JP4770625B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission for a vehicle, and more particularly to a technique for reducing the size thereof.

  2. Description of the Related Art Conventionally, an automatic transmission including a drum connected to an input shaft of a transmission, a hub connected to an output, and a multi-plate clutch connecting and disconnecting the drum and the hub is known ( For example, see Patent Document 1).

In this automatic transmission, a hub portion provided on the inner peripheral side of the multi-plate clutch, a drum portion provided on the outer peripheral side of the multi-plate clutch, a piston that presses the multi-plate clutch, and a hydraulic pressure that controls the piston. It has a servo. The hydraulic servo is usually provided on the drum portion side.
JP 2003-106342 A

  By the way, in recent years, the engine is required to be powered up more and more, but the size of the vehicle is limited.

  However, in the vicinity of the multi-plate clutch of the conventional automatic transmission, the hub portion connected to the output portion and the piston provided on the drum side connected to the input shaft of the transmission are connected and disconnected by the multi-plate clutch. The rotation speed may be different. For this reason, since it is necessary to provide a certain amount of clearance between the hub portion and the piston, the hub portion and the piston cannot be disposed so as to overlap in the axial direction, and the size of the automatic transmission is sufficiently small. There was a problem that could not be done.

  The present invention has been made in view of such a point, and an object of the present invention is to reduce the size of the automatic transmission by arranging the piston and the hub portion so as to overlap each other in the axial direction. is there.

  In order to achieve the above object, in the present invention, the hydraulic servo is provided not on the drum portion side connected to the output portion but on the hub portion side connected to the input shaft.

  Specifically, in the first invention, the first rotating member communicated with the input shaft of the transmission, the second rotating member communicated with the output unit, the first rotating member, and the second rotating member. An automatic transmission including a multi-plate clutch that connects and disconnects a rotating member is intended.

The automatic transmission includes a hub portion provided on the inner peripheral side of the multi-plate clutch,
A drum portion provided on the outer peripheral side of the multi-plate clutch;
A piston that presses the multi-plate clutch;
A hydraulic servo for controlling the piston ;
A transmission case surrounding the transmission;
A boss portion extending in the axial direction at the axial center portion of the transmission case side wall and through which the input shaft is inserted ;
The hydraulic servo is provided on the hub portion or a member connected to the hub portion,
The piston and the hub are each provided with a notch at a plurality of positions shifted in the circumferential direction, and are arranged so as to overlap the part provided with the notch in the axial direction .
The first rotating member is
The hub part;
A sleeve rotatably set on the boss part;
The hub portion and a first annular portion that communicates with the sleeve are configured .

According to the above configuration, since the hydraulic servo is provided on the hub portion connected to the input shaft or a member connected to the hub portion, the piston and the hub portion rotate integrally. For this reason, it is not necessary to provide a clearance for preventing contact between them. Therefore, if the piston and the hub portion are provided with notches at a plurality of positions that are displaced from each other in the circumferential direction, the piston and the hub portion are notched by inserting the portion without the notch portion of the hub portion into the notch portion of the piston. The portions where the portions are provided can overlap each other in the axial direction. In addition, since the hub portion is connected to a sleeve provided rotatably on a boss portion extending from the transmission case via the first annular portion, hydraulic oil pressurized by the hydraulic servo can be supplied from the boss portion. Become. For this reason, it is not necessary to separately provide a high-pressure oil supply path. Therefore, since the axial length can be shortened, the automatic transmission can be downsized.

In the second invention, the piston is
A second annular portion having an inner peripheral portion in sliding contact with the outer periphery of the sleeve and extending radially from the inner peripheral portion;
A cylindrical portion that communicates with the outer peripheral portion of the second annular portion and extends toward the side wall of the transmission case;
A third annular portion that communicates with the end portion of the cylindrical portion on the side wall side of the transmission case and extends in the radial direction.

  According to said structure, since a piston is formed compactly, it is easy to arrange | position a piston to the member connected with the hub part or the hub part. For this reason, since the axial length can be shortened, the automatic transmission can be downsized.

In the third aspect of the invention, the inner peripheral portion is locked to the outer periphery of the sleeve so as not to move toward the side wall of the transmission case. The seal extends radially from the inner peripheral portion and slides in contact with the inner periphery of the cylindrical portion. With a plate,
The pressure receiving chamber of the piston is formed in a region surrounded by the sleeve, the second annular portion, the cylindrical portion, and the seal plate.

  According to the above configuration, since the pressure receiving chamber is formed on the inner peripheral side of the hub portion, the hydraulic servo becomes compact. For this reason, since the axial length can be shortened, the automatic transmission can be downsized.

In a fourth invention, the hub portion includes a fourth annular portion that extends in a cylindrical shape toward the side wall of the transmission case,
The outer peripheral portion of the second annular portion is in sliding contact with the inner peripheral surface of the fourth annular portion,
The balance chamber of the piston is formed in a region surrounded by the sleeve, the first annular portion, the fourth annular portion, and the second annular portion.

  According to the above configuration, since the seal plate of the balance chamber can be shared by the connecting member between the hub portion and the sleeve, the hydraulic servo becomes further compact. For this reason, since the axial length can be shortened, the automatic transmission can be downsized.

In a fifth aspect of the invention, the first annular portion is formed with a hydraulic oil supply guide that supplies hydraulic oil to the hub portion from the side opposite to the piston of the first annular portion.

  According to the above configuration, since the piston is arranged on the inner peripheral side of the hub portion, it is necessary to supply hydraulic oil to the hub portion from the opposite side of the piston, but the hydraulic oil supply guide is provided in the first annular portion. Since it is formed, the hydraulic oil is supplied along the hydraulic oil supply guide. For this reason, there is no need to provide a separate hydraulic oil supply path, the axial length can be shortened, and the automatic transmission can be downsized.

As described above, according to the present invention, the hydraulic servo is provided on the member connected to the hub portion or hub portion is contacted to the input shaft, as well as placing the piston and the hub portion so as to overlap in the axial direction The first rotating member communicated with the input shaft of the transmission is composed of a hub portion, a sleeve rotatably set on the boss portion, and a first annular portion communicating the hub portion and the sleeve . As a result, the axial length can be shortened, and the automatic transmission can be downsized.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 schematically shows the overall structure of the automatic transmission according to the first embodiment of the present invention. As shown in FIG. 1, the automatic transmission 1 includes a torque converter 3 to which an output of the engine 2 is input, and a transmission gear mechanism 6 having first and second planetary gears (planetary gear mechanisms) 4 and 5. It has.

  The torque converter 3 is fixed in a converter case 8 connected to the engine output shaft 7 and is disposed so as to face the impeller pump 9 and is driven by the impeller pump 9 via hydraulic oil. A turbine runner 10, a stator 13 interposed between the impeller pump 9 and the turbine runner 10 and supported by a transmission case 11 via a one-way clutch 12, a converter case 8, and the turbine runner 10. A lock-up clutch 14 provided between the engine output shaft 7 and the turbine runner 10 is provided.

  The output of the engine 2 is input from the engine output shaft 7 to the torque converter 3, subjected to torque conversion, and output to the transmission gear mechanism 6 via the turbine shaft 15 as an input shaft. An oil pump 16 is disposed on the opposite side of the torque converter 3 from the engine, and is driven by the engine output shaft 7 via the converter case 8 and the impeller pump 9.

  The transmission gear mechanism 6 includes a forward clutch 21 as a multi-plate clutch between the turbine shaft 15 and the sun gear 20 of the first planetary gear 4. A reverse clutch 23 is provided between the turbine shaft 15 and the sun gear 22 of the second planetary gear 5. Between the turbine shaft 15 and the pinion carrier 24 of the second planetary gear 5, a 3-4 clutch 25 and a 2-4 brake 26 for fixing the sun gear 22 of the second planetary gear 5 are 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 a low reverse brake 29 and a one-way clutch 30 are arranged in parallel between the ring gear 27 and the transmission case 11. A pinion carrier 31 of the first planetary gear 4 and a ring gear 32 of the second planetary gear 5 are connected to each other, and an output gear 33 as an output unit is connected to them.

  An intermediate composed of a first intermediate gear 40 that always meshes with the output gear 33, an idle shaft 41 to which the first intermediate gear 40 is fixed, and a second intermediate gear 42 fixed to the other side of the idle shaft. A transmission mechanism is provided. The second intermediate gear 42 meshes with the input gear 51 of the differential device 50. As a result, the output of the transmission gear mechanism 6 is transmitted to the differential case 52 and is transmitted to the left and right drive shafts 53 and 54 via the differential device 50.

  Table 1 shows the relationship between the operating states of the friction elements 21, 23, 25, 26, 29 and the one-way clutch 30 and the shift speed.

  Next, the forward clutch 21 and its peripheral structure, which are the features of the present invention, will be described in detail.

  The automatic transmission 1 includes a first rotating member 60 communicated with a turbine shaft 15 as an input shaft, a second rotating member 61 communicated with an output gear 33, the first rotating member 60, and a second rotating member 60. The forward clutch 21 that connects and disconnects the rotating member 61 is provided.

  FIG. 2 shows an enlarged cross section of the forward clutch 21 and its periphery. FIG. 3 shows the forward clutch 21 and its peripheral members. FIG. 4 shows a hub-side clutch disc fitted with a hub portion. FIG. 5 shows a drum-side clutch disk with a drum fitted thereto. FIG. 6 shows the hub portion, and FIG. 7 shows the drum.

  As shown in FIG. 2, the forward clutch 21 includes a plurality of hub side clutch disks 55 on the inner peripheral side and a plurality of drum side clutch disks 56 on the outer peripheral side. A friction material 57 is attached to both surfaces of the hub side clutch disk 55. The friction material 57 is attached to the hub side clutch discs 55 at both ends only on the inner side. On the other hand, the friction material 57 is not attached to the drum-side clutch disk 56. Thus, the reason why the friction material 57 is provided only on the hub side clutch disk 55 connected to the turbine shaft 15 is to reduce the drag torque due to the repulsive force. Note that the hub-side clutch disks 55 at both ends are formed thicker than those provided in the middle in order to prevent collapse and absorb heat.

  A boss portion 72 that extends in the axial direction to the opposite side of the engine 2 and through which the turbine shaft 15 is inserted is formed at the shaft center portion of the transmission case side wall 11a that is the side wall of the transmission case 11 on the engine 2 side. Yes. A first rotating member 60 is rotatably provided on the boss portion 72. That is, as shown in FIG. 6, the first rotating member 60 includes a hub portion 64, a sleeve 73 that is rotatably set on the boss portion 72, and a first portion that connects the hub portion 64 and the sleeve 73. 1 annular portion 74. The hub portion 64 is formed with a hub-side clutch fitting portion 64 a having irregularities formed on the outer periphery so as to correspond to the hub-side clutch disk 55. As shown in FIG. 4, on the inner peripheral side of the hub side clutch disc 55, a hub portion 64 is coupled to the hub side clutch disc 55 so as to rotate together. That is, a clutch-side fitting portion 55a is formed on the inner peripheral side of the hub-side clutch disc 55, and this clutch-side fitting portion 55a is engaged with the hub-side clutch fitting portion 64a. Hub-side notches 71 are provided at a plurality of locations (four locations in the present embodiment) in the circumferential direction of the hub-side clutch fitting portion 64a. On the inner peripheral side of the hub-side clutch fitting portion 64a, a fourth annular portion 85 is formed concentrically with the hub-side clutch fitting portion 64a and extends in a cylindrical shape toward the transmission case side wall 11a.

  On the other hand, as shown in FIG. 5, on the outer peripheral side of the drum-side clutch disc 56 of the forward clutch 21, a drum portion 66 is coupled to the drum-side clutch disc 56 so as to rotate and be integrated with each other.

  As shown in FIG. 2, a piston 68 that presses the forward clutch 21 is provided on the transmission case side wall 11 a side of the hub portion 64. The piston 68 includes a second annular portion 75 extending in the radial direction from the inner peripheral portion 75a, with a lip seal 78 provided on the inner peripheral portion 75a slidingly contacting the outer periphery of the sleeve 73. As shown in FIG. 7, the piston 68 includes a cylindrical portion 76 that communicates with the outer peripheral portion of the second annular portion 75 and extends toward the transmission case side wall 11 a. A third annular portion 77 extends in the radial direction at the end of the cylindrical portion 76 on the transmission case side wall 11a side.

  In the third annular portion 77 of the piston 68, piston-side notches 70 are provided at a plurality of locations (four locations in the present embodiment) shifted in the circumferential direction from the hub-side notch 71 of the hub portion 64. Thus, by having the notch portions 70 and 71, it is possible to insert the portion of the hub portion 64 without the hub-side notch portion 71 into the piston-side notch portion 70 of the piston 68 as shown in FIG. It has become. Further, since the piston 68 is formed compactly, the piston 68 can be easily disposed on the transmission case side wall 11a side of the hub portion 64. As shown in FIG. 2, the hub portion 64 and the piston 68 are compactly arranged so that the portions where the cutout portions 70 and 71 are provided are overlapped in the axial direction. The length of has been shortened.

  A hydraulic servo 69 for controlling the piston 68 is disposed on the inner peripheral side of the hub portion 64. Specifically, a seal plate 79 is provided on the outer periphery of the sleeve 73. An inner peripheral portion 79a of the seal plate 79 is locked by an annular retaining plate 80 so as not to move toward the transmission case side wall 11a. Oil leakage is applied between the inner peripheral portion 79 a of the seal plate 79 and the outer periphery of the sleeve 73 by an O-ring 82. The seal plate 79 extends radially from the inner peripheral portion, and a lip seal 78 provided on the outer peripheral portion is in sliding contact with the inner periphery of the cylindrical portion 76.

  The pressure receiving chamber 86 of the piston 68 is surrounded by a sleeve 73, a second annular portion 75, a cylindrical portion 76, and a seal plate 79, and an area where oil leakage is prevented by two lip seals 78 and an O-ring 82. It is formed with. As described above, since the pressure receiving chamber 86 is formed on the inner peripheral side of the hub portion 64, the hydraulic servo 69 is compact. High pressure oil from the oil pump 16 is supplied to the pressure receiving chamber 86 through a high pressure oil supply passage 87 formed in the boss portion 72 and the sleeve 73. In this way, since the hub portion 64 is connected to the sleeve 73 rotatably provided on the boss portion 72 extending from the transmission case 11 via the first annular portion 74, the oil pump is connected from the boss portion 72 to the hydraulic servo 69. The hydraulic oil pressurized at 16 can be supplied. For this reason, it is not necessary to separately provide a high-pressure oil supply path, so that the axial length can be shortened.

  The lip seal 78 provided on the outer peripheral portion of the second annular portion 75 is in sliding contact with the inner peripheral surface of the fourth annular portion 85. The balance chamber 88 of the piston 68 is surrounded by the sleeve 73, the first annular portion 74, the fourth annular portion 85, and the second annular portion 75, and is formed in an area where oil leakage is prevented by the two lip seals 78. Has been. In the balance chamber 88, a plurality of return springs 89 are arranged in the circumferential direction to press the second annular portion 75 of the piston 68 from the side opposite to the transmission case side wall 11a. Thus, since the seal plate of the balance chamber 88 can be shared by the first annular portion 74 and the fourth annular portion 85 which are connecting members between the hub portion 64 and the sleeve 73, the hydraulic servo 69 is further compact. Yes.

  The first annular portion 74 is formed with a hydraulic oil supply guide 90 for supplying hydraulic oil to the hub portion 64 from the side opposite to the piston 68 of the first annular portion 74. That is, since the piston 68 is arranged on the inner peripheral side of the hub portion 64, it is necessary to supply hydraulic oil to the hub portion 64 from the opposite side of the piston 68, but the hydraulic oil supply guide to the first annular portion 74. Since 90 is formed, the hydraulic oil is supplied along the hydraulic oil supply guide 90. For this reason, it is not necessary to separately provide a hydraulic oil supply path.

-Effect of the embodiment-
Therefore, according to the automatic transmission according to the present embodiment, since the hydraulic servo 69 is provided on the inner peripheral side of the hub portion 64 connected to the turbine shaft 15, the piston 68 and the hub portion 64 rotate integrally. For this reason, it is not necessary to provide a clearance for preventing contact between the piston 68 and the hub portion 64. As described above, if the piston 68 and the hub portion 64 are provided with the cutout portions 70 and 71 at a plurality of positions shifted from each other in the circumferential direction, the portion without the hub-side cutout portion 71 of the hub portion 64 is moved to the piston side of the piston 68. By inserting it into the notch portion 70, the piston 68 and the hub portion 64 can overlap each other in the axial direction. Therefore, since the axial length can be shortened, the automatic transmission 1 can be downsized.

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or a use.

It is a mimetic diagram showing the whole automatic transmission structure concerning an embodiment of the present invention. It is sectional drawing which expands and shows a forward clutch and its periphery. It is a perspective view which shows a forward clutch and its periphery. It is a perspective view which shows what the hub part was fitted by the hub side clutch disc. It is a perspective view which shows what the drum was fitted to the drum side clutch disk. It is the perspective view which looked at the hub part from the transmission case side wall. It is the perspective view which looked at the piston from the side opposite to the transmission case side wall.

DESCRIPTION OF SYMBOLS 1 Automatic transmission 11 Transmission case 11a Transmission case side wall 15 Turbine shaft (input shaft)
21 Forward clutch (multi-plate clutch)
33 Output gear (output unit)
60 First rotating member 61 Second rotating member 64 Hub portion 66 Drum portion 68 Piston 69 Hydraulic servo 70 Piston side notch portion 71 Hub side notch portion 72 Boss portion 73 Sleeve 74 First annular portion 75 In the second annular portion 75a Peripheral portion 76 Cylindrical portion 77 Third annular portion 79 Seal plate 85 Fourth annular portion 86 Pressure receiving chamber 88 Balance chamber 90 Hydraulic oil supply guide

Claims (5)

A first rotating member communicated with the input shaft of the transmission, a second rotating member communicated with the output unit, and a multi-plate clutch that connects and disconnects the first rotating member and the second rotating member. An automatic transmission with which
A hub portion provided on the inner peripheral side of the multi-plate clutch;
A drum portion provided on the outer peripheral side of the multi-plate clutch;
A piston that presses the multi-plate clutch;
A hydraulic servo for controlling the piston ;
A transmission case surrounding the transmission;
A boss portion extending in the axial direction at the axial center portion of the transmission case side wall and through which the input shaft is inserted ;
The hydraulic servo is provided on the hub portion or a member connected to the hub portion,
The piston and the hub are each provided with a notch at a plurality of positions shifted in the circumferential direction, and are arranged so as to overlap the part provided with the notch in the axial direction .
The first rotating member is
The hub part;
A sleeve rotatably set on the boss part;
An automatic transmission comprising: a hub portion and a first annular portion that communicates with the sleeve . The automatic transmission according to claim 1 , wherein
The piston is
A second annular portion having an inner peripheral portion in sliding contact with the outer periphery of the sleeve and extending radially from the inner peripheral portion;
A cylindrical portion that communicates with the outer peripheral portion of the second annular portion and extends toward the side wall of the transmission case;
An automatic transmission comprising: a third annular portion that communicates with an end portion of the cylindrical portion on a side wall side of the transmission case and extends in a radial direction. The automatic transmission according to claim 1 or 2 ,
An inner peripheral portion is locked to the outer periphery of the sleeve so as not to move toward the side wall of the transmission case, and includes a seal plate extending in a radial direction from the inner peripheral portion and slidably contacting the inner periphery of the cylindrical portion,
The automatic pressure transmission is characterized in that the pressure receiving chamber of the piston is formed in a region surrounded by the sleeve, the second annular portion, the cylindrical portion, and the seal plate. The automatic transmission according to claim 3 , wherein
The hub portion includes a fourth annular portion that extends in a cylindrical shape toward the side wall of the transmission case,
The outer peripheral portion of the second annular portion is in sliding contact with the inner peripheral surface of the fourth annular portion,
2. The automatic transmission according to claim 1, wherein the balance chamber of the piston is formed in a region surrounded by the sleeve, the first annular portion, the fourth annular portion, and the second annular portion. The automatic transmission according to any one of claims 1 to 4 ,
The automatic transmission according to claim 1, wherein a hydraulic oil supply guide for supplying hydraulic oil to the hub portion from a side opposite to the piston of the first annular portion is formed in the first annular portion.

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