JP2016156398A - Rotating shaft support structure of transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a rotating shaft support structure of a transmission which reduces a load of a conical roller bearing caused by a thrust load from a gear without employing fixation by the fastening of a nut member to the fixation of the gear which is fit to a rotating shaft, and can secure the durability of the bearing.SOLUTION: A rotating shaft support structure of a transmission comprises a reduction driven gear (driven gear) which transmits a rotation force to a drive pinion shaft (rotating shaft), and a conical roller bearing 100. The drive pinion shaft has a spline part 16, a stepping part 12a and a step part 17. A part of the conical roller bearing 100 has a split flange member 140 (split member) which is fixed to the drive pinion shaft by an integral attachment structure, and is split into two pieces in a peripheral direction, and an annular member 150 for fixing the split flange member 140. With one end face 140a (one portion of the split member) of the split flange member 140 in an axial direction as positioned in the axial direction, a main body of the conical roller bearing is fixed to the stepping part 12a of the drive pinion shaft.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a rotating shaft support structure for a transmission.

  Conventionally, for example, a technique disclosed in Patent Document 1 is known as a rotating shaft support structure of a transmission applied to a transmission such as a belt type continuously variable transmission (CVT). The technique of Patent Document 1 discloses a technique in which a drive pinion gear and a reduction driven gear are provided on a drive pinion shaft as a rotating shaft, and tapered roller bearings are provided on both ends of the drive pinion shaft with respect to the housing. Yes. The drive pinion gear is provided integrally with the drive pinion shaft. The reduction driven gear is spline-fitted to a spline provided on the drive pinion shaft, and one end of the fitting portion of the reduction driven gear is in contact with a side wall region provided on the side of the drive pinion gear.

  A tapered roller bearing is disposed between the stepped portion of the drive pinion shaft and the housing on the shaft end side of the drive pinion shaft where the drive pinion gear is provided. Further, a tapered roller bearing is disposed between the stepped portion of the drive pinion shaft and the housing on the shaft end side of the drive pinion shaft where the reduction driven gear is provided. The tapered roller bearing is pressed against the fitting portion side of the reduction driven gear by tightening a nut member that is screwed into a screw region formed on the surface of the drive pinion shaft. Since the drive pinion shaft, the reduction driven gear, and the drive pinion gear are integrated with each other by fastening the nut member in this manner, it is possible to play a role of canceling the thrust load from each gear generated when the drive pinion shaft rotates.

JP 2005-331064 A

  By the way, it is desirable for such a transmission to be small in terms of mountability. In order to reduce the size of the transmission, it is desirable to eliminate the nut member in order to reduce the axial length of the transmission. Thereby, it is possible to reduce the number of parts and reduce the weight as well as downsizing. However, if the nut member described above is abolished, the drive pinion shaft, the reduction driven gear, and the drive pinion gear cannot be integrated, and it is difficult to cancel the thrust load generated from each gear. Therefore, since the thrust load is applied to the tapered roller bearing that rotatably supports the drive pinion shaft in the housing, there is a concern that the life of the tapered roller bearing may be reduced.

  The present invention was devised in view of the above points, and the problem to be solved by the present invention is that the fixing of the gear fitted to the rotating shaft is not performed by the fixing of the nut member. Another object of the present invention is to provide a rotating shaft support structure for a transmission that can reduce the load on the tapered roller bearing due to the thrust load from the gear and ensure the durability of the bearing.

  In order to solve the above problems, the rotating shaft support structure of the transmission of the present invention takes the following means. First, a rotating shaft support structure for a transmission according to a first aspect of the present invention is a rotating shaft support structure for a transmission, wherein the driven gear is splined to the rotating shaft and transmits rotational force to the rotating shaft, and the transmission. A tapered roller bearing that rotatably supports the rotary shaft with respect to the housing, wherein the rotary shaft includes a spline portion for spline-fitting the driven gear, and a fixing portion for fixing the tapered roller bearing. A part of the tapered roller bearing having a stepped portion recessed at least from the outer peripheral surface of the fixed portion between the spline portion and the fixed portion, and facing one end of the fitting portion of the driven gear, A circumferentially split member that is fixed to the rotating shaft with an integral mounting structure and a circumferentially split member that is split in the circumferential direction are fitted into the stepped portion so that the split state is not separated from the rotating shaft. An annular member to be fixed and front Securing the tapered roller bearing body to a fixed portion of the rotary shaft portion of the split member projecting from the stepped portions radially outwardly as the axial positioning.

  According to the first aspect, since the split member divided in the circumferential direction is fixed to the rotating shaft by an integral mounting structure, the rotating shaft and the driven gear can be made an integral structure. Therefore, in order to offset the thrust load from the gear that occurs when the rotation shaft rotates, the load on the tapered roller bearing due to the thrust load from the gear is reduced, and the rotation shaft support of the transmission can ensure the durability of the bearing It can be a structure.

  Next, a rotating shaft support structure for a transmission according to a second invention is the first invention, wherein the tapered roller bearing includes an inner ring raceway surface having a conical outer peripheral surface and a smaller diameter side of the inner ring raceway surface. The inner ring comprises a small flange part protruding radially outward at the end and a large flange part protruding radially outward at the large diameter end part of the inner ring raceway surface, The inner ring large cage part that constitutes the large collar part and the inner ring raceway part that constitutes the inner ring raceway surface and the small collar part are configured separately, and the inner ring large collar part is A split rod member that is divided at two locations in the circumferential direction as a split member, and an annular member that is fixed to a rotating shaft so as not to be separated in a state where the split rod member is split, The inner diameter is smaller than the inner diameter of the inner ring raceway part.

  According to the second aspect of the present invention, the inner ring is configured such that the inner ring large hook component including the large collar portion and the inner ring race ring component including the inner ring raceway surface and the small collar portion are configured separately. The inner ring large flange part is configured as a split member, and includes a split hook member that is divided at two locations in the circumferential direction, and an annular member that is fixed to the rotating shaft so as not to be separated in a divided state. Have. Here, the tapered roller of the tapered roller bearing revolves while rotating when the rotating shaft supported by the shaft rotates. Here, the rolling surface formed on the tapered surface of the tapered roller makes rolling contact with the inner ring raceway surface. On the other hand, the end surface on the large diameter side of the tapered roller is in sliding contact with the large collar portion of the inner ring. Here, the inner ring large saddle component having the above-described configuration is configured as a split saddle member in which two portions in the circumferential direction are divided as a split member. For this reason, the divided part of the split rod member is filled with a lubricant that forms a minute gap and lubricates the bearing in the minute gap. Therefore, an oil film can be easily formed between the end surface on the large diameter side of the tapered roller that is in sliding contact and the large collar portion of the inner ring, and seizure of the tapered roller can be suppressed.

  A transmission shaft support structure for a transmission according to a third aspect of the present invention is the second aspect of the invention, wherein the split surface of the split rod member is the split rod member when the split rod member is viewed from a radial cross section. It is formed as an inclined surface that intersects with a virtual plane orthogonal to the inner diameter of the.

  According to the third aspect, the split surface of the split collar member is formed as an inclined surface that intersects with a virtual plane orthogonal to the inner diameter of the split collar member when the split collar member is viewed from the radial cross section. This is because the length of the split surface is longer than the virtual plane orthogonal to the inner diameter of the split saddle member. Therefore, it is possible to increase the lubricating oil filled in the split surface.

  According to the present invention, by taking the measures of the above inventions, the load of the tapered roller bearing due to the thrust load from the gear is reduced without fixing the gear fitted to the rotating shaft by fastening the nut member. And it can be set as the rotating shaft support structure of the transmission which can ensure the durability of a bearing.

It is the partial cross section figure which showed the rotating shaft support structure of the transmission as this embodiment. It is the expanded sectional view which expanded the II section of FIG. It is a disassembled perspective view of the rotating shaft support structure of the transmission as this embodiment. FIG.

  Hereinafter, an embodiment of a rotating shaft support structure for a transmission according to the present invention will be described with reference to FIGS. The structure for supporting the rotating shaft of the transmission in this embodiment exemplifies a structure in which both ends of the drive pinion shaft (rotating shaft) are supported by tapered roller bearings with respect to the housing of the belt type continuously variable transmission (CVT). explain.

  The support structure of the drive pinion shaft 12 (rotary shaft) applied to the belt type continuously variable transmission (CVT) 10 as a transmission is as follows. As shown in FIG. 1, a drive pinion gear 14 is integrally provided on the drive pinion shaft 12 (rotary shaft). Further, the drive pinion shaft 12 is fitted with a reduction driven gear 20 (driven gear) on a spline portion 16 formed adjacent to the drive pinion gear 14. Specifically, the reduction driven gear 20 is spline-fitted to the spline 16 provided on the drive pinion shaft 12, and one end side of the fitting portion 22 of the reduction driven gear 20 is provided on a side wall region provided on the side of the drive pinion gear 14. 14a.

  Tapered roller bearings 100 and 200 are provided at both ends of the drive pinion shaft 12 with respect to the housings 30 and 40. A tapered roller bearing 200 is disposed between the stepped portion 12 b of the drive pinion shaft 12 and the housing 40 on the shaft end side of the drive pinion shaft 12 where the drive pinion gear 14 is provided. Further, the tapered roller bearing 100 is disposed between the stepped portion 12 a (fixed portion) of the drive pinion shaft 12 and the housing 30 on the shaft end side of the drive pinion shaft 12 where the reduction driven gear 20 is provided. Yes.

  The drive pinion shaft 12 includes a spline portion 16 for spline-fitting the reduction driven gear 20, a stepped portion 12a as a fixed portion for fixing the tapered roller bearing 100, and at least a stepped portion between the spline portion 16 and the stepped portion 12a. It has a stepped portion 17 that is recessed from the outer peripheral surface of 12a. In the present embodiment, the stepped portion 17 is formed in a groove shape having a smaller diameter than the diameter of the stepped portion 12a as an aspect recessed from the outer peripheral surface of the stepped portion 12a.

  As shown in FIGS. 2 and 3, the tapered roller bearing 100 generally includes an inner ring 110, an outer ring 102, a tapered roller 104, and a cage 106. The inner ring 110 includes an inner ring raceway surface 122 having a conical outer peripheral surface, a small flange portion 126 projecting radially outward at a small diameter side end portion of the inner ring raceway surface 122, and a large diameter side end of the inner ring raceway surface 122. And a large collar portion 134 protruding outward in the radial direction. In the inner ring 110, an inner ring large collar part 130 including the large collar part 134 and an inner ring raceway part 120 including the inner ring raceway surface 122 and the small collar part 126 are configured separately.

  The inner ring large collar part 130 is fixed to the drive pinion shaft 12 so as not to be separated in a state where the divided collar member 140 (split member) formed in an annular shape and divided in two circumferential directions is separated from the divided collar member 140. An annular member 150. Here, the inner diameter dimension 140 d of the split collar member 140 in the inner ring large collar part 130 is smaller than the inner diameter dimension 120 d of the inner ring raceway ring part 120. Further, the inner diameter dimension 140 d of the split rod member 140 is formed to have a dimension 17 d substantially the same as the outer diameter of the stepped portion 17. Further, as shown in FIG. 4, the split surface 142 of the split collar member 140 is formed as an inclined surface that intersects the virtual plane S perpendicular to the inner diameter of the split collar member 140 when the split collar member 140 is viewed from the radial cross section. (Having an inclination angle inclined with respect to the virtual plane S).

  As shown in FIGS. 2 and 3, the outer ring 102 is disposed on the same rotation center line along the outer periphery of the inner ring raceway surface 122 of the inner ring 110, and faces the outer ring 102. A surface 102a is formed. A plurality of tapered rollers 104 are disposed in an annular space between the inner ring raceway surface 122 of the inner ring 110 and the outer ring raceway surface 102a of the outer ring 102 so as to be able to roll.

  The tapered roller 104 is formed with a tapered rolling surface 104c that can roll while being sandwiched between the inner ring raceway surface 122 and the outer ring raceway surface 102a. In the tapered roller 104, a roller small-diameter side end surface 104a is configured on the small-diameter end portion side of the rolling surface 104c. The tapered roller 104 has a roller large-diameter side end surface 104b on the large-diameter end portion side of the rolling surface 104c. A plurality of the tapered rollers 104 are sandwiched between the inner ring 110 and the outer ring 102 while being held in the pocket 106p of the cage 106, and can rotate and revolve on the outer peripheral surface of the drive pinion shaft 12. ing.

  The cage 106 holds the tapered roller 104 in a state where it can rotate and revolve between the inner ring raceway surface 122 and the outer ring raceway surface 102a via the rolling surface 104c. The cage 106 is made of a synthetic resin (for example, a polyamide-based resin, a polyphenylene sulfide resin, etc.) or a metal excellent in oil resistance and heat resistance. As shown in FIGS. 2 and 3, the retainer 106 is provided with a first annular portion 106 a and a second annular portion 106 b on both axial sides of the tapered roller 104. The first annular portion 106 a is disposed to face the roller small diameter side end surface 104 a of the tapered roller 104. The second annular portion 106 b is disposed to face the roller large diameter side end surface 104 b of the tapered roller 104. Between the first annular portion 106a and the second annular portion 106b, a plurality of column portions 106c are spanned and connected in the circumferential direction. A plurality of pockets 106p for accommodating the plurality of tapered rollers 104 are partitioned and formed as rectangular openings by the first annular portion 106a, the second annular portion 106b, and the pillar portion.

  The tapered roller bearing 200 has substantially the same configuration as the outer ring 102, tapered roller 104, and cage 106 of the tapered roller bearing 100. The inner ring 210 of the tapered roller bearing 200 is formed integrally with the inner ring large collar part 130 and the inner ring raceway part 120 in the inner ring 110 of the tapered roller bearing 100, not in a separate configuration. In the tapered roller bearing 200, the same configuration as that of the inner ring 110 of the tapered roller bearing 100 can be applied.

  The assembly process of the drive pinion shaft 12 will be described. As shown in FIGS. 1 to 3, the outer ring 102 is press-fitted into the housing 30 in advance. Next, the reduction driven gear 20 is spline-fitted to the spline portion 16 of the drive pinion shaft 12 until one end side of the fitting portion 22 comes into contact with the side wall region 14 a provided on the side portion of the drive pinion gear 14. In this state, the split collar member 140 divided into two in the circumferential direction is fitted into the stepped portion 17 of the drive pinion shaft 12. Further, the annular member 150 is fitted on the outer peripheral surface of the split collar member 140 so that the divided split collar member 140 is not separated. In this way, the inner ring large collar part 130 (divided collar member 140, annular member 150) which is a part of the tapered roller bearing 100 is fixed to the drive pinion shaft 12 in an integral mounting structure (in other words, the drive pinion shaft 12, the reduction). The driven gear 20 and the drive pinion gear 14 have an integral structure). Further, one axial end surface 140a (part of the split member) of the split rod member 140 protruding radially outward from the stepped portion 17 is set as an axial positioning position. Next, with the tapered roller 104 housed in the pocket 106p of the cage 106, the tapered roller 104 is disposed on the inner ring raceway surface 122 (see FIG. 2) of the inner ring raceway component 120, and the cage 106, the tapered roller 104 and the inner ring raceway component. The tapered roller bearing body 120 is a trinally integrated temporarily assembled state. The tapered roller bearing main body in a three-unit temporarily assembled state is press-fitted from the shaft end of the stepped portion 12a of the drive pinion shaft 12 to a position where it abuts on the one end surface 140a of the split rod member 140. After that, the drive pinion shaft 12 is assembled to a position where the rolling surface 104 c of the tapered roller 104 contacts the outer ring raceway surface 102 a of the outer ring 102. The tapered roller bearing 200 on the side of the stepped portion 12b of the drive pinion shaft 12 is a process of press-fitting the tapered roller bearing main body in a three-piece temporary assembly state because the inner ring is integrated, and the other processes are the same as the above processes. is there.

  Thus, according to the rotating shaft support structure of the transmission of this embodiment, the circumferentially split split rod member 140 (split member) is fixed to the drive pinion shaft 12 with an integral mounting structure. Therefore, the drive pinion shaft 12 and the reduction driven gear 102 can be integrated. Therefore, it is possible to cancel the thrust load from the gear that is generated when the drive pinion shaft 12 rotates. For this reason, it is possible to reduce the load on the tapered roller bearing 100 due to the thrust load from the gear, and to provide a drive pinion shaft 12 support structure for a transmission that can ensure the durability of the bearing.

  In the inner ring 110, an inner ring large collar part 130 including the large collar part 134 and an inner ring raceway part 120 including the inner ring raceway surface 122 and the small collar part 126 are configured separately. The inner ring large collar part 130 is configured as a split member, and is fixed to the drive pinion shaft 12 so as not to be separated in a state where the split collar member 140 and the divided collar member 140 are separated from each other in two circumferential directions. An annular member 150. Here, the tapered roller 104 of the tapered roller bearing 100 revolves while rotating as the drive pinion shaft 12 supporting the shaft rotates. Here, the rolling surface 104 c formed on the conical surface of the tapered roller 104 is in rolling contact with the inner ring raceway surface 122. On the other hand, the roller large-diameter side end surface 104b on the large-diameter side of the tapered roller 104 is in sliding contact with the large collar portion 134 of the inner ring 110. Here, the inner ring large saddle member 130 configured as described above is configured as a split saddle member 140 that is divided at two locations in the circumferential direction as a split member. Therefore, the divided part of the split rod member 140 is filled with a lubricant that forms a minute gap and lubricates the bearing in the minute gap. Therefore, an oil film can be easily formed between the large-diameter roller large-diameter end surface 104b of the tapered roller 104 that makes sliding contact and the large collar portion 134 of the inner ring 110, and seizure of the tapered roller 104 can be suppressed. .

  Further, the split surface 142 of the split collar member 140 is formed as an inclined surface that intersects the virtual plane S orthogonal to the inner diameter of the split collar member 140 when the split collar member 140 is viewed from the radial cross section. This is because the length of the split surface 142 is longer than the virtual plane S that is orthogonal to the inner diameter of the split collar member 140. Therefore, it is possible to increase the lubricating oil filled in the split surface 142.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to embodiment, It can implement in other various embodiment. In the above embodiment, the rotating shaft support structure of a belt type continuously variable transmission (CVT) has been described as a transmission. However, the present invention is not limited to this, and the present invention can be widely applied to a support structure of a rotating shaft configured in a transmission.

10 Belt type continuously variable transmission (CVT) (transmission)
12 Drive pinion shaft (rotary shaft)
12a Stepped part (fixed part)
16 Spline part 17 Step part 20 Reduction driven gear (driven gear)
30 Housing 40 Housing 100 Tapered roller bearing 200 Tapered roller bearing 110 Inner ring 120 Inner ring raceway part 122 Inner ring raceway surface 126 Small collar part 130 Inner ring large collar part 134 Large collar part 140 Divided collar member (split member)
142 Split Face 150 of Divided Scissors Member Annular Member S Virtual Plane

Claims (3)

A structure for supporting a rotating shaft of a transmission,
A driven gear that is spline-fitted to the rotating shaft and transmits the rotational force to the rotating shaft;
A tapered roller bearing that rotatably supports the rotating shaft in the housing of the transmission,
The rotating shaft includes a spline portion for spline-fitting the driven gear, a fixing portion for fixing a tapered roller bearing, and a step provided between the spline portion and the fixing portion at least from the outer peripheral surface of the fixing portion. Part
A part of the tapered roller bearing facing one end of the fitting portion of the driven gear includes a circumferentially split member fixed to the rotating shaft with an integral mounting structure, and a split member of the circumferential direction. An annular member that is fitted to the stepped portion and fixed to the rotating shaft so that the divided state is not separated;
A rotating shaft support structure for a transmission, wherein a tapered roller bearing body is fixed to a fixed portion of the rotating shaft with a part of the split member protruding radially outward from the stepped portion as an axial positioning. It is the rotating shaft support structure of the transmission of Claim 1, Comprising:
The tapered roller bearing includes an inner ring raceway surface having a tapered outer peripheral surface, a small flange portion protruding radially outward at a small diameter side end portion of the inner ring raceway surface, and a large diameter side end portion of the inner ring raceway surface. It has an inner ring that constitutes a large collar portion that protrudes radially outward,
The inner ring is composed of an inner ring large collar part that constitutes the large collar part and an inner ring raceway part that constitutes the inner ring raceway surface and the small collar part as separate bodies,
The inner ring large flange part has a split flange member that is divided at two circumferential positions as the split member, and an annular member that is fixed to the rotating shaft so as not to be separated in the divided state. And
A structure for supporting a rotating shaft of a transmission, wherein an inner diameter of the inner ring collar part is smaller than an inner diameter of the inner ring raceway part. It is the rotating shaft support structure of the transmission of Claim 2, Comprising:
The split shaft member split surface is a rotary shaft support structure for a transmission that is formed as an inclined surface that intersects with a virtual plane orthogonal to the inner diameter of the split rod member when the split rod member is viewed from a radial cross section.

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