JP4274900B2 - Fluid transmission device - Google Patents

Description

  The present invention relates to a fluid transmission device that transmits rotational power between a drive shaft and a driven shaft via a fluid. More specifically, the present invention relates to a direct connection between a drive shaft and a driven shaft to increase power transmission efficiency. The present invention relates to a fluid transmission device including a lockup mechanism capable of performing the above-described operation.

  A fluid transmission device is a device that once converts rotational power input to a drive shaft into kinetic energy of a fluid, then converts it back to rotational power and transmits it to a driven shaft, and is used in a power transmission system of a rotary machine. Yes. Further, as one type of such a fluid transmission device, a torque converter is known which can perform torque amplification when transmitting power from a drive shaft to a driven shaft, and is used in a power device of an automobile. ing.

  A pump impeller is coupled to the drive shaft of the fluid transmission device via a cover member, and a turbine runner is coupled to the driven shaft via a turbine runner hub. The turbine runner is disposed in the inner space of the cover member so as to face the pump impeller. When the drive shaft rotates, the pump impeller rotates, and rotational power is transmitted from the turbine runner and the turbine runner hub to the driven shaft via the fluid. It is configured to be transmitted. In the torque converter, a stator is interposed between the pump impeller and the turbine runner, and torque is amplified by a fluid flow converting action by the stator. Here, in the vehicle torque converter, the drive shaft corresponds to the crankshaft of the engine, and the driven shaft corresponds to the input shaft of the transmission.

  Some torque converters, particularly vehicle-use torque converters, have a lock-up mechanism to perform high-efficiency power transmission by directly connecting an engine crankshaft and a transmission input shaft. Such a lock-up mechanism has a structure in which a piston member extending in the radial direction from the input shaft is pressed against the cover member, as well as a clutch mechanism friction plate provided between the cover member and the turbine runner. A structure called a plate type is known (see the following patent document). Further, in the structure having such a multi-plate clutch mechanism, when the clutch mechanism is engaged, the engine power is suddenly transmitted to the turbine runner and excessive force is input to the torque converter. In order to prevent this, a damper (buffer member) is generally interposed between the turbine runner side member constituting the clutch mechanism and the turbine runner.

In such a configuration, the damper is often composed of a plurality of coil springs, and these coil springs are integrated with a member on the turbine runner side constituting the clutch mechanism so as to be rotatable relative to the input shaft. It is attached so that it may line up in the circumferential direction on the provided damper holding plate. The outer shell of the turbine runner is provided with a protruding member that protrudes toward the damper holding plate, and the protruding member compresses each coil spring when relative rotation occurs between the damper holding plate and the turbine runner. Thus, a buffering force can be obtained.
JP 2001-116110 A JP 2002-195376 A

  However, when the thickness of the damper holding plate to which the coil spring is attached is small and the rigidity thereof is insufficient, the damping performance of the coil spring is not sufficiently exhibited, and as a result, the predetermined lockup performance of the fluid transmission device is obtained. There is a risk of disappearing. In order to avoid such a situation, a support plate extending in the radial direction is provided on the input shaft, and this is brought into contact with one surface side of the damper holding plate, and this is supported so as to prevent the damper holding plate from falling down. However, in such a configuration, the dimension of the torque converter in the axial direction is increased, and the cost is increased because it is necessary to precisely process the contact surface between the support plate and the damper holding plate. In addition, when the uniform contact pressure cannot be obtained over the entire contact surface, the damper cannot exhibit sufficient damping performance.

  The present invention has been made in view of such problems, and ensures sufficient damper damping performance by ensuring sufficient rigidity of the damper holding plate while suppressing an increase in axial dimension. An object of the present invention is to provide a fluid transmission device having a configuration capable of satisfying the requirements.

  The fluid transmission apparatus according to the present invention includes a drive shaft (for example, the crankshaft 10 of the engine in the embodiment) and a driven shaft (for example, the transmission of the transmission in the embodiment) disposed so that the central axis is located on the same axis. 1 is a fluid transmission device (for example, the vehicle torque converter 1 in the embodiment) that is provided between the input shafts 20 and transmits power from the drive shaft to the driven shaft, and is coupled to the drive shaft via a cover member. A pump impeller, a turbine runner coupled to a hub member (for example, the turbine runner hub 33 in the embodiment) fixed to the driven shaft, and provided opposite to the pump impeller in the internal space of the cover member; The first and second ring-shaped members (for example, actual parts) that are attached to the hub member and face the axial direction of the driven shaft A first ring-shaped member 38 and a second ring-shaped member 39), and a guide groove formed on the outer periphery of the ring-shaped member by opening both ring-shaped members facing each other. A damper holding plate having a circumferential surface held slidably movable in a circumferential direction by a guide groove of the holder, a cover side clutch member connected to the cover member, and a damper side clutch member connected to the damper holding plate. A clutch mechanism that engages and releases the cover-side clutch member and the damper-side clutch member by actuating a piston member (for example, the clutch piston 53 in the embodiment) by the hydraulic pressure in the working hydraulic pressure chamber provided between the plate and the plate. And the cover portion when the clutch mechanism is engaged between the damper holding plate and the turbine runner. Between the first and second ring members and the outer peripheral edges of the first and second ring-shaped members constituting the holder are located radially inward of the cover-side clutch member. Yes.

In the first and second ring-shaped members, a plurality of extending portions formed so as to extend from the inner peripheral portion toward the center are alternately arranged in a circumferential direction on a plane perpendicular to the driven shaft. In this state, the hub member is coupled to the hub member .

In this fluid transmission device, the inner peripheral portion of the damper holding plate is bent so as to protrude toward the damper-side clutch member to form a holder accommodating space therein, and the first and It is preferable that the second ring-shaped member positioned on the turbine runner side is positioned so as to be accommodated in the holder accommodating space. Furthermore, it is preferable that a plate member is interposed between the inner wall of the guide groove and the damper holding plate.

  In the fluid transmission device according to the present invention, the holder that holds the inner peripheral surface of the damper holding plate so as to be freely slidable in the circumferential direction in the guide groove of the outer peripheral portion has its outer peripheral edge (the outer peripheral edge of the first ring-shaped member and the first peripheral member). 2 is provided so that the outer peripheral edge of the ring-shaped member 2 is located radially inward of the cover-side clutch member, and thus the distance between the cover-side clutch member and the outer shell of the turbine runner generated thereby. The rigidity of the damper holding plate can be increased by increasing the thickness of the damper holding plate. Therefore, it is possible to ensure sufficient rigidity of the damper holding plate while suppressing an increase in the axial dimension of the fluid transmission device. In such a configuration, the contact surface between the inner wall of the guide groove to be machined with high accuracy and the damper holding plate is extremely small, so that the number of machining steps can be reduced and the manufacturing cost can be reduced. In addition, since the contact area between the guide groove and the damper holding plate is small, the frictional force between the holder and the damper holding plate is stabilized, so that the damping performance of the damper can be fully exhibited and the service life Can also be improved.

Further , the first and second ring-shaped members are alternately arranged in a circumferential direction on a plane perpendicular to the driven shaft, with a plurality of extending portions formed by extending from the respective inner peripheral portions toward the center side. because it has a structure that is coupled to the hub member in a state of being, since the two ring-shaped member so that the fixed directly to the hub member, respectively, the first and second ring-shaped member together the hub member It becomes possible to position accurately with reference to. This also facilitates positioning of the damper holding plate, so that not only the assembly process can be simplified, but also the damper's damping performance can be exhibited sufficiently.

In the above-described fluid transmission device, the inner peripheral portion of the damper holding plate is bent so as to protrude toward the damper-side clutch member, and a holder accommodating space is formed in the inside thereof. If the two ring-shaped members positioned on the turbine runner side are positioned so as to be accommodated in the holder accommodating space, the axial dimension of the fluid transmission device can be shortened. . In addition, if a plate member is interposed between the inner wall of the guide groove and the damper holding plate, sliding wear due to the influence of torque fluctuation between the damper holding plate and the holder during the lock-up operation is prevented. It is possible to reduce.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. 1 and 2 show a vehicle torque converter (hereinafter simply referred to as a torque converter) 1 which is an embodiment of a fluid transmission device according to the present invention. The torque converter 1 is provided between a crankshaft 10 of an engine (not shown) and an input shaft 20 of a transmission (not shown), and is a fluid transmission device that transmits power from the crankshaft 10 to the input shaft 20. A cover member (torque converter cover) 30 coupled to the crankshaft 10, a pump impeller 31 coupled to the cover member 30 and rotating integrally with the crankshaft 10 and the cover member 30, A turbine runner 32 coupled to a turbine runner hub 33 that is spline-fitted to the outer periphery of the input shaft 20 is provided. The turbine runner 32 is provided in the interior space of the cover member 30 so as to face the pump impeller 31, and fluid (here, oil, generally referred to as fluid) is contained in the space surrounded by the pump impeller 31 and the turbine runner 32. Is satisfied. A hollow cylindrical stator shaft 34 fixed to a transmission case (not shown) is provided on the outer peripheral side of the input shaft 20, and the stator 36 is disposed on the outer peripheral surface of the stator shaft 34 via a one-way clutch 35. It is attached.

  The center axis of the crankshaft 10 and the center axis of the input shaft 20 are arranged on the same axis AX, and the center axis of the stator shaft 34 is also arranged on this axis AX. Further, the turbine runner hub 33 has two ring-shaped members (a first ring-shaped member 38 and a second ring-shaped member 39) whose inner peripheral portion is attached to the turbine runner hub 33 and faces the axial direction of the input shaft 20. The holder 37 which consists of is attached. On the outer periphery of the holder 37, there is formed a guide groove 37a that is formed by facing the first ring-shaped member 38 and the second ring-shaped member 39 and opens outward in the radial direction. 37a holds a disk-shaped damper holding plate 41 whose center axis coincides with the axis AX so as to be slidable in the circumferential direction (for this reason, the damper holding plate 41 is fixed to the input shaft 20 and the turbine runner 32). Relative rotation). A ring-shaped sliding member 42 is attached to the inner peripheral portion of the damper holding plate 41 by welding or the like, and the sliding member 42 is supported in the guide groove 37a. Further, as shown in FIG. 1, a thin disk-shaped plate member (thrust washer) is provided between the inner wall of the holder 37 (specifically, the inner wall of the first ring-shaped member 37) and the damper holding plate 41 and the sliding member 42. ) 43 is interposed. The plate member 43 is preferably made of a metal (for example, white metal) that is hard enough to withstand wear, has a small coefficient of friction, and has good thermal conductivity.

  FIG. 3A is a view showing a state in which the holder 37 is combined with the turbine runner hub 33, and FIG. 3B is an exploded view thereof. As described above, the holder 37 is composed of the first ring-shaped member 38 and the second ring-shaped member 39 that are disposed to face each other in the axial direction of the input shaft 20. The first ring-shaped member 38 is disposed on the turbine runner 32 side. The second ring-shaped member 39 is provided on the engine side. Each of the first ring-shaped member 38 and the second ring-shaped member 39 has extended portions 38a and 39a provided extending from the inner peripheral portion toward the center, and these extended portions 38a and 39a are respectively provided. It is attached to the outer periphery of the turbine runner hub 33. Specifically, the extending portion 38a of the first ring-shaped member 38 is riveted at a position where the rivet hole 38b provided in the extending portion 38a and the rivet hole 33a provided in the turbine runner hub 33 match. Thus, the extended portion 39a of the second ring-shaped member 39 is attached to the turbine runner hub 33. The extended portion 39a includes a rivet hole 39b provided in the extended portion 39a and a rivet hole 33a provided in the turbine runner hub 33. Are attached to the turbine runner hub 33 by being riveted at a position where they match. As described above, in the torque converter 12, the plurality of extending portions 38 a included in the first ring-shaped member 38 and the plurality of extending portions 39 a included in the second ring-shaped member 39 are arranged on a plane perpendicular to the input shaft 20. The turbine runner hub 33 is coupled to the turbine runner hub 33 while being alternately arranged in the circumferential direction.

  A multi-plate clutch mechanism 50 is provided between the cover member 30 and the damper holding plate 41. The clutch mechanism 50 includes a cover-side clutch member 51 connected to the cover member 30 and a damper-side clutch member 52 connected to the damper holding plate 41. Between the cover member 30 and the damper holding plate 41 (more Specifically, the clutch piston 53 is actuated by the hydraulic pressure in the hydraulic pressure chamber 55 provided between the cover member 30 and the clutch piston 53 described below to engage the cover side clutch member 51 and the damper side clutch member 52. And the cancellation thereof.

  Here, the cover-side clutch member 51 includes a cylindrical clutch drum 51a fixed to the cover member 30, and a plurality of cover-side clutch plates 51b whose outer ends are fixed to the inner peripheral side of the clutch drum 51a. The damper-side clutch member 52 includes a cylindrical clutch hub 52a formed integrally with the damper holding plate 41, and a plurality of damper-side members whose inner ends are fixed to the outer peripheral side of the clutch hub 52a. It consists of a clutch plate 52b. The clutch piston 53 is provided on the outer peripheral surface of the input shaft 20 so as to be movable in the direction in which the axis AX extends, and is always shown in FIG. 1 (or FIG. 2) by a return spring 54 (not shown in FIG. 1, see FIG. 2). ) Is biased to the right. The clutch hub 52a is fixed to the above-described sliding member 42 attached to the inner peripheral portion of the damper holding plate 41 by welding or the like. Even when the return spring 54 is not provided, the clutch piston 53 is operated to the lock-up release side (right side in FIG. 1 or 2) without any practical problem by using only the hydraulic pressure (pressure in the torque converter 1). It is possible. The use of such a configuration is advantageous in terms of cost reduction and layout. However, when it is necessary to release the lockup at an earlier stage in terms of the function of the vehicle, it is preferable to install the return spring 54 as in the present embodiment.

  Here, as can be seen from FIG. 1, the outer peripheral edge of the holder 37 (the outer peripheral edge of the first ring-shaped member 38 and the outer peripheral edge of the second ring-shaped member 39) is more radially inward than the cover-side clutch member 51. positioned. Similarly, as shown in FIG. 1, the inner peripheral portion of the damper holding plate 41 is bent so as to protrude toward the damper-side clutch member 52 (rightward in FIG. 1), and a holder accommodating space 41a is formed inside thereof. Of the two ring-shaped members 38, 39, the one positioned on the turbine runner 32 side (first ring-shaped member 38) is positioned so as to be accommodated in the holder accommodating space 41a.

  Each of the cover-side clutch plate 51b and the damper-side clutch plate 52b has a structure in which a friction material is bonded to a metal plate, and the clutch plates 51b and 52b are provided so as to be alternately and parallel to the extending direction of the axis AX. It has been. Therefore, when the clutch piston 53 moves to the left in FIG. 1 (or FIG. 2) and the adjacent ones of these clutch plates 51b, 52b are pressed against each other, both clutch plates 51b, 52b Are engaged (coupled) with each other, and when the clutch piston 53 moves to the right in FIG. 1 (or FIG. 2) from this state, the engagement of both clutch plates 51b and 52b is released.

  A plurality of dampers 44 made of coil springs are provided between the damper holding plate 41 and the turbine runner 32, and both ends of the dampers 44 are held by the damper holding plate 41 and centered on the axis AX. Are arranged side by side in the circumferential direction. The outer shell 32a of the turbine runner 32 is provided with a projecting member 45 projecting and extending toward the damper holding plate 41. When the relative rotation occurs between the damper holding plate 41 and the turbine runner 42, the projecting member 45 is provided. However, a compression force is obtained by compressing each of the dampers 44, so that the power of the engine can be prevented from being transmitted to the turbine runner 32 abruptly.

  An oil passage 56 (see FIG. 2) configured to include an oil passage 56 a is connected to the above-described hydraulic pressure chamber 55 formed between the cover member 30 and the clutch piston 53. The oil passage 56 is connected to the outer shell 31a of the pump impeller 31 and extends to the outer peripheral surface side of the stator shaft 34, and a gear 47 (see FIG. 1) attached to the pump drive shaft 46. Is connected to the discharge port of the hydraulic pump P that is driven by (not shown in FIG. 2). Further, as shown in FIG. 2, a control valve 57 is interposed in the oil passage 56, and its spool (not shown) is operated in response to a control signal from a controller (not shown).

  As shown in FIG. 2, the control valve 57 is a two-position three-port valve. When the spool is positioned at the neutral position 57a, the pressure oil supplied from the hydraulic pump P is blocked by the spool and the operating hydraulic chamber 55 Since the inside hydraulic oil is connected to the oil tank T via the oil passage 56, the clutch piston 53 is located at a position moved rightward in FIG. 2 by the urging force of the return spring 54. At this time, since the adjacent ones of the cover side clutch plate 51b and the damper side clutch plate 52b are separated from each other, the clutch drum 51 and the clutch hub 52 are in a power non-transmission state. At this time, engine power is transmitted in the order of the crankshaft 10 → the cover member 30 → the pump impeller 31 → the turbine runner 32 → the turbine runner hub 33 → the input shaft 20. Here, power transmission between the pump impeller 31 and the turbine runner 32 is performed via a fluid. When the vehicle speed is relatively low, the flow of fluid between the pump impeller 31 and the turbine runner 32 is changed by the stator 36 to amplify the torque. It should be noted that the spool of the control valve 57 is thus positioned at the neutral position 57a and the clutch mechanism 50 is disengaged (disengaged) when the vehicle is idling, starting the vehicle, or the like.

  On the other hand, when the spool of the control valve 57 is located at the drive position 57 b, the pressure oil from the hydraulic pump P is supplied from the oil passage 56 into the hydraulic pressure chamber 55, and the clutch piston 53 receives the urging force of the return spring 54. Accordingly, the turbine runner hub 33 moves to the left in FIG. As a result, adjacent ones of the cover side clutch plate 51b and the damper side clutch plate 52b are pressed against each other so that the clutch drum 51 and the clutch hub 52 are coupled, and the damper holding plate 41 is connected to the cover member 30 via the clutch mechanism 50. It becomes the state connected with. At this time, the power of the engine is transmitted in the order of the crankshaft 10 → the cover member 30 → the clutch mechanism 50 → the damper holding plate 41 → the damper 44 → the turbine runner 32 → the turbine runner hub 33 → the input shaft 20. That is, the crankshaft 10 and the input shaft 20 are directly connected (so-called lock-up state). In such a lock-up state, no fluid is interposed in the power transmission between the crankshaft 10 and the input shaft 20, so that no torque amplification effect occurs, but there is little power loss due to fluid friction, etc. Become.

  It is to be noted that the clutch mechanism 50 is engaged in this way so that the crankshaft 10 and the input shaft 20 are directly connected (that is, the spool of the control valve 57 is moved from the neutral position 57a to the drive position 57b). Although it is a controller, the timing is determined based on outputs from a vehicle speed sensor and a throttle opening sensor (both not shown). In a vehicle equipped with the torque converter 1 according to the present embodiment, the torque amplifying function of the torque converter 1 is actively used only at an extremely low speed such as when starting, and lock-up is performed from a relatively low speed. Fuel efficient driving is performed.

  The description of the torque converter 1 is as described above. In the present torque converter 1, as described above, the holder 37 that holds the inner peripheral surface of the damper holding plate 41 in the guide groove 37a on the outer peripheral portion is slidably movable in the circumferential direction. The outer peripheral edge (the outer peripheral edge of the first ring-shaped member 38 and the outer peripheral edge of the second ring-shaped member 39) is provided so as to be located radially inward of the cover-side clutch member 51. The rigidity of the damper holding plate 41 can be increased by increasing the distance between the cover-side clutch member 51 and the outer shell 32a of the turbine runner 32. Therefore, it is possible to ensure sufficient rigidity of the damper holding plate 41 while suppressing an increase in the axial dimension of the torque converter 1. Further, in such a configuration, the contact surface between the inner wall of the guide groove 37a (the inner wall of the first ring-shaped member 37) to be machined with high accuracy and the damper holding plate 41 becomes extremely small. The manufacturing cost can be reduced by reducing the number. Further, since the contact area between the guide groove 37a and the damper holding plate 41 is small, the frictional force between the holder 37 and the damper holding plate 41 is stabilized, so that the damping performance of the damper 44 can be sufficiently exhibited. In addition, the service life can be improved.

  In the torque converter 1, the holder 37 has a configuration in which two ring-shaped members (a first ring-shaped member 38 and a second ring-shaped member 39) are disposed to face each other in the axial direction of the input shaft 20. These two ring-shaped members 38 and 39 are alternately extended in the circumferential direction on the surface perpendicular to the input shaft 20 by extending portions 38a and 39a formed extending from the respective inner peripheral portions toward the center side. It is connected to the turbine runner hub 33 in an aligned state. For this reason, since the two ring-shaped members 38 and 39 are directly fixed to the turbine runner hub 33, both the ring-shaped members 38 and 39 can be accurately positioned with reference to the turbine runner hub 33. is there. This also facilitates the positioning of the damper holding plate 41, so that not only the assembly process can be simplified, but also the damping performance of the damper 44 can be exhibited sufficiently.

  Further, in the torque converter 1, the inner periphery of the damper holding plate 41 is bent so as to protrude toward the damper-side clutch member 52, and the holder accommodating space 41 a is formed in the inside thereof. Of the two ring-shaped members 38, 39, the one positioned on the turbine runner 32 side (first ring-shaped member 38) is positioned so as to be accommodated in the holder accommodating space 41a. It is also possible to shorten the axial dimension. Further, as described above, since the plate member 43 made of a hard material is interposed between the inner wall of the guide groove 37a formed on the outer peripheral portion of the holder 37 and the damper holding plate 41, the lock-up operation is performed. It is possible to reduce sliding wear due to the influence of torque fluctuation between the damper holding plate 41 and the holder 37.

  The preferred embodiments of the present invention have been described so far, but the scope of the present invention is not limited to those shown in the above-described embodiments. For example, in the above-described embodiment, the holder 37 is configured to support the ring-shaped sliding member 42 joined to both the damper holding plate 41 and the clutch hub 52a in the guide groove 37a provided on the outer periphery thereof. However, at least the inner peripheral surface of the damper holding plate 41 may be configured to be slidably movable, and the sliding member 42 is not necessarily attached to the damper holding plate 41 as shown in the above-described embodiment. Is not what you need.

  Moreover, in the above-mentioned embodiment, although the fluid transmission device which concerns on this invention showed the example applied to the torque converter which has a stator in addition to a pump impeller and a turbine runner, the application object of this invention does not have a stator. It may be a fluid transmission device, that is, a fluid coupling device. When the present invention is applied to a fluid coupling device that does not have a stator in this way, the axial direction of the power transmission shaft (in the above example) is equivalent to the absence of a stator between the pump impeller and the turbine runner. For example, there is an advantage that the dimension in the direction in which the axis AX extends is smaller. Moreover, although the case where the fluid transmission device according to the present invention is used for a vehicle is shown in the above-described embodiment, this is an example, and it is needless to say that the present invention can be applied to other rotating machines other than the vehicle. .

It is a section (upper half section) figure of a torque converter concerning one embodiment of the present invention. It is a skeleton figure which shows the structure of the said torque converter. It is a figure which shows the structure of the turbine runner hub and holder which comprise the said torque converter, (A) is a figure which shows the state which combined both, (B) is the exploded view.

Explanation of symbols

1 Vehicle torque converter (fluid transmission)
10 Crankshaft (drive shaft)
20 Input shaft (driven shaft)
30 Cover member 31 Pump impeller 32 Turbine runner 33 Turbine runner hub (hub member)
37 holder 37a guide groove 38 first ring-shaped member (first ring-shaped member)
38a Extension part (extension part)
39 Second ring-shaped member (second ring-shaped member)
39a Extension part (extension part)
41 damper holding plate 41a holder housing space 44 damper 50 clutch mechanism 51 cover side clutch member 52 damper side clutch member 53 clutch piston (piston member)
55 Hydraulic chamber AX Central axis

Claims (3)

A fluid transmission device that is provided between a drive shaft and a driven shaft that are arranged so as to face each other so that a central axis is located on the same axis, and that transmits power from the drive shaft to the driven shaft,
A pump impeller coupled to the drive shaft via a cover member;
A turbine runner coupled to a hub member fixed to the driven shaft and provided facing the pump impeller in an internal space of the cover member;
An inner peripheral portion is formed of first and second ring-shaped members that are attached to the hub member and face each other in the axial direction of the driven shaft, and outward in the radial direction formed by the two ring-shaped members facing each other. A holder having an open guide groove on the outer periphery;
A damper holding plate having an inner circumferential surface held slidably movable in the circumferential direction by the guide groove of the holder;
A cover-side clutch member connected to the cover member and a damper-side clutch member connected to the damper holding plate are provided, and the piston member is operated by hydraulic pressure in an operating hydraulic pressure chamber provided between the cover member and the damper holding plate. A clutch mechanism for engaging and releasing the cover-side clutch member and the damper-side clutch member;
A damper that is interposed between the damper holding plate and the turbine runner and exhibits a buffering force between the cover member and the turbine runner when the clutch mechanism is engaged;
The outer peripheral edges of the first and second ring-shaped members constituting the holder are located radially inward from the cover-side clutch member , and
In the first and second ring-shaped members, a plurality of extending portions formed to extend from the inner peripheral portions toward the center are alternately arranged in a circumferential direction on a plane perpendicular to the driven shaft. a fluid transmission device characterized in that it possess the combined structure to the hub member in a state. An inner peripheral portion of the damper holding plate is bent so as to protrude toward the damper side clutch member to form a holder accommodating space inside thereof, and the first and second ring shapes constituting the holder 2. The fluid transmission device according to claim 1, wherein a member positioned on the turbine runner side is positioned so as to be accommodated in the holder accommodating space. Hydraulic power transmission device according to claim 1 or 2 plate member is characterized in that it is interposed between the inner wall and the damper retaining plate of the guide groove.

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