIG. 6 shows a cross-sectional view of the cage 10 holding the rollers 4 in the circumferential direction of the cage.

As shown in FIG. 2, the pockets 13 of the cage 10 that holds the rollers 4 are formed in a pocket hole 14 formed by stamping the first cage component plate 11 and the second cage component plate 12. It consists of pocket holes 15 formed by stamping. The pocket holes 14 and 15 of the first and second cage constituting plates 11 and 12 are formed by punching by press working using a punching die (not shown). When shearing is performed using a press die, as shown in FIG. 6 (B), the processed surface is from the insertion side of the press die, the drooping portion a, the shearing surface portion b, the fracture surface portion c, and the return portion d. Occurs. In this embodiment, the pocket holes 14 and 15 are punched from the overlapping surface side to the non-overlapping surface side so that the return portions d are on the non-overlapping surface side.
In FIG. 2, at the intermediate position of the edge portion along the radial direction of the cage in the pocket hole 14 of the first cage component plate 11 (the portion corresponding to the central flat portion 11 c), the roller 4 forms the first cage. A roller drop prevention portion 14 a that prevents the plate 11 from falling off is formed in the pocket hole 14 so as to protrude.

  4 shows a plan view of the pocket 13 seen from the direction of arrow A in FIG. 2, and FIG. 5 shows a plan view of the pocket 13 seen from the direction of arrow B in FIG. The width dimension L2 in the cage radial direction of the pocket hole 15 of the second cage component plate 12 constituting the pocket 13 is larger than the width dimension L1 in the cage radial direction of the pocket hole 14 of the first cage component plate 11. Has also been long. Further, the width dimension P1 in the cage circumferential direction of the pocket hole 14 of the first cage component plate 11 is larger than the width dimension P2 in the cage circumferential direction of the pocket hole 15 of the second cage component plate 12. Have been long. By setting the circumferential width dimensions P1 and P2 of the pocket holes 14 and 15 in this way, as shown in FIG. 6, the inner edge of the drop-out preventing portion 14a of the pocket hole 14 and the cage of the pocket hole 15 are obtained. The roller 4 is prevented from coming off from the cage 10 with the inner edge of the edge along the radial direction.

  Further, at the edge portion of the pocket hole 15 of the second cage component plate 12 along the cage radial direction, for example, as shown in FIG. 8 showing a plan view of the pocket 13 seen from the direction of arrow A in FIG. An oil passage port 15a that is a portion in which the width of the pocket hole 15 in the cage circumferential direction is locally increased may be provided. Further, the oil passage port 15a may be plural as shown in FIG. Thus, by providing the oil passage port 15a at the edge of the pocket hole 15 along the radial direction of the cage, the oil permeability can be improved.

  In this embodiment, as shown in FIG. 1, a three-position integral type thrust roller bearing 1 including the cage 10 holding the roller 4, the inner ring 2, and the outer ring 3 is configured. A cage and roller type thrust roller bearing may be configured only by the held cage 10, that is, by only the roller with cage 20. In this case, as indicated by phantom lines in FIG. 2, both members 7, 8 are arranged such that a pair of mating members 7, 8 that are arranged opposite to each other in the axial direction and rotate relative to each other become rolling surfaces that the rollers 4 contact. The cage 10 is disposed between them.

  According to the thrust roller bearing 1 having this configuration, the second cage component plate 12 is formed into a flat shape, and the first cage component plate 11 is held by the inner diameter side folded portion 12b and the outer diameter side folded portion 12c. Therefore, the stress on the bent first retainer constituting plate 11 is reduced with respect to the load in the radial direction. That is, since the second cage component plate 12 does not have a bent portion like the first cage component plate 11, it is strong against a radial force. This strong second cage component plate 12 can reduce the stress on the bent portion of the first cage component plate 11, thereby avoiding a short life of the cage.

  In particular, in the thrust roller bearing 1 with a bearing ring configured as shown in FIG. 1, it is sandwiched between the cylindrical portions 2 b and 3 b of the inner and outer rings 2 and 3 under a rotational condition with a unit eccentric amount larger than the radial clearance inside the bearing. As a result, a radial load is applied to the cage 10. However, as described above, the stress on the bent portion of the cage 10 can be reduced without increasing the size of the bearing. Can be prevented.

  Further, the bent portion of the first cage constituting plate 11 is not a complicated shape like the W-type cage 40A in the conventional example shown in FIG. 12, for example, and a plurality of steps are required for bending by press. Since the bending step is small, the bending thickness is hardly reduced with respect to the original thickness (90% of the thickness before pressing) as illustrated in FIG. more than). As a result, the stress on the bent portion can be further reduced.

  Further, the box type cage 40 and the W type cage 40A in the conventional thrust roller bearing illustrated in FIGS. 11 and 12 have a substantially rectangular cross section, whereas the cross section of the cage 10 in the thrust roller bearing 1 is shown. Since it has a substantially triangular shape, sufficient oil permeability can be secured.

  Further, the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 can be formed into an arcuate curved surface as shown in FIG. 2 and FIG. When the thrust roller bearing 1 is configured, the flowability of the lubricant into the contact surface between the cage 10 and the inner and outer rings 2 and 3 is improved. As shown by the phantom line in FIG. 2, even when the thrust roller bearing is configured only by the cage 10 holding the roller 4, the guide portions 7 a and 8 a of the mating members 7 and 8 that become the rolling surface and the rolling surface of the cage 10 The inflow property of the lubricant to the contact surface is improved.

  In addition, when the inner roller side folded portion 12b and the outer radius side folded portion 12c of the second cage component plate 12 are formed in an arcuate curved surface, when the three-position integrated thrust roller bearing 1 is configured as shown in FIG. The frictional resistance is reduced by reducing the contact area between the inner and outer diameter surfaces of the cage 10 and the inner and outer rings 2 and 3, and the torque can be reduced. As shown in FIG. 2, even when a thrust roller bearing is configured by only the cage 10 holding the roller 4, the contact area between the cage 10 and the guide portions 7a and 8a of the mating members 7 and 8 serving as rolling surfaces is reduced. By reducing the frictional resistance, the torque can be reduced.

  Further, when the three-piece integrated thrust roller bearing 1 is configured as shown in FIG. 1 by making the inner diameter side folded portion 12b and the outer diameter side folded portion 12c of the second cage component plate 12 into an arcuate curved surface, The built-in force in the engagement utilizing the elastic displacement of the cage 10 with the inner and outer rings 2 and 3 can be reduced, and deformation and cracking can be prevented.

  Further, the structure of the cage 10 can expose most of the surface of the roller 4 from the cage 10 as compared with the conventional box-type cage, so that the cooling effect of the roller contact portion is increased. As described above, the oil permeability and the lubrication performance such as the cooling effect of the contact portion can also prevent the life from being reduced due to wear or heat generation even under severe conditions such as lean lubrication.

Moreover, in this embodiment, the 1st and 2nd cage component plates 11 and 12 of the cage 10 are made of heat-treated products of steel plates, and the inner diameter side folded portion 12b and the outer diameter side of the second cage component plate 12 are used. Since the folded portion 12c is a portion formed by crimping in an unheated state (uncured state), it is easy to crimp and can obtain a large tightening force, and can prevent sufficient loosening. is there.
In addition, since heat treatment is performed after caulking, a wide range of wear resistance technologies such as carburizing and quenching, hardening layer upgrade, and surface treatment can be adopted as heat treatment, expanding the range of functions, costs, and productivity. .
In addition, since the crimping process (plastic processing) can be performed before the hardening process by the heat treatment, it is not necessary to perform the roll crimping, and the processing time by the press crimping can be shortened.

  Further, in this embodiment, since the roller 4 is incorporated into the heat-treated cage 10, the cage is secured while securing an appropriate gap between the roller 4 and the pocket 13 of the cage 10 with the roller 4 being sandwiched. It is not necessary to perform 10 caulking, so that high component accuracy and assembly accuracy are not required, and an increase in assembly cost can be suppressed.

  Moreover, in this embodiment, the pocket 13 of the cage 10 is composed of pocket holes 14 and 15 formed by stamping the first and second cage component plates 11 and 12, and each of these pocket holes. Nos. 14 and 15 are not affected by the return part due to shearing, because the return parts caused by shearing by punching are pressed from the side where the rollers 4 come into contact with each other so that the return parts are non-overlapping surfaces. Pocket space can be obtained, and the behavior of the cage 10 can be stabilized.

  Further, in this embodiment, the width dimension L2 in the cage radial direction of the pocket hole 15 of the second cage component plate 12 constituting the pocket 13 of the cage 10 is set to the pocket hole of the first cage component plate 11. 14 is longer than the width dimension L1 in the radial direction of the cage, so that a large amount of lubrication to the end face of the roller 4 can be secured. In this case, the cage 10 has a structure that receives the end surface of the roller 4 at the end surface along the circumferential direction of the cage of the pocket hole 14 of the first retainer constituting plate 11 at a position close to the axis O of the roller 4. Therefore, the inclination of the roller 4 can be suppressed, and even a short roller can be held.

  FIG. 10 shows another embodiment of the present invention. The thrust roller bearing 1 of this embodiment is a three-piece integral type thrust roller bearing 1 shown in FIG. 1, and an outer diameter side gap g1 that is a gap between the outer peripheral surface of the cage 10 and the cylindrical portion 3b of the outer ring 3. In addition, at least one of the inner diameter side gap g2 that is a gap between the inner peripheral surface of the cage 10 and the cylindrical portion 2b of the inner ring 2 is used as an eccentricity amount e of the pair of bearing ring support members 5 and 6. Is larger than Other configurations are the same as those in the embodiment of FIG.

  A three-piece integrated thrust roller bearing having inner and outer rings 2 and 3 is sandwiched between the cylindrical portions 2b and 3b of the inner and outer rings 2 and 3 under a rotational condition with a unit eccentricity e larger than the radial clearance inside the bearing. As a result, a radial load acts on the cage 10. In this embodiment, since the radial clearance in the bearing is larger than the unit eccentric amount (the eccentric amount e of the pair of bearing ring support members 5 and 6), the cage 10 has the inner and outer rings 2 and 3 in the above configuration. It is possible to prevent occurrence of a radial load on the cage 10 due to eccentricity without being sandwiched between the cylindrical portions 2b and 3b.

It is sectional drawing of the thrust roller bearing concerning one Embodiment of this invention. It is sectional drawing of the pocket formation part of the holder | retainer in the thrust roller bearing. It is sectional drawing of a roller holding state. It is sectional drawing of the roller holding | maintenance state of the cage. FIG. 3 is a plan view of a cage pocket viewed from the direction of arrow A in FIG. 2. FIG. 3 is a plan view of a cage pocket viewed from the direction of arrow B in FIG. 2. It is sectional drawing which cut the roller holding | maintenance part of the holder | retainer along the holder circumferential direction, and the expanded sectional view of the one part. It is sectional drawing which shows the other example of a holder | retainer. It is a top view which shows the other example of a holder | retainer pocket. It is a top view which shows the further another example of a holder | retainer pocket. It is sectional drawing of the thrust roller bearing concerning other embodiment of this invention. It is sectional drawing of a prior art example. It is sectional drawing of another prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Thrust roller bearing 2 ... Inner ring 2a ... Raceway disk part 2b ... Cylindrical part 3 ... Outer ring 3a ... Raceway plate part 3b ... Cylindrical part 4 ... Roller 5, 6 ... Bearing ring support member 10 ... Cage 11 ... 1st holding | maintenance Plate 11a ... Inner diameter side flat portion 11b ... Outer diameter side flat portion 11c ... Central flat portion 11d ... Inner diameter side continuous portion 11e ... Outer diameter side continuous portion 12 ... Second cage component plate 12a ... Flat plate portion 12b ... Inner diameter Side folded portion 12c ... Outer diameter side folded portion 13 ... Pocket 14, 15 ... Pocket hole 15a ... Oil passage g1 ... Outer diameter side gap g2 ... Inner diameter side gap

Claims (9)

A thrust roller bearing in which rollers are held in respective pockets provided at a plurality of circumferential positions in a cage composed of at least a first cage component plate and a second cage component plate that are axially overlapped with each other,
The first retainer constituting plate is a flat plate-shaped portion positioned on the inner diameter side and the outer diameter side and facing each other in the axial direction, the inner diameter side flat portion and the outer diameter side flat portion, and the inner diameter side flat portion and the outer portion. A central flat portion that is in the middle of the radial direction with respect to the radial side flat portion and is offset in the axial direction, an inner diameter side continuous portion that extends from the outer peripheral edge of the inner diameter side flat portion to the inner peripheral edge of the central flat portion, and the outer diameter side flat portion Is a cross-sectional shape having an outer diameter side continuous portion continuing from the inner peripheral edge to the outer peripheral edge of the central flat portion,
The second cage component plate overlaps the inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate on a surface opposite to the biasing direction of the central flat portion of the first cage component plate. A flat plate portion, and an inner diameter side folded portion and an outer diameter side folded portion that are folded from the inner and outer peripheral edges of the flat plate portion, respectively, and between the inner diameter side folded portion and the flat plate portion, and the outer diameter A thrust roller bearing characterized in that the inner diameter side flat portion and the outer diameter side flat portion of the first cage constituting plate are sandwiched between a side folded portion and the flat plate portion, respectively.   2. The first cage component plate and the second cage component plate according to claim 1, wherein the first cage component plate and the second cage component plate are heat treated products of steel plates, and the inner diameter side folded portion and the outer diameter side folded portion are crimped in an unheat treated state. Thrust roller bearing which is a part formed by.   The first retainer constituting plate and the second retainer constituting plate according to claim 1 or 2, wherein the first retainer constituting plate and the second retainer constituting plate are heat treated products of steel plates, and the rollers are incorporated in the heat treated retainer. Thrust roller bearing.   4. The pocket of the retainer according to claim 1, wherein the pocket of the retainer is formed by punching and punching the first retainer component plate and the second retainer component plate. This is a thrust roller bearing comprising pocket holes formed by punching, and the pocket holes of the first and second cage component plates have return portions that are non-overlapping surfaces of each other by punching.   The pocket hole of the second cage component plate according to any one of claims 1 to 4, wherein the pocket hole of the second cage component plate has a width dimension in the radial direction of the cage of the pocket hole of the first cage component plate constituting the pocket. Thrust roller bearing with a longer width in the radial direction of the cage.   The pocket of the first cage component plate according to any one of claims 1 to 5, wherein a pocket dimension of the pocket hole of the second cage component plate constituting the pocket is larger than a width dimension of the cage circumferential direction. Thrust roller bearing with a longer width in the circumferential direction of the cage.   7. The width dimension in the cage circumferential direction of the pocket hole is locally determined at an edge of the pocket hole of the second cage component plate along the radial direction of the cage in any one of claims 1 to 6. Thrust roller bearing with an oil passage opening, which is an enlarged part.   8. A flat raceway according to claim 1, wherein the inner race has a flat raceway plate portion and a cylindrical portion extending from the inner peripheral edge of the raceway plate portion, and the flat raceway facing the raceway plate portion of the inner race. An outer ring having a plate part and a cylindrical part extending from the outer peripheral edge of the raceway plate part to the inner ring side, the cage, and the roller, and held by the cage between the raceway plate parts of the inner ring and the outer ring A thrust roller bearing in which the inner ring and the outer ring are respectively supported by a pair of bearing ring support members that are eccentrically rotated with each other interposed between the outer peripheral surface of the cage and the cylindrical portion of the outer ring. At least one of the outer diameter side clearance that is a clearance of the inner ring and the inner diameter side clearance that is the clearance between the inner peripheral surface of the cage and the cylindrical portion of the inner ring. Thrust cylinder larger than eccentricity Bearing. A thrust roller bearing retainer comprising at least a first retainer component plate and a second retainer component plate that are axially overlapped with each other, and pockets in which a plurality of rollers are respectively held are provided at a plurality of circumferential positions. There,
The first retainer constituting plate is a flat plate-shaped portion positioned on the inner diameter side and the outer diameter side and facing each other in the axial direction, the inner diameter side flat portion and the outer diameter side flat portion, and the inner diameter side flat portion and the outer portion. A central flat portion that is in the middle of the radial direction with respect to the radial side flat portion and is offset in the axial direction, an inner diameter side continuous portion that continues from the outer peripheral edge of the inner diameter side flat portion to the central flat portion, and the inner peripheral edge of the outer diameter side flat portion Is a cross-sectional shape having an outer diameter side continuous portion continuing from the outer peripheral edge of the central flat portion,
The second cage component plate overlaps the inner diameter side flat portion and the outer diameter side flat portion of the first cage component plate on a surface opposite to the biasing direction of the central flat portion of the first cage component plate. A flat plate portion, and an inner diameter side folded portion and an outer diameter side folded portion that are folded from the inner and outer peripheral edges of the flat plate portion, respectively, and between the inner diameter side folded portion and the flat plate portion, and the outer diameter A thrust roller bearing retainer, wherein the inner diameter side flat portion and the outer diameter side flat portion of the first retainer constituting plate are sandwiched between a side folded portion and the flat plate portion, respectively.

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