JP2015068365A - Transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a transmission including two clutches connected to a common rotary member.SOLUTION: A first clutch C1, of which a necessary torque capacity is large, is disposed outside of a second clutch C2, a cylindrical portion 90a of a hub drum member 90 as a common member is formed to have the uniform diameter in the axial direction, a first inner friction plate 89 of the first clutch C1 is fitted to an outer peripheral side of the cylindrical portion 90a, and a second outer friction plate 98 of the second clutch C2 is fitted to an inner peripheral side of the cylindrical portion 90a. According to the layout of the first clutch C1 and the second clutch C2, the number of sheets of first outer friction plates 88 and first inner friction plates 89 can be reduced, an outer diameter can be also reduced, further a frictional engagement portion of the first clutch C1 and a frictional engagement portion of the second clutch C2 can be axially overlapped, and an automatic transmission 20 can be axially miniaturized.

Description

  The present invention relates to a vehicle-mounted transmission.

  Conventionally, as this type of transmission, a transmission including a first planetary gear mechanism, a second planetary gear mechanism, three clutches, two brakes, and one one-way clutch has been proposed. (For example, refer to Patent Document 1). The first clutch of the three clutches of this transmission is connected to the first clutch hub that is connected to the input shaft and has a friction plate disposed on the outer peripheral side, and to the carrier of the second planetary gear mechanism. A first clutch drum having a friction plate disposed on the inner peripheral side. The third clutch of the three clutches is connected to the large-diameter sun gear of the first planetary gear mechanism and has a third clutch drum in which a friction plate is disposed on the inner peripheral side, and a first clutch of the first clutch. A third clutch hub connected to the one clutch drum and having a friction plate disposed on the outer peripheral side. The first clutch friction plate and the third clutch friction plate are arranged in series in the axial direction.

JP 2003-106428 A

  However, in the above-described transmission, the first clutch friction plate and the third clutch hub are connected to the common clutch and the first clutch drum of the first clutch and the third clutch hub of the third clutch. Since the clutch friction plates are arranged in series in the axial direction, it is difficult to reduce the axial size of the transmission. In particular, when the torque capacity of the first clutch or the third clutch is large, the number of friction plates increases, and the axial length of the transmission increases.

  The main purpose of the transmission of the present invention is to reduce the size of a transmission including two clutches connected to a common rotating member.

  The transmission of the present invention employs the following means in order to achieve at least the main object described above.

The transmission of the present invention is
A first clutch for connecting and releasing the first rotating member and the second rotating member; and a second clutch for connecting and releasing the first rotating member and the third rotating member. A transmission,
The first clutch includes a first piston, a first friction plate, a first mating plate, a drum member fixed to the second rotating member and fitted with an outer peripheral portion of the first mating plate, A first oil chamber defining member that defines a first engagement oil chamber by the drum member and the first piston and rotates integrally with the second rotating member;
The second clutch includes a second piston, a second friction plate, a second mating plate, a hub member fixed to the third rotating member and fitted with an inner peripheral portion of the second mating plate. A cylinder member that rotates integrally with the hub member, and a second oil chamber defining member that defines a second engagement oil chamber by the second piston and rotates integrally with the third rotating member,
Furthermore, it has a cylindrical portion that is held at the same diameter and is fitted with the inner peripheral portion of the first friction plate and the outer peripheral portion of the second friction plate, and rotates integrally with the first rotating member. Hub drum common member fixed and attached to
It is a summary to provide.

  In the transmission according to the present invention, the cylindrical portion held at the same diameter of the hub drum common member that is mounted and fixed so as to rotate integrally with the first rotating member has an inner periphery of the first friction plate of the first clutch. The peripheral part is fitted, and the outer peripheral part of the second friction plate of the second clutch is fitted to the inner peripheral side thereof. That is, the first friction plate and the first mating plate of the first clutch are arranged on the outer peripheral side from the second friction plate and the second mating plate of the second clutch. Therefore, since it is not necessary to arrange the first friction plate and the first mating plate of the first clutch and the second friction plate and the second mating plate of the second clutch in series in the axial direction, these are arranged in series in the axial direction. The axial length of the transmission can be shortened compared to the one. As a result, it is possible to reduce the axial size of the transmission.

  In such a transmission according to the present invention, at least a part of the first friction plate and the first mating plate of the first clutch is axially arranged such that the second friction plate and the second mating plate of the second clutch. It can also be one that overlaps part of the board. In this way, the axial length of the transmission can be further shortened.

  In the transmission of the present invention, the first clutch may be a clutch having a required torque capacity larger than that of the second clutch. Since the first clutch is arranged on the outer peripheral side than the second clutch, even if the required torque capacity is larger than that of the second clutch arranged on the inner peripheral side, the physique is not so large. For this reason, by arranging one of the two clutches having the larger required torque capacity as the first clutch, the diameter of the transmission is larger than that having the larger required torque capacity arranged as the second clutch. The size of the direction can be reduced.

  The transmission of the present invention further includes four planetary gear mechanisms, four clutches including the first clutch and the second clutch, and two brakes, and the power input to the input member is A combination of four clutches and three of the two brakes may be used to change the speed between 10 forward speeds and reverse speeds and output to the output member. In this case, the first planetary gear mechanism, which is one of the four planetary gear mechanisms, has the first rotation element, the second rotation element, and the third rotation in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. A second planetary gear mechanism, which is one of the four planetary gear mechanisms, includes a fourth rotating element and a fifth rotating element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. And a third planetary gear mechanism, which is one of the four planetary gear mechanisms, has a seventh rotational element and an eighth rotational order in the order corresponding to the gear ratio in the velocity diagram. The fourth planetary gear mechanism, which has a rotation element and a ninth rotation element and is one of the four planetary gear mechanisms, is arranged in the tenth rotation element in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. And an eleventh rotating element and a twelfth rotating element, and the first rotating element The first connecting element that connects the sixth rotating element, the second connecting element that connects the third rotating element and the eighth rotating element, and the seventh rotating element and the twelfth rotating element And a third connecting element that connects the ninth rotating element and the eleventh rotating element, and the first clutch includes the third connecting element as the first rotating member; A clutch for connecting and releasing the second rotating element as the second rotating member, wherein the second clutch is the third connecting element and the third rotating member as the first rotating member; And a third clutch that is one of the four clutches, the fifth rotating element and the tenth rotating element are connected to each other. Connect and release the connection A fourth clutch, which is a latch and is one of the four clutches, is a clutch that connects the fourth rotating element and the tenth rotating element and releases the connection. The first brake, which is one of them, is a brake that engages the fourth rotating element with the case of the transmission in a fixed manner and releases the engagement, and is one of the two brakes. A first brake is a brake that engages the fourth connecting element in a fixed manner with the case and releases the engagement. The input member is connected to the fifth rotating element, and the output member May be connected to the second rotating element. In this way, it is possible to configure a transmission that is 10 forward speeds and 1 reverse speed.

It is a block diagram which shows typically the structure of the automatic transmission 20 of an Example as a skeleton. It is sectional drawing of the automatic transmission 20 of an Example. It is an operation | movement table | surface of the automatic transmission 20 of an Example. It is the elements on larger scale which expand and show the portion containing the 1st clutch C1 and the 2nd clutch C2.

  Next, embodiments of the present invention will be described using examples.

  FIG. 1 is a configuration diagram schematically showing a configuration of an automatic transmission 20 as an embodiment of the present invention as a skeleton, and FIG. 2 is a cross-sectional view of the automatic transmission 20 of the embodiment. The automatic transmission 20 according to the embodiment includes four planetary gear mechanisms 30, 40, 50, 60, four clutches C1, C2, C3, C4, and two brakes B1, B2, and serves as an internal combustion engine (not shown). Is mounted on a vehicle of a type (for example, front engine rear drive type) in which the engine is placed vertically (in the longitudinal direction of the vehicle), and power from the engine is input via a starting device such as a torque converter (not shown). It is configured as a stepped transmission mechanism that inputs from a shaft (input shaft) 23 and shifts the input power to output it to an output shaft (output shaft) 24. The power output to the output shaft 24 is output to the left and right drive wheels via a gear mechanism and a differential gear (not shown). The automatic transmission 20 according to the embodiment includes the second planetary gear mechanism 40, the fourth planetary gear mechanism 60, the third planetary gear mechanism 50, and the first planetary gear mechanism 30 from the input shaft 23 side (left side in FIGS. 1 and 2). Arranged in order.

  The first planetary gear mechanism 30 is configured as a single pinion type planetary gear mechanism, and includes a sun gear 31 as an external gear, a ring gear 32 as an internal gear arranged concentrically with the sun gear 31, and a sun gear. A plurality of pinion gears 33 that mesh with the ring gear 32 and a carrier 34 that connects the plurality of pinion gears 33 and holds them rotatably and revolving. Similarly to the first planetary gear mechanism 30, the second to fourth planetary gear mechanisms 40, 50, 60 are also configured as single pinion type planetary gear mechanisms, and the same sun gears 41, 51, 61, ring gears 42, 52, 62, a plurality of pinion gears 43, 53, 63, and carriers 44, 54, 64. The input shaft 23 of the automatic transmission 20 is connected to the carrier 44 of the second planetary gear mechanism 40, and the output shaft 24 is connected to the carrier 34 of the first planetary gear mechanism 30.

  The sun gear 31 of the first planetary gear mechanism 30 and the ring gear 42 of the second planetary gear mechanism 40 are connected to each other by an intermediate shaft 71 as a first connecting element that is disposed coaxially with the input shaft 23 and the output shaft 24. The ring gear 32 of the first planetary gear mechanism 30 and the carrier 54 of the third planetary gear mechanism 50 are connected by a second connecting element 72. The sun gear 51 of the third planetary gear mechanism 50 and the ring gear 62 of the fourth planetary gear mechanism 60 are connected by a third connecting element 73, and the ring gear 52 of the third planetary gear mechanism 50 and the fourth planetary gear mechanism 60 are connected. The carriers 64 are connected by a fourth connecting element 74.

  The first clutch C <b> 1 is configured as a multi-plate friction clutch that engages or releases the carrier 34 of the first planetary gear mechanism 30 and the third coupling element 73, and the first planetary gear mechanism 30. Between the first planetary gear mechanism 50 and the third planetary gear mechanism 50 in the vicinity of the first planetary gear mechanism 30 side. The second clutch C2 is configured as a multi-plate friction clutch that engages or disengages the intermediate shaft 71 and the third connecting element 73, and the first planetary gear mechanism 30 and the third planetary gear mechanism. The first planetary gear mechanism 50 and the first clutch C1 in the vicinity of the first planetary gear mechanism 50 are disposed on the inner peripheral side. The third clutch C3 is configured as a multi-plate friction clutch that engages or disengages the carrier 44 of the second planetary gear mechanism 40 and the sun gear 61 of the fourth planetary gear mechanism 60. It is arranged on the outer peripheral side in the vicinity of the input side of the planetary gear mechanism 40 (left side in FIGS. 1 and 2). The fourth clutch C4 is configured as a multi-plate friction clutch that engages or releases the sun gear 41 of the second planetary gear mechanism 40 and the sun gear 61 of the fourth planetary gear mechanism 60. It is arranged on the input side from the clutch C3 and on the inner peripheral side from the third clutch C3.

  The first brake B1 is configured as a multi-plate friction brake that non-rotatably connects the sun gear 41 of the second planetary gear mechanism 40 to the case 22 of the automatic transmission 20 and releases the connection, and the third clutch C3. Furthermore, it is arranged on the input side. The second brake B2 connects the fourth connecting element 74 (the ring gear 52 of the third planetary gear mechanism 50, the carrier 64 of the fourth planetary gear mechanism 60) to the case 22 of the automatic transmission 20 in a non-rotatable manner. It is configured as a multi-plate friction brake to be released, and is disposed on the outer peripheral side of the second planetary gear mechanism 40.

  The automatic transmission 20 of the embodiment constructed in this way has an operation table of FIG. 3 by a combination of engagement and release of the four clutches C1, C2, C3 and C4 and engagement and release of the two brakes B1 and B2. As shown, the forward 10th speed and the reverse speed can be switched from the first forward speed. 3 is the gear ratio of the four planetary gear mechanisms 30, 40, 50, 60 (the number of teeth of the sun gear / the number of teeth of the ring gear). This is a case where 0.390, 0.395, 0.460, and 0.555 are used as λ1, λ2, λ3, and λ4.

  The configuration of the first clutch C1 and the second clutch C2 of the automatic transmission 20 according to the embodiment will be described in more detail. FIG. 4 is an enlarged partial view showing a part including the first clutch C1 and the second clutch C2 (rectangular part drawn by a one-dot chain line in FIG. 2).

  The first clutch C <b> 1 is connected to the carrier 34 of the first planetary gear mechanism 30 so as to rotate integrally with the carrier 34, and is rotatably supported by the intermediate shaft 71 and communicates with the oil passage of the intermediate shaft 71. The first cancellation oil chamber 87 is formed by the first piston 82 that defines the first engagement oil chamber 83 by the support member 81a having the oil hole 81b, the first cylinder 81 and the support member 81a, and the first piston 82. A first cancel plate 84, a first return spring 85 supported by the first cancel plate and urging the first piston 82 toward the first cylinder 81 (right side in the figure), and a first planetary gear mechanism 30, the drum member 86 formed integrally with the carrier 34, the hub drum member 90 that also serves as the drum member of the second clutch C 2, and the inner periphery of the drum member 86. It includes a plurality of first outer friction plates 88, a plurality of first inner friction plates 89 fitted to the outer peripheral side of the cylindrical portion 90a arranged in a plurality of alternately with the first outer friction plates 88 of Habudoramu member 90, a.

  The hub drum member 90 has a substantially bottomed cylindrical shape, and the cylindrical portion 90a is formed to have the same diameter in the axial direction. The hub drum member 90 is welded to the inner peripheral member 90b on the inner periphery thereof, and is connected to the sun gear 51 of the third planetary gear mechanism 50 and the ring gear 62 of the fourth planetary gear mechanism 60 via the inner peripheral member 90b. The third connection element 73 is connected to the third connection element 73 and rotates together with the third connection element 73.

  In the first clutch C1, when hydraulic pressure is applied to the first engagement oil chamber 83 from the oil passage of the intermediate shaft 71 through the oil hole 81b of the support member 81a, the first piston 82 is moved to the input shaft 23 side (see FIG. 4) and is moved against the first return spring 85, and the outer peripheral end of the first piston 82 presses the plurality of first outer friction plates 88. A hub drum connected to the third connecting element 73 via an inner peripheral member 90b and a drum member 86 formed integrally with the carrier 34 of the first planetary gear mechanism 30 by friction engagement with the first inner friction plate 89. The member 90 is connected (engaged). At this time, centrifugal oil pressure based on rotation is generated in the outer peripheral portion of the first engagement oil chamber 83, but this centrifugal oil pressure is canceled by the centrifugal oil pressure of the oil in the first cancel oil chamber 87. Since the first clutch C1 is engaged from the fourth forward speed to the seventh forward speed, as shown in the operation table of FIG. 3, the second clutch C2 is engaged from the seventh forward speed to the tenth forward speed. The required torque capacity is larger than that of the first clutch C1, but since the first clutch C1 is formed on the outer peripheral side of the second clutch C2, the engagement of the first outer friction plate 88 and the first inner friction plate 89 is increased. The total area can be easily increased. Therefore, contrary to the embodiment, the number of the first outer friction plates 88 and the first inner friction plates 89 can be reduced as compared with the second clutch C2 disposed on the outer peripheral side of the first clutch C1. The outer diameter can be reduced, and the automatic transmission 20 can be downsized. When the hydraulic pressure of the first engagement oil chamber 83 is released from the friction engagement state, the first piston 82 moves to the first cylinder 81 side (right side in FIG. 4) by the urging force of the first return spring 85, and the first By releasing the pressing of the plurality of first outer friction plates 88 by the outer peripheral end portion of the one piston 82, the frictional engagement between the first outer friction plate 88 and the first inner friction plate 89 is released, and the drum member 86 is released. And the hub drum member 90 are disconnected (engaged).

  The second clutch C <b> 2 is connected to the intermediate shaft 71 and rotates together with the intermediate shaft 71, and the second piston that defines the second engagement oil chamber 93 by the intermediate shaft 71 and the second cylinder 91. 92 and a hub member 96 connected to the intermediate shaft 71 and defining a second cancel oil chamber 97 by the first piston 82, and supported by the hub member 96 to urge the second piston 92 toward the second cylinder 91. A second return spring 95, a hub drum member 90 that also serves as a hub member of the first clutch C1, a plurality of second internal friction plates 98 that are fitted on the inner peripheral side of the hub drum member 90, and a outer peripheral side of the hub member 96. And a plurality of second inner friction plates 98 and a plurality of second outer friction plates 99 arranged alternately.

  As described above, the hub drum member 90 is formed so that the cylindrical portion 90a has the same diameter in the axial direction. Therefore, as shown in FIG. 4, the friction engagement portion of the first clutch C1 including the first outer friction plate 88 and the first inner friction plate 89 of the first clutch C1 on the outer peripheral side of the hub drum member 90, and the hub drum member The friction engagement portion of the second clutch C2 including the second inner friction plate 98 and the second outer friction plate 99 of the second clutch C2 on the inner peripheral side of the 90 can be disposed so as to slightly overlap in the axial direction. . Accordingly, the axial length of the automatic transmission 20 is shortened as compared with the arrangement in which the friction engagement portion of the first clutch C1 and the friction engagement portion of the second clutch C2 are not overlapped. Can do.

  In the second clutch C2, when the hydraulic pressure is applied to the second engagement oil chamber 93 from the oil passage of the intermediate shaft 71, the second piston 92 is pushed to the input shaft 23 side (left side in FIG. 4) by the hydraulic pressure and is When the outer peripheral end of the second piston 92 presses against the plurality of second inner friction plates 98 by moving against the return spring 95, the frictional engagement between the second inner friction plates 98 and the second outer friction plates 99 is achieved. Accordingly, the hub drum member 90 connected to the third connecting element 73 and the hub member 96 connected to the intermediate shaft 71 are connected (engaged) via the inner peripheral member 90b. At this time, centrifugal oil pressure based on rotation is generated in the outer peripheral portion of the second engagement oil chamber 93, but this centrifugal oil pressure is canceled by the centrifugal oil pressure of the oil in the second cancel oil chamber 97. On the other hand, when the hydraulic pressure in the second engagement oil chamber 93 is released from the friction engagement state, the second piston 92 moves to the second cylinder 91 side (right side in FIG. 4) by the urging force of the second return spring 95. By releasing the pressing of the plurality of second inner friction plates 98 by the outer peripheral end of the second piston 92, the frictional engagement between the second inner friction plates 98 and the second outer friction plates 99 is released, and the hub drum The connection (engagement) between the member 90 and the hub member 96 is released.

  According to the automatic transmission 20 of the embodiment described above, the cylindrical portion 90a of the hub drum member 90 is formed to have the same diameter in the axial direction, and the first internal friction of the first clutch C1 is formed on the outer peripheral side of the cylindrical portion 90a. The friction engagement portion of the first clutch C1 and the friction engagement portion of the second clutch C2 are fitted by fitting the plate 89 and fitting the second inner friction plate 98 of the second clutch C2 on the inner peripheral side of the cylindrical portion 90a. Can be arranged so as to overlap with each other in the axial direction, the length of the automatic transmission 20 in the axial direction can be shortened, and the size of the automatic transmission 20 in the axial direction can be reduced. Further, by arranging the first clutch C1 having a large required torque capacity outside the second clutch C2, the number of the first outer friction plates 88 and the first inner friction plates 89 can be reduced and the outer diameter can be reduced. Thus, the size of the automatic transmission 20 in the axial direction and the radial direction can be reduced, and the automatic transmission 20 can be downsized. As a result, it is possible to reduce the size of the relatively large automatic transmission 20 capable of shifting between the forward 10 speed and the reverse speed by using the four planetary gear mechanisms, the four clutches, and the two brakes.

  In the automatic transmission 20 of the embodiment, the friction engagement portion of the first clutch C1 and the friction engagement portion of the second clutch C2 are arranged so as to slightly overlap in the axial direction. It arrange | positions so that about half of an engaging part may overlap with the friction engaging part of the 2nd clutch C2, or arrange | positions so that all the friction engaging parts of the 1st clutch C1 may overlap with the friction engaging part of the 2nd clutch C2. On the contrary, it is arranged so that about half of the friction engagement portion of the second clutch C2 overlaps the friction engagement portion of the first clutch C1, or all of the friction engagement portions of the second clutch C2 are the first. You may arrange | position so that it may overlap with the friction engagement part of clutch C1.

  The automatic transmission 20 according to the embodiment is configured as a transmission that includes four planetary gear mechanisms 30, 40, 50, and 60, four clutches C1, C2, C3, and C4 and two brakes B1 and B2. Any transmission can be used as long as it has two clutches that connect (engage) the members to be engaged.

  Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. In the embodiment, the third connecting element 73 connected to the sun gear 51 of the third planetary gear mechanism 50 corresponds to the “first rotating member”, and the carrier 34 of the first planetary gear mechanism 30 corresponds to the “second rotating member”. The intermediate shaft 71 as the first connecting element corresponds to the “third rotating member”, the first clutch C1 corresponds to the “first clutch”, and the second clutch C2 becomes the “second clutch”. Equivalent to. The first piston 81 corresponds to the “first piston”, the first inner friction plate 89 corresponds to the “first friction plate”, the first outer friction plate 89 corresponds to the “first mating plate”, and the drum member 86 corresponds to a “drum member”, the first engagement oil chamber 83 corresponds to a “first engagement oil chamber”, and the first cylinder 81 corresponds to a “first oil chamber defining member”. The second piston 92 corresponds to a “second piston”, the second inner friction plate 98 corresponds to a “second friction plate”, the second outer friction plate 99 corresponds to a “second mating plate”, The hub member 96 corresponds to a “hub member”, the second engagement oil chamber 93 corresponds to a “second engagement oil chamber”, and the second cylinder 91 corresponds to a “second oil chamber defining member”. Further, the hub drum member 90 corresponds to a “hub drum common member”, and the cylindrical portion 90a corresponds to a “cylindrical portion”. The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is the same as that of the embodiment described in the column of means for solving the problem. It is an example for specifically explaining the best mode for doing so, and does not limit the elements of the invention described in the column of means for solving the problem. That is, the interpretation of the invention described in the column of means for solving the problems should be made based on the description of the column, and the examples are those of the invention described in the column of means for solving the problems. It is only a specific example.

  The best mode for carrying out the present invention has been described with reference to the embodiments. However, the present invention is not limited to these embodiments, and various modifications can be made without departing from the gist of the present invention. Of course, it can be implemented in the form.

  The present invention can be used in the manufacturing industry of automatic transmissions.

  20 automatic transmission, 22 case, 23 input shaft, 24 output shaft, 30 first planetary gear mechanism, 40 second planetary gear mechanism, 50 third planetary gear mechanism, 60 fourth planetary gear mechanism, 31, 41, 51, 61 Sun gear, 32, 42, 52, 62 Ring gear, 33, 43, 53, 63 Pinion gear, 34, 44, 54, 64 Carrier, 71 Intermediate shaft (first connecting element), 72 Second connecting element, 73 Third connecting Element, 74 fourth connecting element, 81 first cylinder, 81a support member, 81b oil hole, 82 first piston, 83 first engagement oil chamber, 84 first cancel plate, 85 first return spring, 86 drum member, 87 first cancel oil chamber, 88 first outer friction plate, 89 first inner friction plate, 90 hub drum member, 90a cylindrical portion, 90b inner peripheral member, 91 2 cylinders, 92 second piston, 93 second engagement oil chamber, 95 second return spring, 96 hub member, 97 second cancel oil chamber, 98 second inner friction plate, 99 second outer friction plate, C1 first Clutch, C2 second clutch, C3 third clutch, C4 fourth clutch, B1 first brake, B2 second brake.

Claims (4)

A first clutch for connecting and releasing the first rotating member and the second rotating member; and a second clutch for connecting and releasing the first rotating member and the third rotating member. A transmission,
The first clutch includes a first piston, a first friction plate, a first mating plate, a drum member fixed to the second rotating member and fitted with an outer peripheral portion of the first mating plate, A first oil chamber defining member that defines a first engagement oil chamber by the drum member and the first piston and rotates integrally with the second rotating member;
The second clutch includes a second piston, a second friction plate, a second mating plate, a hub member fixed to the third rotating member and fitted with an inner peripheral portion of the second mating plate. A cylinder member that rotates integrally with the hub member, and a second oil chamber defining member that defines a second engagement oil chamber by the second piston and rotates integrally with the third rotating member,
Furthermore, it has a cylindrical portion that is held at the same diameter and is fitted with the inner peripheral portion of the first friction plate and the outer peripheral portion of the second friction plate, and rotates integrally with the first rotating member. Hub drum common member fixed and attached to
A transmission comprising: The transmission according to claim 1, wherein
At least a part of the first friction plate and the first mating plate of the first clutch overlaps a part of the second friction plate and the second mating plate of the second clutch in the axial direction. ,
transmission. The transmission according to claim 1 or 2,
The first clutch is a clutch having a required torque capacity larger than that of the second clutch.
transmission. The transmission according to any one of claims 1 to 3,
Comprising four planetary gear mechanisms, four clutches including the first clutch and the second clutch, and two brakes,
The power input to the input member is shifted to the forward 10 speed and the reverse speed by a combination of three of the four clutches and the two brakes, and is output to the output member.
transmission.