KR101786805B1 - Actuator for dual clutch - Google Patents

Abstract

Disclosed is an actuator for a dual clutch. The dual clutch comprises: a first clutch that selectively transmits rotational power of an input shaft to a first output shaft; a second clutch configured to selectively transmit the rotational power of the input shaft to a second output shaft; a first piston configured to always transmit the rotational power of the input shaft transmitted to the first clutch to the second clutch and selectively move in an axial direction by an axial force to operate the first clutch; and a second piston being movable in the axial direction irrespective of the axial movement of the first piston, and selectively moving in the axial direction by the axial force to operate the second clutch. The actuator is adapted to transmit the axial force to the first piston or the second piston, respectively. As such, the actuator for a dual clutch using hydraulic pressure suitable for alternating operation of not only the dual clutch but also various dual clutches is provided.

Description

TECHNICAL FIELD [0001] The present invention relates to an actuator for a dual clutch,

The present invention relates to an actuator for a dual clutch, more particularly, to a dual clutch actuator having a first clutch for selectively transmitting power of a power source to a first output shaft, and a second clutch for selectively transmitting power of the power source to a second output shaft To an actuator for a dual clutch.

Eco-friendly technology in vehicles is a core technology with survival of the future automobile industry, and car makers are concentrating on developing environment-friendly vehicles to achieve environmental and fuel efficiency regulations. Further, studies on a double clutch transmission or a double clutch transmission (DCT) as a transmission that can be applied to the environmentally friendly automobile are being actively conducted. The DCT is designed to improve efficiency and convenience by applying two clutches to the manual transmission structure.

That is, the DCT is a transmission in which a shift is performed while alternately operating the hole means and the even means by using two clutches. The mechanism for alternately operating the hole means and the even means is a shift mechanism It is possible to improve the torque cut-off feeling, and it is advantageous that the shift operation is easy.

The DCT is provided with two clutches for selectively transmitting the rotational power of the input shaft to the first and second output shafts. Due to structural considerations, the two clutches do not interfere with each other in operation, and conventionally, one clutch receives the rotational power of the input shaft, and the one clutch and the other clutch are connected by the power transmitting member, To be transmitted to the two clutches. In addition, a piston or a diaphragm spring for operating each clutch is provided separately from the power transmitting member.

According to the related art, various means have been applied to prevent interference between the power transmitting member and the piston or the diaphragm spring, but there has been a problem that the number of parts increases and the structure becomes complicated.

In order to solve such a problem, Korean Patent Application No. 10-2015-0133933 was filed by the present inventor. The Korean Patent Application No. 10-2015-0133933 allows the rotational power of the first clutch housing to be transmitted to the second clutch housing through the first piston for operating the first clutch, thereby reducing the number of parts and reducing the production cost There is an advantage.

It is an object of the present invention to provide an actuator for a dual clutch using hydraulic pressure suitable for the alternating operation of various double clutches as well as the dual clutches.

Particularly, in the present invention, when the operating oil pressure is supplied to one operating piston chamber, the operation of the operating oil pressure supplied to the other operating piston chamber is smoothly performed, so that the alternating operation is smooth and the hydraulic working area of the piston is increased And to provide an actuator for a dual clutch that can lower the working oil pressure and can easily process the housing.

The actuator according to an embodiment of the present invention includes a first clutch configured to selectively transmit rotational power of an input shaft to a first output shaft, a second clutch configured to selectively transmit rotational power of the input shaft to a second output shaft, A first piston which selectively moves in the axial direction by an axial force and operates the first clutch, and a second piston which selectively moves in the axial direction by the axial force and operates the second clutch. The actuator is adapted to transmit an axial force to the first piston or the second piston, respectively.

The actuator includes an actuator housing spaced apart from each other in the radial direction and including an axially protruding actuator housing inner circumference and a housing protrusion, and forming an actuating piston space between the housing inner housing and the housing protrusion; A first actuating piston mounted in the actuating piston space and providing axial force to the first piston through a first release bearing; And a second operating piston mounted in the operating piston space and providing operating force to the second piston through a second release bearing.

The second operating piston includes a second operating piston inner periphery that is in close contact with the inner periphery of the actuator housing and extends in the axial direction and a second operating piston inner periphery extending radially outward from the rear end of the inner periphery of the second operating piston, 2 operating piston, and the inner circumferential surface of the first operating piston may be in close contact with the inner circumferential portion of the second operating piston and the outer circumferential surface of the first operating piston may be in close contact with the housing protruding portion.

A first actuating piston chamber may be formed between the first actuating piston, the second actuating piston inner circumference and the housing protrusion, and a second actuating piston chamber may be formed between the second actuating piston and the actuator housing.

A first supply passage for supplying operating oil pressure to the first operating piston chamber, a second supply passage for supplying operating oil pressure to the second operating piston chamber, 3 supply passage may be formed.

The actuator may further include a return spring for providing an elastic force to the first operating piston, and the return spring may be axially supported by at least one spring seat fixedly mounted on the inner circumference of the actuator housing.

Wherein at least one mounting hole is formed in a circumferential direction in a circumference of the inner circumference of the second operating piston, a stepped portion having a small diameter is formed in a circumference of the inner circumference of the actuator housing, And can be axially supported by the stepped portion and the snap ring.

Wherein the actuator further comprises an additional spring seat interposed between the return spring and the first actuating piston on the opposite side of the spring seat, at least a portion of the additional spring seat being inserted into the mounting hole to be axially movably mounted .

Wherein the first clutch includes a first clutch housing operatively connected to the input shaft and rotates together with the input shaft and the second clutch is operatively connected to the first clutch housing through the first piston, And a second clutch housing which rotates together with the clutch housing.

The first piston may be splined to the inner circumferential surface of the first clutch housing, and the second clutch housing may be coupled to the first piston.

Wherein the first clutch housing includes a first disk portion having an inner end coupled to the input shaft and extending radially outwardly and a first cylindrical portion extending axially rearward from an outer end of the first disk portion, The first clutch further comprises a plurality of first separate plates spline-coupled to the inner circumferential surface of the first cylindrical portion; A first actuating hub operatively coupled to the first output shaft; A plurality of first friction disks splined to an outer circumferential surface of the first actuating hub, the first friction disks being alternately disposed with the plurality of first separate plates; And at least one first separating spring disposed between neighboring first separate plates at a radially outer side of the plurality of first friction disks.

A first support portion for axially supporting the first separate plate is formed on the radially outer side of the first disk portion, and a second support portion for supporting the first separate plate on the outer side of the first piston for providing an axial force to the first separate plate, The ends can be splined.

The second clutch housing is joined to the first piston in the radial direction of the first clutch and the second clutch is splined to the inner circumferential surface of the second clutch housing; A second actuating hub operatively coupled to the second output shaft; A plurality of second separate plates spline-coupled to the outer circumferential surface of the second actuating hub, the second separate plates being alternately arranged with the plurality of second friction discs; And at least one second separating spring disposed between adjacent second separate plates at radially inner sides of the plurality of second friction disks.

A second support portion for axially supporting the second separate plate is coupled to a front outer circumferential surface of the second operating hub and a second piston for providing axial force to the second separate plate is provided on a rear inner circumferential surface of the second clutch housing, Can be splined.

A front cover may be mounted on the front side of the first clutch housing in the axial direction between the transmission housing and the input shaft.

A sealing member and a bearing may be sequentially mounted from the front side to the rear side between the inner circumferential surface of the front cover and the outer circumferential surface of the input shaft.

And a second lubricating oil passage for supplying lubricating oil to the bearing may be formed at a position of the first clutch housing corresponding to the bearing.

A bearing is mounted between the inner circumferential surface of the actuator housing and the inner circumferential surface of the second actuating hub. A sealing member may be formed between the inner circumferential surface of the actuator housing and the outer circumferential surface of the second output shaft.

And a passage connecting hole for supplying lubricating oil to the bearing may be formed inside the actuator housing.

A bearing may be disposed between the inner circumferential portion of the first clutch housing and the inner circumferential portion of the first operating hub and between the inner circumferential portion of the first operating hub and the inner circumferential portion of the second operating hub.

As described above, according to the embodiment of the present invention, when the operating oil pressure is supplied to the first operating piston chamber, the working oil pressure supplied to the second operating piston chamber is smoothly discharged, and when the operating oil pressure is supplied to the second operating piston chamber The operating oil pressure supplied to the first operating piston chamber is smoothly discharged, so that the alternate operation can be smoothly performed. In addition, the hydraulic operating area of the piston can be increased to lower the working oil pressure, and the housing can be easily machined, thereby reducing the production cost.

1 is a cross-sectional view of a dual clutch according to an embodiment of the present invention.
2 is a cross-sectional view of a dual clutch according to another embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

The dual clutch according to the embodiment of the present invention can be used, for example, in a double clutch transmission or a dual clutch transmission (DCT). In the dual clutch transmission, a plurality of input gears are dispersedly disposed on two input shafts, and a plurality of output gears each gear-coupled with the plurality of input gears are dispersedly disposed on two output shafts. In addition, the dual clutch transmission includes a plurality of synchronizer mechanisms, which selectively operate to couple one of the plurality of output gears and one of the two output shafts. In addition, the dual clutch is adapted to transmit the power of a power source (e.g., an engine or a motor) to any one of two output shafts. As the dual clutch, a dry or wet clutch may be used.

It should be understood, however, that the input shaft and the first and second output shafts in the present specification and claims relate to the flow of power in the context of a dual clutch. That is, the input shaft means a shaft for inputting rotational power to the dual clutch, and may be a crankshaft of the engine, a motor shaft of the drive motor, or a separate shaft connected to the motor shaft, and the output shaft means an axis outputting rotational power from the dual clutch And may be a transmission input shaft or the like.

In addition, the fact that the two members are operatively connected means that the rotational power of one member is connected to the other member, and the means such as welding, bolt, rivet, spline coupling, Means that the two members are rotatably connected together.

FIG. 1 is a cross-sectional view of a dual clutch according to an embodiment of the present invention, and FIG. 2 is a cross-sectional view of a dual clutch according to another embodiment of the present invention.

As shown in FIG. 1, the dual clutch 1 according to the embodiment of the present invention selectively transmits the rotational power of the input shaft 2 to the first output shaft 46 or the second output shaft 72, A first clutch (20), a second clutch (50), and an actuator (90). The first clutch (20), the second clutch (50) and the actuator (90) are disposed inside the transmission housing (4). The transmission housing 4 is formed in a generally cylindrical shape with a space therein and includes a transmission housing outer periphery 6 and a transmission housing rear face. As noted above, the present disclosure is described in the context of a dual clutch, meaning that the rear of the transmission housing does not refer to the rear of the actual transmission housing 4, but to the rear of the transmission housing 4 to which the dual clutch 1 is mounted. .

The input shaft 2, the first output shaft 46, and the second output shaft 72 are disposed at the center of the transmission housing 4. Any one of the first output shaft 46 and the second output shaft 72 is related to the implementation of the hole means (for example, first stage, third stage, fifth stage, seventh stage, etc.) The other one of the first output shaft 46 or the second output shaft 72 is associated with the implementation of even means (e.g., two, four, six, eight, etc.). That is, the rotational power of the input shaft 2 is selectively transmitted to the first output shaft 46 or the second output shaft 72 through the operation of the first clutch 20 or the second clutch 50, So that the shifting is performed.

The input shaft 2 is for inputting the rotational power of a power source (e.g., an engine or a motor) to the dual clutch 1 and may be a crankshaft or a motor shaft or a separate shaft connected thereto. In the present embodiment, the input shaft 2 is illustrated as an axis connected to a crankshaft or a motor shaft through a torque damper 10, but is not limited thereto.

The first output shaft 46 and the second output shaft 72 may be two input shafts of the dual clutch transmission, respectively. The second output shaft 72 is formed as a hollow shaft and the first output shaft 46 is disposed inside the second output shaft 72 without rotating interference with the second output shaft 72. The front end of the first output shaft 46 protrudes axially forward from the front end of the second output shaft 72 and extends to the end of the input shaft 2. A bearing 112 is disposed between the end of the input shaft 2 and the front end of the first output shaft 46 to facilitate relative rotation between the input shaft 2 and the first output shaft 46. A bearing 110 is disposed between the rear end of the first output shaft 46 and the rear end of the second output shaft 72 so that relative rotation between the first output shaft 46 and the second output shaft 72 is smooth . A sealing member 108 is disposed between the rear end of the first output shaft 46 and the rear end of the second output shaft 72 to the front side of the bearing 110 and the lubricating oil supplied to the double clutch leaks to the outside Prevent leaving. A spline or gear teeth are formed on the outer peripheral surface of the front end of the first output shaft 46 and a spline or gear teeth are formed on the outer peripheral surface of the front end of the second output shaft 72. However,

The local damper 10 serves to attenuate the torsional vibration of the rotational power transmitted from the crankshaft or the motor shaft. The construction of the local damper 10 is well known to those skilled in the art, and a description thereof will be omitted in this specification. The output of the local damper 10 is transmitted to the input shaft 2.

The first clutch (20) is disposed radially outward within the transmission housing (4). That is, the first clutch 20 is disposed close to the outer circumferential surface 6 of the transmission housing. The first clutch 20 selectively transmits the rotational power of the input shaft 2 to the first output shaft 42. The first clutch housing 22 includes a first disk pack 32, 34 and a first actuating hub 44.

The inner side of the first clutch housing 22 is operatively coupled to the input shaft 2 and extends radially outward to form a space in which the components constituting the first clutch 20 can be mounted. The first clutch housing 22 includes a first disc portion 24 extending in the radial direction and a second disc portion 24 formed at the outer end of the first disc portion 24 to support the first disc pack 32 in the axial direction And a first cylindrical portion 26 extending axially rearward from an outer end of the first support portion 25. The first support portion 25 includes a first support portion 25, The shape of the first clutch housing 22 can be determined by a person skilled in the art according to the design intention, and is not limited to the shape shown in this specification and the drawings.

The first disc pack 32 is disposed between the first clutch housing 22 and the first operating hub 44 to selectively transmit the rotational power of the first clutch housing 22 to the first operating hub 44 . The first disc pack 32 includes a first separate plate 28, a first friction disc 29, and a first separating spring 30. Although not limited thereto, the first separating spring 30 may be omitted if necessary.

The plurality of first separate plates 28 are spline-coupled to the inner circumferential surface of the first cylindrical portion 26.

A plurality of first friction discs 29 are splined to the outer peripheral surface of the first actuating hub 44 and disposed alternately with the plurality of first separate plates 28.

At least one first separating spring 30 is disposed between the neighboring first separate plates 28 outside the radius of the first friction disc 29 to provide an axial elastic force to the first separate plate. The first separating spring 30 maintains the interval between the first separate plates 28 when the first clutch 20 is disengaged to reduce the drag torque and smooth the disengagement of the first clutch 20 .

The first piston 34 selectively engages the first disc pack 32 to selectively transmit the rotational power of the first clutch housing 22 to the first actuating hub 44. The first piston 34 is spline-coupled to the inner circumferential surface of the first cylindrical portion 26 from the rear side of the plurality of first separate plates 28 to be movable in the axial direction. The first pressing portion 36, A connecting portion 38, a first cervical extension 40, and a first receiving portion 42.

The first pressing portion 36 is formed at the radially outer side portion of the first piston 34 at a corresponding position of the first separate plate 28. The first pressing portion 36 applies an axial force to the first separate plate 28 to frictionally couple the first separate plate 28 and the first friction disk 29 to each other.

The first connecting portion 38 is formed on the radially inner side of the first pressing portion 36 and is adapted to transmit the power of the first clutch housing 22 to the second clutch 50.

The first radial extension 40 is formed radially inward of the first connection 38 and extends to the actuator 90.

The first receiving portion 42 is formed in the radially inward portion of the first radial extension portion 40 and is adapted to receive the first release bearing 48. [

The shape of the first piston 34 can be determined by a person skilled in the art according to the design intention, and is not limited to the shape shown in this specification and the drawings.

The first operating hub 44 transmits the rotational power of the first clutch housing 22 transmitted through the first disk pack 32 to the first output shaft 46. Splines or gear teeth are formed on the inner circumferential surface of the first actuating hub 44 so that power can be transmitted by engaging with splines or gear teeth of the first output shaft 46. A bearing 118 is interposed between the radially inner side of the first operating hub 44 and the radially inner side of the first clutch housing 22 to engage the first operating hub 44 and the first clutch housing 22 Thereby supporting the first operating hub 44 in the axial direction while smoothly rotating.

The second clutch (50) is disposed radially inward of the first clutch (20) inside the transmission housing (4). The second clutch (50) is connected to the first clutch housing (22) to selectively transmit the rotational power of the first clutch housing (22) to the second output shaft (72) A first piston 52, a second disk pack 60, a second piston 62, a second actuating hub 70, and a second support 54.

The second clutch housing 52 is formed in a cylindrical shape to form a space in which the components constituting the second clutch 50 can be mounted. The second clutch housing 52 is connected to the first connecting portion 38 of the first piston 34 to receive the rotational power of the first clutch housing 22 at all times. The shape of the second clutch housing 52 can be determined by a person skilled in the art according to the design intention, and is not limited to the shape shown in this specification and the drawings.

The second disk pack 60 is disposed between the second clutch housing 52 and the second operating hub 70 to selectively transmit the rotational power of the second clutch housing 52 to the second operating hub 70 . The second disk pack 60 includes a second separate plate 56, a second friction disk 57, and a second separating spring 58. Although not limited thereto, the second separating spring 58 may be omitted if necessary.

The plurality of second separate plates 56 are spline-coupled to the outer peripheral surface of the second actuating hub 70.

The plurality of second friction discs 57 are spline-coupled to the inner circumferential surface of the second clutch housing 52 and disposed alternately with the plurality of second separate plates 56.

At least one second separating spring 58 is disposed between the adjacent second separate plates 56 radially inward of the second friction disc 57 to provide an axial elastic force to the second separate plate. The second separating spring 58 maintains the gap between the second separate plates 56 during the disengagement of the second clutch 50 to reduce the drag torque and smooth the disengagement of the second clutch 50 .

The second piston 62 selectively couples the second disk pack 60 to frictionally transfer the rotational power of the second clutch housing 52 to the second operating hub 70 selectively. The second piston 62 is spline-coupled to the inner circumferential surface of the second clutch housing 52 from the rear side of the plurality of second separate plates 56 to be movable in the axial direction. The second pressing portion 64 and the second And includes a receiving portion 66.

The second pressurizing portion 64 is formed at a radially outer side portion of the second piston 62 at a corresponding position of the second separate plate 56. The second pressing portion 64 may apply an axial force to the second separate plate 56 to frictionally couple the second separate plate 56 and the second friction disk 57 to each other.

The second receiving portion 66 is formed at the radially inner side portion of the second piston 62 and is adapted to receive the second release bearing 68. [

The shape of the second piston 62 can be determined by a person skilled in the art according to the design intention, and is not limited to the shape shown in this specification and the drawings.

The second operating hub 70 transmits the rotational power of the second clutch housing 52, which is transmitted through the second disk pack 60, to the second output shaft 72. Splines or gear teeth are formed on the inner circumferential surface of the second actuating hub 70 so that power can be transmitted by engaging with splines or gear teeth of the second output shaft 72. A bearing 116 is interposed between the radially inner side of the second actuating hub 70 and the radially inner side of the first actuating hub 44 so that the relative position of the second actuating hub 70 and the first actuating hub 44 Thereby supporting the second operating hub 70 in the axial direction while smoothly rotating.

The second support portion 54 is disposed on the front side of the outer circumferential surface of the second actuating hub 70 to support the second separate plate 56 in the axial direction. Therefore, when the second piston 62 moves to the left in the drawing, the second support portion 54 supports the second separate plate 56 so that an axial force can act.

The actuator 90 may be mounted with a fixing bolt 114 on the rear side of the transmission housing within the transmission housing 4 by providing operating force (axial force) to the first piston 34 and the second piston 62 . To this end, the fixing bolt 114 is inserted into the first clutch housing 22, the first actuating hub 44, the second actuating hub 70, the second piston 62 and the first piston 34 Tool holes 121, 122, 123, 124, and 125 are formed so as to be able to work. However, the combination of the actuator 90 and the transmission housing 4 is not limited to those described in the present specification and drawings.

The actuator 90 includes an actuator housing 132. The actuator housing 132 is formed in a thick disc shape and the actuator housing inner circumference 134 and the housing protrusion 133 outside the radius of the actuator housing inner circumference 134 protrude axially forward, , And two operating pistons (136, 150) are mounted. A step 135 having a small diameter is formed on the front side of the main housing 134 in the actuator housing.

A bearing 104 is interposed between the inner peripheral surface of the actuator housing 132 and the inner side of the second actuating hub 70 to assist in the smooth rotation of the second actuating hub 70, Direction and radial direction.

The first actuating piston 136 is for providing an axial force to the first piston 34 through the first release bearing 48 and the second actuating piston 150 is for providing axial force to the first piston 34 via the second release bearing 68. [ 2 piston 62. In this way,

The second operating piston 150 is mounted in a radial space between the actuator housing inner peripheral portion 134 and the housing projection 133 and includes a second operating piston inner peripheral portion 154 extending in the axial direction, And a second operating piston disk portion 152 extending radially outward from the rear end of the second working piston inner peripheral portion 154. [ The first operating piston 136 is mounted in a radial space between the second operating piston inner peripheral portion 154 and the housing projection 133 and is disposed on the front side in the axial direction of the second operating piston 150 do. A first actuating piston chamber 138 is formed between the first actuating piston 136, the second actuating piston inner circumference 154 and the housing protrusion 133. The second actuating piston 150 and the actuator housing And a second operating piston chamber 160 is formed between the first operating piston chamber 132 and the second operating piston chamber 160.

The first actuating piston 136 is operatively connected to the first release bearing 48 and moves axially forward by the actuating hydraulic pressure supplied to the first actuating piston chamber 138, (48). The inner circumferential surface of the first actuating piston 136 and the outer circumferential surface of the first actuating piston 136 and the inner circumferential surface of the first actuating piston 136 and between the outer circumferential surface of the first actuating piston 136 and the housing protrusion 133, Sealing members 162 and 164 may be mounted between the inner peripheral portions 154, respectively. A stopper 140 protruding radially outward is formed on the front side of the first operating piston 136. The stopper 140 is in contact with the end of the housing projection 133 so that when the operating oil pressure that has been supplied to the first operating piston chamber 138 is discharged and the first operating piston 136 moves axially rearward, Thereby restricting the axial rearward movement of the cam member 136.

The second actuating piston 150 extends axially forward through the first actuating piston 136 and is operatively connected to the second release bearing 48. Accordingly, the second operating piston 150 moves axially forward by the operating oil pressure supplied to the second operating piston chamber 160, and exerts an axial force on the second release bearing 68. Between the second operating piston inner peripheral portion 154 and the inner peripheral portion 134 of the actuator housing and between the outer peripheral end of the second operating piston circular plate portion 152 and the outer peripheral end of the second operating piston chamber 160, Sealing members 166 and 168 may be mounted between the first and second sealing members 133 and 133, respectively.

The actuator housing 132 is provided with a first supply passage 95 and a first supply hole 92 for supplying a working oil pressure to the first operating piston chamber 138, A second supply passage 96, a second supply hole 94 and a third supply passage 97 for supplying oil for lubrication and cooling to the double clutch 1 are formed. The first supply passage 95 and the first supply hole 92 are in fluid communication with the first operating piston chamber 138 and the second supply passage 96 and the second supply hole 94 are communicated with the second And is in fluid communication with the working piston chamber (160). The first, second, and third supply passages 95, 96, 97 may be located at different positions along the circumferential direction and may not communicate with each other. Accordingly, the oil supplied to the first, second and third supply passages 95, 96 and 97 can be independently controlled. On the other hand, in order to smoothly perform the alternate operation of the first and second clutches 20 and 50, the first and second supply passages 95 and 96 receive oil from one oil supply source, And the oil can be supplied by switching the flow path of the switching valve mounted on the switching valve. In this case also, the oil supplied to the third supply passage 97 can be independently controlled.

In addition, a channel connecting hole 100 and a first lubrication passage 102 are formed in the actuator housing 132. The oil passage hole 100 is in fluid communication with the third supply passage 97 and supplies oil to the space between the inner circumferential surface 134 of the actuator housing and the second output shaft 72 and the second operation hub 70 do. The supplied oil lubricates the bearing (104). A sealing member 106 is disposed between the inner circumferential surface 134 of the actuator housing 104 and the outer circumferential surface of the second output shaft 72 at the rear side of the bearing 104 to prevent the supplied oil from leaking to the outside.

The first lubricating oil passage 102 communicates with the oil passage connecting hole 100 and supplies oil to the space between the second operating hub 70 and the second piston 62. The oil supplied to the space is radially outwardly moved by centrifugal force to lubricate and cool the second clutch (50) and the first clutch (20). To this end, the first clutch housing 22, the first operating hub 44, the second clutch housing 52, and the second operating hub (corresponding to the first disk pack 32 and the second disk pack 60) 70 may be formed with a discharge passage.

The actuator 90 further includes a return spring 180 and a spring seat 170.

The return spring 180 is supported by the spring seat 170 and provides an elastic force to the first operating piston 136 against axial force by the operating hydraulic pressure supplied to the first operating piston chamber 138.

The spring seat 170 is mounted on the inner circumferential surface 134 of the actuator housing. In one embodiment, at least one mounting hole 156 is formed along the circumferential direction in the second operating piston inner peripheral portion 134, and at least one spring seat 170 is passed through the mounting hole 156 And is in contact with the stepped portion 135 formed on the inner circumferential portion 134 of the actuator housing. As a result, the spring seat 170 is restricted from moving axially rearward. In order to limit the axial movement of the spring seat 170, the spring seat 170 is in contact with the spring seat 170 so that the snap ring 172 is fixed to the inner circumferential portion 134 of the actuator housing Respectively.

On the other hand, as shown in FIG. 2, the return spring 180 may be brought into contact with the additional spring seat 192 instead of contacting the first operating piston 136. In this case, at least a part of the additional spring seat 192 is inserted into the mounting hole 156 and is movably mounted in the axial direction. The additional spring seat 192 is adapted to move in the axial direction together with the first operating piston 136 by the axial force of the first operating piston 136 and the elastic force of the return spring 180. In this case, the mounting hole 156 has a diameter capable of securing a range of movement of the additional spring seat 192 moving together with the first operating piston 136. The additional spring seat 192 is adapted to move in the axial direction together with the second operating piston 150 by the axial force of the second operating piston 150 and the elastic force of the return spring 180.

The dual clutch 1 according to the embodiment of the present invention further includes a front cover 80 for supporting the first clutch housing 22 and preventing oil supplied to the space in the double clutch 1 from leaking out do. The front cover 80 is mounted between the transmission housing 4 and the input shaft 2 on the front side of the first clutch housing 22. The outer end of the front cover 80 is mounted on the outer circumferential surface 6 of the transmission housing and is axially supported by the retaining ring 84. The inner end of the front cover 80 is mounted on the input shaft 2 do. A bearing 86 is mounted between the inner circumferential surface of the front cover 80 and the outer circumferential surface of the input shaft 2 to support the first clutch housing 22 in the axial and radial directions.

On the other hand, the oil supplied to the space between the inner circumferential surface of the actuator housing 132 and the second output shaft 72 and the second actuating hub 70 and between the second actuating hub 70 and the second piston 62 Is moved through gear teeth or splines or tool holes 121-125 or through the discharge passage to lubricate the bearings 116 and 118 and move into the space between the first clutch housing 22 and the first actuating hub 44 do. Some of this oil may be used to lubricate the bearings 112 and to exit to the oil reservoir and others to lubricate the bearings 86. A second lubricating oil passage 120 is formed at a position corresponding to the bearing 86 of the first clutch housing 22 to supply oil to the bearing 86. [ A sealing member 88 is mounted between the inner peripheral surface of the front cover 80 and the outer peripheral surface of the input shaft 2 in front of the bearing 86 so that the oil supplied to the bearing 86 does not leak . For the same reason, a sealing member 82 is mounted between the outer circumferential surface of the front cover 80 and the outer circumferential surface 6 of the transmission housing.

Hereinafter, the operation of the dual clutch according to the embodiment of the present invention will be described in detail.

The power of the crankshaft or the motor shaft is input to the input shaft 2 after the torsional vibration is attenuated through the local damper 10. At this time, since the first clutch housing 22 is operatively coupled to the input shaft 2, the first clutch housing 22 rotates together with the input shaft 2. Since the second clutch housing 52 is joined to the first connecting portion 38 of the first piston 34 and the first piston 34 is splined to the first clutch housing 22, The housing 52 also rotates together. That is, the input shaft 2, the first clutch housing 22, the first piston 34, and the second clutch housing 52 rotate together by the same rotational power.

In this state, when the operating oil pressure is supplied to the first operating piston chamber 138 through the first supply passage 95 and the first supply hole 92, the first operating piston 136 moves to the left in the drawing The first release bearing 48 is pushed to the left in the figure. At this time, the working oil pressure supplied to the first operating piston chamber 138 pushes the second operating piston 150 to the right in the figure to bring the second operating piston 150 into contact with the front surface of the actuator housing 132 2 to smoothly discharge the working hydraulic pressure supplied to the working piston chamber 160. [ In addition, the first piston 34 moves in the axial direction to the left in the drawing, and exerts an axial force on the first separate plate 28. The first separate plate 28 and the first friction disc 29 are frictionally engaged and the rotational power of the first clutch housing 22 (that is, the rotational power of the input shaft 2 Is output to the first output shaft 46. [ At this time, the second clutch housing 52 joined to the first piston 34 also moves axially to the left in the drawing, and the second piston 62 and the second friction disk 57 move in the second clutch housing 52, the second piston 62 and the second friction disk 57 do not move in the axial direction. In addition, the second separating spring 58 disposed between the adjacent second separate plates 56 maintains the interval between the second separate plates 56. Therefore, the second clutch (50) maintains the disengaged state.

When the operating oil pressure supplied to the first operating piston chamber 138 disappears in this state, the first piston 34 moves to the right in the drawing due to the elastic force of the first separating spring 30. Thus, the first clutch is released. The first actuating piston 136 is urged by the resilient force of the first separating spring 30 transmitted to the first actuating piston 136 through the first release bearing 48 and the elastic force of the return spring 180, Moves to the right in the drawing. Thus, the discharge of the working hydraulic pressure supplied to the first working piston chamber 138 is smoothly performed. At this time, the distance that the first operating piston 136 can move backward in the axial direction by the stopper 140 is limited.

At the same time, when the operating oil pressure is supplied to the second operating piston chamber 160 through the second supply passage 96 and the second supply hole 94, the second operating piston 150 moves to the left in the drawing, 2 release bearing 68 is pushed to the left in the figure. At this time, the volume of the first working piston chamber 138 is reduced, and the discharge of the working hydraulic pressure supplied to the first working piston chamber 138 is facilitated. Further, the second piston 62 moves in the axial direction to the left in the drawing, and exerts an axial force on the second separate plate 56. The second separate plate 56 and the second friction disc 57 are frictionally engaged and the rotational power of the second clutch housing 52 through the second operating hub 70 Is output to the second output shaft (72).

In this state, when the operating oil pressure supplied to the second operating portion 94 disappears, the second piston 62 moves to the right in the drawing due to the elastic force of the second separating spring 58. Thus, the second clutch is released. The second actuating piston 150 is also moved to the right in the drawing by the elastic force of the second separating spring 58 transmitted to the second actuating piston 136 through the second release bearing 68. [ Thus, the discharge of the operating hydraulic pressure supplied to the second operating piston chamber 160 is smoothly performed.

2, when the additional spring seat 192 is movably mounted in the mounting hole 156, when the second operating piston 150 moves to the left in the drawing, an additional spring seat 192 The return spring 180 is compressed and the additional spring seat 192 transfers the elastic force of the return spring 180 to the second actuating piston 150 as the second actuating piston 150 moves to the right in the figure. Accordingly, the elastic force of the return spring 180 can smoothly discharge the working oil pressure that was supplied to the second operating piston chamber 160.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, And all changes to the scope that are deemed to be valid.

Claims (19)

A first clutch for selectively transmitting the rotational power of the input shaft to the first output shaft, a second clutch for selectively transmitting the rotational power of the input shaft to the second output shaft, In order to transmit the axial force to the first piston or the second piston in the double clutch including the first piston which operates the first clutch and the second piston which selectively moves axially by the axial force and operates the second clutch In the actuator,
The actuator
An actuator housing spaced apart from each other in a radial direction and including an axially protruding inner circumference of the actuator housing and a housing protrusion, the actuator housing forming a working piston space between the inner circumference of the actuator housing and the housing protrusion;
A first actuating piston mounted in the actuating piston space and providing axial force to the first piston through a first release bearing; And
A second actuating piston mounted within said actuating piston space and providing an actuating force to said second piston through a second release bearing;
And an actuator for a dual clutch. The method according to claim 1,
The second operating piston includes a second operating piston inner periphery that is in close contact with the inner periphery of the actuator housing and extends in the axial direction and a second operating piston inner periphery extending radially outward from the rear end of the inner periphery of the second operating piston, 2 operating piston,
Wherein the inner circumferential surface of the first operating piston is in close contact with the inner circumferential surface of the second operating piston and the outer circumferential surface thereof is in close contact with the housing protruding portion. 3. The method of claim 2,
A first working piston chamber is formed between the first working piston, the second working piston inner periphery and the housing projection,
And a second actuating piston chamber is formed between the second actuating piston and the actuator housing. The method of claim 3,
A first supply passage for supplying operating oil pressure to the first operating piston chamber, a second supply passage for supplying operating oil pressure to the second operating piston chamber, 3 supply passage is formed in the second clutch. 3. The method of claim 2,
Wherein the actuator further comprises a return spring for providing an elastic force to the first operating piston,
Wherein the return spring is axially supported by at least one spring seat fixedly mounted on the inner circumference of the actuator housing. 6. The method of claim 5,
At least one mounting hole is formed in a circumferential direction in a circumference of the second operating piston, a stepped portion having a small diameter is formed in a circumference of the actuator housing,
Wherein the at least one spring seat passes through the at least one mounting hole and is mounted on the inner circumference of the actuator housing, and is axially supported by the stepped portion and the snap ring. The method according to claim 6,
The actuator further comprises an additional spring seat interposed between the return spring and the first actuating piston on the opposite side of the spring seat,
And at least a part of the additional spring seat is inserted into the mounting hole and is movably mounted in the axial direction. The method according to claim 1,
The first clutch includes a first clutch housing operatively connected to the input shaft and rotated together with the input shaft,
And the second clutch includes a second clutch housing operatively connected to the first clutch housing through the first piston and rotated together with the first clutch housing. 9. The method of claim 8,
Wherein the first piston is splined to the inner circumferential surface of the first clutch housing and the second clutch housing is joined to the first piston. 9. The method of claim 8,
Wherein the first clutch housing includes a first disk portion having an inner end coupled to the input shaft and extending radially outwardly and a first cylindrical portion extending axially rearward from an outer end of the first disk portion,
The first clutch
A plurality of first separate plates spline-coupled to the inner circumferential surface of the first cylindrical portion;
A first actuating hub operatively coupled to the first output shaft;
A plurality of first friction disks splined to an outer circumferential surface of the first actuating hub, the first friction disks being alternately disposed with the plurality of first separate plates; And
At least one first separating spring disposed between neighboring first separate plates at a radially outer side of the plurality of first friction disks;
And an actuator for a dual clutch. 11. The method of claim 10,
A first support portion for axially supporting the first separate plate is formed on the radially outer side of the first disk portion, and a second support portion for supporting the first separate plate on the outer side of the first piston for providing an axial force to the first separate plate, And the end portions are spline-coupled. 12. The method of claim 11,
The second clutch housing is joined to the first piston in the radial direction of the first clutch,
The second clutch
A plurality of second friction disks spline-coupled to an inner circumferential surface of the second clutch housing;
A second actuating hub operatively coupled to the second output shaft;
A plurality of second separate plates spline-coupled to the outer circumferential surface of the second actuating hub, the second separate plates being alternately arranged with the plurality of second friction discs; And
At least one second separating spring disposed between neighboring second separate plates at radially inner sides of the plurality of second friction disks;
And an actuator for a dual clutch. 13. The method of claim 12,
A second support portion for axially supporting the second separate plate is coupled to a front outer circumferential surface of the second operating hub and a second piston for providing axial force to the second separate plate is provided on a rear inner circumferential surface of the second clutch housing, Is splined to the outer end of the second clutch. 13. The method of claim 12,
And a front cover is mounted on the front side of the first clutch housing in the axial direction between the transmission housing and the input shaft. 15. The method of claim 14,
Wherein a sealing member and a bearing are sequentially mounted from the front side to the rear side between the inner peripheral surface of the front cover and the outer peripheral surface of the input shaft. 16. The method of claim 15,
And a second lubrication passage for supplying lubricating oil to the bearing is formed at a position of the first clutch housing corresponding to the bearing. 13. The method of claim 12,
A bearing is mounted between the inner circumferential surface of the actuator housing and the inner circumferential surface of the second actuating hub and a sealing member is formed between the inner circumferential surface of the actuator housing and the outer circumferential surface of the second output shaft, The actuator for the double clutch. 18. The method of claim 17,
And an oil passage hole for supplying lubricating oil to the bearing is formed inside the actuator housing. 13. The method of claim 12,
Wherein a bearing is disposed between the inner peripheral portion of the first clutch housing and the inner peripheral portion of the first operating hub and between the inner peripheral portion of the first operating hub and the inner peripheral portion of the second operating hub, Actuators.

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