JP2017190800A - transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission configured to switch connection/disconnection between a plurality of clutches with reciprocating motion of a piston to change a speed, which can prevent the plurality of clutches from being simultaneously under an engagement release state.SOLUTION: A transmission includes a first planetary gear mechanism 20 configured to switch connection/disconnection of a first clutch 5 and a second clutch 10 with reciprocating motion of a piston 25 to change a speed; and a switching device 30 configured to reciprocate the piston 25 to switch connection/disconnection of the first clutch 5 and the second clutch 10. Movement to one side in a reciprocation direction of the piston 25 causes a first shift stage state of disconnecting the first clutch 5 and connecting the second clutch 10, and movement to the other side in the reciprocation direction of the piston 25 causes a second shift stage state of connecting the first clutch 5 and disconnecting the second clutch 10.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a transmission.

As a transmission used for a vehicle or the like, for example, a transmission disclosed in Patent Document 1 below is known.
A transmission disclosed in this document includes an input shaft that receives a driving force, an output shaft that is connected to a wheel side, and a transmission mechanism that is provided between the two shafts and switches between connecting and disconnecting a pair of friction clutches. And a pair of hydraulic cylinders as switching means for individually operating the pair of friction clutches, and a pair of pistons reciprocally moved by the hydraulic cylinders to connect and disconnect the clutches. Yes.

Japanese Patent No. 2776932

  By the way, in order to implement | achieve a brake state using the transmission of the said literature, it is necessary to put both a pair of clutches into an engagement state. However, if each clutch is operated by a separate piston, both clutches may be disengaged at the same time, that is, a substantially neutral state may occur.

  The present invention has been made in view of the above technical problem, and in a transmission that changes gears by switching the connection and disconnection of a plurality of clutches by reciprocating movement of a piston, the plurality of clutches are simultaneously placed in a disengaged state. The purpose is to prevent.

As a means for solving the above-described problems, the present invention provides a transmission mechanism that changes speed by switching between connection and disconnection of the first clutch and the second clutch by reciprocation of the piston, and the first clutch and the second clutch by reciprocating the piston. Switching means for switching between connection and disconnection of the piston, and by moving the piston to one side in the reciprocating direction, the first clutch is disengaged and the second clutch is connected, and the piston reciprocates. There is provided a transmission that is in a second shift state in which the first clutch is connected and the second clutch is disconnected by movement in the other direction.
According to this configuration, even if the piston moves in any direction in the reciprocating direction, one of the two clutches is maintained in the engaged state, so that both the clutches are not placed in the disengaged state at the same time. For this reason, it is possible to prevent the transmission from being unintentionally in a neutral state and to realize a reliable brake state.

In the present invention, the first clutch and the second clutch are arranged coaxially around a transmission shaft, the piston can reciprocate in the axial direction of the transmission shaft, and the first clutch and the second clutch A cylindrical clutch support member disposed coaxially with the clutch, wherein the clutch support member has one of the first engagement member of the first clutch and the second engagement member of the second clutch disposed radially inward. It is good also as a structure which supports and supports the other of said 1st engagement member and 2nd engagement member on the outer side of radial direction.
In this case, the engaging members of both clutches can be efficiently supported by the common clutch support member.

In the present invention, the first urging force is received in the reciprocating direction of the piston so as to bring the first engaging member into an engaged state, and the first urging force is resisted by the movement of the piston to one side in the reciprocating direction. And a second urging force opposite to the first urging force in the reciprocating direction of the piston so as to bring the second engagement member into an engaged state. And a second retainer that releases the engagement of the second engagement member against the second urging force by moving the piston to the other side in the reciprocating direction.
In this case, since the urging means for urging each retainer accumulates the urging force in different directions in the reciprocating direction of the piston, each retainer can be reliably urged in different directions. Therefore, the piston can more reliably engage one of the clutches and release the other by reciprocating movement.

In the present invention, a housing that houses the first clutch and the second clutch and is fixed to the outside, and a first urging means and a second urging member that urge the first retainer and the second retainer in the reciprocating direction, respectively. Biasing means, wherein the piston is disposed between the first clutch and the second clutch and the clutch facing wall of the housing in the reciprocating direction, and one of the first retainer and the second retainer is A piston-side retainer supported by the piston, and one of the first biasing means and the second biasing means is a piston-side biasing means for biasing the piston-side retainer, and the piston-side biasing means is Further, it may be configured to penetrate the piston and be supported by the clutch facing wall of the housing.
In this case, even when both retainers acting on both clutches are arranged on the clutch side of the piston, the piston-side urging means for urging the piston-side retainer penetrates the piston and is supported by the clutch facing wall of the housing. The piston side retainer can be efficiently biased without the biasing reaction force of the piston side retainer being input to the piston. In addition, since the piston-side urging means and the piston-side retainer are close to the piston, it is possible to prevent the parts from being concentrated around the clutch support member and becoming large.

In the present invention, the first clutch and the second clutch are arranged coaxially around a transmission shaft, the piston can reciprocate in the axial direction of the transmission shaft, and the transmission shaft is axially moved to the transmission shaft. A clutch hub supported movably, wherein one of the first retainer and the second retainer is a hub side retainer disposed on the opposite side of the piston across the clutch hub in the axial direction; The hub may have a configuration in which one end in the axial direction is connected to the hub side retainer and the other end in the axial direction is connected to the piston.
In this case, even if one of the retainers (hub side retainer) receiving the biasing force in the opposite direction in the axial direction of the transmission shaft (reciprocating direction of the piston) is arranged on the opposite side of the piston with the clutch hub interposed therebetween, the piston The hub side retainer can be operated efficiently through the clutch hub.

  According to the present invention, it is possible to prevent a plurality of clutches from being simultaneously disengaged in a transmission that switches gears by switching the connection and disconnection of a plurality of clutches by reciprocation of a piston.

It is a schematic diagram of the transmission in the embodiment of the present invention. It is a schematic diagram of the 1st gear stage state of the said transmission. It is a schematic diagram of the 2nd gear stage state of the said transmission.

Embodiments of the present invention will be described below with reference to the drawings.
As shown in FIG. 1, a transmission 1 is provided between an input shaft 2 and an output shaft 3 that are coaxial with each other and between the input / output shafts 2 and 3, and a pair of multi-plate clutches 5, 10 (hereinafter, (Referred to as first clutch 5 and second clutch 10). The first planetary gear mechanism 20 changes speed by switching connection and disconnection, and the first clutch 5 and the first planetary gear mechanism 20 move in the axial direction (axial direction) of the first planetary gear mechanism 20. A piston 25 that selectively connects / disconnects the second clutch 10, and a reciprocating movement of the piston 25 in the axial direction to selectively connect / disconnect the first clutch 5 and the second clutch 10 to change the speed of the first planetary gear mechanism 20. And a switching device 30 for switching.

  The input / output shafts 2 and 3 are arranged such that the central axis C1 is substantially horizontal and the central axis C1 is along the left-right direction in FIG. The input / output shafts 2 and 3 have the central axis C1 aligned with the central axis of the first planetary gear mechanism 20 (the central axis of the sun gear 21). In the following description, the left side in the drawing in the axial direction (axial direction) along the central axis C1 is referred to as one side in the axial direction, and the right side in the drawing is referred to as the other side in the axial direction. A direction orthogonal to the axial direction is referred to as a radial direction. The axial direction is also the reciprocating direction of the piston 25.

  A drive source M such as a hydraulic motor is connected to one end of the input shaft 2 in the axial direction. Torque at the center of the axis C <b> 1 is input from the drive source M to the input shaft 2. A sun gear 21 of the first planetary gear mechanism 20 is supported at the other axial end of the input shaft 2 so as to be integrally rotatable. The other axial end of the input shaft 2 faces the one axial end of the output shaft 3 in the axial direction. The input / output shafts 2 and 3 constitute a pair of transmission shafts that are separate and coaxial with each other. A sun gear 51 of a second planetary gear mechanism 50 described later is supported on the other axial end of the output shaft 3.

  The first planetary gear mechanism 20 supports a sun gear 21 that rotates integrally with the input shaft 2, a ring gear 22 that is spaced apart from the outer periphery of the sun gear 21, a planetary gear 23 that meshes between the sun gear 21 and the ring gear 22, and the planetary gear 23. A planetary carrier 24 supported at one end in the axial direction of the output shaft 3 so as to be integrally rotatable. The ring gear 22 is rotatably supported by the housing 35 of the transmission 1 via a bearing 22a. The ring gear 22 is connected to a clutch support member 36 described later so as to be integrally rotatable.

  The first planetary gear mechanism 20 alternately switches between connection and disconnection of the first clutch 5 and the second clutch 10, so that the first planetary gear mechanism 20 has two stages of a relatively low speed first speed stage state and a relatively high speed second speed stage state. Change the gear ratio to.

  The output shaft 3 outputs torque to the output member 37 arranged on the other side in the axial direction of the housing 35 via, for example, the second planetary gear mechanism 50 and the third planetary gear mechanism 55. The output member 37 is coaxial with the input / output shafts 2 and 3 and has a bottomed cylindrical shape that opens to the transmission 1 side (the other side in the axial direction), and the second and third planetary gear mechanisms 55 are disposed on the inner peripheral side.

  In the figure, reference numeral 51 denotes a sun gear of the second planetary gear mechanism 50, reference numeral 52 denotes a ring gear of the second planetary gear mechanism 50, reference numeral 53 denotes a planetary gear of the second planetary gear mechanism 50, and reference numeral 54 denotes a planetary carrier of the second planetary gear mechanism 50. Respectively. In the figure, reference numeral 56 denotes a sun gear of the third planetary gear mechanism 55, reference numeral 57 denotes a ring gear of the third planetary gear mechanism 55, reference numeral 58 denotes a planetary gear of the third planetary gear mechanism 55, and reference numeral 59 denotes a planetary gear of the third planetary gear mechanism 55. Each carrier is shown.

  The housing 35 houses the first planetary gear mechanism 20 together with the first clutch 5 and the second clutch 10. The housing 35 is fixed to the outside such as a body frame, for example. The housing 35 is formed in a cylindrical shape coaxial with the input / output shafts 2 and 3. The housing 35 extends in the axial direction to accommodate the first clutch 5 and the second clutch 10 on the inner circumferential side, and a clutch facing wall 35b extending from the other axial end of the trunk 35a toward the inner circumferential side. A second clutch facing wall 35c extending from the one axial end of the trunk portion 35a to the inner peripheral side, and a reduced diameter barrel portion 35d continuous to the one axial side of the second clutch facing wall 35c.

  On the outer periphery of the diameter-reduced body portion 35d of the housing 35, the inner periphery on the open side (the other side in the axial direction) of the output member 37 is rotatably supported via a pair of bearings 37a. A space between the reduced diameter body portion 35d of the housing 35 and the open side of the output member 37 is sealed in an oil-tight manner. The other end in the axial direction of the housing 35 is oil-tightly sealed so as to be accessible to the input shaft 2. An oil chamber 38 capable of storing oil is formed inside the housing 35 and the output member 37.

  The transmission 1 includes a cylindrical clutch support member 36 that is coaxial with the first clutch 5 and the second clutch 10. The clutch support member 36 is rotatably supported by the housing 35 together with the sun gear 21 of the first planetary gear mechanism 20. The clutch support member 36 includes a cylindrical portion 36a extending along the axial direction, a first flange 36b extending radially inward from one axial end of the cylindrical portion 36a, and a radial direction from the other axial end of the cylindrical portion 36a. A second flange 36c extending inward.

  The clutch support member 36 supports the plurality of first clutch plates 6 of the first clutch 5 on the radially inner side of the cylindrical portion 36a, and the plurality of second clutch plates 11 of the second clutch 10 on the radially outer side of the cylindrical portion 36a. Support. The clutch support member 36 is engaged with the clutch plates 6 and 11 through unevenness extending in the axial direction, and supports the clutch plates 6 and 11 so as to be integrally rotatable and movable in the axial direction.

  The plurality of first clutch plates 6 are stacked with a plurality of first mating plates 27 supported on the outer periphery of a clutch hub 26, which will be described later, alternately overlapping in the axial direction. The plurality of second clutch plates 11 and the plurality of second mating plates 39 supported on the inner periphery of the body portion 35a of the housing 35 are alternately stacked in the axial direction. The clutch hub 26 and the housing 35 are engaged with the clutch plates 27 and 39 in the same configuration as the clutch support member 36. The plurality of first clutch plates 6 and the first counterpart plate 27 are alternately overlapped to form the first laminated body 7, and the plurality of second clutch plates 11 and the second counterpart plate 39 are alternately overlapped with each other. The two laminated body 12 is comprised.

  The first clutch 5 includes a first retainer 8 that presses the first laminated body 7 in the axial direction so that the first laminated body 7 including the first clutch plate 6 and the first mating plate 27 is integrally engaged. ing. The first retainer 8 is disposed on one side of the first laminate 7 in the axial direction. A first flange 36b of the clutch support member 36 is disposed on one side in the axial direction of the first retainer 8 so as to be separated from each other. Between the first flange 36b and the first retainer 8, a first biasing member 9 such as a coil spring that biases the first retainer 8 toward the other side in the axial direction is provided. A second flange 36 c of the clutch support member 36 is disposed on the other side in the axial direction of the first stacked body 7. The first retainer 8 that has received the first urging force of the first urging member 9 sandwiches the first laminated body 7 with the second flange 36c of the clutch support member 36 to bring it into an engaged state.

  The clutch hub 26 is supported on the outer periphery of the intermediate portion in the axial direction of the input shaft 2 so as to be integrally rotatable and axially movable via a spline or the like. A radially inner side of the first retainer 8 can be brought into contact with one end in the axial direction of the clutch hub 26 via a first bearing 28. A radially inner side of the piston 25 can be brought into contact with the other axial end of the clutch hub 26 via a second bearing 29.

  The first retainer 8 can be moved to one axial direction via the clutch hub 26 by the movement of the piston 25 to one axial direction. At this time, the first retainer 8 moves to one side in the axial direction against the first biasing force of the first biasing member 9 and releases the engagement of the first stacked body 7.

  The second clutch 10 includes a second retainer 13 that presses the second laminated body 12 in the axial direction so that the second laminated body 12 including the second clutch plate 11 and the second mating plate 39 is integrally engaged. ing. The second retainer 13 is disposed on the other side in the axial direction of the second stacked body 12. On the other side in the axial direction of the second retainer 13, a clutch facing wall 35 b of the housing 35 is disposed so as to be separated from the piston 25. Between the clutch facing wall 35b and the second retainer 13, there is provided a second biasing member 14 such as a coil spring that penetrates the piston 25 and biases the second retainer 13 to one side in the axial direction. A second clutch facing wall 35 c of the housing 35 is disposed on one side in the axial direction of the second stacked body 12. The second retainer 13 that has received the second urging force of the second urging member 14 sandwiches the second laminated body 12 with the second clutch facing wall 35c to bring it into an engaged state.

  The second retainer 13 can move to the other side in the axial direction via the piston side engaging portion 25d of the piston 25 and the retainer side engaging portion 13d of the second retainer 13 by the movement of the piston 25 to the other side in the axial direction. is there. At this time, the second retainer 13 moves to the other side in the axial direction against the second urging force of the second urging member 14 and releases the engagement of the second stacked body 12. The second retainer 13 is supported on the clutch side (one side in the axial direction) of the piston 25 so as to be movable in the axial direction. The second stacked body 12 is arranged so as to be shifted to the other side in the axial direction with respect to the first stacked body 7.

  The piston 25 has a disk shape that is fitted into the body 35 a of the housing 35, and is disposed between the first clutch 5 and the second clutch 10 and the clutch facing wall 35 b of the housing 35 in the axial direction. The piston 25 includes a disc-shaped piston main body 25a, an annular fitting portion 25b extending from the radially outer end of the piston main body 25a to the other axial direction, and an annular projecting from the radially outer side of the piston main body 25a to the one axial side. Guide protrusion 25c.

  The fitting portion 25b is fitted into an annular recess 40 formed on the inner periphery of the body portion 35a of the housing 35 so as to be movable in the axial direction. A first oil chamber 41 in which the piston 25 can be moved to one side in the axial direction by supplying hydraulic pressure from the outside is formed on the other side in the concave portion 40 in the axial direction of the fitting portion 25b. A second oil chamber 42 capable of moving the piston 25 to the other side in the axial direction by supplying hydraulic pressure from the outside is formed in the concave portion 40 on one side in the axial direction of the fitting portion 25b.

  A first hydraulic supply / discharge port 43 that communicates with the first oil chamber 41 and a second hydraulic supply / discharge port 44 that communicates with the second oil chamber 42 are formed in the body 35 a of the housing 35. A hydraulic supply / discharge circuit (not shown) is connected to both supply / discharge ports 43 and 44. The switching device 30 of the transmission 1 includes both oil chambers 41 and 42 and both supply / discharge ports 43 and 44.

  A first seal member 45 and a second seal member 46 that are in sliding contact with the inner periphery of the body 35a of the housing 35 are mounted on the outer periphery of the fitting portion 25b and the guide protrusion 25c, respectively. A third seal member 47 slidably in contact with the inner periphery of the fitting portion 25 b is attached to the inner wall portion of the recess 40 in the housing 35.

Next, the operation of this embodiment will be described.
FIG. 1 shows a state in which the piston 25 is in the neutral position (intermediate position in the axial direction of the recess 40), for example, when the hydraulic pressure supply to both the oil chambers 41 and 42 is stopped. At this time, the piston 25 is moved to the neutral position by the urging force of the urging members 9 and 14.
That is, when the hydraulic pressure supply is stopped from the first gear position (see FIG. 2) in which the piston 25 moves to one side in the axial direction and the first clutch 5 is disengaged and the second clutch 10 is engaged. The first retainer 8 receiving the urging force of the first urging member 9 of the first clutch 5 moves the piston 25 to the other side in the axial direction via the clutch hub 26, and stops the piston 25 in the neutral position.
Further, when the hydraulic pressure supply is stopped from the second gear position (see FIG. 3) in which the piston 25 moves to the other side in the axial direction, the first clutch 5 is engaged, and the second clutch 10 is disengaged. The second retainer 13 receiving the urging force of the second urging member 14 of the second clutch 10 moves the piston 25 to one side in the axial direction, and stops the piston 25 in the neutral position.

  A gap can be formed between at least one of the neutral position piston 25 and the clutch hub 26 (and hence the first retainer 8) and between the neutral position piston 25 and the second retainer 13. Accordingly, the first clutch 5 is clamped by clamping the first stacked body 7 by the biasing force of the first biasing member 9 without causing the axial movements of the retainers 8 and 13 to interfere with each other via the piston 25. In addition, the second clutch 10 is also brought into the engaged state when the second laminated body 12 is clamped by the second urging member 14 in the engaged state.

  As shown in FIG. 2, when the hydraulic pressure P is supplied to the first oil chamber 41 through the first hydraulic supply / discharge port 43, the piston 25 moves to one side in the axial direction. Then, the radially inner side of the piston 25 moves the first retainer 8 to the one side in the axial direction against the first urging force of the first urging member 9 via the clutch hub 26. As a result, the first stacked body 7 is disengaged and the first clutch 5 is disengaged. On the other hand, on the outer side in the radial direction of the piston 25, both the engaging portions 25d and 13d are only separated from each other, and the second stacked body 12 is maintained in the engaged state.

  Thus, when torque is input to the input shaft 2, the input shaft 2 and the sun gear 21 rotate while the second clutch 10, the clutch support member 36, and the ring gear 22 are fixed to the housing 35 so as not to rotate. As a result, the first gear stage state is established in which the torque of the input shaft 2 is decelerated by the first planetary gear mechanism 20 and transmitted to the output shaft 3. A portion that rotates in the first gear stage state is indicated by hatching in FIG.

  As shown in FIG. 3, when the hydraulic pressure P is supplied to the second oil chamber 42 via the second hydraulic supply / discharge port 44, the piston 25 moves to the other side in the axial direction. Then, the piston 25 is only separated from the clutch hub 26 inside the piston 25 in the radial direction, and the first clutch 5 is maintained in the engaged state. On the other hand, on the radially outer side of the piston 25, the second retainer 13 is moved to one side in the axial direction against the second urging force of the second urging member 14 via both engaging portions 25d and 13d. As a result, the second laminated body 12 is disengaged and the second clutch 10 is disengaged.

  Thus, when torque is input to the input shaft 2, the clutch support member 36 and the ring gear 22 rotate integrally with the input shaft 2 via the first clutch 5, and the planetary carrier 24 also rotates at a constant speed with the input shaft 2. . As a result, a second gear state is established in which the torque of the input shaft 2 is transmitted to the output shaft 3 at a constant speed. The portion that rotates in the second shift state is shown by hatching in FIG.

In the transmission 1, in the first gear stage state, power is transmitted at a low speed with an emphasis on torque, and in the second gear stage state, power is transmitted by increasing the rotational speed. In the first gear position, the bearings 28 and 29 on both sides of the clutch hub 26 serve as contact points between the rotation side and the fixed side in the transmission 1. That is, by disposing the bearings 28 and 29 at the contact points between the rotation side and the fixed side, heat generation of oil due to friction is reduced as compared with the case where the rotation side and the fixed side are simply in contact.
In the first gear stage state, the clutch hub 26 and the first mating plate 27 in the first clutch 5 are located on the rotation side, and the other parts are located on the fixed side. That is, fewer members rotate with respect to the fixed side. Therefore, when the first clutch 5 is lubricated by the lubricating oil introduced separately from the hydraulic pressure of the piston 25, there is an advantage that the lubricating oil does not jump off so much and can easily reach the portion that performs the relative rotation. .

  On the other hand, in the second gear position where the rotational speed is relatively high, the piston 25 is separated from the clutch hub 26 and the second retainer 13 is separated from the second laminated body 12, so that the rotation side and the fixed side in the transmission 1 are separated. There will be fewer contacts. For this reason, heat generation of oil due to friction is further reduced. In other words, relative rotation occurs between the second clutch plate 11 and the second mating plate 39 due to the disengagement, but there is no portion that rotates relative to the bearings 28 and 29, so heat generation itself disappears. For this reason, although the oil generates heat, the amount of generated heat becomes very small.

  Since the piston 25 is on the fixed side together with the housing 35, the seal members 45 to 47 forming the oil chambers 41 and 42 between the piston 25 and the housing 35 do not come into contact with the rotating sliding portion, and the seal members 45 to 47 Wear is suppressed. Since the oil chambers 41 and 42 are formed between the piston 25 and the housing 35 on the fixed side, the oil passage does not straddle the rotating sliding portion. That is, it is possible to eliminate the need for a seal member for the rotary sliding portion, suppress an increase in maintenance frequency, and facilitate management around the oil passage for clutch operation.

As described above, the transmission 1 according to the above embodiment reciprocates between the first planetary gear mechanism 20 that changes speed by switching the connection and disconnection of the first clutch 5 and the second clutch 10 by the reciprocation of the piston 25 and the piston 25. And a switching device 30 that switches the connection and disconnection of the first clutch 5 and the second clutch 10 to disengage the first clutch 5 and move the first clutch 5 by moving the piston 25 to one side in the reciprocating direction. The first gear stage is connected with the two clutches 10, and the second gear stage is connected with the first clutch 5 and disconnected with the second clutch 10 by the movement of the piston 25 to the other side in the reciprocating direction. .
According to this configuration, even if the piston 25 moves in any direction in the reciprocating direction, one of the clutches 5 and 10 is maintained in the engaged state, so that both the clutches 5 and 10 are simultaneously disengaged. Is no longer placed in For this reason, the transmission 1 can be prevented from unintentionally entering a neutral state, and a reliable brake state can be realized.

In the transmission 1, the first clutch 5 and the second clutch 10 are arranged coaxially around the input / output shafts 2 and 3, and the piston 25 reciprocates in the axial direction of the input / output shafts 2 and 3. A cylindrical clutch support member 36 that is movable and arranged coaxially with the first clutch 5 and the second clutch 10 is provided, and the clutch support member 36 is disposed radially inward of the first clutch 5. One of the first clutch plate 6 and the second clutch plate 11 of the second clutch 10 is supported, and the other of the first clutch plate 6 and the second clutch plate 11 is supported on the outside in the radial direction.
According to this configuration, the clutch plates 6 and 11 of both the clutches 5 and 10 can be efficiently supported by the common clutch support member 36.

The transmission 1 receives a first biasing force in the reciprocating direction of the piston 25 so as to bring the first clutch plate 6 into an engaged state, and moves the first clutch 25 toward the one side in the reciprocating direction. The first retainer 8 that releases the engagement of the first clutch plate 6 against the urging force, and the first urging force in the reciprocating direction of the piston 25 so that the second clutch plate 11 is engaged. A second retainer 13 that receives a second biasing force in the opposite direction and releases the engagement of the second clutch plate 11 against the second biasing force by moving the piston 25 to the other side in the reciprocating direction; Is provided.
According to this configuration, the urging means that urges the retainers 8 and 13 accumulates the urging force in different directions in the reciprocating direction of the piston 25, so that the retainers 8 and 13 are surely moved in different directions. Can be energized. Therefore, the piston 25 can more reliably engage one of the clutches 5 and 10 and release the other by reciprocating movement.

The transmission 1 houses the first clutch 5 and the second clutch 10 and urges the housing 35 fixed to the outside and the first retainer 8 and the second retainer 13 in the reciprocating direction. And the piston 25 is disposed between the first clutch 5 and the second clutch 10 and the clutch facing wall 35b of the housing 35 in the reciprocating direction. One of the first retainer 8 and the second retainer 13 is a piston side retainer supported by the piston 25, and one of the first biasing member 9 and the second biasing member 14 is the piston side. The piston side urging means for urging the retainer passes through the piston 25 and is connected to the housing 35. It is supported by the pitch opposed wall 35b.
According to this configuration, even when both retainers 8 and 13 acting on both clutches 5 and 10 are arranged on the clutch side with respect to the piston 25, the piston-side urging means for urging the piston-side retainer penetrates the piston 25. Therefore, the piston side retainer can be efficiently biased without the biasing reaction force of the piston side retainer being input to the piston 25. Further, since the piston-side urging means and the piston-side retainer are configured close to the piston 25, it is possible to prevent the parts from being concentrated around the clutch support member 36 and becoming larger.

In the transmission 1, the first clutch 5 and the second clutch 10 are arranged coaxially around the input / output shafts 2 and 3, and the piston 25 reciprocates in the axial direction of the input / output shafts 2 and 3. A clutch hub 26 that is movable and supported by the input shaft 2 so as to be movable in the axial direction is provided, and one of the first retainer 8 and the second retainer 13 supports the clutch hub 26 in the axial direction. The clutch hub 26 is connected to the hub side retainer at one end in the axial direction and connected to the piston 25 at the other end in the axial direction. Is done.
According to this configuration, one of the retainers 8 and 13 (hub side retainer) receiving the biasing force in the opposite direction in the axial direction of the input / output shafts 2 and 3 (reciprocating direction of the piston 25) sandwiches the clutch hub 26. Even if it is arranged on the side opposite to the piston 25, the piston 25 can efficiently operate the hub side retainer via the clutch hub 26.

In addition, this invention is not restricted to the said embodiment, For example, the input shaft 2 may be connected with other types of drive sources, such as an electric motor, instead of a hydraulic motor.
Each urging member 9, 14 is not limited to a coil spring but may be a disc spring or the like. Here, since the transmission 1 engages the clutches 5 and 10 using a mechanical spring and disengages the clutches 5 and 10 by supplying hydraulic pressure, the clutches 5 and 10 are engaged when the hydraulic pressure supply is stopped. It will be in a state and it will be in a brake state reliably at the time of a stop of an onboard vehicle.
Instead of the planetary gear mechanism 20, various speed change mechanisms may be employed.
Instead of the hydraulic switching device 30, a mechanical or electrical switching device may be employed.
The configuration in the above embodiment is an example of the present invention, and various modifications can be made without departing from the scope of the invention.

1 Transmission 2 Input shaft (transmission shaft)
3 Output shaft (transmission shaft)
5 First clutch 6 First clutch plate (first engagement member)
8 First retainer (Hub side retainer)
9 First urging member (first urging means)
10 Second clutch 11 Second clutch plate (second engagement member)
13 Second retainer (Piston side retainer)
14 Second urging member (second urging means, piston side urging means)
20 First planetary gear mechanism (transmission mechanism)
25 piston 26 clutch hub 30 switching device (switching means)
35 Housing 36 Clutch support member 35b Clutch facing wall

Claims (5)

A speed change mechanism that changes speed by switching between connection and disconnection of the first clutch and the second clutch by reciprocation of the piston;
Switching means for reciprocating the piston to switch between connection and disconnection of the first clutch and the second clutch, and
By moving the piston to one side in the reciprocating direction, the first clutch is disengaged and the second clutch is connected to the first shift state,
A transmission in which the first clutch is connected and the second clutch is disconnected by moving the piston to the other side in the reciprocating direction. The first clutch and the second clutch are arranged coaxially around a transmission shaft, and the piston can reciprocate in the axial direction of the transmission shaft; and
A cylindrical clutch support member disposed coaxially with the first clutch and the second clutch;
The clutch support member supports one of the first engagement member of the first clutch and the second engagement member of the second clutch on the inner side in the radial direction, and the first engagement member and the second engagement member on the outer side in the radial direction. The transmission according to claim 1, wherein the other of the two engaging members is supported. The first urging force is received in the reciprocating direction of the piston so as to bring the first engaging member into an engaged state, and the first urging force is resisted by the movement of the piston toward one side in the reciprocating direction. A first retainer for releasing the engagement of the engagement member;
The second engagement member receives a second urging force opposite to the first urging force in the reciprocating direction of the piston so that the second engaging member is engaged. The transmission according to claim 2, further comprising a second retainer that releases the engagement of the second engagement member against an urging force. A housing that houses the first clutch and the second clutch and is fixed to the outside;
First urging means and second urging means for urging the first retainer and the second retainer in the reciprocating direction, respectively,
The piston is disposed between the first and second clutches and the clutch facing wall of the housing in the reciprocating direction;
One of the first retainer and the second retainer is a piston side retainer supported by the piston,
One of the first biasing means and the second biasing means is a piston side biasing means for biasing the piston side retainer,
The transmission according to claim 3, wherein the piston-side urging means penetrates the piston and is supported by a clutch facing wall of the housing. The first clutch and the second clutch are arranged coaxially around a transmission shaft, and the piston can reciprocate in the axial direction of the transmission shaft; and
A clutch hub supported on the transmission shaft so as to be movable in the axial direction;
One of the first retainer and the second retainer is a hub side retainer disposed on the opposite side of the piston across the clutch hub in the axial direction,
5. The transmission according to claim 3, wherein the clutch hub has one end in the axial direction connected to the hub side retainer and the other end in the axial direction connected to the piston.

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