JP2007333074A - Connection construction of fluid gearing and output member, and output member used therefor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve the problem wherein the cooling efficiency is reduced as an input side rotation element is rotated at a higher speed while controlling the slippage of a lock-up clutch device. <P>SOLUTION: Connection construction is provided with: an input side rotation element A connected by an input shaft 23; an output side rotation element B; a torque converter 10 having the lock-up clutch device C which is connected to the output side rotation element B and can be integrally connected to the input side rotation element A; and an input shaft 23 connected to the output side rotation element B of the torque converter 10, having a central oil passage 26 formed inside, and forming a cylindrical shape. The input shaft 23 comprises: a piston support 23a inserted in a hub portion 17a of the lock-up piston 17 to support this; a power transmission 23c adjoining the piston support 23a, and being connected by a turbine hub 15 of the output side rotation element B; and an oil passage 30 for cooling, having one end opened between the power transmission 23c and the piston support 23a, and having the other end communicating with the central oil passage 26. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a connection structure between a fluid transmission device and an output member, and an output member capable of realizing this connection structure.

  While a fluid transmission device such as a torque converter incorporated between the engine and the transmission can reduce the torque fluctuation of the engine and transmit it to the transmission side, a loss due to intervening fluid occurs, It has the disadvantage of causing a reduction in fuel consumption. For this reason, it is common practice to incorporate a lock-up clutch device that can integrally connect an input-side rotating element and an output-side rotating element in a fluid transmission device in a high-speed region of an engine with little torque fluctuation. . In recent years, in order to further improve the fuel efficiency and efficiency of the engine, consideration has been given to keep the lockup clutch device in a connected state as much as possible even in a region where the vibration of the engine is relatively large. From this point of view, a damper device is incorporated between the lock-up clutch device and the output-side rotating element, and further, the lock-up piston is not completely integrated with the input-side rotating element, and is pushed in a so-called half-clutch state. Slip control is performed.

  However, when performing slip control of the lockup clutch device, frictional heat is generated by sliding friction between the lockup piston and the input side rotating element. For this reason, there is a possibility that the temperature of the fluid (hereinafter referred to as hydraulic oil) intervening in the fluid transmission device will rise excessively and accelerate its deterioration. In order to solve such problems, torque with a lock-up clutch in which a through-hole for cooling is formed in the lock-up piston so as to communicate with the engagement-side oil chamber and the engagement-side oil chamber partitioned by the lock-up piston. A converter is disclosed in Patent Document 1. According to this, the hydraulic fluid intervening in the engagement side oil chamber is guided to the engagement release side oil chamber by the differential pressure between the engagement side oil chamber and the engagement release side oil chamber, and into the engagement side oil chamber. It facilitates the flow of the intervening hydraulic fluid. As a result, the cooling of the heat generating portion is promoted, and as a result, the high temperature deterioration of the hydraulic oil can be suppressed.

JP 2002-48216 A

  In the torque converter disclosed in Patent Document 1, the cooling through-hole formed in the lock-up piston is separated radially outward from the rotation axis of the torque converter, and the following problems arise. That is, during the slip control, the rotational speed of the input-side rotating element and the rotational speed of the output-side rotating element are different from each other, so that it is affected by the hydraulic oil pressure fluctuation due to the centrifugal force generated accordingly. More specifically, the hydraulic pressure of the hydraulic oil in the engagement side oil chamber (hereinafter referred to as centrifugal hydraulic pressure) generated by the centrifugal force according to the rotation speed of the output side rotation element, and the rotation of the input side rotation element Due to the pressure difference between the hydraulic oil in the disengagement side oil chamber and the centrifugal oil pressure generated by the centrifugal force according to the rotation speed between the speed and the rotation speed of the output side rotation element, cooling from the engagement side oil chamber The flow rate of the hydraulic oil flowing through the hole to the disengagement side oil chamber changes. In particular, when the rotational speed of the input side rotating element becomes higher than the rotational speed of the output side rotating element as in the case of acceleration of the vehicle, the centrifugal hydraulic pressure in the disengagement side oil chamber increases accordingly, The hydraulic pressure in the disengagement side oil chamber is relatively increased with respect to the hydraulic pressure in the engagement side oil chamber. As a result, the differential pressure between the hydraulic pressure in the engagement side oil chamber and the hydraulic pressure in the disengagement side oil chamber is reduced, and the operation flows from the engagement side oil chamber through the cooling through hole to the disengagement side oil chamber. The oil flow rate will decrease.

  Thus, in the conventional torque converter disclosed in Patent Document 1, slip control is performed in a state in which the rotational speed of the input side rotational element is higher than the rotational speed of the main force side rotational element, such as during acceleration of the vehicle. As a result, the differential pressure of the hydraulic oil in the engagement side oil chamber and the engagement release side oil chamber facing the cooling through hole is reduced, and the flow rate of the hydraulic oil passing through the cooling through hole is reduced. It may be difficult to quickly dissipate the generated frictional heat.

  Note that when the vehicle decelerates during slip control and the rotational speed of the output-side rotational element becomes higher than the rotational speed of the input-side rotational element, the centrifugal hydraulic pressure in the engagement-side oil chamber and the engagement-side oil chamber is reduced. The differential pressure increases, and the hydraulic pressure in the engagement side oil chamber becomes relatively higher than the hydraulic pressure in the engagement release side oil chamber. Therefore, it should be noted that the flow rate of the hydraulic fluid passing through the cooling through hole does not decrease as in the case of acceleration.

  An object of the present invention is to provide a connection structure between a fluid transmission device and an output member that is hardly affected by centrifugal hydraulic pressure even when slip control is performed during acceleration of a vehicle, and an output member that can realize this connection structure. It is in.

According to a first aspect of the present invention, there is provided an input-side rotating element to which an input member is connected, an output-side rotating element including a turbine hub, and the input-side rotating element connected to the output-side rotating element without a fluid. A fluid transmission device having a lockup clutch device including a lockup piston that can be integrally connected to
The fluid transmission device is connected to the output-side rotating element, and has a connecting structure with a cylindrical output member in which a fluid passage is formed,
A piston support portion formed on the output member and inserted into and supported by the hub portion of the lockup piston, and a turbine hub of the output-side rotating element formed on the output member adjacent to the piston support portion. And a second passage formed in the output member such that one end opens between the power transmission portion and the piston support portion and the other end communicates with the passage. It is characterized by comprising.

  In the present invention, the passage of the output member communicating with the disengagement side liquid chamber partitioned by the lockup piston, the gap between the turbine hub and the lockup piston constituting a part of the engagement side liquid chamber, Are communicated with each other via a second passage formed in the output member located on the innermost radial direction with respect to the rotation axis of the fluid transmission device. The hydraulic pressure of the hydraulic fluid at both open ends of the second passage is hardly affected by the centrifugal force generated by the rotation of the fluid transmission device, and the engagement side liquid chamber and the engagement side liquid chamber are not affected. In response to the differential pressure, the hydraulic fluid flows from the gap between the turbine hub and the lockup piston to the passage of the output member.

  The connection structure between the fluid transmission device and the output member according to the first aspect of the present invention may further include a seal member interposed between the output member and the turbine hub.

  A first rotating element that rotates integrally with the output-side rotating element, a second rotating element that rotates together with the lock-up piston of the lockup clutch device, and the first and second rotating elements. The damper device may further include an elastic deformation element that allows relative rotation of the first and second rotation elements and elastically deforms in accordance with the relative rotation.

  The power transmission portion of the output member and the turbine hub may be spline-fitted.

  The output member may be an input shaft of a CVT or an automatic transmission whose speed ratio is switched using hydraulic oil.

  According to a second aspect of the present invention, there is provided an input side rotating element to which an input member is connected, an output side rotating element including a turbine hub, and the input side rotating element connected to the output side rotating element without passing a fluid. A fluid output device having a lock-up clutch device including a lock-up piston that can be integrally connected to the output-side rotating element, and a fluid output passage having a cylindrical shape formed therein. A piston support portion in which a hub portion of the lockup piston is slidably fitted, a power transmission portion adjacent to the piston support portion and fitted in a turbine hub of the output side rotating element, and the power One end is opened between the transmission portion and the piston support portion, and the other end is provided with a second passage communicating with the passage.

  According to the present invention, the piston support portion inserted into and supported by the hub portion of the lockup piston is formed in the output member, and the power transmission portion to which the turbine hub of the output side rotating element is connected is adjacent to the piston support portion. The output member is formed with a second passage having one end opened between the power transmission portion and the piston support portion and the other end communicating with the passage. At both ends of the second passage, The pressure of the fluid supplied so as to urge the lock-up piston to the engagement side and the lock-up piston are disengaged almost without being affected by the centrifugal force generated by the rotation of the fluid transmission device. The fluid interposed between the power transmission portion and the piston support portion can be caused to flow from the second passage into the passage of the output member in accordance with the differential pressure with respect to the pressure of the fluid supplied to. For this reason, even if the rotational speed of the input side rotational element becomes higher than the output side rotational speed during the slip control, the frictional heat generated by the slip between the input side rotational element and the lockup piston is passed through the fluid. It can be dissipated quickly.

  When a seal member is interposed between the output member and the turbine hub, the fluid can be more reliably flowed radially inward along the lock-up piston that generates heat, and the cooling effect of the lock-up piston is enhanced. Can do.

  The first rotating element that rotates integrally with the output-side rotating element, the second rotating element that rotates integrally with the lockup piston of the lockup clutch device, and the first rotating element and the second rotating element. When the damper device further includes an elastic deformation element that allows relative rotation of the first and second rotation elements and elastically deforms in accordance with the relative rotation, the lock-up clutch device is turned on, that is, locked. In a state where the up piston is integrally connected to the input side rotating element, a sudden torque fluctuation generated in the input member can be absorbed by the damper device.

  An embodiment in which the connection structure between a fluid transmission device and an output member according to the present invention is applied to a connection portion between a vehicle torque converter and an automatic transmission will be described in detail with reference to FIG. 1 showing its cross-sectional structure (upper half). explain. However, the present invention is not limited to such an embodiment, and any change or modification included in the concept of the present invention described in the claims is possible, and any other option belonging to the spirit of the present invention is possible. Of course, it can be applied to these technologies.

  The torque converter 10 according to the present embodiment is integrally connected to the input-side rotating element A including the pump impeller 11 and the front cover 12, the turbine runner 13, and the inner peripheral end of the turbine runner 13 via a welded portion 14. A lockup clutch device C including an output-side rotating element B including a turbine hub 15, a lockup piston 17 having a friction plate 16 pressed against the front cover 12 joined to an outer peripheral end portion, and the lockup clutch device C of FIG. A damper device D is provided across the lockup piston 17 and the turbine hub 15 of the output side rotating element B.

  The pump impeller 11 described above has a blade 18 and an annular pump shell 19 having the blade 18 attached to the inside. In addition to the pump impeller 11, the input side rotating element A has a disk shape in which a pump shell 19 is joined at an outer peripheral edge portion, and a drive plate connected to a crankshaft of an engine (not shown) as an input member is screwed. The front cover 12 and an extension sleeve 20 whose outer peripheral edge is joined to the inner peripheral edge of the pump shell 19 are further included.

  The turbine runner 13 of the output side rotating element B is opposed to the pump impeller 11 and includes a blade 21 and a turbine shell 22 that holds the blade 21.

  The output-side rotating element B has a transmission (not shown) as an output member, for example, an automatic transmission (AT) using a plurality of planetary gear devices, a pair of pulleys capable of changing the groove width, and an endless coil wound around them. An input shaft 23 of a continuously variable transmission (CVT) using a belt is connected.

  The lock-up clutch device C having the lock-up piston 17 includes the hydraulic pressure of the hydraulic oil supplied to the engagement-side oil chamber 24 defined between the lock-up piston 17 and the pump shell 19, the front cover 12 and the lock. The friction plate 16 of the lock-up piston 17 is integrally pressed against the front cover 12 by controlling the hydraulic pressure of the hydraulic oil supplied to the disengagement side oil chamber 25 defined between the up-piston 17. Thus, the front cover 12 and the lockup piston 17 can be held in a directly connected state, or the front cover 12 and the friction plate 16 of the lockup piston 17 can be held in a half-clutch state. Yes. More specifically, the pressure of the hydraulic oil supplied to the engagement side oil chamber 24 from between the extension sleeve 20 and the input shaft 23 and a central oil passage 26 formed inside the cylindrical input shaft 23. Is operated using a hydraulic control device (not shown) so that the lockup piston 17 is opposed to the front cover 12, that is, the torque converter 10 It can be displaced along a direction parallel to the rotation axis 10a.

  In a region where the vehicle speed is relatively low, pressure oil is supplied to the disengagement side oil chamber 25 and the lockup piston 17 is displaced toward the turbine hub 15 side. As a result, the front cover 12 and the friction plate 16 of the lock-up piston 17 are not in contact with each other, that is, the lock-up clutch device C is not connected. As a result, the power from the input side rotating element A is transmitted to the output side rotating element B in a state where the torque is enhanced via the hydraulic oil. Normally, such a non-connected state of the lockup clutch device C is performed in a torque converter operating region where the rotation of the stator 27 described later does not occur.

  Further, in a region where the vehicle speed is relatively high, the differential pressure of the hydraulic oil loaded on both surfaces of the lockup piston 17 is operated using a hydraulic control device (not shown). As a result, the lockup piston 17 is displaced toward the front cover 12 to bring the friction plate 16 of the lockup piston 17 and the front cover 12 into close contact. As a result, the input side rotating element A and the output side rotating element B are integrally coupled via the lockup clutch device C, and the driving force of the input side rotating element A is transmitted via the lockup clutch device C and the damper device D. Is transmitted to the output side rotation element B. Normally, such a connection state of the lock-up clutch device C is also achieved in a non-functional region of the torque converter where the rotational speeds of the input side rotation element A and the output side rotation element B become substantially equal and the stator 27 starts idling. Is done.

  Further, slip control for slipping the friction plate 16 of the lockup piston 17 with respect to the front cover 12 is performed in an operation region intermediate between the non-connection operation region and the connection operation region of the lockup clutch device C described above.

  In the case of an engine with a relatively large output, a plurality of clutch plates may be incorporated between the front cover 12 and the lockup piston 17 to distribute the load on the friction plate 16. The present invention can also be applied to a fluid transmission device incorporating the lock-up clutch device having such a configuration.

  A small-diameter piston is provided at the axial end of the input shaft 23 that forms a central oil passage 26, that is, a passage for automatic transmission oil or CVT oil (hereinafter collectively referred to as hydraulic oil). A support portion 23a is formed on the outer periphery thereof. The piston support portion 23 a has a cylindrical hub portion 17 a formed at the radially inner end of the lockup piston 17 and protruding toward the front cover 12 along a direction parallel to the rotational axis 10 a of the torque converter 10. It is slidably fitted and supported. Further, a seal ring 28 for sealing a gap between the piston support portion 23a and the inner peripheral surface of the hub portion 17a of the lockup piston 17 is mounted. The presence of the seal ring 28 prevents hydraulic oil from leaking from the gap between the input shaft 23 and the lockup piston 17 to the front cover 12 side or the turbine hub 15 side, and the lockup piston 17 is controlled by hydraulic control. Responsiveness can be improved.

  A male spline 15a formed on the inner peripheral surface of the turbine hub 15 is slidably fitted and supported on the power transmission portion 23c of the input shaft 23 following the piston support portion 23a via the step portion 23b. Splines 29 are formed. In this embodiment, the female spline 15a formed on the turbine hub 15 is formed not on the entire inner peripheral surface but only on the end opposite to the lockup piston 17.

  A cooling oil passage 30 as a second passage of the present invention communicating with the central oil passage 26 of the input shaft 23 is formed at a boundary portion between the piston support portion 23 a and the step portion 23 b of the input shaft 23. The cooling oil passage 30 is for flowing hydraulic oil interposed between the turbine hub 15 and the lockup piston 17 to the central oil passage 26 side of the input shaft 23 during slip control. Needless to say, it is necessary to open 30 to a position where the opening portion is not blocked by the hub portion 17a of the lock-up piston 17. As described above, in this embodiment, during the slip control, the hydraulic oil in the engagement side oil chamber 24 is caused to flow to the engagement release side oil chamber 25 to slip between the friction plate 16 of the lockup piston 17 and the front cover 12. The cooling oil passage 30 for dissipating the heat generated along with the outside to the outside is formed on the input shaft 23 closest to the torque converter 10 rotation axis 10a. For this reason, the differential pressure of the working oil at both opening ends of the cooling oil passage 30 generated by the centrifugal force accompanying the rotation of the torque converter 10 can be reduced to an almost negligible level. The hydraulic fluid is passed through the cooling oil passage 30 in accordance with a differential pressure between the pressure of the hydraulic oil supplied to the hydraulic pressure and the pressure of the hydraulic oil supplied to the disengagement side oil chamber 25. .

  The O-ring 31 accommodated in the stepped portion 23b of the input shaft 23 is in contact with the end portion on the lockup piston 17 side of the inner peripheral surface of the turbine hub 15 where the female spline 15a is not formed. A gap between the hub 15 and the hub 15 is sealed. Due to the presence of the O-ring 31 described above, the hydraulic oil supplied from the gap between the input shaft 23 and the extension sleeve 20 into the engagement-side oil chamber 24 passes through the gap between the input shaft 23 and the turbine hub. The flow to the central oil passage 26 side through 30 is prevented. That is, the hydraulic oil in the engagement gum oil chamber 24 flows radially inward along the lockup piston 17 from the gap between the turbine hub 15 and the lockup piston 17, and from the cooling oil passage 30 to the central oil passage 26. It can be made to flow into. Thereby, the frictional heat generated with the slip between the friction plate 16 of the lockup piston 17 and the front cover 12 is efficiently propagated to the hydraulic fluid, and the torque converter 10 is cooled.

  The damper device D in the present embodiment disposed between the turbine hub 15 and the lockup piston 17 is a pair of rings that are integrally connected to the lockup piston 17 of the lockup clutch device C via a rivet 32. Drive plates 33a and 33b (hereinafter, these may be collectively referred to as 33) and a female spline 34a that is spline-fitted to a male spline 15b formed on the outer peripheral surface of the turbine hub 15. An annular driven plate 35 formed on the inner peripheral surface of the portion 34 and a plurality of coil spring units 36 disposed across the drive plate 33 and the driven plate 35 are provided. The damper device D can be displaced integrally with the lockup piston 17 along a direction parallel to the rotation axis 10a. In this case, the hub portion 34 of the driven plate 35 abuts against the turbine shell 22 opposed to the hub portion 34 so that the displacement toward the turbine shell 22 is defined. The coil spring unit 36 in the present embodiment includes a thick outer wire spring 36a having a large spring force and a thin inner wire spring 36b having a small spring force.

  The pair of drive plates 33 and the driven plate 35 arranged therebetween are formed with notches 37 and 38 for accommodating the coil spring units 36, respectively. The widths of the notches 37 and 38 along the circumferential direction substantially correspond to the free length of the outer coil spring 36a, and both end surfaces of the outer coil spring 36a are in the rotational direction of the drive plate 33 and the driven plate 35. It is in the state contact | abutted to the side end surface of each notch part 37 and 38 which faces along. In the present embodiment, consideration is given to obtain a non-linear spring characteristic by setting the free length of the inner coil spring 36b to be shorter than the free length of the outer coil spring 36a.

  The lock-up piston 17 is in a direction parallel to the rotational axis 10a of the torque converter 10 along with the drive plate 33, the driven plate 35, and the coil spring unit 36 with respect to the turbine hub 15 and the transmission input shaft 23 (left-right direction in FIG. 1). It can be displaced along. Further, power transmission between the drive plate 33 and the driven plate 35 is performed via the coil spring unit 36. That is, the torque fluctuation generated on the drive plate 33 side causes the relative rotation between the drive plate 33 and the driven plate 35. At this time, the coil spring unit 36 is compressed to absorb the sudden torque fluctuation. Yes. In this embodiment, the outer coil spring 36a is first compressed to enable relative rotation between the drive plate 16 and the driven plate 35, and the inner coil spring 36b is also compressed when a large torque fluctuation occurs. It has linear characteristics.

  A spring receiving portion 37a for preventing the coil spring unit 36 from coming off from the notch 37 is formed in the notch 37 of the drive plate 33a far from the lock-up piston 17. In this embodiment, the spring receiving portion 37a is prevented. A similar function is given to the end face of the lockup piston 17. That is, the coil spring unit 36 is sandwiched between the lock-up piston 17 and the spring receiving portion 37a of the inner drive plate 33a in a direction parallel to the rotation axis 10a of the torque converter 10.

  The torque converter 10 in this embodiment includes a stator 27 interposed between the turbine runner 13 and the pump impeller 11, a one-way clutch 39 that allows the stator 27 to rotate only in the same direction as the rotation direction of the turbine runner 13, and the like. It also has more.

  The stator 27 held on the transmission case side (not shown) via the one-way clutch 39 causes the hydraulic oil flowing into the turbine runner 13 of the output side rotating element B by the pump impeller 11 of the input side rotating element A again to the pump impeller 11 side. This causes a known torque increase.

  The one-way clutch 39 in the present embodiment is an inner ring in which a female spline 41a is formed on the inner peripheral surface to be fitted to a male spline 40a formed at the tip of a support cylinder 40 that constitutes a part of a transmission case (not shown). 41, an outer ring 43 integral with an annular holder 42 press-fitted into the inner peripheral side of the stator 27, a sprag 44 held between the inner ring 41 and the outer ring 43, and an outer peripheral edge portion connected to the holder 42. An inner ring 41, a sprag 44, a holding plate 45 that holds the outer ring 43, and the like are included. Thrust bearings 46 are respectively interposed between the turbine hub 15 and the extension sleeve 20 and the one-way clutch 33, so that the one-way clutch 39 can be rotated relative to the extension sleeve 20 and the turbine hub 15.

  Note that the one-way clutch 39 described above can employ other known structures as appropriate in addition to those using the sprags 44. In the above-described embodiment, the fluid transmission device according to the present invention is applied to the vehicle torque converter 10. However, the fluid transmission device is applied to a fluid transmission device that includes a lock-up clutch device and does not have a function of increasing drive torque. Of course it is also possible.

It is sectional drawing showing the internal structure of one Embodiment which applied the connection structure of the fluid power transmission apparatus and output member by this invention to the connection part of a torque converter for vehicles, and an automatic transmission, and the one side is made on the boundary of the rotating shaft Only the upper half is shown.

Explanation of symbols

A Input side rotating element B Output side rotating element C Lockup clutch device D Damper device 10 Torque converter 10a Rotating axis 11 Pump impeller 12 Front cover 13 Turbine runner 15 Turbine hub 15a Female spline 15b Male spline 16 Friction plate 17 Lockup piston 17a Hub part 19 Pump shell 22 Turbine shell 23 Input shaft 23a Piston support part 23b Step part 23c Power transmission part 24 Engagement side oil chamber 25 Disengagement side oil chamber 26 Central oil path 28 Seal ring 30 Cooling oil path 31 O ring 33a, 33b Drive plate 34 Hub portion 34a Female spline 35 Driven plate 36 Coil spring unit

Claims (4)

An input-side rotating element to which an input member is coupled, an output-side rotating element including a turbine hub, and a lock-up that is coupled to the output-side rotating element and can be integrally connected to the input-side rotating element without fluid. A fluid transmission device having a lock-up clutch device including a piston;
The fluid transmission device is connected to the output-side rotating element, and has a connecting structure with a cylindrical output member in which a fluid passage is formed,
A piston support part formed on the output member and inserted into and supported by the hub part of the lock-up piston;
A power transmission part formed on the output member adjacent to the piston support part, to which a turbine hub of the output side rotating element is coupled;
A fluid transmission comprising: a second passage formed in the output member so that one end opens between the power transmission portion and the piston support portion and the other end communicates with the passage. Connection structure between the device and the output member.   The connection structure between the fluid transmission device and the output member according to claim 1, further comprising a seal member interposed between the output member and the turbine hub.   The first rotating element that rotates integrally with the output-side rotating element, the second rotating element that rotates integrally with the lockup piston of the lockup clutch device, and straddling the first and second rotating elements The damper device according to claim 1, further comprising a damper device provided and having an elastic deformation element that allows relative rotation of the first and second rotation elements and elastically deforms in accordance with the relative rotation. A connection structure between the fluid transmission device according to claim 2 and an output member. An input-side rotating element to which an input member is coupled, an output-side rotating element including a turbine hub, and a lock-up that is coupled to the output-side rotating element and can be integrally connected to the input-side rotating element without fluid. A cylinder-shaped output member connected to the output-side rotating element of the fluid transmission device having a lockup clutch device including a piston and having a fluid passage formed therein;
A piston support part into which a hub part of the lock-up piston is slidably fitted;
A power transmission part adjacent to the piston support part and fitted with a turbine hub of the output side rotation element;
An output member comprising: a second passage having one end opened between the power transmission portion and the piston support portion and the other end communicating with the passage.

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