JP5304989B2 - Transmission lubrication structure - Google Patents

Description

  The present invention relates to a transmission lubrication structure, and more specifically to a transmission lubrication structure having a planetary gear.

  2. Description of the Related Art Conventionally, a lubrication structure is known in which lubricating oil is supplied to a planetary gear rotating element in a transmission, particularly a pinion gear bearing, to prevent wear caused when the rotating element rotates (for example, Patent Document 1). ). The lubrication structure described in Patent Document 1 includes an axial oil passage extending in an axial direction in a pinion shaft of a pinion gear of a planetary gear, and a circumferential oil extending in a circumferential direction from the axial oil passage toward a bearing of the pinion shaft. A road is provided. These oil passages are supplied with lubricating oil that passes through the output passage of the hydraulic power transmission device such as a torque converter and the oil passage in the carrier plate, and the lubricating oil is a centrifugal generated when the output shaft and the carrier plate rotate. It is scattered toward a rotating element such as a bearing of a planetary gear pinion gear through an axial oil passage or the like by force.

JP 2007-270865 A

By the way, when the transmission is multistaged, for example, the rotational speed of the pinion gear may be much higher than that of other rotating elements. The apparatus as described above cannot cope with such high rotation, and there is a problem that the lubricating oil is difficult to reach the bearing between the pinion shaft and the pinion gear.
In addition, even if the rotation speed of the pinion gear is low, when the carrier plate connected to the pinion gear is stopped, the centrifugal force does not act on the lubricating oil flowing through the flow path in the carrier plate, and the pinion shaft and the pinion There was a problem that lubrication was difficult to reach the bearing between the gears.
These problems were particularly noticeable in the bearings above the output shaft when the carrier plate stopped.

  The present invention has been made to solve the above-described problems, and an object thereof is to provide a lubricating structure for a transmission that can supply sufficient lubricating oil between a pinion shaft and a pinion gear with a simple structure. And

According to the present invention, a planetary gear includes a pinion gear that revolves around a sun gear, a pinion shaft that rotatably supports the pinion gear via a bearing, and a carrier plate that is fixed to the pinion shaft. A lubrication structure for a transmission including a gear, which is provided at an edge in a circumferential direction of a carrier plate and opens toward the outer circumferential direction of the carrier plate, and receives lubricating oil that has entered the opening. An oil receiver having an oil receiver, an oil inlet provided in the oil receiver, and an oil receiver oil passage communicating with the oil inlet, extending in the pinion shaft and supplying lubricating oil to the bearing, The oil receiver has drooped from its periphery when the carrier plate rotates and the opening is facing upwards Namerayu being adapted to be supplied to the oil receiver oil passage of lubricating oil by gravity receiving a transmission comprises at least two planetary gears provided adjacent to each other, the oil receiver, whereas The planetary gear is provided on a carrier plate on the side facing the other planetary gear, and the outer peripheral side of the provided oil receiver receives lubricating oil scattered by the rotation of a predetermined rotating member of the other planetary gear. Further, there is provided a lubricating structure for a transmission characterized in that an oil guide extending from the carrier plate is provided.

According to such a configuration, when the carrier plate is rotated by the oil receiver and the oil receiver is facing upward, the lubricating oil dripping from the periphery can be received and received. The lubricating oil is supplied to the bearing through the oil receiver oil passage. Therefore, normally, the lubricating oil in the output shaft and the carrier plate is only supplied by centrifugal force, but according to the present invention, in addition to such lubricating oil, the lubricating oil drooping from above due to gravity is also included. Can be supplied. Therefore, for example, even if the rotation speed of the pinion gear is much higher than that of other rotating elements, or even if the rotation of the carrier plate attached to the pinion shaft becomes low or stops, the pinion shaft and the pinion gear Sufficient lubricating oil can be supplied to the bearings between and between them. As a result, wear of the pinion gear, pinion shaft and bearing can be prevented, malfunction can be prevented, and bearing lubrication can be prevented. Furthermore, since it is only necessary to provide an oil receiver and an oil receiver oil passage on the carrier plate, the structure becomes simple.
Moreover, in this invention comprised in this way, the lubricating oil scattered by the rotation element of an adjacent planetary gear can be received using an oil guide. The lubricating oil received by the oil guide drops in the oil receiver through the oil guide, so that the lubricating oil can be more reliably supplied to the pinion gear and its bearing.

  According to the present invention, a pinion gear that revolves around the sun gear, a pinion shaft that rotatably supports the pinion gear via a bearing, and a carrier plate that is fixed to the pinion shaft, A lubrication structure of a transmission including a planetary gear having an opening provided at a circumferential edge of a carrier plate and opening outward in the circumferential direction of the carrier plate, and lubricating oil entering the opening An oil receiver having an oil receiving portion for receiving the oil, an oil inlet provided in the oil receiving portion, an oil receiver oil passage communicating with the oil inlet, extending in the pinion shaft and supplying lubricating oil to the bearing; The oil receiver hangs from its periphery when the carrier plate rotates and the opening is facing upwards The lubricating oil can be supplied to the oil receiver oil passage by gravity after receiving the lubricating oil, and the lubricating structure of the transmission further includes a carrier plate oil passage provided in the carrier plate and a pinion. An axial oil passage provided in the shaft, extending in parallel with the oil receiver oil passage and connected to the carrier plate oil passage, and a radial oil passage extending from the axial oil passage to the peripheral surface of the pinion shaft; The oil receiver oil passage is provided inward in the circumferential direction with respect to the axial oil passage.

  According to such a configuration, when the carrier plate is rotated by the oil receiver and the oil receiver is facing upward, the lubricating oil dripping from the periphery can be received and received. The lubricating oil is supplied to the bearing through the oil receiver oil passage. Therefore, normally, the lubricating oil in the output shaft and the carrier plate is only supplied by centrifugal force, but according to the present invention, in addition to such lubricating oil, the lubricating oil drooping from above due to gravity is also included. Can be supplied. Therefore, for example, even if the rotation speed of the pinion gear is much higher than that of other rotating elements, or even if the rotation of the carrier plate attached to the pinion shaft becomes low or stops, the pinion shaft and the pinion gear Sufficient lubricating oil can be supplied to the bearings between and between them. As a result, wear of the pinion gear, pinion shaft and bearing can be prevented, malfunction can be prevented, and bearing lubrication can be prevented. Furthermore, since it is only necessary to provide an oil receiver and an oil receiver oil passage on the carrier plate, the structure becomes simple.
  Further, in the present invention configured as described above, it is possible to provide the inner diameter side end portion of the oil receiver on the inner diameter side, and the degree of freedom of the oil receiver layout can be increased.

According to a preferred aspect of the present invention, a plurality of oil receivers are provided at substantially equal intervals at positions corresponding to the pinion gears.
  According to such a configuration, even if the carrier plate stops in any state, at least one oil receiver can reliably receive the lubricating oil dripping from above.

According to a preferred aspect of the present invention, the oil receiving portion is branched into at least two from the radially inner side to the outer side of the carrier plate, and the branched oil receiving portion is in a radial direction of the carrier plate. An opening is provided for each of the branched oil receiving portions.
  According to such a configuration, even when the opening portion does not completely face upward, the oil receiving portion extending obliquely with respect to the radial direction of the carrier plate causes the opening portion to be left or right with respect to the upper side. Since the opening opens relatively upward on the side, the lubricating oil dripping from above can be reliably received by the oil receiving surface and poured into the oil inlet.

In the present invention, preferably, the planetary gear is provided on the outer peripheral side from the oil receiver and has a ring gear that rotates even when the rotation of the carrier plate is stopped. It is designed to be received at the receiver.
  In the present invention configured as described above, for example, even when the carrier plate is stopped, the ring gear is located on the outer peripheral side from the pinion gear and its bearing. The oil can be effectively received by the oil receiver, and the lubricating oil can be more reliably supplied to the pinion gear and its bearing.

  Thus, according to the present invention, sufficient lubricating oil can be supplied between the pinion shaft and the pinion gear with a simple structure.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a block diagram showing an automatic transmission 1 according to the first embodiment and its peripheral members.

  The automatic transmission 1 includes, for example, an automatic transmission (AT), a torque converter 5 that amplifies an output of an output shaft 3 of an engine (not shown), and a shift that changes the output of the torque converter 5 to a plurality of shift stages. And a mechanism 7. The output of the engine output shaft 3 is amplified by a torque converter 5 including a pump 9, a turbine 11, and a stator 13, and is input to the transmission mechanism 7 via the output shaft 15.

  The speed change mechanism 7 includes three planetary gears, a first planetary gear 17, a second planetary gear 19, and a third planetary gear 21 that are adjacent to each other. The speed change mechanism 7 generates six forward speeds and reverse speeds by combining rotation and stop of the rotation elements included in the planetary gears 17, 19, and 21. The planetary gears 17, 19, 21 are sun gears 23, 25, 27 that can be connected to the output shaft 15, pinion gears 29, 31, 33 that mesh with the sun gears 23, 25, 27, and pinion gears 29, 31, 33. Carrier plates 35, 37, and 39, and ring gears 41, 43, and 45 that mesh with the pinion gears 29, 31, and 33. The pinion gears 29, 31, and 33 are rotatably supported by a pinion shaft 61 (see FIG. 3) via a bearing B (see FIG. 3), and the pinion shaft 61 is freely rotatable by carrier plates 35, 37, and 39. Is attached.

  The automatic transmission 1 also includes a first clutch 47, a second clutch 49, a first brake 51, and a second clutch as frictional engagement elements that are engaged with the rotation elements of the planetary gears 17, 19, and 21 to control rotation. A brake 53 and a third brake 55 are provided. The first clutch 47 connects or disconnects the sun gear 27 of the third planetary gear 21 and the output shaft 15, and connects or disconnects the sun gear 25 of the second planetary gear 19 and the output shaft 15. It has become. In addition, the second clutch 49 connects or disconnects the carrier plate 37 of the second planetary gear 19 and the output shaft 15.

  The first brake 51, the second brake 53, and the third brake 55 are each a multi-plate brake fixed to the transmission case 57 of the automatic transmission 1, and are fastened to or released from the rotating element. It is supposed to be. Specifically, the first brake 51 stops the ring gear 45 of the third planetary gear 21 and the carrier plate 37 of the second planetary gear 19. Further, the second brake 53 stops the ring gear 43 of the second planetary gear 19 and the carrier plate 35 of the first planetary gear 17, and the third brake 55 stops the ring gear 41 of the first planetary gear 17. It has become. The rotation direction of the ring gear 45 of the third planetary gear and the carrier plate 37 of the second planetary gear 19 are restricted by the one-way clutch 59.

  And in such a speed change mechanism 7, in order to form a predetermined gear stage, a fastening torque capacity is added to two friction engagement elements among the plurality of friction engagement elements. As a result, the gears constituting the planetary gears 17, 19, and 21 rotate, revolve, or stop. At this time, the relationship between the operating frictional engagement element and the shift speed is as shown in Table 1.

The gear stage created by driving or stopping the frictional engagement element and the rotation element is output to a differential device (not shown) provided between the wheels via the counter drive gear 61. The
In the present embodiment, the transmission is described as a so-called normal automatic transmission (AT). However, in addition to this, an automated manual transmission (ATM), a twin clutch type transmission, a CVT, a toroidal type, etc. Such a continuously variable transmission includes a transmission having a planetary gear.

FIG. 2 shows a cross-sectional view of the automatic transmission 1 according to the present embodiment.
As shown in FIG. 2, the first planetary gear 17, the second planetary gear 19, and the third planetary gear 21 of the automatic transmission 1 are accommodated in a transmission case 57. The transmission case 57 includes a substantially cylindrical case body 57a and an end case 57b attached to the case body 57a. The case main body 57a is configured such that the output shaft 15 is inserted into one side and the end case 57b is attached to the other side. The planetary gears 17, 19, 21 are arranged in the order of the first planetary gear 17, the second planetary gear 19, and the third planetary gear 21 from the end case side. The sun gears 23, 25, 27 of the planetary gears 17, 19, 21 are arranged so as to be coaxial with the output shaft 15.

  The output shaft 15 is hollow, and lubricating oil for the automatic transmission 1 flows through the hollow portion. Then, the lubricating oil flowing through the hollow portion is scattered in the automatic transmission 1 by the centrifugal force generated by the rotation of the output shaft 15.

FIG. 3 is an enlarged cross-sectional view of the vicinity of the first planetary gear 17 according to the present embodiment.
As shown in FIG. 3, the first planetary gear 17 is mainly fixed with a sun gear 23, a pinion gear 29 that meshes with the sun gear 23, and a pinion shaft 61 that rotatably supports the pinion gear 29 via a bearing B. And a carrier plate 35 that revolves the pinion gear 29 around the sun gear 23, and a ring gear 41 that meshes with the pinion gear 29. In the present embodiment, a planetary gear having five pinion gears 29 is taken as an example. However, according to the present invention, any number of pinion gears may be used.

  The teeth 29a of the pinion gear 29 mesh with the outer teeth 23a of the sun gear 23, and further rotate around the pinion shaft 61 provided on the carrier plate 35. A predetermined gap is provided between the pinion gear 29 and the pinion shaft 61, and a bearing B is disposed in the gap. An object of the present invention is to supply a sufficient amount of lubricating oil between the pinion gear 29 on which the bearing B is disposed and the pinion shaft 61.

  In the pinion shaft 61, two oil passages extending in the axial direction are provided. Specifically, an oil receiver oil passage 65 that supplies the lubricating oil supplied from the oil receiver 63 to the peripheral surface of the pinion shaft 61 and a wall of the transmission case 57 are provided in the pinion shaft 61. An in-shaft oil passage 67 and an in-shaft oil passage 71 for supplying lubricating oil supplied through the in-carrier oil passage 69 to the peripheral surface of the pinion shaft 61 are provided.

  First, the shaft oil passage 71 includes an axial oil passage 71a connected to the carrier oil passage 69, and a radial oil passage 71b extending from the axial oil passage 71a to the peripheral surface of the pinion shaft 61. Have. The in-shaft oil passage 71 is a pinion for lubricating oil supplied through the in-case oil passage 67 provided in the wall of the transmission case 57 and the in-carrier oil passage 69 provided in the carrier plate 35. A bearing B between the gear 29 and the pinion shaft 61 is supplied. The in-case oil passage 67 is connected to an oil pump (not shown) via a hydraulic control device (not shown).

  Further, the case internal oil passage 67 is connected to the carrier internal oil passage 69 through a hole 73 a provided in the bearing member 73. An oil groove 77 extending in the circumferential direction of the carrier 35 is provided between the end of the oil passage 67 in the case and the bearing member 73. The carrier oil passage 69 is connected to the shaft oil passage 71 through the inside of the carrier 35. The lubricating oil flowing through the case oil passage 67 flows into the carrier oil passage 69 via the bearing member 73 due to the pressure of the oil pump. Then, the lubricating oil in the carrier oil passage 69 reaches the shaft oil passage 71 by the centrifugal force generated by the rotation of the carrier 35.

  Next, the oil receiver oil passage 65 communicates with the oil introduction port 79 and extends in the pinion shaft 61 to supply lubricating oil to the bearing B. The oil receiver oil passage 65 includes a first oil passage 65a extending in the axial direction from the oil introduction port 79, and a second oil passage 65b extending from the first oil passage 65a to the peripheral surface of the pinion shaft 61. Have Here, the pinion shaft 61 is fixed to the carrier plate 35, and the carrier plate 35 is fixed to the ring gear 43 of the adjacent second planetary gear 19. And as above-mentioned, if the 2nd brake 53 act | operates in 2nd speed or 6th speed, the carrier plate 35 will stop. When the carrier plate 35 stops, the pinion gear 29 stops revolving around the sun gear 23 and rotates by the rotation of the ring gear 41 or the sun gear 23.

  Even in such a case, the oil receiver oil passage 65 can supply a sufficient amount of lubricating oil between the pinion gear 29 and the pinion shaft 61. The oil introduction port 79 provided at one end of the first oil passage 65 a is provided at the end of the pinion shaft 61 exposed on the surface of the carrier plate 35. The oil introduction port 79 is covered with an oil receiver 63 that can receive lubricating oil from above. The lubricating oil that has flowed into the oil receiver 63 flows between the pinion gear 29 and the pinion shift 61 from the oil introduction port 79 through the first oil passage 65 a and the second oil passage 65 b in the pinion shaft 61. As a result, the lubricating oil is supplied between the pinion gear 29 and the pinion shaft 61 and the bearing B.

  FIG. 4 shows an elevation view of the carrier plate 35 according to the present embodiment.

  As shown in the figure, a plurality of oil receivers 63 a, 63 b,..., 63 e are provided along the vicinity of the circumferential edge of the carrier plate 35. The oil receivers 63a, 63b,..., 63e are provided in the vicinity of the edge 35b of the disk surface 35a of the carrier plate 35, and are arranged at substantially equal intervals at positions corresponding to the pinion shaft 61 and the pinion gear 29. Has been. In the figure, as an example, five oil receivers 63a, 63b,..., 63e are illustrated in association with the number of pinion gears, but the number of oil receivers is not limited to this. Absent.

  The oil receiver 63a is configured to receive the lubricating oil dripping from above when the carrier plate 35 stops and is above the rotation axis X of the carrier plate 35. FIG. 5 shows an enlarged perspective view of the oil receiver 63a according to the present embodiment. The oil receiver 63a includes openings 81a and 81b that open outward in the circumferential direction of the carrier plate 35, an oil receiving part 83 that receives the lubricating oil that has entered the opening, and oil receiving surfaces 85a and 85b.

  The oil receiving portion 83 is branched into two and has a substantially V shape. The branched oil receiving portion 83 extends obliquely with respect to the radial direction of the carrier plate 35. The branched oil receiving portions 83 extend obliquely with respect to the radial direction of the carrier plate 35, and are configured to have openings 81a and 81b for the branched oil receiving portions 83, respectively.

  Furthermore, the openings 81 a and 81 b are provided along the edge of the carrier plate 35. Here, since the example of the oil receiver having the oil receiving surfaces 85a and 85b is shown in the same figure, the opening is branched into two in the middle to form the opening 81a and the opening 81b. When the oil receiving surfaces 85 a and 85 b are not provided, one opening may be continuously opened along the edge of the carrier plate 35.

  The side wall 83a of the oil receiving portion 83 has one end forming an outer edge of the opening 81a and the other end forming an outer edge of the opening 81b. The central portion of the side wall 83a extends at an acute angle with the radial direction of the carrier plate 35 from the end thereof to the inner side in the circumferential direction from the oil introduction port 79 in the carrier plate 35. Then, the lubricating oil hanging from the upper side of the carrier plate 35 and received by the side wall 83a flows along the side wall 83a toward the oil introduction port 79 provided in the oil receiving portion 83.

  The oil receiving surfaces 85a and 85b are formed continuously and are substantially V-shaped. One end of the oil receiving surface 85a is located outward in the circumferential direction from the oil introduction port 79. The oil receiving surface 85a has an edge at an acute angle with respect to the radial direction of the carrier plate 35 so that the other end is close to one end of the side wall 83a. It extends to the vicinity of the part. Furthermore, one end of the oil receiving surface 85b is positioned outward in the circumferential direction from the oil introduction port 79, and the oil receiving surface 85b extends in the radial direction of the carrier plate 35 so that the other end is close to the other end of the side wall 83a. On the other hand, it extends from the outer circumferential direction to the vicinity of the edge of the carrier plate 35 from the oil introduction port 79 at an acute angle. A front wall 83b is provided between the side wall 83a and the oil receiving surfaces 85a and 85b, and a lubricating oil flow path is formed by the side wall 83a and the oil receiving surfaces 85a and 85b. The front wall 83 b is inclined in the direction of the disc surface 35 a of the carrier plate 35 in the vicinity of the oil introduction port 79, and guides the lubricating oil toward the introduction port 79.

According to such an oil receiver 63, as shown in FIG. 4, the oil receiver 63b or 63e located at the height between the top of the carrier plate 35 and the rotation axis X of the carrier plate 35 is The lubricating oil dripping from above is received by the oil receiving surfaces 85 a and 85 b and poured into the oil receiving portion 83.
In the present embodiment, the oil receiver 63 is branched into two and has two oil receiving surfaces. However, the number of oil receiving surfaces is not limited to two. There can be any number.

As described above, the carrier plate 35 is stopped by the second brake 53 when the automatic transmission 1 forms the second speed or the sixth speed. When the carrier plate 35 is stopped, the lubricating oil flowing out of the oil passage 67 in the case almost flows above the oil groove 77 as shown by arrows B ₁ and B ₂ in FIG. Instead, the lubricating oil that has reached the oil groove 77 hangs down in the direction of the pinion shaft 61 located below due to gravity. In such a case, the lubricating oil of the rotating pinion gear 29 is insufficient. However, according to the lubricating structure of the present invention, the lubricating oil pumped up and scattered by the rotation of the ring gear 41 is supplied from the corresponding oil receiver 63 to the pinion shaft 61 above the oil groove 77. A sufficient amount of lubricating oil can be supplied to the pinion gear 29.

Next, a second embodiment of the present invention will be described in detail.
The lubricating structure according to the second embodiment differs from the first embodiment in the position of the oil receiver, and the structure of other parts is the same as that of the first embodiment. Here, only the configuration different from the first embodiment will be described.

  FIG. 6 is a cross-sectional view of the lubricating structure according to the second embodiment. As shown in the figure, the oil receiver 101 is provided on the second planetary gear 19 side. The ring gear 43 of the second planetary gear 19 is provided with an oil guide 103 extending in the direction of the first planetary gear 17.

  The oil guide 103 has a predetermined width in the rotation direction of the carrier plate 35, one end is fixed to the ring gear 43, and the other end is fixed to the carrier plate 35. Then, the lubricating oil splashed by the pinion gear 31 and the ring gear 43 of the second planetary gear 19 flows through the oil guide 103 into the oil receiver 101, and the axial oil path 105 a of the oil receiver oil path 105 It flows to the bearing B between the pinion gear 29 and the pinion shaft 61 through the radial oil passage 105b.

  Thus, similarly to the first embodiment, according to the second embodiment, a sufficient amount of lubricating oil can be supplied between the pinion gear 29 and the pinion shaft 61.

The operation according to each embodiment of the present invention will be described.
First, according to the embodiment of the present invention, the oil receiver 63 can receive the lubricating oil dripping from the periphery when the carrier plate 35 is rotated and the oil receiver 63 faces upward. The received lubricating oil is supplied to the bearing B through the oil receiver oil passage 65. Therefore, normally, the lubricating oil in the output shaft 15 and the carrier plate 35 is only supplied by centrifugal force. However, according to the embodiment of the present invention, the lubricating oil hangs down from above. Lubricating oil can also be supplied. Therefore, for example, even if the rotation speed of the pinion gear 29 is much higher than that of the other rotation elements, or even if the rotation of the carrier plate 35 attached to the pinion shaft 61 becomes low or stops, the pinion shaft 61 Sufficient lubricating oil can be supplied to the bearing B between and between the pinion gear 29, and as a result, wear of the pinion gear 29, the pinion shaft 61 and the bearing B can be prevented, and malfunctions can be suppressed. In addition, the poor lubrication of the bearing B can be prevented. These actions are particularly effective in the pinion gear 29 and the bearing B that are located above the output shaft 15 when the carrier plate 35 is stopped, where the lubricating oil is difficult to reach due to gravity. Furthermore, since the oil receiver 63 is provided on the carrier plate 35 and only the oil receiver oil passage 65 is provided, the structure is simple.

Even if the carrier plate 35 stops in any state, at least one oil receiver 63 can reliably receive the lubricating oil dripping from above.
Further, even when the opening 81 is not completely facing directly upward, the oil receiving portion 83 extending obliquely with respect to the radial direction of the carrier plate 35 causes the opening 81 to be left or right with respect to the directly above. Since the opening opens relatively upward on the side, the lubricating oil dripping from above can be reliably received by the oil receiving surface and poured into the oil inlet.

Further, for example, even when the carrier plate 35 is stopped, the ring gear 41 and the like are on the outer peripheral side from the pinion gear 29 and the bearing B thereof, so that the lubricating oil scattered by utilizing the rotation of the ring gear 41 and the like is removed. The oil can be effectively received by the oil receiver 63 and the lubricating oil can be supplied to the pinion gear 29 and its bearing B more reliably.
Furthermore, the oil guide 103 is used to effectively receive the lubricating oil scattered by the rotating elements of the adjacent planetary gear (second planetary gear 19) by the oil receiver 63, and the lubricating oil is applied to the pinion gear 29 and its bearing B. It can be supplied more reliably.

Furthermore, the lubricating oil pumped up and scattered by the rotation of the ring gear 43 of the second planetary gear 19 can be made to flow into the oil receiver 63 through the oil guide 103. That is, even with such a configuration, it is possible to supply sufficient lubricating oil between the pinion shaft 61 and the pinion gear 29 to prevent the pinion gear 29 and the pinion shaft 61 from being worn.
Furthermore, by providing the inner diameter side end of the oil receiver 63 on the inner diameter side, the degree of freedom in the layout of the oil receiver 63 can be increased.

It is a block diagram which shows the automatic transmission concerning 1st Embodiment, and its peripheral member. 1 is a cross-sectional view of an automatic transmission according to an embodiment of the present invention. It is an expanded sectional view of the 1st planetary gear by the embodiment of the present invention. 2 is an elevation view of a carrier plate according to an embodiment of the present invention. FIG. It is an expansion perspective view of the oil receiver by the embodiment of the present invention. It is sectional drawing of the lubrication structure concerning 2nd Embodiment.

Explanation of symbols

1 automatic transmission 23 sun gear 29 pinion gear 35 carrier plate 61 pinion shaft 63 oil receiver 65 oil receiver oil passage 71 oil introduction port 81 opening 83 oil receiving portion

Claims (5)

A transmission comprising a planetary gear having a pinion gear that revolves around a sun gear, a pinion shaft that rotatably supports the pinion gear via a bearing, and a carrier plate fixed to the pinion shaft. A lubrication structure,
An oil receiver having an opening provided at a circumferential edge of the carrier plate and opening outward in the circumferential direction of the carrier plate; and an oil receiving portion that receives the lubricating oil that has entered the opening;
An oil inlet provided in the oil receiver;
An oil receiver oil passage that communicates with the oil introduction port and extends in the pinion shaft to supply lubricating oil to the bearing;
The oil receiver can receive the lubricating oil drooping from the periphery when the carrier plate rotates and the opening faces upward, and can supply the lubricating oil to the oil receiver oil passage by gravity. has become way,
The transmission has at least two planetary gears provided adjacent to each other,
The oil receiver is provided on the carrier plate of one planetary gear on the side facing the other planetary gear,
An oil guide extending from the carrier plate is provided on the outer peripheral side of the provided oil receiver in order to receive the lubricating oil scattered by the rotation of a predetermined rotating member of the other planetary gear. A transmission lubrication structure characterized by the above.   A transmission comprising a planetary gear having a pinion gear that revolves around a sun gear, a pinion shaft that rotatably supports the pinion gear via a bearing, and a carrier plate fixed to the pinion shaft. A lubrication structure,
  An oil receiver having an opening provided at a circumferential edge of the carrier plate and opening outward in the circumferential direction of the carrier plate; and an oil receiving portion that receives the lubricating oil that has entered the opening;
  An oil inlet provided in the oil receiver;
  An oil receiver oil passage that communicates with the oil introduction port and extends in the pinion shaft to supply lubricating oil to the bearing;
  The oil receiver can receive the lubricating oil drooping from the periphery when the carrier plate rotates and the opening faces upward, and can supply the lubricating oil to the oil receiver oil passage by gravity. And
  The transmission lubrication structure further includes:
  A carrier plate oil passage provided in the carrier plate;
  An axial oil passage provided in the pinion shaft, extending in parallel with the oil receiver oil passage and connected to the carrier plate oil passage;
  An oil passage in the shaft having a radial oil passage extending from the axial oil passage to the peripheral surface of the pinion shaft, and
  The transmission lubricating structure, wherein the oil receiver oil passage is provided inward in the circumferential direction with respect to the axial oil passage. A plurality of the oil receivers are provided at substantially equal intervals at a position corresponding to the pinion gear.
The lubricating structure of the transmission according to claim 1 or 2 . The oil receiving portion is branched into at least two from the radially inner side to the outer side of the carrier plate, and the branched oil receiving portion extends obliquely with respect to the radial direction of the carrier plate. The opening is provided with respect to the oil receiving portion of
The lubricating structure of the transmission according to any one of claims 1 to 3 . The planetary gear is provided on the outer peripheral side from the oil receiver, has a ring gear that rotates even when the carrier plate stops rotating, and receives the lubricating oil scattered by the rotation of the ring gear by the oil receiver. Has become,
The lubricating structure of the transmission according to any one of claims 1 to 4 .

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