JP4661424B2 - Rotation support - Google Patents

Description

  The present invention relates to an improvement in a rotation support portion for rotatably supporting a gear with respect to a main shaft of an automobile transmission, for example.

  Conventionally, for example, structures as described in Patent Documents 1 and 2 are widely known as a structure of a rotation support portion that rotatably supports a gear on a main shaft incorporated in an automobile transmission. FIG. 14 shows an example of the structure described in Patent Document 2 among them. The shaft member 1 includes a shaft main body 2 and a pair of flange members 3 a and 3 b that are separate from the shaft main body 2 and are externally fitted and fixed to the shaft main body 2. The mutually opposing surfaces of the flange members 3a and 3b are flat surfaces 4a and 4b orthogonal to the central axis of the shaft body 2, and the outer peripheral surface of the shaft body 2 is formed between the flat surfaces 4a and 4b. The intermediate portion 5 located between them has a cylindrical surface centered on the central axis. Further, a gear 6, which is a ring body described in the scope of claims, is disposed around the portion 5.

A thickness T ₆ in the axial direction of the gear 6 is smaller than a distance D ₄ between the flat surfaces 4 a and 4 b (T ₆ <D ₄ ), and an inner diameter r _{6 of the} gear 6 is equal to that of the intermediate portion 5. It is larger than the outer diameter d ₅ (r ₆ > d ₅ ). A radial roller bearing 7 is inserted between the inner peripheral surface of these gears 6 and the outer peripheral surface of the interspace 5 between the axial end surfaces 8a, 8b of the gear 6 and the flat surfaces 4a, 4b. By providing roller bearings 9a and 9b, the gear 6 can be freely rotated with respect to the shaft member 1. Regarding the radial roller bearing 7, the inner peripheral surface of the gear 6 is an outer ring raceway, and the outer peripheral surface of the intermediate portion 5 is an inner ring raceway. Further, with respect to the thrust roller bearings 9a and 9b, the axial end faces 8a and 8b of the gear 6 themselves are used as thrust raceways.

  Of the roller bearings 7, 9 a, 9 b, the radial roller bearing 7 includes a plurality of radial rollers 10 each having a central axis arranged in parallel with the central axis of the shaft member 1, and a cylindrical radial cage 11. It can be held freely by rolling. The thrust roller bearings 9a and 9b are configured such that a plurality of thrust rollers 12a and 12b each having a central axis arranged in the diametrical direction of the gear 6 can be rolled by ring-shaped thrust retainers 13a and 13b. Hold it. The thrust roller bearings 9a and 9b are respectively provided with thrust traces 14a and 14b, and the thrust traces 14a and 14b are brought into contact with the flat surfaces 4a and 4b.

  Further, bent portions 15a and 15b which are bent in the directions approaching each other are formed on the inner peripheral edge portions of both the thrust traces 14a and 14b. Then, both axial end edges of the radial cage 11 are at the leading edges of the two bent portions 15a and 15b, and the inner peripheral edges of the thrust cages 13a and 13b are at the outer peripheral surfaces of the both bent portions 15a and 15b, respectively. It is in sliding contact or close proximity. The cages 11, 13a, 13b are prevented from interfering with each other so that the functions of the roller bearings 7, 9a, 9b are not impaired by the interference.

  In the case of the conventional structure shown in FIG. 14 described above, both the thrust traces 14a and 14b are indispensable in order to prevent interference between the cages 11, 13a and 13b. On the other hand, in the recent trend of reducing the size and weight of automobile parts, it has been considered to omit the race for the rotation support portion inside the automobile transmission. In this case, it is not possible to employ an interference prevention structure between the cages 11, 13a, 13b by the races 14a, 14b. In this case, as shown in FIG. 15, if the flange portion 16 is an integral structure with the shaft main body 2a constituting the shaft member 1a, a part of the shaft main body 2a is similar to the left portion of FIG. By forming the stepped portion 17, it is possible to prevent interference between the radial cage 11 and any of the thrust cages 13a. However, even in this case, the other flange member 3c needs to be separated from the shaft body 2a in order to assemble the gear 6, so that the right portion of FIG. It is difficult to provide such a structure for preventing interference.

  As shown in the right part of FIG. 15, when the structure for preventing interference between the retainers 11 and 13b is not provided, for example, as shown in FIG. 16, the axial end edge of the radial retainer 11 is a thrust retainer. There is a possibility that the thrust retainer 13b is inclined by striking a portion closer to the inner diameter of one side surface of the axial direction 13b (the left side surface in FIG. 16). When the thrust retainer 13b is inclined, the inner peripheral edge of the pocket provided in the thrust retainer 13b and the rolling surface of each thrust roller 12b come into strong friction with each other, and the thrust roller bearing 9b. Rotational resistance (dynamic torque) increases significantly. As a result, not only does the power loss within the automobile transmission increase, but it may cause damage such as seizure if it is significant. Although not shown, the axial length of the radial cage is increased and the inner diameter of the thrust cage is increased so that the axial end of the radial cage enters the inner diameter side of the thrust cage. The structure to be made is also considered. In the case of such a structure, the radial retainer tilts due to interference caused by the radial displacement of the thrust retainer, and the dynamic torque of the radial roller bearing increases, resulting in the same problem.

  In order to prevent this inconvenience, as shown in FIG. 17, a spacer 18 is externally supported (fixed or rotated freely) in a part of the shaft body 2a adjacent to one side surface of the flange member 3c in the axial direction. Fit). Such a spacer 18 is installed, and the axial end edge of the radial retainer 11 is slidably contacted or brought close to one axial surface of the spacer 18 and the inner peripheral edge of the thrust retainer 13b is contacted with the outer peripheral surface of the spacer 18, respectively. If facing each other, the cages 11 and 13b can be prevented from interfering with each other. However, in the case of such a structure shown in FIG. 17, the spacer 18 must be manufactured and assembled. The spacer 18 is a member provided only for preventing interference between the cages 11 and 13b, and the necessity of manufacturing and assembling such a member causes an increase in cost. Although the spacer 18 may be integrated with the flange member 3c to reduce the number of parts, the manufacturing operation becomes complicated and causes an increase in cost.

JP-A-2-163509 JP-A-6-213230

  In view of the circumstances as described above, the present invention realizes a structure capable of preventing an increase in dynamic torque based on interference between both radial and thrust cages without using a separate member necessary only for preventing interference. Invented accordingly.

Each of the rotation support portions of the present invention includes a shaft member, an annular body, a radial roller bearing, and a thrust roller bearing.
Among these, the shaft member has an outer peripheral surface shape in which a large diameter portion and a small diameter portion are continuous at a stepped portion.
The ring body has an inner diameter larger than the outer diameter of the small-diameter portion of the shaft member, and is arranged around the shaft member, and the inner peripheral surface itself is a cylindrical outer ring raceway .
Further, the radial roller bearing has a plurality of cores arranged between the inner peripheral surface of the ring body and the outer peripheral surface of the small diameter portion in a state where the respective central axes are arranged in parallel with the central axis of the shaft member. A radial roller is rotatably held by a cylindrical radial cage disposed in a cylindrical space between the two peripheral surfaces.
Further, the thrust roller bearing includes a plurality of thrust rollers arranged between the axial end surface of the ring body and the stepped portion in a state where the respective central axes are arranged in the diameter direction of the ring body. It is rotatably held by an annular thrust cage disposed between the end face in the axial direction and the stepped portion.
And the relative rotation of the said shaft member and the said ring body is made free.

In particular, in the rotation support portion described in claims 1 and 2 , the inner diameter of the thrust cage is made smaller than the outer diameter of the radial cage. In the first and second aspects of the invention, in order to hold the thrust rollers for rolling, the opening edges of pockets provided at a plurality of locations in the circumferential direction of the thrust retainer and the thrusts are provided. The thrust retainer is positioned in the axial direction by engagement with the rolling surface of the roller.
Furthermore, in the case of the invention described in claim 1, by projecting at least a portion closer to the inner diameter of one side of the axial direction of the thrust retainer toward the stepped portion than a portion in the middle of the radial direction or a portion closer to the outer diameter, The position of the thrust retainer is regulated by the raceway guide by causing the inner diameter portion and the stepped portion to be in sliding contact or in close proximity to each other.
On the other hand, in the case of the invention described in claim 2, a part of the step portion is projected toward a portion closer to the inner diameter of one axial surface of the thrust retainer to form a convex portion. The position of the thrust retainer is regulated by the raceway guide by causing the shift portion and the convex portion of the stepped portion to slidably contact or closely face each other.

In the rotation support portion described in claim 3, the inner diameter of the thrust cage is made larger than the outer diameter of the radial cage. At the same time, the axial length of the radial cage is set such that one end thereof does not come out from the inner diameter side of the thrust cage regardless of the axial displacement of the radial roller bearing. The inner circumferential surface of the thrust cage and the outer circumferential surface of the end portion of the radial cage are in direct sliding contact or in close proximity to each other.
Further, in the case of the rotation support portion described in claim 3, in order to hold the radial rollers in a freely rolling manner, opening edges of pockets provided at a plurality of locations in the circumferential direction of the radial cage and the radials are provided. The radial retainer is positioned in the radial direction by engagement with the rolling surface of the roller. At the same time, among the axial ends of the radial cage, the inner circumferential surface of one end existing on the inner diameter side of the thrust cage is protruded toward the outer circumferential surface of the shaft member as compared with the axial middle portion or the other end portion. Thus , the attitude of the radial cage is regulated by the inner ring guide by making the inner peripheral surface of the one end and the outer peripheral surface slidably contact or close to each other.

Any rotation support portion of the present invention configured as described above can prevent an increase in dynamic torque due to interference between the radial and thrust cages without using a separate member necessary only for preventing interference.
First, in the case of the invention described in claims 1 and 2 , when the radial cage is displaced in the axial direction due to skew or the like, the axial end edge of the radial cage is It hits the inner diameter side of one side in the axial direction. Even in this state, since the attitude of the thrust cage is regulated by the raceway guide, the thrust cage does not tilt. For this reason, the inner peripheral edge of the pocket provided in the thrust cage and the rolling surface of each thrust roller do not rub against each other, and the rotational resistance (dynamic torque) of the thrust roller bearing does not increase. The reaction force applied from the thrust cage to the radial cage along with the abutment is applied in parallel to the axial direction of the radial cage, so that the radial cage is not inclined, and the radial roller bearing Rotational resistance does not increase.

In the case of the invention described in claims 1 and 2, the radial cage is displaced in the axial direction, and the axial end edge of the radial cage is located near the inner diameter of the other axial surface of the thrust cage. When a thrust force is applied to the thrust retainer, the force can be effectively (linearly) supported by the stepped portion. For this reason, no moment is applied to the thrust cage, and the tilt of the thrust cage can be more reliably prevented. In addition, since a gap having a sufficient thickness can be interposed between the radial intermediate portion of the thrust cage on one side in the axial direction or a portion close to the outer diameter and the step portion, Lubricating oil can be efficiently fed into the rolling contact portion with the rolling surface of the thrust roller. For this reason, the durability of the thrust roller bearing can be sufficiently ensured even under severe conditions.

In the case of the invention described in claim 3, when the thrust retainer is displaced in the radial direction due to the influence of skew or gravity, the inner peripheral edge of the thrust retainer is the axis of the outer peripheral surface of the radial retainer. It hits the end of the direction. Even in this state, since the attitude of the radial cage is regulated by the inner ring guide, the radial cage does not tilt. For this reason, the inner peripheral edge of the pocket provided in the radial cage and the rolling surface of each radial roller do not rub against each other strongly, and the rotational resistance of the radial roller bearing does not increase. The reaction force applied from the radial cage to the thrust cage along with the abutment is applied in parallel to the radial direction of the thrust cage, so that the thrust cage does not tilt and the thrust roller bearing Rotational resistance does not increase.
Further, the thrust cage is displaced in the radial direction, and the inner peripheral edge of the thrust cage hits the outer peripheral surface of one end portion in the axial direction of the radial cage, and a force directed radially inward is applied to the radial cage. When applied, this force can be effectively (linearly) supported by the outer peripheral surface of the shaft member. For this reason, no moment is applied to the radial cage, and the radial cage can be more reliably prevented from tilting. In addition, a gap having a sufficient thickness can be interposed between the axially intermediate portion or the other end of the inner peripheral surface of the radial cage and the outer peripheral surface of the shaft member. And the lubricating oil can be efficiently fed to the rolling contact portion between the radial roller and the rolling surface of each radial roller. For this reason, even when the use conditions are severe, the durability of the radial roller bearing can be sufficiently secured.
Furthermore, in any case, it is not necessary to provide a portion that becomes a great resistance to the flow of lubricating oil, such as a bent portion of a race, a stepped portion or a spacer, so that the lubricity of each roller bearing is improved. As a result, the durability of each of these roller bearings can be ensured.

In carrying out the present invention, as described in claim 4 , the shaft member is composed of a shaft body and a flange member that is separated from the shaft body and is externally fixed to the shaft body. The portion is defined as one axial side surface of the flange member.
The present invention can also be implemented with a structure in which a flange portion is integrally provided on the outer peripheral surface of the shaft body. However, in the case of such a structure, a structure having an integral stepped portion 17 as shown on the left side of FIG.
On the other hand, in the structure as described in claim 4 above, when the race is omitted for size and weight reduction, and the increase in rotational resistance (dynamic torque) of each thrust roller bearing is suppressed. Applying the present invention is effective in terms of suppressing an increase in cost.

1 to 6 show a first embodiment of the present invention corresponding to claims 1 and 4 . The present embodiment has a structure in which the present invention is applied to a rotation support portion disposed between a pair of rotation shafts 19 and 20 which are arranged concentrically with each other and relatively rotate while supporting a thrust load in a direction approaching each other. It shows. A cylindrical portion 21 corresponding to the ring described in the claims is provided concentrically with the rotary shaft 19 at the end of one (left side in FIGS. 1 to 3) of the rotary shaft 19. The inner peripheral surface itself of the cylindrical portion 21 is used as an outer ring raceway for a radial roller bearing 7a described below. In addition, a ring-shaped hook ring 22 is externally fixed by shrink fitting or the like on the other end (right side of FIGS. 1 to 3) of the intermediate shaft at the end of the intermediate portion, and the shaft member described in the claims. Is configured. A portion protruding from the saddle wheel 22 at the tip portion (left end portion in FIGS. 1 to 3) of the rotating shaft 20 is a small diameter portion described in the claims, and an outer peripheral surface of the saddle wheel 22 is also a large diameter portion. The one axial side surface (the left side surface in FIGS. 1 to 3) of the saddle wheel 22 also corresponds to a stepped portion.

A radial roller is provided between the inner peripheral surface of the cylindrical portion 21 and the outer peripheral surface of the tip end portion of the other rotary shaft 20 in order to allow relative rotation of the rotary shafts 19 and 20 while supporting the thrust load. A bearing 7a is provided. The radial roller bearing 7a is formed by holding a plurality of radial rollers 10 by a cylindrical radial cage 11a so as to be freely rollable. Each of the radial rollers 10 has an inner peripheral surface of the cylindrical portion 21 that is an outer ring raceway together with the radial cage 11a in a state where the respective central axes are arranged in parallel with the central axis of the rotating shaft 20 . It arrange | positions in the cylindrical space 23 between the front-end | tip part outer peripheral surfaces of the said rotating shaft 20 which is an inner ring track .

  A thrust roller bearing 9c is provided between the tip end surface of the cylindrical portion 21 (the right end surface in FIGS. 1 to 3) and one axial side surface of the saddle wheel 22. The thrust roller bearing 9c is formed by holding a plurality of thrust rollers 12c by a ring-shaped thrust retainer 13c so as to roll freely. Each of the thrust rollers 12c has a central axis disposed in the diametrical direction of the saddle wheel 22, together with the thrust retainer 13c, one axial side surface of the saddle wheel 22 and the tip of the cylindrical portion 21. It arrange | positions in the annular space 24 between surfaces. With such a configuration, the two rotation shafts 19 and 20 can be rotated relative to each other.

In this embodiment, in such a structure described above, the inner diameter R ₁₃ of the thrust cage 13c, is smaller (R ₁₃ <D ₁₁₎ than the outer diameter D ₁₁ of the radial retainer 11a. Therefore, the portion closer to the inner diameter of the thrust retainer 13c always has an axial end edge of the radial retainer 11a and one axial side surface of the saddle wheel 22 regardless of the radial displacement of the thrust retainer 13c. It exists between the parts closer to the inner diameter. As shown in FIG. 3, a small-diameter step for allowing a portion closer to the inner diameter of the thrust retainer 13c to enter a radially inner portion of the thrust retainer 13c with respect to the axial direction in the tip portion of the rotating shaft 20. The part 33 can also be formed. In this case, the inner peripheral edge of the thrust retainer 13c is slidably contacted or closely opposed to the outer peripheral surface of the small diameter step 33.

  In the case of the present embodiment, the portion closer to the inner diameter of one axial side surface (the right side surface in FIGS. 1 to 3) of the thrust retainer 13c is slidably contacted with the inner diameter portion closer to the axial one side surface of the saddle ring 22. Alternatively, the posture of the thrust retainer 13c is regulated by the raceway guide by making it face each other. Therefore, in the case of the present embodiment, the inner diameter portion of the thrust retainer 13c on the one side surface in the axial direction is compared with the inner diameter portion on the one side in the axial direction or the inner diameter portion on the one side surface in the axial direction of the saddle wheel 22. The entire surface is directed toward the side portion or is intermittently projected in the circumferential direction.

  The material and structure of the thrust cage 13c are not particularly limited. A machined cage made of a synthetic resin or a copper alloy such as brass can be used. In the case of the present embodiment, a press retainer is used which is formed by bending a metal plate such as a steel plate or a stainless steel plate by press working so that the whole is formed into a ring shape with a corrugated cross section. The basic structure of the thrust retainer 13c, which is such a press retainer, has been widely known in the past, and the circumferential edges of the pockets 25, 25 and the rolling surfaces of the thrust rollers 12c Based on the engagement, the thrust retainer 13c is positioned in the axial direction.

  In particular, in the case of the thrust retainer 13c incorporated in the present embodiment, the flat surface portion 27 of the inner diameter side rim portion 26 present in the portion closer to the inner diameter than the pockets 25, 25 is replaced with the central flat portion present in the radial intermediate portion. 28 and the above-mentioned pockets 25, 25 are made to protrude in the axial direction from the end edge of the outer diameter side rim portion 29 present in the portion closer to the outer diameter than the pockets 25 and 25. In the assembled state of the thrust retainer 13c, the flat surface portion 27 of the inner diameter side rim portion 26 is slidably contacted or closely opposed to a portion closer to the inner diameter of one side surface of the saddle wheel 22.

  According to the structure of the present embodiment configured as described above, the thrust traces 14a and 14b are used as in the structure shown in FIG. 14, or the spacer is used as in the structure shown in FIG. Even if 18 is not provided, it is possible to prevent an increase in dynamic torque due to interference between the radial and thrust cages 11a and 13c. That is, in the case of the structure of the present embodiment, when the radial holder 11a is displaced in the axial direction, as shown in FIG. 2, the axial edge of the radial holder 11a becomes the thrust holder 13c. It strikes against a portion closer to the inner diameter of the other side surface in the axial direction (the left side surface in FIGS. 1 to 3). Even in this state, since the attitude of the thrust holder 13c is regulated by the raceway guide, the thrust holder 13c does not tilt.

  That is, the flat surface portion 27 of the inner diameter side rim portion 26 of the thrust retainer 13c and the inner diameter side portion of the saddle wheel 22 closer to the inner diameter on the one side surface are the axial end edges of the radial retainer 11a of the thrust retainer 13c. Before coming into contact with the inner diameter side portion of the other side surface in the axial direction, it is in sliding contact or in close proximity. Therefore, even if the axial edge of the radial retainer 11a pushes a portion closer to the inner diameter of the other axial side surface of the thrust retainer 13c, the displacement in the axial direction of this portion is zero or slight. For this reason, even if the portion closer to the inner diameter of the other axial side surface of the thrust retainer 13c is pushed in this way, the attitude of the thrust retainer 13c is not changed or hardly changed. Accordingly, the inner peripheral edges of the pockets 25, 25 provided in the thrust cage 13c and the rolling surfaces of the thrust rollers 12c do not rub against each other, and the rotational resistance (dynamic torque) of the thrust roller bearing 9c is reduced. It will never grow. Further, the reaction force applied from the thrust retainer 13c to the radial retainer 11a along with the abutment is applied in parallel to the axial direction of the radial retainer 11a. Therefore, the radial retainer 11a is not inclined. In addition, the rotational resistance of the radial roller bearing 7a does not increase.

  The axial positioning of the thrust cage 13c is basically achieved by engaging the opening edges of the pockets 25 and 25 with the rolling surfaces of the thrust rollers 12c. Therefore, a gap having a sufficient thickness exists between the thrust retainer 13c and one side surface in the axial direction of the saddle wheel 22 at a portion closer to the outer diameter than the flat surface portion 27. Therefore, sufficient lubricating oil can be fed into the rolling contact portion between the rolling surface of each thrust roller 12c and one axial side surface of the saddle wheel 22. If the groove which crosses the flat surface portion 27 in the radial direction is formed at a plurality of locations in the circumferential direction of the flat surface portion 27, the lubricating oil can be fed more effectively.

  Note that the thrust retainer that can stabilize the posture regardless of the end of the radial retainer as in this embodiment is not limited to the structure shown in FIGS. That is, among the axial side surfaces of the thrust retainer 13c shown in FIGS. 4 to 6, the central flat portion 28 together with the flat surface portion 27 protrudes in the axial direction, and slides on one axial side surface of the saddle wheel 22. It can also be in close contact or in close proximity. Also in this case, since the attitude of the thrust retainer 13c can be regulated by the raceway guide, the axial end edge of the radial retainer 11a has a portion closer to the inner diameter of the other axial side surface of the thrust retainer 13c. Even if it is pushed, this thrust retainer 13c can be prevented from tilting. Moreover, if the groove | channel which crosses to a radial direction is formed in the said flat surface part 27 and the said center flat part 28, respectively, lubricating oil can be sent in effectively.

  Further, as the thrust retainer usable in the present embodiment, a structure as shown in any of FIGS. 7, 8, and 9 to 10 can be used in addition to the above-described machined retainer. Of these, the thrust retainer 13d shown in FIG. 7 has the portions closer to the inner diameters on both sides in the axial direction protruding in the same direction in the opposite direction with respect to the axial direction. That is, of the inner diameter side rim portion 26a of the thrust retainer 13d, the flat surface portion 27 formed on one axial side surface and the flat surface portion 27a formed on the other axial side surface have the same amount of protrusion in the axial direction. With such a configuration, it is not necessary to consider the assembling direction of the thrust retainer 13d, so that the assembling property of the thrust retainer 13d can be improved. In the case of the structure shown in FIGS. 4 to 6 described above, when the central flat portion 28 is protruded in the axial direction on one side surface in the axial direction of the thrust retainer 13c, Of the other side surfaces in the axial direction, it is preferable that the flat portion 34 (see FIGS. 4 to 5) closer to the inner diameter protrudes in the same direction in the opposite direction with respect to the axial direction from the viewpoint of improving assemblability.

  Further, the thrust holder 13e, which is a press holder shown in FIG. 8, is obtained by improving the rigidity of the inner diameter side rim portion 26b, assuming that the inner diameter side rim portion 26b is closed in cross section. . Further, with respect to the thrust retainer 13e as well, the both side surfaces in the axial direction of the inner diameter side rim portion 26b are projected in the same direction in the opposite direction with respect to the axial direction to improve the assemblability. In this case, the portions protruding in the axial direction are not limited to both axial side surfaces of the inner diameter side rim portion 26b. In any case, in order to improve the assemblability, when both axial side surfaces protrude in the axial direction, concave grooves are formed in the radial direction at multiple locations in the circumferential direction of the protruding portion to lubricate. Allows oil distribution.

  The thrust cage 13f shown in FIGS. 9 to 10 is a combination of annular elements 30a and 30b each having a U-shaped cross section. In the assembled state to the rotation support portion, the outer surface of one of the elements 30a and 30b is slidably contacted or closely opposed to one axial side surface (see FIGS. 1 and 2) of the collar 22. The posture of the thrust cage 13f is regulated. On the other hand, the outer surface of the other element 30b is also protruded in the axial direction to improve the assemblability. When such a thrust retainer 13f is used, as shown in FIG. 10, the element 30a is formed in the portion between the pockets 25a and 25a adjacent to each other in the circumferential direction on the outer surface of the element 30a (30b). It is preferable to form the concave grooves 31, 31 continuous from the inner peripheral edge to the outer peripheral edge of (30b). Each of the concave grooves 31, 31 circulates lubricating oil in each of them, and is sufficient for a rolling contact portion between the rolling surface of the thrust roller constituting the thrust roller bearing and one axial side surface of the saddle wheel 22. Ensure that the amount of lubricant is supplied. If such concave grooves 31, 31 are formed, one axial side surface of the thrust retainer 13f is slidably contacted or closely opposed to one axial side surface of the collar 22 from the inner peripheral edge to the outer peripheral edge. May be.

11 to 12 show a second embodiment of the present invention corresponding to claims 3 and 4 . In the case of the present embodiment, the inner diameter of the thrust holder 13g is made larger than the outer diameter of the radial holder 11b. At the same time, the axial length of the radial cage 11b is set such that one end thereof does not come out from the inner diameter side of the thrust cage 13g regardless of the axial displacement of the radial roller bearing 7b. The radial cage 11b is positioned in the radial direction by engaging the opening edges of pockets 32 provided at a plurality of locations in the circumferential direction of the radial cage 11b with the rolling surfaces of the radial rollers 10. Further, among the axial ends of the radial cage 11b, the inner peripheral surface of the one end portion present on the inner diameter side of the thrust cage 13g is compared with the tip end portion of the rotary shaft 20 as compared with the axial intermediate portion or the other end portion. The entire surface is directed toward the outer peripheral surface or is intermittently protruded in the circumferential direction. And the attitude | position of the said radial holder | retainer 11b is made by making the inner peripheral surface of this protrusion part slidably contact or adjoins the outer peripheral surface of the front-end | tip part of the said rotating shaft 20, which is an inner ring track of the said radial roller bearing 7b. Regulated by inner ring guidance.

In the case of this embodiment having such a configuration, when the thrust retainer 13g is displaced in the radial direction, the inner peripheral edge of the thrust retainer 13g is the axial end of the outer peripheral surface of the radial retainer 11b. I hit the part. Even in this state, since the attitude of the radial cage 11b is regulated by the inner ring guide, the radial cage 11b does not tilt. Therefore, the inner peripheral edge of the pocket 32 provided in the radial cage 11b and the rolling surface of each radial roller 10 do not rub against each other, and the rotational resistance of the radial roller bearing 7b increases. Absent. The reaction force applied to the thrust retainer 13g from the radial retainer 11b along with the abutment is applied in parallel to the radial direction of the thrust retainer 13g. Therefore, the thrust retainer 13g is not inclined. The rotational resistance of the thrust roller bearing 9d does not increase.
About the structure and effect | action of another part, it can consider similarly to the case of the above-mentioned Example 1 except that the relationship between a radial holder and a thrust holder was reversed.

FIG. 13 shows a third embodiment of the present invention corresponding to claims 2 and 4 . In the case of the present embodiment, the axial portion of the saddle ring 22a is closer to the inner diameter portion of the axial direction than the intermediate portion of the radial direction to the outer diameter portion of the thrust retainer 13b. Convex portions 35 are provided around the circumference or intermittently projecting in the circumferential direction. Then, by making this convex portion 35 slidably contact or closely oppose to a portion closer to the inner diameter of one axial side surface of the thrust retainer 13b, the attitude of the thrust retainer 13b is regulated by the raceway guide. Further, in the case of the present embodiment, a thrust retainer having a conventional structure that does not have a protruding portion in the axial direction can be used as the thrust retainer 13b, so that an increase in cost can be suppressed. The configuration and operation of the other parts are almost the same as those in the first embodiment.

The present invention can be implemented not only in the transmission for an automobile but also in the rotation support part of other mechanical devices as long as the radial roller bearing and the thrust roller bearing are arranged adjacent to each other.

1 is a partial cross-sectional view showing a first embodiment of the present invention in a state where a radial roller bearing is in a neutral position. FIG. Similarly, the partial sectional view shown in the state where the radial roller bearing was displaced. The fragmentary sectional view equivalent to FIG. 1 shown in the state which incorporated the other example of the rotating shaft used for Example 1. FIG. The partial side view which shows the 1st example of the thrust holder | retainer built in Example 1 in the state seen from the right side of FIGS. AA sectional drawing of FIG. BB sectional drawing. FIG. 4 is a partial enlarged cross-sectional view showing a second example of a thrust cage incorporated in Example 1. The fragmentary sectional view which shows the 3rd example. The fragmentary sectional view which shows the 4th example. The figure seen from the side of FIG. The fragmentary sectional view which shows Example 2 of this invention in the state in which a thrust roller bearing exists in a neutral position. The partial sectional view shown in the state where the thrust roller bearing was displaced similarly. The fragmentary sectional view which shows Example 3 of this invention. The fragmentary sectional view which shows one example of the conventional structure. The fragmentary sectional view which shows an example of the structure which abbreviate | omits the thrust trace considered previously. Sectional drawing equivalent to the right part of FIG. 15 for demonstrating the inconvenience which arises in the structure considered previously. The fragmentary sectional view which shows an example of the structure considered previously in order to eliminate this inconvenience.

DESCRIPTION OF SYMBOLS 1, 1a Shaft member 2, 2a Shaft main body 3a, 3b, 3c Flange member 4a, 4b Flat surface 5 Intersection 6 Gear 7, 7a, 7b Radial roller bearing 8a, 8b End surface 9a, 9b, 9c, 9d Thrust roller bearing 10 Radial roller 11, 11a, 11b Radial cage 12a, 12b, 12c Thrust roller 13a, 13b, 13c, 13d, 13e, 13f, 13g Thrust cage 14a, 14b Thrust trace 15a, 15b Bending portion 16 Flange portion 17 Stepped portion 18 Spacer 19 Rotating shaft 20 Rotating shaft 21 Cylindrical portion 22, 22a Hook ring 23 Cylindrical space 24 Annular space 25, 25a Pocket 26, 26a, 26b Inner diameter side rim portion 27, 27a Flat surface portion 28 Central flat portion 29 Outer diameter Side rim 30a, 30b Element 31 Groove 32 Pocket 33 Small-diameter step 34 Flat part near inner diameter 35 Convex

Claims (4)

  A shaft member having an outer peripheral surface shape in which a large diameter portion and a small diameter portion are continuous at a step portion, an inner diameter larger than the outer diameter of the small diameter portion of the shaft member, and disposed around the shaft member, An annular body having a cylindrical outer ring raceway as a peripheral surface, and an inner peripheral surface of the annular body and an outer peripheral surface of the small-diameter portion in a state in which each central axis is arranged in parallel with the central axis of the shaft member. A plurality of radial rollers disposed between them, and a radial roller bearing which is rotatably held by a cylindrical radial cage disposed in a cylindrical space between the two peripheral surfaces; A plurality of thrust rollers arranged between the axial end face of the ring body and the stepped portion in a state where the central axis is arranged in the diameter direction of the ring body, between the axial end surface and the stepped portion. A thrust roller bearing which is rotatably held by an annular thrust cage disposed; And a rotation support portion that allows relative rotation between the shaft member and the ring body, wherein the inner diameter of the thrust cage is made smaller than the outer diameter of the radial cage, and the thrust rollers are rotated. Positioning of the thrust retainer in the axial direction is achieved by engagement of opening edges of pockets provided at a plurality of positions in the circumferential direction of the thrust retainer and rolling surfaces of the thrust rollers to hold the thrust retainer freely. Furthermore, by projecting at least the inner diameter portion of one axial surface of the thrust cage toward the step portion as compared with the radially intermediate portion or the outer diameter portion, the inner diameter portion is slidably contacted with the step portion. Or the rotation support part characterized by having controlled the attitude | position of this thrust holder | retainer by the race ring guide by making it adjoin and oppose.   A shaft member having an outer peripheral surface shape in which a large diameter portion and a small diameter portion are continuous at a step portion, an inner diameter larger than the outer diameter of the small diameter portion of the shaft member, and disposed around the shaft member, An annular body having a cylindrical outer ring raceway as a peripheral surface, and an inner peripheral surface of the annular body and an outer peripheral surface of the small-diameter portion in a state in which each central axis is arranged in parallel with the central axis of the shaft member. A plurality of radial rollers disposed between them, and a radial roller bearing which is rotatably held by a cylindrical radial cage disposed in a cylindrical space between the two peripheral surfaces; A plurality of thrust rollers arranged between the axial end face of the ring body and the stepped portion in a state where the central axis is arranged in the diameter direction of the ring body, between the axial end surface and the stepped portion. A thrust roller bearing which is rotatably held by an annular thrust cage disposed; And a rotation support portion that allows relative rotation between the shaft member and the ring body, wherein the inner diameter of the thrust cage is made smaller than the outer diameter of the radial cage, and the thrust rollers are rotated. Positioning of the thrust retainer in the axial direction is achieved by engagement of opening edges of pockets provided at a plurality of positions in the circumferential direction of the thrust retainer and rolling surfaces of the thrust rollers to hold the thrust retainer freely. Furthermore, by projecting a part of the step portion toward the inner diameter portion of one axial surface of the thrust cage to form a convex portion, the inner diameter portion and the convex portion of the step portion are slid. A rotation support unit characterized in that the attitude of the thrust cage is regulated by a raceway guide by contact or proximity. A shaft member having an outer peripheral surface shape in which a large diameter portion and a small diameter portion are continuous at a step portion, an inner diameter larger than the outer diameter of the small diameter portion of the shaft member, and disposed around the shaft member, An annular body having a cylindrical outer ring raceway as a peripheral surface, and an inner peripheral surface of the annular body and an outer peripheral surface of the small-diameter portion in a state in which each central axis is arranged in parallel with the central axis of the shaft member. A plurality of radial rollers disposed between them, and a radial roller bearing which is rotatably held by a cylindrical radial cage disposed in a cylindrical space between the two peripheral surfaces; A plurality of thrust rollers arranged between the axial end face of the ring body and the stepped portion in a state where the central axis is arranged in the diameter direction of the ring body, between the axial end surface and the stepped portion. A thrust roller bearing which is rotatably held by an annular thrust cage disposed; And a rotation support section that allows relative rotation between the shaft member and the ring body, wherein the inner diameter of the thrust holder is larger than the outer diameter of the radial holder, and the shaft of the radial holder is Regardless of the axial length displacement of the radial roller bearing, the length in the direction is set so that one end thereof does not come out from the inner diameter side of the thrust cage, and the inner circumferential surface of the thrust cage and the end of the radial cage The opening edges of the pockets provided at a plurality of locations in the circumferential direction of the radial cage and the radials of the radial holders so that the outer peripheral surfaces of the radial rollers are in direct sliding contact or close to each other and the radial rollers are rotatably held. The radial retainer is positioned in the radial direction by engaging with the rolling surface of the roller, and the inner circumference of one end existing on the inner diameter side of the thrust retainer among the axial ends of the radial retainer. And to protrude radially inwardly toward the outer peripheral surface of the comparison shaft member in the axial direction intermediate portion to the other end, the one end portion inner peripheral surface by which the outer peripheral surface in sliding contact with or closely opposed to, the radial Rotation support part characterized in that the attitude of the cage is regulated by the inner ring guide. The shaft member includes a shaft body, which consist in the shaft body and the other body and fitted fixed flange member to the shaft main body, the stepped portion is an axial one side of the flange member, claim The rotation support part described in any one of 1-3 .

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