JP2005233386A - Lubricating structure of automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To attain compatibility between securing of lubricating oil supplied to a pinion gear and a pinion shaft of a planetary gear and securing of rigidity of a countershaft while making an auxiliary transmission mechanism of an automatic transmission compact. <P>SOLUTION: A communicating oil passage for supplying lubricating oil to the pinion gear 77 and the pinion shaft 75 is composed of a communicating oil passage 91 in a pinion carrier 43 and a communicating passage 82, the inlet of which is connected to a lubricating oil supply oil passage 80 in a counter driven gear support part 47a position, the outlet thereof facing to an inlet of the communicating oil passage 91 in the pinion carrier 43, whereby the need of providing a communicating oil passage in a countershaft for supplying lubricating oil to the pinion gear 77 and the pinion shaft 75 in a small-diameter planetary gear support part 47a is eliminated to prevent lowering of rigidity. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to lubrication of an automatic transmission, and more particularly, to lubrication of a pinion gear and a pinion shaft of a planetary gear on the auxiliary transmission mechanism side of an automatic transmission having a main transmission mechanism and an auxiliary transmission mechanism.

  In general, an automatic transmission mounted on an automobile includes a torque converter, a transmission mechanism including a planetary gear (planetary gear mechanism), and a plurality of frictional engagement elements such as a clutch and a brake. By engaging and switching the power transmission path of the transmission gear mechanism, a shift stage according to the operating state is automatically obtained. The planetary gear includes a sun gear, a ring gear, a pinion gear interposed between them, and a carrier that supports the pinion gear. For example, in the case of a multi-plate clutch or multi-plate brake, the clutch or brake that is a frictional engagement element is usually composed of a drum (case in the case of a brake), a hub, and a friction plate interposed between them. is there. These are selectively connected to form a power transmission path for realizing a required shift speed.

In particular, in an automatic transmission having a main transmission mechanism and a sub-transmission mechanism, a counter shaft that supports the sub-transmission mechanism is disposed in parallel with the primary shaft that supports the main transmission mechanism, and the counter shaft is configured to A counter driven gear supporting portion that supports a counter driven gear that meshes with the counter drive gear on the side through a bearing, and a planetary gear supporting portion that supports a planetary gear adjacent to the counter driven gear, with both end portions of the shaft being attached to the transmission case. Usually supported. In such an automatic transmission, for each component that requires lubrication of the auxiliary transmission mechanism, a counter is provided at the position of each component from a lubricating oil supply oil passage that extends in the axial direction at the center of the counter shaft. 2. Description of the Related Art Conventionally, lubricating oil is supplied through respective communication oil passages formed in the radial direction of the shaft (see, for example, Patent Documents 1 and 2).
JP 11-82647 A Japanese Patent No. 3110486

  As described above, in an automatic transmission having a main transmission mechanism and a sub-transmission mechanism, lubrication of the sub-transmission mechanism is formed in the radial direction of the counter shaft at the position of each component relative to the component requiring lubrication. Conventionally, the lubricating oil is supplied through the communication oil passage in the counter shaft. In this case, the planetary gear pinion gear and the communication oil passage for supplying the lubricating oil to the pinion shaft are the planetary gear of the counter shaft. Formed on the support. However, in such an automatic transmission, there is a demand for reducing the diameter of the planetary gear support portion of the countershaft in particular for compactness. If the diameter of the planetary gear support portion is reduced as required, the planetary gear support portion of the countershaft is referred to as a planetary gear support portion. Because the position is adjacent to the counter-driven gear support, and the deflection due to the driving torque when the counter-driven gear is engaged with the counter drive gear and driven is large, it is a part that particularly requires rigidity, and should have a small diameter. In addition to being rigorous in itself, a small step makes a step between the counter-driven gear support and the stepped part becomes a weak point in rigidity, and a communication oil passage for lubricating the planetary gear on top of that. As a result, it is more difficult to ensure rigidity.

  Therefore, in the sub-transmission mechanism of the automatic transmission, there has been a problem of ensuring both the securing of the lubricating oil supplied to the pinion gear and the pinion shaft of the planetary gear and the rigidity of the counter shaft while achieving a compact size.

  The present invention has been made to solve the above-described problems, and a counter shaft that supports a sub-transmission mechanism is disposed in parallel with a primary shaft that supports the main transmission mechanism, and the counter shaft is arranged at the center in the axial direction. The planetary gear support portion has a counter driven gear support portion that supports a counter driven gear that meshes with a counter drive gear on the transmission mechanism side via a bearing, and has a planetary gear support portion that supports a planetary gear adjacent to the counter driven gear support portion. Lubricating structure for an automatic transmission that is smaller in diameter than the counter-driven gear support portion, has a lubricating oil supply oil passage extending in the axial direction at the shaft center portion, and both ends of the shaft are supported by a transmission case For planetary gear lubrication for supplying lubricating oil to the pinion gear and pinion shaft of the planetary gear The oil passage is connected to the carrier communication oil passage provided in the pinion carrier that supports one end of the pinion shaft of the planetary gear and the lubricant oil supply oil passage so that the lubricant is supplied to the carrier communication oil passage. The counter shaft communication oil passage is provided in the counter shaft, and the counter shaft communication oil passage is connected to the lubricating oil supply oil passage at the counter driven gear support portion at the center of the counter shaft. The outlet is an inclined hole inclined to the radial direction of the counter shaft, facing the inlet of the in-carrier communication oil passage.

  As a result, it is not necessary to provide an oil passage in the countershaft for supplying the lubricating oil to the pinion gear and the pinion shaft in the planetary gear support portion, and it is possible to prevent a decrease in the rigidity of the planetary gear support portion and to reduce the diameter of the planetary gear support portion of the counter shaft Thus, it is possible to achieve both the securing of the lubricating oil supplied to the pinion gear and the pinion shaft of the planetary gear of the auxiliary transmission mechanism and the rigidity of the counter shaft, while reducing the size of the automatic transmission.

  Here, the outlet of the countershaft communication oil passage facing the inlet of the carrier communication oil passage may be opened radially outward of the planetary gear support portion on the wall surface of the stepped portion of the counter driven gear support portion with the planetary gear support portion. .

  As a result, the lubricating oil can be effectively supplied to the in-carrier communication oil passage, and the counter-shaft communication oil passage can be moved away from the planetary gear support portion, thereby effectively preventing a reduction in the rigidity of the counter shaft.

  In the lubricating structure of the present invention, the bearing lubricating communication oil path provided in the counter shaft is configured to supply the lubricating oil to the bearing that supports the counter driven gear, and the counter shaft is configured to supply the lubricating oil to the pinion gear and the pinion shaft. It may be provided so as to be arranged on the same straight line as one of the internal communication oil passages.

  In this case, one of the countershaft communication oil passages for supplying lubricating oil to the pinion gear and the pinion shaft and the bearing oil communication oil passage can be formed by one hole machining, and the number of holes processed in the communication oil passage can be reduced. In addition, it is possible to achieve both the securing of the lubricating oil to the pinion gear and the pinion shaft and the rigidity of the counter shaft at a low cost.

  As described above, according to the present invention, in an automatic transmission having a main transmission mechanism and a sub-transmission mechanism, it is possible to secure the lubricating oil supplied to the pinion gear and the pinion shaft of the planetary gear of the sub-transmission mechanism and reduce the counter shaft while achieving compactness. It is possible to ensure both rigidity.

  1 to 4 show an example (first example) of an embodiment of the present invention. 1 is a schematic diagram showing the overall structure of an automatic transmission, FIG. 2 is a longitudinal sectional view of a subtransmission mechanism, FIG. 3 is a longitudinal sectional view of a subassembly including a counter shaft, and FIG. 4 is a sectional view taken along line AA in FIG. It is.

  As shown in FIG. 1, an automatic transmission 1 according to this embodiment includes a torque converter 3 to which an output of an engine 2 is input, and first and second planetary gears (planetary gear mechanisms) 4 and 5. A main transmission mechanism 6 and an auxiliary transmission mechanism 8 having a third planetary gear (planetary gear mechanism) 7 disposed on an axis parallel to the axis of the main transmission mechanism 6 are provided. The output of the engine 2 is input from the engine output shaft 9 to the torque converter 3, subjected to torque conversion, and output to the main transmission mechanism 6 via the turbine shaft 10 (input shaft of the main transmission mechanism 6). The oil pump 11 is disposed on the opposite side of the torque converter 3 from the engine and is driven by the engine output shaft 9 via the converter case 12 and the pump impeller 13.

  The main transmission mechanism 6 includes a forward clutch 21 between the turbine shaft 10 and the sun gear 20 of the first planetary gear 4, and includes a reverse clutch 23 between the turbine shaft 10 and the sun gear 22 of the second planetary gear 5. A 3-4 clutch 25 is provided between the turbine shaft 10 and the pinion carrier 24 of the second planetary gear 5, and a 2-4 brake 26 for fixing the sun gear 22 of the second planetary gear 5 is provided. The ring gear 27 of the first planetary gear 4 and the pinion carrier 24 of the second planetary gear 5 are connected, and the low reverse brake 29 and the main transmission one-way clutch 30 are arranged in parallel between the ring gear 27 and the transmission case 28. Has been. Further, the pinion carrier 31 of the first planetary gear 4 and the ring gear 32 of the second planetary gear 5 are connected, and a counter drive gear 33 is connected to them.

  The subtransmission mechanism 8 includes a counter driven gear 40 that always meshes with the counter drive gear 33. The counter driven gear 40 is connected to the ring gear 41 of the third planetary gear 7, and the sun gear 42 and the pinion of the third planetary gear 7 are connected. A direct coupling clutch 44 is provided between the carrier 43 and an auxiliary transmission one-way clutch 45 and a deceleration brake 46 are arranged in parallel between the sun gear 42 and the transmission case 28. The pinion carrier 43 of the third planetary gear 7 is connected to the counter shaft 47 that is the output shaft of the automatic transmission 1, and the output gear 48 fixed to the counter shaft 47 is engaged with the input gear 50 of the differential device 49. ing. As a result, the output of the auxiliary transmission mechanism 8 is transmitted to the left and right drive shafts 51 and 52 via the differential device 49.

  The automatic transmission 1 is configured as described above, and each frictional engagement element (forward clutch 21, reverse clutch 23, 3-4 clutch 25, 2-4 brake 26, low reverse brake 29) of the main transmission mechanism 6 and the auxiliary transmission mechanism 8 is configured. By selectively operating the main transmission one-way clutch 30, the direct coupling clutch 44, the auxiliary transmission one-way clutch 45, and the deceleration brake 46), five forward speeds and one reverse speed are obtained. The auxiliary transmission one-way clutch 45 is provided mainly for smoothly shifting from the fourth speed to the fifth speed. That is, in the 4-5 upshift, the deceleration brake 46 of the subtransmission mechanism 8 is released and the direct coupling clutch 44 is engaged. At this time, even if the deceleration brake 46 is released first, the one-way clutch 45 is locked until the direct coupling clutch 44 is engaged, and the engine 2 is prevented from being blown up.

  The specific structure of the auxiliary transmission mechanism 8 is as shown in FIG. The counter shaft 47 has a rear end portion (on the opposite side of the engine) supported rotatably via a bearing 61 inside a boss portion 28b extending forward (engine side) from the side wall portion 28a of the transmission case 28. (Engine side) is rotatably supported via a bearing 63 on a side wall 62 a of a transmission cover 62 that covers the torque converter 3. The third planetary gear 7, the direct coupling clutch 44, the deceleration brake 46, and the auxiliary transmission one-way clutch 45 are arranged on the counter shaft 47 and behind the counter driven gear 40.

  The sun gear 42 is provided with a boss portion 42 a at the rear end, and the boss portion 42 a is fitted with a spline on the boss portion 70 a at the engine side end portion of the rotating member 70 connected to the auxiliary transmission one-way clutch 45 and the deceleration brake 46. Are combined. A bearing 71 and an oil seal 72 are provided between the rotating member 70 and the boss portion 28 b of the transmission case 28. The ring gear 41 is fixed to the counter driven gear 40, and the counter driven gear 40 is supported on the counter shaft 47 via the bearing 73.

  In the counter shaft 47, the diameter of the counter driven gear support 47a that supports the counter driven gear 40 via the bearing 73 is relatively large, whereas the planetary gear support that supports the planetary gear 7 adjacent to the counter driven gear support 47a. The diameter of 47b is small, and there is a step between them. The counter driven gear support portion 47a forms a carrier fixing portion 47c having a larger diameter at the rear end portion, and the wall surface 47d of the stepped portion is formed substantially vertically, and between the wall surface 47d and the sun gear 42, A total roller type bearing 74 is interposed.

  The pinion carrier 43 is fixed to a carrier fixing portion 47 c at the rear end of the counter driven gear support portion 47 a of the counter shaft 47. Pinion shafts 75 are fixed to the pinion carrier 43 at predetermined positions that are spaced apart in the circumferential direction, and pinion gears 77 are rotatably supported by the three pinion shafts 75 via bearings 76, respectively.

  2 and 3, the countershaft 47 is provided with a lubricating oil supply oil passage 80 extending in the axial direction through the central portion of the shaft, and at one end at a predetermined position in the axial direction. Is connected to the lubricating oil supply oil passage 80, and the other end is opened radially outward of the counter shaft 47, and the lubricating oil is supplied from the lubricating oil supply oil passage 80 to each part around the counter shaft 47 (components of the auxiliary transmission mechanism). To supply the lubricating oil to the bearing 73 that supports the counter driven gear 40, and supply the lubricating oil to the pinion gear 77 and the pinion shaft 75 of the planetary gear 7. In addition to the communication oil path 82 (the planetary gear lubrication communication oil path), communication oil paths 81, 82, 83, and 84 are provided at a plurality of locations.

  In this embodiment, the communication oil passages 81, 83, 84 other than the communication oil passage 82 for planetary gear lubrication among the communication oil passages 81, 82, 83, 84 provided in a plurality of parts in the counter shaft 47 are: These holes are each processed in the radial direction so as to be connected to the lubricating oil supply oil passage 80 at the center of the counter shaft 47. On the other hand, three communicating oil passages 82 for planetary gear lubrication are provided at substantially equal intervals in the circumferential direction, and the respective inlets are connected to the lubricating oil supply oil passage 80 at the position of the counter driven gear support portion 47a at the center of the counter shaft 47. The outlet is a slanted oblique hole formed so as to open outward in the radial direction of the planetary gear support 47b on the wall surface 47d of the stepped portion of the counter driven gear support 47a with the planetary gear support 47b.

  As shown in FIG. 4, the pinion carrier 43 has a communication oil passage 91 (communication oil in the carrier) that communicates with the lubricating oil passages 75a, 75b, and 75c in the pinion shaft 75 at fixed positions of the three pinion shafts 75, respectively. Road) is formed. The inlets of the communication oil passages 91 in these carriers open to positions facing the stepped portions of the counter shaft 47, and the outlets of the communication oil passages 82 in the counter shaft 47 are connected to the communication oil passages 91 in the pinion carriers 43. It is a setting facing the entrance.

  In this embodiment, a planetary gear lubrication communication oil path for supplying lubricating oil to the pinion gear 77 and the pinion shaft 75 of the planetary gear 7 of the auxiliary transmission mechanism 8 is connected to a communication oil path 91 (intra-carrier communication) provided in the pinion carrier 43. An oil passage) and an inlet is connected to the lubricating oil supply oil passage 80 at the position of the counter driven gear support 47a, and an outlet is a communication oil passage 82 (counter) that is an oblique hole facing the inlet of the communication oil passage 91 in the pinion carrier 43. In-shaft communication oil passage). Therefore, there is no need to provide a counter-shaft communication oil passage for supplying lubricating oil to the pinion gear 77 and the pinion shaft 75 in the small-diameter planetary gear support 47a, and the rigidity of the planetary gear support 47b can be prevented from being lowered.

  5 to 8 show the main structure of another example (second example) of the embodiment of the present invention. 5 is a longitudinal sectional view of the sub-assembly including the counter shaft, FIG. 6 is a front view of the sub-assembly, FIG. 7 is a sectional view taken along the line AA in FIG. 6, and FIG.

  In this embodiment, a communication oil path 81 (communication oil communication path for bearing lubrication) provided in the counter shaft 47 so as to supply lubricating oil to the bearing 73 that supports the counter driven gear 40 is lubricated to the pinion gear 77 and the pinion shaft 75. It is provided so as to be aligned with one of the three communicating oil passages 82 (counter shaft communicating oil passages) for supplying oil. In this case, the communication oil passage 81 for bearing lubrication and one of the communication oil passages 82 in the counter shaft 47 can be formed by one hole machining. Others are the same as those of the automatic transmission of the first example. In the figure, the same reference numerals are given to the portions common to the first example and corresponding portions.

It is a mimetic diagram showing the whole automatic transmission structure concerning an embodiment of the invention. It is a longitudinal cross-sectional view of the auxiliary transmission mechanism of the automatic transmission of the first example of the embodiment of the present invention. It is a longitudinal cross-sectional view of the subassembly containing the counter shaft of the 1st example of embodiment of this invention. It is AA sectional drawing of FIG. It is a longitudinal cross-sectional view of the subassembly containing the counter shaft of the 2nd example of embodiment of this invention. It is a front view of the subassembly containing the counter shaft of the 2nd example of an embodiment of the invention. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG.

Explanation of symbols

1 Automatic transmission 2 Engine 4, 5, 7 Planetary gear (planetary gear mechanism)
6 Main transmission mechanism 8 Sub transmission mechanism 33 Counter drive gear 40 Counter driven gear 41 Ring gear 42 Sun gear 43 Pinion carrier 47 Counter shaft 47a Counter driven gear support portion 47b Planetary gear support portion 47c Carrier fixing portion 47c
47d Wall surface of stepped portion 61, 63, 73 Bearing 75 Pinion shaft 76 Bearing 77 Pinion gear 80 Lubricating oil supply oil passage 81 Communication oil passage (communication oil passage for bearing lubrication)
82 Communication oil passage (Communication oil passage for planetary gear lubrication)
91 Communication oil passage (carrier oil passage in carrier)

Claims (3)

A counter shaft that supports the sub-transmission mechanism is arranged in parallel with the primary shaft that supports the main transmission mechanism, and the counter shaft has a counter-driven gear that meshes with the counter drive gear on the main transmission mechanism side through a bearing at the center in the axial direction. A counter-driven gear support portion for supporting and a planetary gear support portion for supporting the planetary gear adjacent to the counter-driven gear support portion, the diameter of the planetary gear support portion being smaller than the diameter of the counter-driven gear support portion, In a lubricating structure of an automatic transmission that includes a lubricating oil supply oil passage that extends in the axial direction at the part, and both ends of the shaft are supported by a transmission case,
A planetary gear lubrication communication passage for supplying lubricating oil to the pinion gear and pinion shaft of the planetary gear, a carrier communication oil passage provided in a pinion carrier that supports one end of the pinion shaft of the planetary gear, and the lubricant supply oil A counter-shaft communication oil passage provided in the counter shaft so as to supply lubricating oil to the communication oil passage in the carrier connected to the passage,
The countershaft communication oil passage is connected to the lubricating oil supply oil passage at the counter driven gear support portion at the center of the countershaft, and the outlet faces the inlet of the carrier communication oil passage. A lubrication structure for an automatic transmission, characterized in that the hole is inclined with respect to the radial direction. The outlet of the countershaft communication oil passage facing the inlet of the carrier communication oil passage is opened radially outward of the planetary gear support portion on the wall surface of the stepped portion of the counter driven gear support portion with the planetary gear support portion. The lubricating structure for an automatic transmission according to claim 1. The bearing lubrication communicating oil passage provided on the counter shaft so as to supply the lubricating oil to the bearing supporting the counter driven gear is identical to one of the countershaft communicating oil passages supplying the lubricating oil to the pinion gear and the pinion shaft. The lubricating structure for an automatic transmission according to claim 1 or 2, wherein the lubricating structure is provided so as to be lined up on a line.

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