JP2005155856A - Planetary gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent the occurrence of damage such as abnormal abrasion, scoring and seizing on a washer 34a on one side in slide contact with an end face of a planetary gear 32. <P>SOLUTION: On the end faces of the planetary gear 32 in the axial direction, cylindrical recessed parts 35 are provided by making each end face to be recessed axially. Then, a part of one washer 34a and the planetary gear 32 are superimposed radially by making a part of the washer 34a enter axially into the recessed part 35. In addition to this, positioning is performed concerning the radial direction of the washer 34a by means of inner peripheral face of the recessed part 35 by proximately opposing a part entered into each recessed part 35 on the outer peripheral face of the washer 34a to the inner peripheral face of the recessed part 35. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an improvement of a planetary gear device that constitutes an automatic transmission for an automobile, for example. Specifically, it prevents the occurrence of abnormal wear, galling, seizure, or other damage to the planetary gear and the washer that is in sliding contact with the end face of the planetary gear, thereby realizing a structure having excellent durability.

  Conventionally, a structure as shown in FIGS. 5 to 6 is widely known as a planetary gear device that constitutes an automatic transmission for an automobile. Such a conventionally known planetary gear device includes a sun gear 1 having teeth 1a formed on the outer peripheral surface, and a ring gear 2 arranged concentrically with the sun gear 1 and having teeth 2a formed on the inner peripheral surface. Between them, a plurality (generally 3 to 4) of planetary gears 3 and 3 are arranged at equal intervals in the circumferential direction. The teeth 3a formed on the outer peripheral surfaces of the plurality of planetary gears 3 and 3 are meshed with the teeth 1a and 2a.

  The plurality of planetary gears 3 and 3 are rotatably supported via radial needle bearings 5 around the intermediate portions in the axial direction of the planetary support shafts 4 and 4, respectively. Each of these radial needle bearings 5 has a cylindrical inner ring raceway 6 at the intermediate outer peripheral surface of each of the planetary support shafts 4, 4 and a cylindrical outer ring raceway 7 at the inner peripheral surface of each of the planetary gears 3, 3. It is said. The rolling surfaces of the needles 8 and 8 are brought into rolling contact with the inner ring raceway 6 and the outer ring raceway 7.

  The planet support shafts 4 and 4 are supported by a carrier 9 that is rotatable around the sun gear 1. In the illustrated example, both end portions in the axial direction of the planetary support shafts 4 and 4 are respectively supported by a pair of support plates 10 a and 10 b that are parallel to each other and that constitute the carrier 9. Further, the sun gear 1 is formed in a cylindrical shape, and one of the support plates 10a and 10b constituting the carrier 9 (on the right side in the drawing) is circularly formed with an L-shaped cross section. It is formed in a ring shape. The cylindrical portion 11 formed on the inner peripheral edge of the one support plate 10a is spline-engaged with the outer peripheral surface of the rotary shaft 12.

  The sun gear 1 is supported around the rotary shaft 12 so as to be rotatable relative to the rotary shaft 12. The ring gear 2 is supported around the sun gear 1, the carrier 9 and the rotating shaft 12 so as to be rotatable relative to the members 1, 9 and 12. Further, between the respective planetary gears 3, 3 and the respective radial needle bearings 5, the respective needles 8, 8, and the respective inner side surfaces of the respective support plates 10 a, 10 b constituting the carrier 9, Ring-shaped washers 13a and 13b are respectively provided. These washers 13a and 13b regulate the displacement of the planetary gears 3 and 3 and the needles 8 and 8 in the axial direction while supporting the thrust load applied to the planetary gears 3 and 3.

  The planetary gear device as described above uses the rotary shaft 12 as a drive shaft or a driven shaft, and connects the center of the sun gear 1 or the ring gear 2 to the driven shaft or the drive shaft. Then, by switching which gears 1, 2, and 3 are rotatable and which gears 1, 2, and 3 are non-rotatable, the shift between the drive shaft and the driven shaft and the conversion of the rotation direction are switched. To do. Since the configuration and operation of such a planetary gear device itself are well known in the art and are not related to the gist of the present invention, detailed description thereof is omitted.

  Conventionally, as an automatic transmission for an automobile equipped with the planetary gear device as described above, a combination of a plurality of planetary gear devices, or a planetary gear type formed by combining a plurality of such planetary gear devices. A combination of a transmission and a toroidal continuously variable transmission is widely known. Of these, automatic transmissions composed of a combination of a plurality of planetary gear devices are described in many publications such as Non-Patent Document 1, and are actually well-known in many automobiles. Also, automatic transmissions comprising a combination of a toroidal-type continuously variable transmission and a planetary gear type transmission are well known and described in numerous publications such as Patent Documents 2 to 3.

  As an example of an automatic transmission incorporating such a planetary gear device, FIG. 7 shows a continuously variable transmission described in Patent Document 2. This continuously variable transmission is formed by combining a toroidal continuously variable transmission 14 and a planetary gear type transmission 15 formed by combining a plurality of planetary gear devices. Of these, the toroidal-type continuously variable transmission 14 transmits rotation between a pair of input side disks 17, 17 and output side disk 18 that rotate together with the input shaft 16 by a plurality of power rollers 19, 19. By changing the inclination angle of each of the power rollers 19, 19, the gear ratio between the disks 17, 18 is changed.

  The planetary gear type transmission 15 has a plurality of planetary gears 21a, 21b, and 21c connected to the input shaft 16 and a carrier 20 fixedly coupled to one (right side in FIG. 7) of the input side disk 17 with the input. A plurality of planetary gears 24a and 24b are rotatably supported on a second carrier 23 coupled and fixed to an output shaft 22 provided concentrically with the shaft 16. Further, both ends of a transmission shaft 26 disposed concentrically with the shafts 22 and 16 between the distal end portion of the hollow rotary shaft 25 coupled and fixed to the output side disk 18 and the output shaft 22 and the input shaft 16. The sun gears 27a, 27b, and 27c are fixed to the respective parts. Further, a ring gear 28 is provided around the carrier 20, and a second ring gear 29 is provided around the second carrier 23. A low speed clutch 30 is provided between the ring gear 28 and the second carrier 23, and a high speed clutch 31 is provided between the second ring gear 29 and a fixed part such as a housing. Yes.

  In the case of the continuously variable transmission shown in FIG. 7 as described above, in the state where the low speed clutch 30 is connected and the high speed clutch 31 is disconnected, the transmission ratio of the toroidal continuously variable transmission 14 is set. By changing the gear ratio, the gear ratio of the continuously variable transmission can be changed to infinity. That is, by adjusting the gear ratio of the toroidal-type continuously variable transmission 14, the rotation state of the output shaft 22 is kept forward with the rotation state of the output shaft 22 between the stop state and the input shaft 16 being rotated in one direction. , Reverse conversion is possible. On the other hand, when the low speed clutch 30 is disconnected and the high speed clutch 31 is connected, the speed of the continuously variable transmission is changed according to the change in the gear ratio of the toroidal continuously variable transmission 14. The ratio changes.

  In the case of the continuously variable transmission as described above and the case of a known automatic transmission as described in Non-Patent Document 1, for example, the carrier 9 has a structure as shown in FIGS. On the other hand, the planetary gears 3 and 3 are rotatably supported. Washers 13a and 13b are disposed between inner surfaces of the support plates 10a and 10b constituting the carrier 9 and the opposite end surfaces of the planetary gears 3 and 3 facing the inner surfaces. Is provided. As described above, the washers 13a and 13b support the thrust loads applied to the planetary gears 3 and 3, and the needles 8 and 8 constituting the planetary gears 3 and 3 and the radial needle bearing 5 (see FIG. ) Is controlled.

  Such washers 13a and 13b are each paired between the end surfaces of the planetary gears 3 and 3 and the inner surfaces of the support plates 10a and 10b, as in the structure shown in FIGS. It is preferable to provide two). If one pair is provided in this way, the relative rotational speeds of the adjacent support plates 10a and 10b, the washers 13a and 13b, and the planetary gears 3 and 3 can be reduced compared to the case of providing one by one. The sliding speed between the members 10a, 10b, 13a, 13b, and 3 can be reduced.

  In addition, when providing a pair of washers 13a and 13b in this way, the side surfaces of one of the washers 13a and 13a that are in sliding contact with the end faces of the planetary gears 3 and 3b of the washers 13a and 13b are the planets. Only the radially outer half is in sliding contact with the end faces of the gears 3 and 3. That is, since the radial needle bearing 5 exists inside each of the planetary gears 3, 3, the portion of the side surface of the one washer 13 a, 13 a that is in sliding contact with the end surface of each planetary gear 3, 3 has a diameter of Only the outer half is in the direction. On the other hand, the side surface of the other washer 13b, 13b slidably in contact with the inner side surface of each of the support plates 10a, 10b constituting the carrier 9 among the respective washers 13a, 13b is the inner side surface of the support plate 10a, 10b. Slid over the entire surface.

  For this reason, the surface pressure of the sliding contact portion between the end surfaces of the planetary gears 13a and 13b and the side surfaces of the one washer 13a and 13a is the inner surface of the support plates 10a and 10b and the side surface of the other washer 13b and 13b. It becomes larger than the surface pressure of the sliding contact portion. In this way, the one washer 13a, 13a in which the surface pressure of the sliding contact portion increases is preferably made of an iron-based material in order to ensure wear resistance. On the other hand, it is preferable that the other washer 13b, 13b having a small contact pressure at the sliding contact portion is made of a copper-based material to ensure slidability. Further, as described in Patent Document 4, a concave groove extending in the radial direction can be provided on the side surface of each washer so that the lubricating oil can be easily taken into the sliding contact portion as described above.

  By the way, in the case of the conventional structure as described above, the positioning of the washers 13a and 13b in the radial direction is performed by making the inner peripheral surfaces of the washers 13a and 13b and the outer peripheral surfaces of the planetary support shafts 4 and 4 close to each other. It is done by things. That is, during operation, the washers 13a and 13b rotate while being guided by the outer peripheral surfaces of the planetary support shafts 4 and 4. However, when positioning of the washers 13a and 13b in the radial direction is performed by the planetary support shafts 4 and 4, when the planetary gears 3 and 3 rotate at a high speed, the planetary gears 3 and 3 and There is a possibility that damage such as abnormal wear or seizure may occur in one of the washers 13a and 13a that are in sliding contact with the end faces of the planetary gears 3 and 3.

  That is, during operation, the planetary gears 3 and 3 revolve based on the rotation of the carrier 9 while rotating at high speed. Due to this revolving motion, a large centrifugal force based on its own weight is applied to each of the washers 13a and 13b revolving while rotating together with the planetary gears 3 and 3. In particular, one of the washers 13a and 13b, which is in sliding contact with the end surfaces of the planetary gears 3 and 3 of each of the washers 13a and 13b, is compared with the other washer 13b and 13b in sliding contact with the inner surface of the support plates 10a and 10b. The centrifugal force tends to increase because it is made of an iron-based material having a large specific gravity. Then, when a large centrifugal force is applied to one of the washers 13a and 13a as described above, when the one washer 13a and 13a rotates on the planetary gears 3 and 3 at a high speed, the one washer 13a , 13a, a large frictional force is applied to the sliding contact portions between the radially inner portions of the support plates 10a and 10b and the outer peripheral surfaces of the planetary support shafts 4 and 4, respectively. Such a frictional force hinders rotation (autorotation) of the one washer 13a, 13a (rotational resistance), and the one washer 13a, 13a is difficult to rotate smoothly.

  When the one washer 13a, 13a is difficult to rotate smoothly in this way, the inner peripheral surface and the side surface of the one washer 13a, 13a, the outer peripheral surface of the planetary support shafts 4, 4, and the planetary gears 3 In addition, in the extreme case, the inner peripheral surface of the one washer 13a, 13a rubs the planetary support shafts 4 and 4 to support this planetary support. There is a possibility that the shaft 4 or 4 cannot rotate. When one of the washers 13a and 13a becomes non-rotatable with respect to the planetary support shafts 4 and 4 in this way, the side surface of the one washer 13a is placed on the end face of the planetary gears 3 and 3 and the planetary gears. There is a possibility that the first washer 13a and each of the planetary gears 3 and 3 may be damaged by abnormal wear or seizure.

JP 2002-235841 A JP 2000-220719 A JP 2002-310252 A JP 7-317885 A Mitsuhiko Kuroda, “Introduction to Automotive Engineering”, Grand Prix Publishing, Inc., April 25, 1990, p. 122-123

  In view of the circumstances as described above, the present invention provides excellent durability by preventing the planetary gear and the washer that is in sliding contact with the end face of the planetary gear from being damaged due to abnormal wear, galling, seizure, etc. The present invention has been invented in order to realize a planetary gear device having the same.

The planetary gear device of the present invention includes a planetary gear and a planetary support shaft.
Of these planetary support shafts, the planetary gear is rotatably supported around an axially intermediate portion, and both ends in the axial direction are supported by a pair of support plates constituting a carrier disposed on both axial sides of the planetary gear. It is a thing.
A pair of ring-shaped washers is provided between the inner side surfaces of the support plates facing each other and the axial end surfaces of the planetary gears facing the inner side surfaces.
In particular, in the planetary gear device of the present invention, a cylindrical recess is provided in the axial end surface of the planetary gear so as to be recessed from the end surface in the axial direction. Then, by causing at least a part of one washer in sliding contact with the end face of the planetary gear of the pair of washers to enter the recess, a part of the one washer and the planetary gear Are superimposed in the radial direction.
At the same time, the portion of the outer surface of the one washer that has entered the concave portion is positioned close to the inner peripheral surface of the concave portion, thereby positioning the one washer in the radial direction by the inner peripheral surface of the concave portion. Is doing.

  According to the planetary gear device of the present invention configured as described above, the positioning in the radial direction of one washer that is in sliding contact with the planetary gear is positioned within the concave portion provided on the outer peripheral surface of the one washer and the end surface of the planetary gear. Therefore, the one washer can be easily rotated smoothly, and the one washer can be prevented from being gnawed to the planet support shaft. For this reason, it is possible to prevent an increase in wear and temperature rise at the sliding contact portion between the inner peripheral surface and the side surface of the one washer and the planetary support shaft and the planetary gear, and abnormal wear on the one washer and the planetary gear. It is possible to prevent damage such as seizure. Moreover, since the radial gap between the inner peripheral surface of the one washer and the outer peripheral surface of the planetary support shaft can be increased, the lubricating oil can be easily distributed through the gap. This eliminates the need for additional processing to facilitate the flow of the lubricating oil, such as providing an oil supply hole penetrating in the axial direction of the one washer, and prevents the processing cost of this one washer from increasing. it can. Furthermore, the axial distance between the pair of support plates constituting the carrier can be reduced by overlapping a part of the one washer in the axial direction and the planetary gear in the radial direction, and the axial direction of the planetary gear device can be reduced. The size can be reduced.

In the case of carrying out the present invention, preferably, a side surface of one washer that is in sliding contact with the end surface of the planetary gear is provided with a concave groove in a state of being recessed from this side surface, and a state in which the inner and outer peripheral surfaces of the one washer are communicated. Provide. Providing such a concave groove makes it easy to take in lubricating oil between the side surface of this one washer and the end surface (side surface) of a member (planetary gear, the other washer) that is in sliding contact with this side surface. Can be more reliably prevented from being worn away and a significant increase in temperature.
More preferably, the surface of at least one of the pair of washers is subjected to a film treatment for ensuring wear resistance and reducing a friction coefficient. As a film formed by such a film treatment, a chemical conversion film (manganese phosphate, zinc phosphate, etc.), a hard film {hard chrome plating, DLC (diamond-like carbon), nickel plating, etc.}, PTFE (polytetrafluoroethylene) Resin) film, PTFE composite film, etc. can be applied. In this way, if the washer is coated, sufficient durability can be ensured even under severe use conditions.

  1-3 show Example 1 of the present invention. The feature of this embodiment is that the structure of the sliding contact portion between the planetary gear 32 and the one washer 34a, 34a that is in sliding contact with the end face of the planetary gear 32 is devised to make the one washer 34a, 34a abnormal. This is to prevent damage such as wear, galling, and seizure. The structure and operation of the other parts are known in the art including the conventionally known planetary gear unit shown in FIGS. 5 to 6 and the continuously variable transmission shown in FIG. Since it is the same as that of the planetary gear device that constitutes the transmission, the illustration and description of the equivalent parts will be omitted or simplified, and the following description will focus on the features of the present invention.

  Both ends of the planetary support shaft 4 in the axial direction are supported and fixed at a plurality of locations in the circumferential direction of a pair of support plates 10a and 10b that constitute the carrier 9 and are parallel to each other. And the planetary gear 32 is rotatably supported through the radial needle bearing 5a around the intermediate portion in the axial direction of the planetary support shaft 4. The radial needle bearing 5a holds a plurality of needles 8 and 8 by a retainer 33 so as to be rotatable, and an outer peripheral surface of the intermediate portion of the planetary support shaft 4 serves as a cylindrical inner ring raceway 6 so that the planetary gear 32 is provided. The inner peripheral surface of this needle is a cylindrical outer ring raceway 7, and the rolling surfaces of the needles 8, 8 are in rolling contact with the inner ring raceway 6 and the outer ring raceway 7. A pair of ring-shaped washers 34a and 34b are provided between both axial end surfaces of the planetary gear 32 and the inner surfaces of the support plates 10a and 10b facing each other. The axial displacement of the planetary gear 32 is regulated while supporting the applied thrust load.

In the case of this embodiment, cylindrical concave portions 35 and 35 are provided on both end surfaces in the axial direction of the planetary gear 32 so as to be recessed in the axial direction from these end surfaces. And by making the axial direction part of one washer 34a, 34a slidably contact with the end surface of the planetary gear 32 of the pair of washers 34a, 34b loosely enter the respective recesses 35, 35, the above-mentioned A part of each one washer 34a, 34a and the planetary gear 32 are overlapped in the radial direction. At the same time, a portion of the outer peripheral surface of each one of the washers 34a and 34a that has entered the concave portions 35 and 35 is brought close to and opposed to the inner peripheral surface of the concave portions 35 and 35. , 35 is used to position the one washer 34a, 34a in the radial direction. Therefore, the difference between the inner diameter R ₃₅ of each of the recesses 35, ₃₅ and the outer diameter D ₃₄ of each of the washers 34 a, 34 a is determined as the inner diameter R ₃₄ of each of the washers 34 a, _{34 a} and the outer diameter of the planetary support shaft 4. It is smaller than the difference from D ₄ {(R ₃₅ −D ₃₄ ) <(R ₃₄ −D ₄ )}.

  On the other hand, of the washers 34a, 34b, the other washer 34b, 34b that is in sliding contact with the inner surface of the support plate 10a, 10b rotates (spins) at a lower speed than the one washer 34a, 34a. Moreover, since each of these washers 34b and 34b is made of a copper-based alloy, each of the washers 34b and 34b can improve lubricity with a mating surface made of steel. Therefore, the positioning of the other washer 34b, 34b in the radial direction is performed in the same manner as in the conventional structure shown in FIGS. 5 to 6 described above, and the outer peripheral surface of each of the washer 34b, 34b and the planetary support shaft 4. Is done by making them face each other. However, if necessary, a cylindrical recess is provided in the inner side surface of each of the support plates 10a and 10b in a state of being axially recessed, and the inner peripheral surface of the recess causes the other washer 34b and 34b in the radial direction. You may plan positioning about.

Further, as described above, the outer peripheral surface of each one washer 34a, 34a is guided by the inner peripheral surface of each of the recesses 35, 35. Therefore, the inner peripheral surface of each one of the washers 34a, 34a and the planetary support It is not necessary to make the outer peripheral surface of the shaft 4 face each other. Therefore, in this embodiment, the inner diameter of each one of the washers 34a, 34a is increased, and the portion between the inner peripheral surface of each one of the washers 34a, 34a and the outer peripheral surface of the planetary support shaft 4 is increased. Through the (gap), the lubricating oil can be freely distributed. That is, the lubricating oil fed into the radial needle bearing 5a through the oil supply passage 36 provided at the center of the planetary support shaft 4 is passed through the intermediate portion and the side surfaces of the one washer 34a, 34a and the other washer 34b. , 34b can be fed freely into the sliding contact portion with the side surface. The inner diameter R ₃₄ of the one washer 34a, 34a is within a range in which the needles 8, 8 and the cage 33 constituting the radial needle bearing 5a can be prevented from projecting greatly in the axial direction from the end face of the planetary gear 32. And you can make it bigger.

  In the case of the present embodiment, one of the washers 34a and 34b is made of an iron-based material and has sufficient hardness by being subjected to a heat treatment such as nitriding. In addition, as shown in FIG. 3, a plurality of the washers 34a and 34a are inserted into both side surfaces in the axial direction from the respective side surfaces (in the illustrated example, two on each side surface, a total of four). The concave grooves 37, 37 are provided in such a manner that the inner and outer peripheral surfaces of the one washer 34a, 34a communicate with each other. Each of the concave grooves 37, 37 is provided on each side surface of the one washer 34a, 34a so as to be equidistant in the circumferential direction (180 degrees in the illustrated example) and so as not to overlap in the axial direction. Providing such concave grooves 37, 37 makes it easy to take in lubricating oil between both side surfaces of the one washer 34a, 34a and the end surface of the planetary gear 32 and the side surface of the other washer 34b. It is possible to more reliably prevent the surface from being worn greatly and the temperature from rising significantly.

  More preferably, the surface of at least one of the washers 34a and 34b is subjected to a film treatment for ensuring wear resistance and reducing the friction coefficient. Films formed by such film treatment include chemical conversion treatment films (manganese phosphate, zinc phosphate, etc.), hard films {hard chromium, DLC (diamond-like carbon), nickel plating, etc.}, PTFE (polytetrafluoroethylene resin) ) A film or a PTFE composite film can be applied. In this way, if each washer 34a, 34b is coated, sufficient durability can be ensured even under severe use conditions.

  As described above, according to the present embodiment, the positioning in the radial direction of each one washer 34a, 34a that is in sliding contact with the planetary gear 32 is performed on the outer peripheral surface of each one washer 34a, 34a and the end surface of the planetary gear 32. This is performed by engaging with the inner peripheral surface of each of the recessed portions 35 and 35 provided. Therefore, the one washer 34a, 34a can be positioned effectively in the radial direction, and the one washer 34a, 34a can be easily rotated smoothly. At the same time, it is possible to prevent the inner peripheral side portion of each one of the washers 34a and 34a from being gnawed to the outer peripheral surface of the planetary support shaft 4. For this reason, it is possible to prevent an increase in wear and temperature rise at the sliding contact portion between the inner peripheral surface and the side surface of the one washer 34a, 34a and the planetary support shaft 4 and the planetary gear 32. 34a, 34b and the planetary gear 32 can be hardly damaged such as abnormal wear and seizure.

  In addition, as described above, the radial clearance between the inner peripheral surface of each of the one washers 34a and 34a and the outer peripheral surface of the planetary support shaft 4 can be increased, so that lubricating oil can be circulated through the clearance. Easy to do. For this reason, there is no need for a separate process for facilitating the circulation of the lubricating oil, such as providing an oil supply hole penetrating in the axial direction of one of the washers 34a, 34a, and the processing cost of the one washer 34a, 34a. Can be prevented from increasing. Furthermore, the axial distance between the pair of support plates 10a and 10b constituting the carrier 9 is reduced by overlapping a part of the one washer 34a, 34a in the axial direction and the planetary gear 32 in the radial direction. This can reduce the axial dimension of the planetary gear device.

  Next, FIG. 4 shows Embodiment 2 of the present invention. In the case of this example, concave grooves 37a and 37a are provided on both side surfaces in the axial direction of one washer 34a that is in sliding contact with the planetary gear 32 (see FIGS. 1 and 2), in the tangential direction of the inner peripheral surface of this one washer 34a. ing. That is, each of the concave grooves 37a and 37a is provided in parallel with a tangent to the inner peripheral surface of the one washer 34a. In the case of this embodiment as well, as in the first embodiment, both side surfaces of the one washer 34a, the end surface of the planetary gear 32, and the side surface of the other washer 34b (see FIGS. 1 and 2). The lubricating oil can be easily taken in between, and it can be surely prevented that these surfaces are greatly worn and the temperature rise is remarkably increased. Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. The A section enlarged view of FIG. The figure which took out the washer and was seen from the side of FIG. The figure similar to FIG. 3 which shows Example 2 of this invention. The schematic side view which shows one example of a planetary gear apparatus. BB sectional drawing of FIG. 1 is a schematic cross-sectional view showing an example of a continuously variable transmission.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Sun gear 1a Tooth 2 Ring gear 2a Tooth 3 Planetary gear 3a Tooth 4 Planet support shaft 5, 5a Radial needle bearing 6 Inner ring track 7 Outer ring track 8 Needle 9 Carrier 10a, 10b Support plate 11 Cylindrical part 12 Rotating shaft 13a, 13b Washer 14 Toroidal continuously variable transmission 15 Planetary gear type transmission 16 Input shaft 17 Input side disk 18 Output side disk 19 Power roller 20 Carriers 21a, 21b, 21c Planetary gear 22 Output shaft 23 Second carrier 24a, 24b Planetary gear 25 Hollow rotating shaft 26 Transmission shaft 27a, 27b, 27c Sun gear 28 Ring gear 29 Second ring gear 30 Low speed clutch 31 High speed clutch 32 Planetary gear 33 Cage 34a, 34b Washer 35 Recess 36 Oil supply passage 37, 37a Recessed groove

Claims (3)

  A planetary gear and a planetary support shaft are provided. The planetary support shaft rotatably supports the planetary gear around an axially intermediate portion, and has a carrier in which both axial ends are arranged on both sides of the planetary gear in the axial direction. Each of the support plates is supported by a pair of support plates, and each of the support plates has an annular washer between an inner surface facing each other and both end surfaces in the axial direction of the planetary gear facing each inner surface. In the planetary gear device in which one pair is provided, a cylindrical recess is provided on the axial end face of the planetary gear in a state of being recessed in the axial direction from the end face, and the planetary gear of the pair of washers is provided. By allowing at least a part of one washer in sliding contact with the end surface of the shaft to enter the recess, the part of the one washer and the planetary gear are overlapped in the radial direction, and the outer periphery of the one washer In terms of By closely opposed entry portions in serial recess on the inner peripheral surface of the recess, the planetary gear unit, characterized in that for positioning in the radial direction of one of the washer above the inner circumferential surface of the recess.   2. The planet according to claim 1, wherein a groove is provided in a side surface of one washer that is in sliding contact with an end surface of the planetary gear so as to be recessed from the side surface, and the inner and outer peripheral surfaces of the one washer are in communication with each other. Gear device. The planetary gear device according to any one of claims 1 and 2, wherein a film treatment is applied to a surface of at least one of the pair of washers.

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