JP2006349046A - Pinion support structure of planetary gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pinion support structure of a planetary gear, capable of avoiding problems of skewing, etc., at a high rotation or a heavy load. <P>SOLUTION: The pinion support structure of the planetary gear is supported by a pinion PG and a pinion shaft revolving integrally with a pinion carrier. Angular ball bearings 41 and 42 are installed between the pinion PG and the pinion shaft. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a pinion support structure for a planetary gear, and more particularly to a pinion bearing structure for a hybrid vehicle including a planetary gear mechanism in which an engine and a motor are connected.

Conventionally, a hybrid vehicle using a transmission including a planetary gear mechanism that uses one engine, two first motor generators, and a second motor generator as power sources has been proposed (see, for example, Patent Document 1). In this hybrid vehicle, in addition to the engine, a plurality of modes in which the vehicle travels by inputting the rotation speed and torque from each motor generator are set.
JP 2003-32808 A

  In the above-described hybrid vehicle, when the gear ratio is controlled by the motor generator, a rotational speed higher than the engine rotational speed is input to the planetary gear mechanism. Specifically, the maximum pinion rotation speed of a planetary gear applied to an automatic transmission of a normal engine vehicle is about 10,000 rpm, whereas the maximum pinion rotation speed of a planetary gear applied to the hybrid vehicle is 17000 rpm. It also extends. In general, a needle bearing in which a plurality of cylindrical rollers are arranged in the circumferential direction is used for supporting the pinion, and the radial direction is supported by line contact, while the axial direction is supported via a washer. However, skew (rolling of the roller) occurs when the load is high, and the peripheral speed of the washer increases during high rotation, and there is a possibility that sufficient lubrication cannot be performed.

  The present invention has been made paying attention to the above problem, and an object of the present invention is to provide a pinion support structure for a planetary gear that can avoid problems such as skew during high rotation and high load.

  To achieve the above object, in the present invention, in a pinion support structure of a planetary gear that supports a pinion by a pinion shaft that revolves integrally with a pinion carrier, an angular ball bearing is provided between the pinion and the pinion shaft. It was.

  The angular ball bearing can support the inner race and the outer race by point contact, and can avoid skew and insufficient lubrication. In addition, the angular ball bearing can define both the radial direction and the axial direction, and it is possible to avoid insufficient lubrication by eliminating the washer and the like.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS A best mode for realizing a hybrid vehicle control device to which a planetary pinion support structure of the present invention is applied will be described below based on a first embodiment shown in the drawings.

First, the configuration will be described.
[Hybrid transmission drive system]
FIG. 1 is an overall system diagram showing a hybrid transmission to which a shift driving force control apparatus according to a first embodiment is applied.

  As shown in FIG. 1, the drive system of the hybrid transmission in the first embodiment has an engine E, a first motor generator MG1, and a second motor generator MG2 as power sources. A differential gear transmission in which these power sources E, MG1, MG2 and an output shaft OUT (output member) are coupled includes a first planetary gear PG1, a second planetary gear PG2, and a third planetary gear PG3. It has an engine clutch EC, a low brake LB (engagement element), a high clutch HC (engagement element), and a high / low brake HLB (engagement element).

  The first planetary gear PG1, the second planetary gear PG2, and the third planetary gear PG3 that constitute the differential gear transmission are all single-pinion type planetary gears. The first planetary gear PG1 includes a first sun gear S1, a first pinion carrier PC1 that supports the first pinion P1, and a first ring gear R1 that meshes with the first pinion P1. The second planetary gear PG2 includes a second sun gear S2, a second pinion carrier PC2 that supports the second pinion P2, and a second ring gear R2 that meshes with the second pinion P2. The third planetary gear PG3 includes a third sun gear S3, a third pinion carrier PC3 that supports the third pinion P3, and a third ring gear R3 that meshes with the third pinion P3.

  The first sun gear S1 and the second sun gear S2 are directly connected by a first rotating member M1, and the first ring gear R1 and the third sun gear S3 are directly connected by a second rotating member M2, and the second pinion carrier PC2 And the third ring gear R3 are directly connected by a third rotating member M3. Accordingly, the three planetary gears PG1, PG2, and PG3 include the first rotating member M1, the second rotating member M2, the third rotating member M3, the first pinion carrier PC1, the second ring gear R2, and the third pinion carrier PC3. 6 rotation elements.

  A connection relationship among the power sources E, MG1, MG2, the output shaft OUT, the engine clutch EC, and the engagement elements LB, HC, HLB for the six rotating elements of the differential gear transmission will be described. The second rotating member M2 is in a free state that is not connected to any of these, and the remaining five rotating elements are connected as follows.

  The engine output shaft of the engine E is connected to the third rotating member M3 via the engine clutch EC. That is, when the engine clutch EC is engaged, the second pinion carrier PC2 and the third ring gear R3 are set to the engine speed via the third rotation member M3.

  The first motor generator output shaft of the first motor generator MG1 is directly connected to the second ring gear R2. Further, a high / low brake HLB is interposed between the first motor generator output shaft and the transmission case TC. That is, when releasing the high / low brake HLB, the second ring gear R2 is set to the rotation speed of the first motor generator MG1. When the high / low brake HLB is engaged, the rotation of the second ring gear R2 and the first motor generator MG1 is stopped.

  The second motor generator output shaft of the second motor generator MG2 is directly connected to the first rotating member M1. Further, a high clutch HC is interposed between the second motor generator output shaft and the first pinion carrier PC1, and a low brake LB is interposed between the first pinion carrier PC1 and the transmission case TC. Is done. That is, when only the low brake LB is engaged, the first pinion carrier PC1 is stopped, and when only the high clutch HC is engaged, the first sun gear S1, the second sun gear S2, and the first pinion carrier PC1 are connected to the second motor generator MG2. Set the rotation speed. Further, when the low brake LB and the high clutch HC are engaged, the first sun gear S1, the second sun gear S2, and the first pinion carrier PC1 are stopped.

  The output shaft OUT is directly connected to the third pinion carrier PC3. A driving force is transmitted from the output shaft OUT to the left and right rear wheels 16 through a front differential and a drive shaft (not shown). On the other hand, a third motor MG3 is provided in the drive portion of the left and right front wheels 17, and the driving force from the third motor MG3 is transmitted to the left and right rear wheels via a reduction gear, a clutch, a rear differential, and a drive shaft. .

  As a result, as shown in FIGS. 2 and 3, on the nomograph, the first motor generator MG1 (R2), the engine E (PC2, R3), the output shaft OUT (PC3), the second motor generator MG2 (S1 , S2, PC1) can be introduced in order of rotation speed, and a rigid lever model can be introduced that can simply represent the dynamic behavior of the planetary gear train.

  Here, the “collinear diagram” is a velocity diagram used in a simple and easy-to-understand method of drawing instead of the method of obtaining by equation when considering the gear ratio of the differential gear. Take the number of rotations (rotation speed) of the rotating elements, take each rotating element such as ring gear, carrier, sun gear, etc. on the horizontal axis, and set the spacing between each rotating element to the gear ratio of the sun gear and ring gear (α, β, δ) It is arranged to become. 2A is a collinear diagram of the first planetary gear PG1, (2) is a collinear diagram of the second planetary gear PG2, and (3) is a third planetary gear PG3. FIG.

  The engine clutch EC is a multi-plate friction clutch that is fastened by hydraulic pressure, and is disposed at a position that coincides with the rotational speed axis of the engine E on the alignment charts of FIGS. 2 and 3. And torque are input to the third rotating member M3 which is an engine input rotating element of the differential gear transmission.

  The low brake LB is a multi-plate friction brake that is fastened by hydraulic pressure, and is disposed on the outer side of the rotational speed axis of the second motor generator MG2 on the alignment chart of FIGS. As shown in (a), (b) of FIG. 3 and (a), (b) of FIG. 3, a low-side transmission ratio mode for sharing the low-side transmission ratio is realized.

  The high clutch HC is a multi-plate friction clutch that is engaged by hydraulic pressure, and is disposed at a position that coincides with the rotational speed axis of the second motor generator MG2 on the alignment chart of FIGS. As shown in (d), (e) of FIG. 2 and (d), (e) of FIG. 3, the high side gear ratio mode for sharing the high side gear ratio is realized.

  The high / low brake HLB is a multi-plate friction brake that is fastened by hydraulic pressure, and is arranged at a position that coincides with the rotational speed axis of the first motor generator MG1 on the collinear diagrams of FIGS. The gear ratio is fixed to the low gear ratio on the underdrive side by fastening together with the high gear ratio, and the gear ratio is fixed to the high gear ratio on the overdrive side by fastening with the high clutch HC.

  [Driving mode]

  As shown in FIG. 2, the traveling mode includes a low fixed speed ratio mode (hereinafter referred to as “Low mode”), a low-side continuously variable speed ratio mode (hereinafter referred to as “Low-iVT mode”), and 2-speed fixed mode (hereinafter referred to as “2nd mode”), high-side continuously variable gear ratio mode (hereinafter referred to as “High-iVT mode”), and high fixed gear ratio mode (hereinafter referred to as “High mode”). And 5) driving modes.

  As shown in FIG. 2, the Low mode is obtained by engaging the low brake LB, releasing the high clutch HC, and engaging the high / low brake HLB. The Low-iVT mode is obtained by engaging the low brake LB, releasing the high clutch HC, and releasing the high / low brake HLB. The 2nd mode is obtained by engaging the low brake LB, engaging the high clutch HC, and releasing the high / low brake HLB. The High-iVT mode is obtained by releasing the low brake LB, engaging the high clutch HC, and releasing the high / low brake HLB. The High mode is obtained by releasing the low brake LB, engaging the high clutch HC, and engaging the high / low brake HLB.

  Regarding these five driving modes, the electric driving mode (hereinafter referred to as “EV mode”) in which only the motor generators MG1 and MG2 are driven without using the engine E, and the engine E and both motor generators MG1 and MG2 are used. And a hybrid driving mode (hereinafter referred to as “HEV mode”). Therefore, as shown in FIGS. 2 and 3, when the EV mode and the HEV mode are combined, ten driving modes are realized. Figure 2 shows the EV-Low mode collinear diagram, EV-Low-iVT mode collinear diagram, EV-2nd mode collinear diagram, EV-High-iVT mode collinear diagram, EV-High A collinear chart of each mode is shown. Fig. 3 shows the alignment chart of HEV-Low mode related to HEV mode, alignment chart of HEV-Low-iVT mode (high driving force running mode), alignment chart of HEV-2nd mode, HEV-High-iVT mode The alignment chart and HEV-High mode alignment chart are shown respectively.

  FIG. 4 is a front view showing the pinion carrier PC1 and the pinion PG of the first planetary gear PG1, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. The pinion carrier PC1 is slidably supported on the outer circumference of the first carrier plate 1, the second carrier plate 2, the first inner race 31 and the second inner race 32 provided on each plate, and the inner races 31, 32. And the two angular ball bearings 41 and 42 interposed between the inner races 31 and 32 and the pinion PG. Further, the first carrier plate 1 and the second carrier plate 2 are integrally fixed via bolts 5.

  The first carrier plate 1 has an annular flat plate shape, and four pinions PG are arranged at equal intervals along the circumference. The first carrier plate 1 is provided with a support hole 11 that supports the first inner race 31 at a position where the pinion PG is disposed. On the pinion PG side of the support hole 11 is provided a pedestal portion 13 that rises in a cylindrical shape for positioning a first inner race 31 described later in the axial direction. Bolt insertion holes 12 for inserting the bolts 5 are arranged at equal intervals on the circumference of the first carrier plate 1 and between the support holes 11.

  The second carrier plate 2 is composed of a flat plate-like portion 2a and a portion 2b erected in the axial direction. A support hole 21 is provided in the flat plate-shaped portion 2a at a position facing the support hole 11 of the first carrier plate 1 in the axial direction. Further, a first carrier plate support portion 22 is provided at a portion 2 b erected at a position facing the bolt insertion hole 12 of the first carrier plate 1 in the axial direction. The first carrier plate support portion 22 includes a first carrier plate support surface 22a extending toward the first carrier plate 1 in the axial direction, and a nut portion 22b provided in the first carrier plate support portion 22 and screwed with the bolt 5. Is provided.

  FIG. 5 is an enlarged partial sectional view of the pinion carrier PC1 in the vicinity of the pinion PG. The first inner race 31 of the first angular ball bearing 41 is inserted into the support hole 11 of the first carrier plate 1. The first inner race 31 includes an insertion shaft 31 a that is inserted into the support hole 11 and a diameter-expanded portion 31 b that abuts the pedestal portion 13 in the axial direction. On the outer periphery of the enlarged diameter portion 31b, an inclined surface 31c having a diameter reduced toward the second carrier plate 2 side is provided, and the ball 41a is supported by point contact together with the cage.

  The second inner race 32 of the second angular ball bearing 42 is inserted into the support hole 21 of the second carrier plate 2. The second inner race 32 includes an insertion shaft 32a that is inserted into the support hole 21 and a diameter-expanding portion 32b that abuts the pedestal portion 23 in the axial direction. On the outer periphery of the enlarged diameter portion 32b, there is provided an inclined surface 32c whose diameter is reduced toward the first carrier plate 1, and supports the ball 42a by point contact together with the cage. In other words, the first inner race 31 and the second inner race 32 are symmetrical in the axial direction.

  A first outer race portion 510 of the first angular ball bearing 41 and a second outer race portion 520 of the second angular ball bearing 42 are formed on the inner periphery of the pinion PG. The first outer race portion 510 is formed in an inclined surface shape whose diameter is reduced toward the first carrier plate 1 side. The second outer race part 520 is formed in an inclined surface shape whose diameter is reduced toward the second carrier plate 2 side.

Next, the assembly of the pinion PG will be described.
First step: The second inner race 32 is assembled in each of the four support holes 11 of the second carrier plate 2.
Second step: A second angular ball bearing 42 is assembled to the outer periphery of each second inner race 32.
Third step: The pinion PG is assembled to the outer periphery of the second angular ball bearing 42, respectively.
Fourth step: The first angular ball bearing 41 is assembled to the inner periphery of each pinion PG.
Fifth step: The first inner race 31 is assembled to each inner periphery of the first angular ball bearing 41.
Sixth step: The first carrier plate 1 is assembled.
Seventh step: The bolt 5 is inserted into the bolt insertion hole 12 and tightened with the nut portion 22b, and a preload is applied to the first angular ball bearing 41 and the second angular ball bearing 42 to form a sub-assembly.

  Here, the effect | action of preload provision by the volt | bolt 5 is demonstrated. When the bolt 5 is tightened, a force that moves to the left in FIG. 5 acts on the first carrier plate 1, while the second carrier plate 2 moves to the right in FIG. 5 by the nut portion 22 b. When an axial pressing force is applied to the side wall 31b of the first inner race 31 by the pedestal portion 13 of the first carrier plate 1, this pressing force is transmitted from the inclined surface 31c → the ball 41a → the inclined surface of the first outer race portion 510. Then, a preload is applied to the first angular ball bearing 41.

  On the other hand, when an axial pressing force is applied to the side wall 32b of the second inner race 32 by the pedestal portion 23 of the second carrier plate 2, the pressing force is applied to the inclined surface 32c → the ball 42a → the inclined surface of the second outer race portion 520. And a preload is applied to the second angular ball bearing 42.

  That is, when the bolt 5 is tightened, a preload can be applied to both the first angular ball bearing 41 and the second angular ball bearing 42.

  In addition, since an angular contact ball bearing causes generation | occurrence | production of abnormal noise and a vibration if preload is not provided, it is very important to give preload. At this time, in the conventional pinion support structure, a needle bearing is provided between the pinion shaft and the pinion, and the pinion shaft and the carrier plate are engaged by a pin or the like. Therefore, even if an angular ball bearing is simply arranged, a preload is applied. Can not do it. On the other hand, in Example 1, it becomes possible to apply a preload by tightening a bolt, and even if there is a variation between components, the optimum preload can be surely applied.

Next, the effect of Example 1 is demonstrated.
(1) Angular ball bearings 41 and 42 are provided between the pinion PG and the pinion shaft (inner races 31 and 32). The angular ball bearings 41 and 42 can be supported by point contact between the inner races 31 and 32 and the outer race (inner periphery of the pinion PG), and can avoid skew and insufficient lubrication. Further, the angular ball bearings 41 and 42 can define both the radial direction and the axial direction, and lack of lubrication can be avoided by eliminating a washer or the like.

  (2) The pinion carrier is removed from the first carrier plate 1, the second carrier plate 2, and the bolt 5 that integrally connects the first and second carrier plates 1 and 2 provided on both side surfaces of the planetary gear in the axial direction. The preload is applied to the angular ball bearings 41 and 42 by tightening the bolt 5. Therefore, it is possible to adjust the preload simultaneously by tightening the bolt 5 and to support it stably.

  (3) A first angular ball bearing 41 and a second angular ball bearing 42 having an axial biasing force opposite to the axial biasing force of the first angular ball bearing 41 are provided in parallel. In other words, the two angular ball bearings 41 and 42 are urged in a direction facing each other in the axial direction, and therefore can be positioned more reliably. Therefore, stable pinion support can be achieved.

  (4) The pinion shaft is a first inner race 31 that is a first pinion shaft member provided on the first carrier plate 1 side, and a second pinion shaft member that is provided on the second carrier plate 2 side. The inner race 32 was divided into angular ball bearings 41 and 42, respectively. Therefore, durability can be improved by sharing the load on the pinion PG.

  (5) The outer race of the angular ball bearing members 41 and 42 was formed on the inner periphery of the pinion PG. Therefore, the number of parts can be reduced.

  (6) The inner races 31 and 32 of the angular ball bearings 41 and 42 are pinion shafts. Therefore, the number of parts can be reduced.

  (7) The pinion PG can be stably supported even when applied to a unit in which the pinion rotates at a high speed as in a hybrid vehicle.

  still,

  Next, Example 2 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 6 is a front view illustrating the pinion carrier PC1 and the pinion PG of the first planetary gear PG1 of the second embodiment, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. In the first embodiment, the first carrier plate 1 and the second carrier plate 2 are separated from the first inner race 31 and the second inner race 32. However, in the second embodiment, the first carrier plate 1 and the second carrier plate 2 are separated. It differs in that it is integrated with the plate 2.

  The pinion carrier PC1 includes a first carrier plate 1, a second carrier plate 2, a first pinion shaft member 100 and a second pinion shaft member 200 erected in the axial direction from each plate, and first and second pinions. The pinion PG is slidably supported on the outer periphery of the shaft members 100 and 200, and the two angular ball bearings 41 and 42 are interposed between the first and second pinion shaft members 100 and 200 and the pinion PG. ing. Further, the first carrier plate 1 and the second carrier plate 2 are integrally fixed via bolts 5.

  The first carrier plate 1 has an annular flat plate shape, and four pinions PG are arranged at equal intervals along the circumference. Bolt insertion holes 12 through which the bolts 5 are inserted are arranged at equal intervals around the circumference of the first carrier plate 1 and between the first pinion shaft members 100.

  The second carrier plate 2 is composed of a flat plate-like portion 2a and a portion 2b erected in the axial direction. A second pinion shaft member 200 is provided at the flat plate-like portion 2a at a position facing the first pinion shaft member 100 of the first carrier plate 1 in the axial direction. Further, a first carrier plate support portion 22 is provided at a portion 2 b erected at a position facing the bolt insertion hole 12 of the first carrier plate 1 in the axial direction. The first carrier plate support portion 22 includes a first carrier plate support surface 22a extending toward the first carrier plate 1 in the axial direction, and a nut portion 22b provided in the first carrier plate support portion 22 and screwed with the bolt 5. Is provided.

  FIG. 7 is an enlarged partial sectional view of the pinion carrier PC1 in the vicinity of the pinion PG. A first inner race 101 ′ of the first angular ball bearing 41 is inserted into the outer periphery of the first pinion shaft member 100 of the first carrier plate 1. The first inner race 101 'is made of a material having higher wear resistance than the first carrier plate 1, and the first carrier plate 1 is made of, for example, a lightweight aluminum-based material, so that weight reduction and easy processing are possible. Ensure sex. On the outer periphery of the first inner race 101 ′, an inclined surface 101 ′ c that decreases in diameter toward the second carrier plate 2 side is provided, and the ball 41 a is supported by point contact together with the cage.

  A second inner race 201 ′ of the second angular ball bearing 42 is inserted into the outer periphery of the second pinion shaft member 200 of the second carrier plate 2. The second inner race 201 ′ is made of a material having higher wear resistance than that of the second carrier plate 2. The second carrier plate 2 is made of, for example, a light aluminum-based material, so that weight reduction and easy processing are possible. Ensure sex. On the outer periphery of the second inner race 201 ', there is provided an inclined surface 201'c whose diameter is reduced toward the first carrier plate 1, and supports the ball 42a by point contact together with the cage. That is, the first inner race 101 'and the second inner race 201' are symmetrical in the axial direction.

  A first outer race portion 510 of the first angular ball bearing 41 and a second outer race portion 520 of the second angular ball bearing 42 are formed on the inner periphery of the pinion PG. The first outer race portion 510 is formed in an inclined surface shape whose diameter is reduced toward the first carrier plate 1 side. The second outer race part 520 is formed in an inclined surface shape whose diameter is reduced toward the second carrier plate 2 side.

Next, the assembly of the pinion PG will be described.
First step: The second inner race 201 ′ is assembled to each of the four second pinion shaft members 200 of the second carrier plate 2.
Second step: A second angular ball bearing 42 is assembled to the outer periphery of each second inner race 201 ′.
Third step: The pinion PG is assembled to the outer periphery of the second angular ball bearing 42, respectively.
Fourth step: The first angular ball bearing 41 is assembled to the inner periphery of each pinion PG.
Fifth step: The first inner race 101 ′ is assembled to each of the first pinion shaft members 100 of the first carrier plate 1.
Sixth step: The first carrier plate 1 is assembled to the inner circumference of the first angular ball bearing 41 so that the first inner race 101 ′ is assembled.
Seventh step: The bolt 5 is inserted into the bolt insertion hole 12 and tightened with the nut portion 22b, and a preload is applied to the first angular ball bearing 41 and the second angular ball bearing 42 to form a sub-assembly.

  Here, the action of applying a preload by the bolt 5 will be described. When the bolt 5 is tightened, a force that moves to the left in FIG. 5 acts on the first carrier plate 1, while the second carrier plate 2 moves to the right in FIG. 5 by the nut portion 22 b. When an axial pressing force is applied to the first pinion shaft member 100 of the first carrier plate 1, this pressing force is transmitted from the inclined surface 101c → the ball 41a → the inclined surface of the first outer race portion 510, and the first angular ball A preload is applied to the bearing 41.

  On the other hand, when an axial pressing force is applied to the second pinion shaft member 100 of the second carrier plate 2, this pressing force is transmitted from the inclined surface 201c → the ball 42a → the inclined surface of the second outer race portion 520, so that the second A preload is applied to the angular ball bearing 42.

  That is, when the bolt 5 is tightened, a preload can be applied to both the first angular ball bearing 41 and the second angular ball bearing 42.

Next, the second embodiment can obtain the following operation and effect in addition to the operation and effect of the first embodiment.
(8) The first pinion shaft member 100 and the second pinion shaft member 200 are provided integrally with the first carrier plate 1 and the second carrier plate 2. Therefore, the pinion shaft can be eliminated and the number of parts can be reduced. Further, the first carrier plate 1 and the second carrier plate 2 do not need to be processed with support holes and the like, and the processability can be improved.

  (9) The first inner race 101 'and the second inner race 201' are separate members, and a material with high wear resistance is used. Therefore, it is not necessary to require wear resistance for each carrier plate. For example, when an aluminum material or the like is applied, the weight can be reduced and the processability can be improved.

  Next, Example 3 will be described. Since the basic configuration is the same, different points will be described. FIG. 8 is a front view showing the pinion carrier PC1 and the pinion PG of the first planetary gear PG1 of the third embodiment, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. The pinion carrier PC1 includes a first carrier plate 1, a second carrier plate 2, a pinion shaft 30 penetrating each plate, a pinion PG slidably supported on the outer periphery of the pinion shaft 30, and a pinion shaft 30. And two angular ball bearings 41 and 42 interposed between the pinion PG and the pinion PG. Further, the first carrier plate 1 and the second carrier plate 2 are integrally fixed via a nut 5 '.

  The first carrier plate 1 has an annular flat plate shape, and four pinions PG are arranged at equal intervals along the circumference. The first carrier plate 1 is provided with a support hole 11 that supports the pinion shaft 30 at a position where the pinion PG is disposed. On the pinion PG side of the support hole 11, a pedestal portion 13 that rises in a cylindrical shape is provided to position a first inner race 41 c described later in the axial direction.

  The second carrier plate 2 is composed of a flat plate-like portion 2a and a portion 2b erected in the axial direction. A support hole 21 is provided in the flat plate-shaped portion 2a at a position facing the support hole 11 of the first carrier plate 1 in the axial direction. On the pinion PG side of the support hole 21 is provided a pedestal portion 23 that rises in a cylindrical shape to position a second inner race 42c described later in the axial direction. Further, on the side of the support hole 21 that faces the pinion PG, an engagement groove 2d that engages with a snap ring 33 as a stopper provided on the pinion shaft 30 in the axial direction is provided.

  FIG. 9 is an enlarged partial sectional view in the vicinity of the pinion PG of the pinion carrier PC1. On the right end side (second carrier plate side) of the pinion shaft 30 in FIG. 9, a circumferential groove 32 that engages with the second carrier plate 2 and a snap ring 33 that engages in the axial direction is formed. Further, on the left end side (first carrier plate side) in FIG. 9 of the pinion shaft 30, a screw portion 31 that is screwed with the nut 5 'is formed.

  The pinion shaft 30 is inserted into the support hole 11 of the first carrier plate 1, and the first inner race 41 c of the first angular ball bearing 41 is inserted into the outer periphery of the pinion shaft 30 and the inner periphery of the pinion PG. ing. The side wall of the first inner race 41c is provided with a thick portion 410 that abuts the pedestal portion 13 in the axial direction, and an inclined surface 411 that becomes thinner toward the second carrier plate 2 side. It is supported by point contact.

  The pinion shaft 30 is inserted into the support hole 21 of the second carrier plate 2, and the second inner race 42 c of the second angular ball bearing 42 is inserted into the outer periphery of the pinion shaft 30 and the inner periphery of the pinion PG. ing. The side wall of the second inner race 42c is provided with a thick portion 420 that contacts the pedestal portion 23 in the axial direction, and an inclined surface 421 that becomes thinner toward the first carrier plate 1 side. It is supported by point contact. That is, the first inner race 41c and the second inner race 42c are symmetrical in the axial direction.

  On the inner periphery of the pinion PG, the side wall of the first outer race 41b of the first angular ball bearing 41 and the side wall of the second outer race 42b of the second angular ball bearing 42, the outer side convex portion 51 that abuts in the axial direction, respectively. A first collecting portion 52 that contacts the outer peripheral surface of the first outer race 41b and a second collecting portion 53 that contacts the outer peripheral surface of the second outer race 42b are formed. The first outer race 41b is provided with a thick portion 412 that abuts the outer side convex portion 51 in the axial direction, and an inclined surface 413 that becomes thinner toward the first carrier plate 1 side. The second outer race 42b is provided with a thick part 422 that abuts the outer convex part 51 in the axial direction, and an inclined surface 423 that becomes thinner toward the second carrier plate 2 side.

Next, the assembly of the pinion PG will be described.
First step: A snap ring is fitted into the circumferential groove 32 of the pinion shaft 30.
Second step: The pinion shaft 30 is inserted from the right side of the second carrier plate 2 in FIG.
Third step: The second angular ball bearing 42 is inserted into the outer periphery of the pinion shaft 30.
Fourth step: The pinion PG is inserted into the outer periphery of the second angular ball bearing 41, and the second angular ball bearing 41 is received in the second receiving portion 53 of the pinion PG, and the outer convex portion 51 and the second outer race are set. 42b is brought into contact with the side wall.
Fifth step: The first angular ball bearing 41 is mounted on the first receiving portion 52 of the pinion PG on the outer periphery of the pinion shaft 30, and the outer side convex portion 51 and the first outer race 41b side wall are brought into contact with each other. .
Sixth step: The first carrier plate 1 is assembled so that the pinion shaft 30 is inserted into the support hole 11.
Seventh step: The nut 5 ′ is screwed onto the threaded portion 31 of the pinion shaft 30 and tightened to apply preload to the first angular ball bearing 41 and the second angular ball bearing 42 to form a sub-assembly.

  Here, the preloading action by the nut 5 'will be described. When the nut 5 ′ is tightened, a force that moves to the left in FIG. 9 acts on the pinion shaft 30, and the second carrier plate 2 moves to the left in FIG. 9 via the snap ring 33. On the other hand, the first carrier plate 1 moves the first carrier plate 1 to the right in FIG. 9 by the nut 5 '. When an axial pressing force is applied to the side wall of the first inner race 41c by the pedestal portion 13 of the first carrier plate 1, this pressing force is transmitted from the inclined surface 411 to the ball 41a to the inclined surface 413 of the first outer race 41b. Further, preload is applied to the first angular ball bearing 41 by the axial contact between the outer-side convex portion 51 and the first outer race 41b.

  On the other hand, when an axial pressing force is applied to the side wall of the second inner race 42c by the pedestal 23 of the second carrier plate 2, the pressing force is changed from the inclined surface 421 to the ball 42a to the inclined surface 423 of the second outer race 42b. Further, a preload is applied to the second angular ball bearing 42 by the axial contact between the outer convex portion 51 and the second outer race 42b.

  That is, when the nut 5 ′ is tightened, a preload can be applied to both the first angular ball bearing 41 and the second angular ball bearing 42 by the contact with the outer side convex portion 51.

  Next, the effect of Example 3 is demonstrated.

  (10) The pinion carrier is composed of a first carrier plate 1 and a second carrier plate 2 provided on both axial sides of the planetary gear, and one end of the pinion shaft 30 is attached to the second carrier plate 2 by a snap ring. On the other hand, the preload is applied to the angular ball bearings 41 and 42 by restricting in the axial direction and tightening the nut 5 'from the first carrier plate 1 side. Therefore, it is possible to adjust the preload simultaneously by tightening the nut 5 ′, and stable support can be achieved.

  (11) On the inner periphery of the pinion PG, an outer convex portion 51 for positioning the axial direction of the outer races 41b, 42b of the angular ball bearings 41, 42 is provided, and on the side surfaces of the first and / or second carrier plates 1, 2. The base portions 13 and 23 for urging the inner races 41c and 42c of the angular ball bearings 41 and 42 in the axial direction are provided. Therefore, preload can be applied to the angular ball bearings 41 and 42 by tightening the nut 5 '. In the first embodiment, two angular contact ball bearings are arranged in parallel. However, when only one angular contact ball bearing is arranged, the inner race is pressed in the axial direction by one carrier plate, and the other carrier plate. Therefore, the outer race may be pressed in the axial direction.

  Next, Example 4 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 10 is a front view showing the pinion carrier PC1 and the pinion PG of the first planetary gear PG1 of the fourth embodiment, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. FIG. 11 is an enlarged partial sectional view of the pinion carrier PC1 in the vicinity of the pinion PG. In the third embodiment, the snap ring 33 is provided on the pinion shaft 30, but the fourth embodiment is different in that the diameter-expanded portion 34 is integrally formed on the pinion shaft 30. Since other configurations are the same, description thereof is omitted.

Next, the assembly of the pinion PG will be described.
First step: The pinion shaft 30 is inserted from the right side of the second carrier plate 2 in FIG.
Second step: The second angular ball bearing 42 is inserted into the outer periphery of the pinion shaft 30.
Third step: The pinion PG is inserted into the outer periphery of the second angular ball bearing 41, and the second angular ball bearing 41 is received in the second receiving portion 53 of the pinion PG, and the outer convex portion 51 and the second outer race are set. 42b is brought into contact with the side wall.
Fourth step: The first angular ball bearing 41 is accommodated on the outer periphery of the pinion shaft 30 and the first accommodation portion 52 of the pinion PG, and the outer side convex portion 51 and the first outer race 41b side wall are brought into contact with each other. .
Fifth step: The first carrier plate 1 is assembled so that the pinion shaft 30 is inserted into the support hole 11.
Sixth step: The nut 5 ′ is screwed onto the threaded portion 31 of the pinion shaft 30 and tightened to apply a preload to the first angular ball bearing 41 and the second angular ball bearing 42, thereby forming a sub-assembly.

Next, Example 4 can obtain the following effects in addition to the effects of Example 3.
(12) The pinion shaft 30 is provided with an enlarged diameter portion 34. Therefore, the snap ring can be eliminated, and the number of parts can be reduced and the number of assembly steps can be reduced.

  Next, Example 5 will be described. FIG. 12 is a front view showing the pinion carrier PC1 and the pinion PG of the first planetary gear PG1, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. The pinion carrier PC1 includes a first carrier plate 1, a second carrier plate 2, a pinion shaft 30 penetrating each plate, a pinion PG slidably supported on the outer periphery of the pinion shaft 30, and a pinion shaft 30. And two angular ball bearings 41 and 42 interposed between the pinion PG and the pinion PG. Bolt insertion holes 12 for inserting the bolts 5 are arranged at equal intervals on the circumference of the first carrier plate 1 and between the support holes 11.

  The first carrier plate 1 has an annular flat plate shape, and four pinions PG are arranged at equal intervals along the circumference. The first carrier plate 1 is provided with a support hole 11 that supports the pinion shaft 30 at a position where the pinion PG is disposed. On the pinion PG side of the support hole 11, a pedestal portion 13 that rises in a cylindrical shape is provided to position a first inner race 41 c described later in the axial direction.

  The second carrier plate 2 is composed of a flat plate-like portion 2a and a portion 2b erected in the axial direction. A support hole 21 is provided in the flat plate-shaped portion 2a at a position facing the support hole 11 of the first carrier plate 1 in the axial direction. Further, a first carrier plate support portion 22 is provided at a portion 2 b erected at a position facing the bolt insertion hole 12 of the first carrier plate 1 in the axial direction. The first carrier plate support portion 22 includes a first carrier plate support surface 22a extending toward the first carrier plate 1 in the axial direction, and a nut portion 22b provided in the first carrier plate support portion 22 and screwed with the bolt 5. Is provided.

  FIG. 13 is an enlarged partial sectional view in the vicinity of the pinion PG of the pinion carrier PC1. On the right end side (second carrier plate side) of the pinion shaft 30 in FIG. 13, an engagement portion 31 that engages with the second carrier plate 2 and the pinion side side surface in the axial direction is formed. The engaging portion 31 abuts on the second carrier plate 2 on the side wall on the second carrier plate side, and abuts on a second inner race 42c described later on the side wall on the pinion side.

  The pinion shaft 30 is inserted into the support hole 11 of the first carrier plate 1, and the first inner race 41 c of the first angular ball bearing 41 is inserted into the outer periphery of the pinion shaft 30 and the inner periphery of the pinion PG. ing. The side wall of the first inner race 41c is provided with a thick portion 410 that abuts the pedestal portion 13 in the axial direction, and an inclined surface 411 that becomes thinner toward the second carrier plate 2 side. It is supported by point contact.

  The pinion shaft 30 is inserted into the support hole 21 of the second carrier plate 2, and the second inner race 42 c of the second angular ball bearing 42 is inserted into the outer periphery of the pinion shaft 30 and the inner periphery of the pinion PG. ing. The side wall of the second inner race 42c is provided with a thick part 420 that abuts the side wall of the engaging part 31 in the axial direction, and an inclined surface 421 that becomes thinner toward the first carrier plate 1 side. The ball 42a is supported by point contact. That is, the first inner race 41c and the second inner race 42c are symmetrical in the axial direction.

  On the inner periphery of the pinion PG, the side wall of the first outer race 41b of the first angular ball bearing 41 and the side wall of the second outer race 42b of the second angular ball bearing 42, the outer side convex portion 51 that abuts in the axial direction, respectively. A first collecting portion 52 that contacts the outer peripheral surface of the first outer race 41b and a second collecting portion 53 that contacts the outer peripheral surface of the second outer race 42b are formed. The first outer race 41b is provided with a thick portion 412 that abuts the outer side convex portion 51 in the axial direction, and an inclined surface 413 that becomes thinner toward the first carrier plate 1 side. The second outer race 42b is provided with a thick part 422 that abuts the outer convex part 51 in the axial direction, and an inclined surface 423 that becomes thinner toward the second carrier plate 2 side.

Next, the assembly of the pinion PG will be described.
1st process: The said pinion shaft 30 is inserted from the right side in FIG. 13 of the 2nd carrier plate 2, and the side wall of the engaging part 31 and the 2nd carrier plate 2 are contact | abutted.
Second step: The second angular ball bearing 42 is inserted into the outer periphery of the pinion shaft 30.
Third step: The pinion PG is inserted into the outer periphery of the second angular ball bearing 41, and the second angular ball bearing 41 is received in the second receiving portion 53 of the pinion PG, and the outer convex portion 51 and the second outer race are set. 42b is brought into contact with the side wall.
Fourth step: The first angular ball bearing 41 is mounted on the first receiving portion 52 of the pinion PG at the outer periphery of the pinion shaft 30, and the outer convex portion 51 and the first outer race 41b side wall are brought into contact with each other. .
Fifth step: The first carrier plate 1 is assembled so that the pinion shaft 30 is inserted into the support hole 11.
Sixth step: The bolt 5 is screwed onto the threaded portion 22b of the second carrier plate 2 and tightened to apply a preload to the first angular ball bearing 41 and the second angular ball bearing 42 to form a sub-assembly.

  Here, the effect | action of preload provision by the volt | bolt 5 is demonstrated. When the bolt 5 is tightened, a force that moves to the left in FIG. 13 acts on the first carrier plate 1. On the other hand, the second carrier plate 2 is moved to the right in FIG. When an axial pressing force is applied to the side wall of the first inner race 41c by the pedestal portion 13 of the first carrier plate 1, this pressing force is transmitted from the inclined surface 411 to the ball 41a to the inclined surface 413 of the first outer race 41b. Further, preload is applied to the first angular ball bearing 41 by the axial contact between the outer-side convex portion 51 and the first outer race 41b.

  On the other hand, when a pressing force acts on the side wall of the engaging portion 31 from the second carrier plate 2 and an axial pressing force acts on the side wall of the second inner race 42c from the side wall of the engaging portion 31, the pressing force is inclined. It is transmitted from the surface 421 to the ball 42a to the inclined surface 423 of the second outer race 42b, and further, a preload is applied to the second angular ball bearing 42 by the axial contact between the outer convex portion 51 and the second outer race 42b. The

  That is, when the bolt 5 is tightened, a preload can be applied to both the first angular ball bearing 41 and the second angular ball bearing 42 by the contact with the outer side convex portion 51.

Next, the effect of Example 5 is demonstrated.
(13) At the end of the pinion shaft 30, there is provided an engaging portion 31 that abuts against the side wall on the pinion side of the second carrier plate 2 and abuts against the side wall of the inner race 42c of the second angular ball bearing 42. A pedestal portion 13 that contacts the inner race 41c side wall of the first angular ball bearing 41 is provided on the pinion side side wall of the plate 1, and the inner periphery of the pinion PG contacts the outer race 41b side wall of the first angular ball bearing 41. The outer side convex part 51 which contact | abuts the outer race 42b side wall of the 2nd angular ball bearing 42 was provided, and the preload was given to the 1st and 2nd angular ball bearings 41 and 42 by the bolt 5 tightening. Therefore, the positioning of the pinion shaft 30 itself and the positioning of the second inner race 42c of the second angular ball bearing 42 can be performed by the engaging portion 31 provided on the pinion shaft 30. Further, by tightening the bolt 5, a preload can be applied to the angular ball bearings 41 and 42.

  Next, Example 6 will be described. FIG. 14 is a front view showing the pinion carrier PC1 and the pinion PG of the first planetary gear PG1, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. The pinion carrier PC1 includes a first carrier plate 1, a second carrier plate 2, and two first and second angular ball bearings 41 and 42 that rotatably support the pinion PG. Further, the first carrier plate 1 and the second carrier plate 2 are integrally fixed via bolts 5. The first angular ball bearing 41 includes a ball 41a, a first outer race 41b, and a first inner race 41c. The second angular ball bearing 42 includes a ball 42a, a second outer race 42b, and a second inner race 42c.

  The first carrier plate 1 has an annular flat plate shape, and four pinions PG are arranged at equal intervals along the circumference. The first carrier plate 1 is provided with a receiving portion 1c for receiving the first angular ball bearing 41 at a position where the pinion PG is disposed. The side surface of the housing portion 1c opposite to the pinion PG has a shape protruding in the axial direction, and measures such as heat and load transmitted from the bearing (heat capacity and strength ensured) are taken. Moreover, the cylindrical part 10c which positions the 1st outer race 41b to radial direction, and the bottom part 10d which positions the 1st outer race 41b to an axial direction are provided in the pinion side of the accommodating part 1c. Bolt insertion holes 12 through which the bolts 5 are inserted are arranged at equal intervals around the circumference of the first carrier plate 1 and between the first pinion shaft members 100.

  The second carrier plate 2 is composed of a flat plate-like portion 2a and a portion 2b erected in the axial direction. A receiving portion 2c for receiving the second angular ball bearing 42 is provided in a flat plate-like portion 2a at a position facing the first pinion shaft member 100 of the first carrier plate 1 in the axial direction. The side surface of the housing portion 2c opposite to the pinion PG has a shape protruding in the axial direction, and measures such as heat and load transmitted from the bearing (heat capacity and strength ensured) are taken.

  Moreover, the cylindrical part 20c which positions the 2nd outer race 42b to radial direction, and the bottom part 20d which positions the 2nd outer race 42b to an axial direction are provided in the pinion side of the accommodating part 2c. Further, a first carrier plate support portion 22 is provided at a portion 2 b erected at a position facing the bolt insertion hole 12 of the first carrier plate 1 in the axial direction. The first carrier plate support portion 22 includes a first carrier plate support surface 22a extending toward the first carrier plate 1 in the axial direction, and a nut portion 22b provided in the first carrier plate support portion 22 and screwed with the bolt 5. Is provided.

  FIG. 15 is an enlarged partial sectional view in the vicinity of the pinion PG of the pinion carrier PC1. The first inner race 41c of the first angular ball bearing 41 is inserted into the first pinion shaft member 100 extending from the side surface of the pinion PG. The first inner race 41c is a side surface of the pinion PG and extends toward the first carrier plate 1 and a diameter-enlarged portion 411 that contacts the contact portion 101 provided on the outer periphery of the first pinion shaft member 100 in the axial direction. An inclined surface 411 having a reduced diameter is provided, and the ball 41a is supported by point contact together with the cage. The side surface of the first outer race 41b and the pinion side surface 102 are preferably in a non-contact state.

  The second inner race 42c of the second angular ball bearing 42 is inserted into the second pinion shaft member 200 extending from the side surface of the pinion PG. The second inner race 42c is a side surface of the pinion PG and is provided on the outer periphery of the second pinion shaft member 200. The second inner race 42c is provided on the outer side of the second pinion shaft member 200. An inclined surface 423 that decreases in diameter is provided, and the ball 42a is supported by point contact together with the cage. The side surface of the second outer race 42b and the pinion side surface 202 are preferably in a non-contact state.

  The first outer race 41b is provided with a diameter-enlarged portion 413 that abuts the bottom portion 10d of the housing portion 1c in the axial direction and an inclined surface 412 that decreases in diameter toward the pinion side, and supports the ball 41a together with the cage by point contact. is doing.

  The second outer race 42b is provided with a diameter-enlarged portion 422 that abuts the bottom portion 20d of the housing portion 2c in the axial direction and an inclined surface 421 that decreases in diameter toward the pinion side, and supports the ball 42a by point contact together with the cage. is doing. That is, the first outer race 41b and the second outer race 42b are symmetrical in the axial direction.

Next, the assembly of the pinion PG will be described.
First step: The second angular ball bearing 42 is assembled to each of the four receiving portions 2 c of the second carrier plate 2.
Second step: The second pinion shaft member 200 is inserted into the inner periphery of the second angular ball bearing 42, and the pinion PG is assembled.
3rd process: The 1st angular ball bearing 41 is assembled | attached to the outer periphery of the 1st pinion shaft member 100 of each pinion PG.
Fourth step: Assembling the first carrier plate 1 so that the first angular ball bearing 41 is accommodated in the receiving portion 1c.
Fifth step: The bolt 5 is inserted into the bolt insertion hole 12 and tightened with the nut portion 22b, preload is applied to the first angular ball bearing 41 and the second angular ball bearing 42, and sub-assembly is performed.

  Here, the effect | action of preload provision by the volt | bolt 5 is demonstrated. When the bolt 5 is tightened, a force that moves to the left in FIG. 15 acts on the first carrier plate 1. On the other hand, the second carrier plate 2 is moved to the right in FIG. When an axial pressing force acts on the side wall of the first outer race 41b by the bottom 10d of the first carrier plate 1, this pressing force is transmitted from the inclined surface 412 to the ball 41a to the inclined surface 411 of the first inner race 41c, Further, preload is applied to the first angular ball bearing 41 by the axial contact between the first inner race 41c and the contact portion 101 of the pinion PG.

  On the other hand, when a pressing force is applied to the side wall of the second outer race 42b by the bottom portion 20d of the second carrier plate 2, this pressing force is transmitted from the inclined surface 421 → the ball 42a → the inclined surface 423 of the second inner race 42c. Preload is applied to the second angular ball bearing 42 by the axial contact between the second inner race 42c and the contact portion 201 of the pinion PG.

  That is, when the bolt 5 is tightened, a pressing force acts between the bottom portions 10d and 20d and the contact portions 101 and 201, and preload is applied to both the first angular ball bearing 41 and the second angular ball bearing 42. Can do.

Next, the effect of Example 7 is demonstrated.
(14) The first pinion shaft member 100 and the second pinion shaft member 200 are provided integrally with the pinion PG. Therefore, the pinion shaft can be eliminated and the number of parts can be reduced.

  Next, Example 7 will be described. FIG. 16 is a front view showing the pinion carrier PC1 and the pinion PG of the first planetary gear PG1, and a partial cross-sectional view of the pinion carrier PC1 near the pinion and the bolt. The pinion carrier PC1 includes a first carrier plate 1, a second carrier plate 2, and two first and second angular ball bearings 41 and 42 that rotatably support the pinion PG. Further, the first carrier plate 1 and the second carrier plate 2 are integrally fixed via bolts 5. The first angular ball bearing 41 includes a ball 41a, a first outer race 41b, and a first inner race 41c. The second angular ball bearing 42 includes a ball 42a, a second outer race 42b, and a second inner race 42c.

  The first carrier plate 1 has an annular flat plate shape, and four pinions PG are arranged at equal intervals along the circumference. The first carrier plate 1 is provided with a first pinion shaft member 100 that supports the first inner race 41c at a position where the pinion PG is disposed. Further, a contact portion 101 that is raised in a cylindrical shape for positioning the first inner race 41c in the axial direction is provided. Bolt insertion holes 12 through which the bolts 5 are inserted are arranged at equal intervals around the circumference of the first carrier plate 1 and between the first pinion shaft members 100.

  The second carrier plate 2 is composed of a flat plate-like portion 2a and a portion 2b erected in the axial direction. A second pinion shaft member 200 is provided at the flat plate-like portion 2a at a position facing the first pinion shaft member 100 of the first carrier plate 1 in the axial direction. Further, a first carrier plate support portion 22 is provided at a portion 2 b erected at a position facing the bolt insertion hole 12 of the first carrier plate 1 in the axial direction. The first carrier plate support portion 22 includes a first carrier plate support surface 22a extending toward the first carrier plate 1 in the axial direction, and a nut portion 22b provided in the first carrier plate support portion 22 and screwed with the bolt 5. Is provided.

  FIG. 17 is an enlarged partial sectional view of the pinion carrier PC1 in the vicinity of the pinion PG. A first inner race 41 c of a first angular ball bearing 41 is inserted into the first pinion shaft member 100 of the first carrier plate 1. The first inner race 41c is provided with an enlarged diameter portion 410 that abuts against the abutting portion 101 in the axial direction, and an inclined surface 411 that decreases in diameter toward the second carrier plate 2 side. It is supported by contact.

  A second inner race 42 c of a second angular ball bearing 42 is inserted into the second pinion shaft member 200 of the second carrier plate 2. The second inner race 42c is provided with an enlarged diameter portion 420 that abuts against the abutting portion 201 in the axial direction, and an inclined surface 421 that decreases in diameter toward the first carrier plate 1 side. It is supported by contact. That is, the first inner race 41c and the second inner race 42c are symmetrical in the axial direction.

  The first outer race 41b is provided with a diameter-enlarged portion 412 that is in axial contact with a side wall of an outer-side convex portion 51, which will be described later, and an inclined surface 413 that decreases in diameter toward the first carrier plate 1 side. 41a is supported by point contact.

  The second outer race 42b is provided with a diameter-enlarged portion 422 that is in axial contact with the side wall of an outer-side convex portion 51, which will be described later, and an inclined surface 423 that decreases in diameter toward the second carrier plate 2 side. 42a is supported by point contact. That is, the first outer race 41b and the second outer race 42b are symmetrical in the axial direction.

  On the inner periphery of the pinion PG, a first housing portion 52 that houses the first outer race 41b of the first angular ball bearing 41 and a second housing that houses the second outer race 42b of the second angular ball bearing 42. A portion 53 is formed. In addition, an outer-side convex portion 51 that abuts against the side walls of the first and second outer races 41 b and 42 b is formed between the first housing portion 52 and the second housing portion 53.

Next, the assembly of the pinion PG will be described.
First step: A second angular ball bearing 42 is assembled to each of the four second pinion shaft members 200 of the second carrier plate 2.
Second step: The pinion PG is assembled to the outer periphery of the second angular ball bearing 42, respectively.
Third step: The first angular ball bearing 41 is assembled to the inner periphery of each pinion PG.
4th process: The 1st pinion shaft member 100 is inserted in each inner periphery of the 1st angular ball bearing 41, and the 1st carrier plate 1 is assembled | attached.
Fifth step: The bolt 5 is inserted into the bolt insertion hole 12 and tightened with the nut portion 22b, preload is applied to the first angular ball bearing 41 and the second angular ball bearing 42, and sub-assembly is performed.

  Here, the effect | action of preload provision by the volt | bolt 5 is demonstrated. When the bolt 5 is tightened, a force that moves to the left in FIG. 17 acts on the first carrier plate 1. On the other hand, the second carrier plate 2 is moved to the right in FIG. When an axial pressing force acts on the side wall of the first inner race 41c by the contact portion 101 of the first carrier plate 1, this pressing force is transmitted from the inclined surface 411 to the ball 41a to the inclined surface 413 of the first outer race 41b. Further, a preload is applied to the first angular ball bearing 41 by the axial contact between the outer convex portion 51 and the first outer race 41b.

  On the other hand, when a pressing force is applied to the side wall of the second inner race 42c by the contact portion 201 of the second carrier plate 2, this pressing force is transmitted from the inclined surface 421 → the ball 42a → the inclined surface 423 of the second outer race 42b. Further, a preload is applied to the second angular ball bearing 42 by the axial contact between the outer-side convex portion 51 and the second outer race 42b.

  That is, when the bolt 5 is tightened, a pressing force is applied between the contact portions 101 and 201 and the outer side convex portion 51, and preload is applied to both the first angular ball bearing 41 and the second angular ball bearing 42. be able to.

Next, the effect of Example 7 is demonstrated.
(15) The first pinion shaft member 100 and the second pinion shaft member 200 are formed integrally with the first carrier plate 1 and the second carrier plate 2, and the contact portions 101 and 201 are formed. Therefore, the number of assembling steps can be reduced most in the above embodiments.

1 is a skeleton diagram illustrating a hybrid transmission according to a first embodiment. FIG. FIG. 5 is a collinear diagram illustrating five travel modes in an electric vehicle mode in the hybrid transmission according to the first embodiment. FIG. 5 is a collinear diagram illustrating five travel modes in a hybrid vehicle mode in the hybrid transmission according to the first embodiment. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 1, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. 3 is an enlarged partial cross-sectional view of the pinion carrier of Example 1 in the vicinity of the pinion. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 2, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. FIG. 6 is an enlarged partial cross-sectional view of the pinion carrier of Example 2 in the vicinity of the pinion. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 3, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. FIG. 6 is an enlarged partial cross-sectional view of the pinion carrier of Example 3 in the vicinity of the pinion. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 4, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. FIG. 6 is an enlarged partial cross-sectional view of the pinion carrier of Example 4 in the vicinity of the pinion. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 5, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. FIG. 10 is an enlarged partial cross-sectional view of the pinion carrier of Example 5 in the vicinity of the pinion. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 6, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. It is an expanded partial sectional view of the pinion vicinity of the pinion carrier of Example 6. It is the front view showing the pinion carrier and pinion of the 1st planetary gear of Example 7, and the fragmentary sectional view near the pinion and bolt of a pinion carrier. It is an expanded partial sectional view of the pinion vicinity of the pinion carrier of Example 7.

Explanation of symbols

E engine
MG1 1st motor generator
MG2 Second motor generator
MG3 3rd motor
OUT Output shaft (output member)
PG1 1st planetary gear
PG2 2nd planetary gear
PG3 3rd planetary gear
EC engine clutch
LB Low brake (engagement element)
HC high clutch (engagement element)
HLB High / Low brake (engagement element)
DESCRIPTION OF SYMBOLS 1 1st carrier plate 1c Storage part 2 2nd carrier plate 2c Storage part 2d Engaging groove 5 'Nut 5 Bolt 10c Cylindrical part 10d, 20d Bottom part 11,21 Support hole 12 Bolt insertion hole 13,23 Base part 21 Support hole 22 Carrier plate support portion 22a Carrier plate support surface 22b Nut portion 30 Pinion shaft 31 Engagement portion 33 Snap ring 34 Expanded portion 41 First angular ball bearing 42 Second angular ball bearing 41a, 42a Ball 41b, 42b Outer race 41c 42c Inner race 51 Outer side convex part
100, 200 Pinion shaft member
PG pinion

Claims (10)

In a pinion support structure of a planetary gear that supports a pinion by a pinion shaft that revolves integrally with a pinion carrier,
A planetary gear pinion support structure, wherein an angular ball bearing is provided between the pinion and the pinion shaft. The pinion support structure for a planetary gear according to claim 1,
The pinion carrier comprises a first carrier plate provided on both axial sides of the planetary gear, a second carrier plate, and a bolt that integrally connects the first and second carrier plates;
A pinion support structure for a planetary gear, wherein a preload is applied to the angular ball bearing by tightening the bolt. The pinion support structure for a planetary gear according to claim 1,
The pinion carrier comprises a first carrier plate and a second carrier plate provided on both axial sides of the planetary gear;
Screwed with a nut at the end of the pinion shaft, and provided with a threaded portion integrating the first and / or second carrier plate and the pinion shaft;
A pinion support structure for a planetary gear, wherein a preload is applied to the angular ball bearing by tightening the nut.   The angular ball bearing has a configuration in which a first angular ball bearing and a second angular ball bearing having an axial biasing force opposite to the axial biasing force of the first angular ball bearing are provided in parallel. A pinion support structure for a planetary gear. The pinion support structure for a planetary gear according to any one of claims 1 to 4,
The pinion shaft is divided into a first pinion shaft member provided on the first carrier plate side and a second pinion shaft member provided on the second carrier plate side, and the first pinion shaft member and the A planetary gear pinion support structure, wherein each of the second pinion shaft members is provided with the angular ball bearing. The pinion support structure for a planetary gear according to claim 4,
On the inner periphery of the pinion, an outer side convex portion for positioning the outer race of the first and second angular ball bearings in the axial direction is provided.
A pinion support structure for a planetary gear, wherein a pedestal for positioning an inner race of the first and / or second angular ball bearing in the axial direction is provided on a side surface of the first and / or second carrier plate. The pinion support structure for a planetary gear according to claim 6,
At the end of the pinion shaft, an engagement portion is provided that contacts the pinion side wall of the first carrier plate and contacts the inner race side wall of the second angular ball bearing,
A pinion support structure for a planetary gear, wherein a preload is applied to the first and second angular ball bearings by tightening the bolt. The pinion support structure for a planetary gear according to any one of claims 1 to 7,
A planetary gear pinion support structure, wherein an outer race of the angular ball bearing is formed on an inner periphery of the pinion. The pinion support structure for a planetary gear according to any one of claims 1 to 8,
A pinion support structure for a planetary gear, wherein an inner race of the angular ball bearing is formed on an outer periphery of the pinion shaft. The pinion support structure for a planetary gear according to any one of claims 1 to 9,
In the planetary gear, four or more input / output elements are arranged on a collinear diagram, one of the two elements arranged inside the input / output elements is input from the engine, and the other is supplied to the drive system. And a differential device for a hybrid vehicle in which a first motor generator and a second motor generator are respectively connected to two elements arranged on both outer sides of the inner element. Pinion support structure for planetary gears.

Images