JP2007255636A - Torque converter device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque converter device wherein a rivet joining an output member of a lockup clutch to a clutch side input member of a damper has one end extending to form a rivet extension portion which is made to abut on a fluid joint side input member via oblong holes formed in the output member for supporting the axial load of the lockup clutch and which is used as a restricting means for restricting relation rotation between the input member and the output member, while solving problems wherein a radial layout is limited when the outside dimension of the rivet extension portion is larger and spaces between adjacent oblong holes are smaller producing insufficient strength when the number of the rivets is increased. <P>SOLUTION: A plurality of protruded portions 12d protruded toward a fluid joint 3 in the axial direction are formed on the inner periphery side of the clutch side input member 12 at approximately equal spaces along the circumferential direction, while oblong holes 14b are formed in the output member 14 at positions corresponding to the protruded portions 12d along a circular arc with the axial center of the output member 14 as a center. The protruded portions 12d are inserted through the oblong holes 14b so that their front ends can abut on a turbine hub 21. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a torque converter device used as a torque converter for an automatic transmission.

  As a conventional torque converter device, for example, the one described in Patent Document 1 is known. This torque converter device is a component member of a built-in damper, and a left clutch-side input member of a pair of input members that are rivet-coupled to each other at the outer peripheral portion is a rivet to an output member of a multi-plate lockup clutch. On the other hand, the right fluid coupling side input member is coupled to a turbine which is an output member of the fluid coupling. An output member disposed between the clutch-side input member and the fluid coupling-side input member in the axial direction is coupled to an output hub disposed at the axial center of the output member, and the output hub is disposed on the inner peripheral surface thereof. It is connected to an input shaft of a transmission (not shown) through the formed spline teeth.

  In order to support the axial load from the lockup clutch by the fluid coupling side input member or the turbine while allowing relative rotation between the pair of input members and the single output member, some of the rivets One end of the rivet is formed to form a rivet extension, while the output member is formed with an arc-shaped elongated hole, and the rivet extension is inserted into the elongated hole so that the tip of the rivet is brought into contact with the fluid coupling side input member. ing.

As the rivet extension moves within the slot, the pair of input members and the single output member rotate relative to each other to maintain the function of reducing torsional vibration. When a load is applied, the load is supported by the fluid coupling side input member and the turbine via the rivet extension, and the rivet extension functions as a support means for the axial load.
German Patent Application Publication No. DE 10 204 029 157 A1

  However, the rivet extension portion as the support means and the long hole for allowing the rivet extension portion to move in the circumferential direction are formed by a pair of input members constituting the damper and a single output member. It is difficult to use as a restricting means for restricting relative rotation.

  The reason for this is that, for example, it is necessary to increase the overall dimensions of the rivet or increase the number of rivet extensions so that the strength is sufficient when receiving a large torque from the turbine. This is because the radial layout of the torque converter device is limited, and if the number of rivet extensions is increased, the distance between the long holes adjacent in the circumferential direction is reduced and the strength necessary for torque transmission cannot be obtained. is there.

  That is, it is difficult to use as a restricting means for restricting relative rotation, and a restricting means for restricting relative rotation must be provided separately.

  Accordingly, the present invention provides a torque converter device that solves the above-described problems and functions not only as a support means for supporting the clutch-side input member in the axial direction but also as a restriction means for restricting relative rotation. Objective.

  According to the first aspect of the present invention, a lockup clutch connected to a crankshaft of an engine is connected to a transmission via a damper, and a fluid coupling connected to the crankshaft is connected to the transmission directly or via the damper. The damper is connected, the input member connected to only the lockup clutch or both the lockup clutch and the fluid coupling, the output member connected to the transmission, and the input member and the output in the rotational direction. A torque converter device including an elastic member interposed between the member and the clutch-side input member connected to the lock-up clutch, and a protruding portion protruding in the axial direction is formed along the circumferential direction; A restriction frame into which the protruding portion is fitted is centered on the output member and the shaft center of the output member. Formed along the arc, characterized in that the tip of the projecting portion and the contactable to a member to rotate together with the clutch side input member.

  According to the present invention, when the vehicle starts, the torque of the engine is transmitted to the damper and further to the transmission through the fluid coupling, and the lockup clutch is connected to the damper and further to the damper directly without passing through the fluid coupling when the vehicle travels constant. Is transmitted to the transmission.

  When the lockup clutch is engaged or when operating under slip control, an axial load may be generated on the output member of the lockup clutch, and this load is transmitted to the clutch side input member and functions as a support means. It is supported by a member that rotates together with the clutch-side input member via the protrusion.

  When the vehicle starts, the difference in rotational speed between the crankshaft and the turbine, which is the output member of the fluid coupling, is large. Therefore, the torque amplification function of the stator that constitutes the fluid coupling works, and a torque larger than the torque from the crankshaft Although it is input, the end face of the protrusion comes into contact with the end wall surface of the restriction frame, and the protrusion and the restriction frame function as restriction means for restricting relative rotation of the input member with respect to the output member.

  The invention according to claim 2 is the torque converter device according to claim 1, wherein the input member is integrally coupled to the clutch side input member, the clutch side input member, and is coupled to the fluid coupling. A fluid coupling side input member is formed, and a long hole is formed as the restriction frame, and a tip of the protruding portion inserted through the long hole can contact the fluid coupling side input member. .

  According to this invention, the member that supports the clutch-side input member in the axial direction is the fluid coupling-side input member, and the member that restricts the protruding portion of the clutch-side input member in the circumferential direction is the output member. Further, since there is no relative rotation between the clutch side input member and the fluid coupling side input member, friction (hysteresis) is generated between them at the contact portion between the tip of the protrusion and the fluid coupling side input member. Absent.

  According to a third aspect of the present invention, in the torque converter device according to the first aspect, the input member is constituted only by the clutch-side input member, the fluid coupling is directly connected to the output member, and the restriction frame And a tip of the projecting portion loosely fitted in the groove can be brought into contact with the bottom surface of the groove.

  According to this invention, both the member that supports the clutch-side input member in the axial direction and the member that restricts the protruding portion of the clutch-side input member in the circumferential direction are output members.

  According to a fourth aspect of the present invention, in the torque converter device according to any one of the first to third aspects, the circumferential width dimension of the protrusion is set larger than the radial thickness of the protrusion. It is characterized by being.

  According to the present invention, since the circumferential width dimension of the projecting portion fitted into the restriction frame is larger than the radial plate thickness dimension, a predetermined torque is provided between the clutch-side input member and the output member of the damper. Even if the above torque acts and a large bending force acts on the protruding portion, it has sufficient bending strength and is difficult to deform.

  According to a fifth aspect of the present invention, in the torque converter device according to any one of the first to fourth aspects, a clearance dimension between the end surface of the protrusion and the end wall surface of the restriction frame in the neutral state of the damper is on the coast side. It is characterized by being set smaller than the drive side.

  According to the present invention, the clearance dimension between the projecting portion end surface and the end wall surface of the restricting frame is smaller on the coast side than on the drive side, and accordingly, the portion of the portion between the restricting frame and the restricting frame of the output member. The cross-sectional area can be increased in the circumferential direction, and high torque torsional characteristics can be accommodated.

  According to a sixth aspect of the present invention, in the torque converter device according to any one of the first to fifth aspects, the radial positions of the projecting portion and the restriction frame are determined by the turbine constituting the fluid coupling and the turbine. It is characterized in that it corresponds to the position in the radial direction of a thrust bearing arranged between adjacent stators.

  According to the present invention, since the radial position of the projecting portion and the restriction frame is made to correspond to the position of the thrust bearing, the axial load generated in the output member of the lockup clutch is affected by the clutch-side input member and the projecting portion thereof. It is supported by the thrust bearing through.

  According to the torque converter device of the present invention, the clutch-side input member constituting the damper is formed with the protruding portion that protrudes in the axial direction, the restriction frame into which the protruding portion is fitted is formed on the output member, and the protruding portion Since the front end of the clutch can be brought into contact with a member that rotates together with the clutch-side input member, not only as a support means for supporting the clutch-side input member in the axial direction, but also the relative rotation of the input member with respect to the output member is restricted. It also functions as a regulation means.

  Moreover, since the protrusion is formed integrally with the clutch-side input member, it can be provided without increasing the number of parts compared to the conventional configuration.

Embodiments of a torque converter device according to the present invention will be described below.
(A) Embodiment 1
First, the first embodiment is shown in FIG.

  An engine crankshaft (not shown) is arranged on the left side in the drawing, and a transmission (not shown) is arranged on the right side. A front cover 1 is coupled to the right end surface of the crankshaft. That is, the front cover 1 is centered directly on the end surface of the crankshaft, and the outer peripheral portion is coupled to the crankshaft via a disk-shaped drive plate (not shown). The front cover 1 has a long outer periphery extending toward the transmission side opposite to the crankshaft, and a lockup clutch 2 is connected to the left side of the front cover 1. On the other hand, a fluid coupling 3 is connected to the right side of the front cover 1. A damper 4 is disposed between the lock-up clutch 2 and the fluid coupling 3, and the damper 4 is connected to the transmission.

  The lock-up clutch 2 includes an input-side spline 5 coupled to the front cover 1, an output-side spline 6 disposed inside the input-side spline 5, and an input-side spline 5 and an output-side spline 6. A plurality of ring-shaped friction plates 7a and 7b arranged between teeth and arranged alternately, and a piston 8 that presses the friction plates 7a and 7b against each other.

  The fluid coupling 3 is disposed between a pump impeller 9 welded to the right side of the front cover 1, a turbine 10 disposed so as to face the pump impeller 9, and between the turbine 10 and the pump impeller 9. The stator 11 is configured to perform a torque amplification function and output a larger torque to the turbine 10 when the difference between the rotational speeds is large.

  The damper 4 includes a clutch-side input member 12 connected to the output-side spline 6 of the lockup clutch 2 and a fluid coupling connected to the turbine 10 and integrally coupled to the clutch-side input member 12 via a plurality of rivets 23. Side input member 13, output member 14 disposed between both of these input members and connected to the transmission, and elasticity interposed between clutch side input member 12 and fluid coupling side input member 13 in the rotational direction. And a spring 15 as a member. Here, the spring 15 has a configuration of a parent-child spring in which a child spring 15b is accommodated inside the parent spring 15a. As shown in FIG. 2, the clutch-side input member 12 is formed with four windows 12a for holding the spring 15, and a plurality of holes 12b and 12c for inserting the rivet 23 and a rivet 17 described later are provided in the circumferential direction. It is formed at substantially equal intervals. The fluid coupling side input member 13 is also formed with four windows 13 a for holding the spring 15. As shown in FIG. 3, the output member 14 is formed with four pressing portions 14a for pressing the springs 15 at substantially equal intervals in the circumferential direction. When assembled, the springs 15 are arranged between the pressing portions 14a. Will be placed between.

  And the connection part of the lockup clutch 2, the damper 4, and the fluid coupling 3 is comprised as follows. An input shaft of a transmission (not shown) is disposed at the axial center position in FIG. 1, and spline teeth 16a of the output hub 16 are splined to the input shaft. The inner periphery of the output member 14 is coupled to the outer periphery of the output hub 16 via a welded portion 24. The inner peripheral part of the clutch-side input member 12 and the inner peripheral part of the output-side spline (output member) 6 are coupled via a plurality of rivets 17. A sleeve 19 is disposed on the left side of the output hub 16 via a thrust bearing 18a. The sleeve 19 is inserted through an input shaft (not shown) via an O-ring 25. The piston 8 is provided between the outer peripheral surface of the sleeve 19 and the inner peripheral surface of the input-side spline 5 so as to be slidable in the axial direction via O-rings 20 and 29. A turbine hub 21 is rotatably provided on an outer peripheral surface of the output hub 16 in a centered state, and an inner peripheral portion of the turbine 10 is coupled to a right side surface of the outer peripheral portion of the turbine hub 21. . Further, the inner peripheral portion of the fluid coupling side input member 13 is engaged with the outer peripheral portion of the turbine hub 21 via a spline coupling portion 22. A thrust bearing 18 b is provided between the turbine hub 21 and the stator 11, and a thrust bearing 18 c is provided between the stator 11 and the pump impeller 9.

  On the inner peripheral side of the clutch-side input member 12, a protruding portion 12d that protrudes in the axial direction toward the fluid coupling 3 is provided every 120 degrees in the present embodiment along the circumferential direction as shown in FIG. On the other hand, three long holes (restricting frames) 14b are formed in the output member 14 along an arc centered on the axis of the output member 14, as shown in FIG. The projecting portion 12d is inserted into the elongated hole 14b, and the tip of the projecting portion 12d can come into contact with the turbine hub 21, which is a member that rotates together with the clutch-side input member 12.

  As shown in FIG. 3, the circumferential width W of the protrusion 12d is set larger than the radial thickness t of the protrusion 12d, which is the same as the thickness of the clutch-side input member 12. Yes. This is to ensure sufficient strength so that the protrusion 12d does not deform even when it receives a bending load in the circumferential direction. The clearances A and B between the end surface of the protruding portion 12d and the end wall surfaces 14c and 14d at both ends of the long hole 14b in the neutral state of the damper 4 are set smaller on the coast side than on the drive side. This is because the torsional characteristics of the damper are not required to a very high torque on the coast side. In addition, 26-28 are oil holes.

  Next, the operation of the torque converter device will be described.

  According to this invention, when the vehicle starts, the torque of the engine is transmitted from the crankshaft via the fluid coupling 3 to the damper 4 and further to the transmission. On the other hand, during a constant travel, oil is supplied from the hole 26 to the piston 8 and the front cover 1 so that the piston 8 moves to the right in FIG. 1 and presses the friction plate 7a and the friction plate 7b to each other. To do. As a result, the lockup clutch 2 is connected, and the rotation of the crankshaft is directly transmitted to the damper 4 and further to the transmission without passing through the fluid coupling 3.

  When the lock-up clutch 2 is connected or during operation under slip control, an axial load may be generated on the output-side spline 6 of the lock-up clutch 2, and this load is transmitted to the clutch-side input member 12, It is supported by a turbine hub 21 that rotates together with the clutch-side input member 12 via a protrusion 12d that functions as a support means.

  When the vehicle starts, the difference in rotational speed between the crankshaft and the turbine 10 is large, so that the torque amplifying function of the stator 11 works and a torque larger than the torque from the crankshaft is input to the damper 4. The end surface abuts on the end wall surface 14c of the long hole 14b in FIG. 3, and the protruding portion 12d and the long hole 14b function as a restricting means for restricting the relative rotation of the input member 12 with respect to the output member 14. That is, the member that supports the clutch-side input member 12 in the axial direction via the protrusion 12d is the fluid coupling-side input member 13, and the member that restricts the protrusion 12d of the clutch-side input member 12 in the circumferential direction is the output member. 14

  Since there is no relative rotation between the clutch-side input member 12 and the fluid coupling-side input member 13, friction between the tip of the protruding portion 12d and the fluid coupling-side input member 13 ( (Hysteresis) does not occur.

  According to the present invention, since the circumferential width dimension W of the protruding portion 12d inserted through the long hole 14b is larger than the radial thickness, the clutch-side input member 12 and the output member 14 of the damper 4 Even if a torque greater than a predetermined torque acts during this time and a large bending force acts on the projecting portion 12d, it has sufficient bending strength and is not easily deformed.

  According to the present invention, the gap dimension between the end face of the projecting portion 12d and the end wall surfaces 14c, 14d of the long hole 14b is made smaller than the gap dimension B on the coast side than the gap dimension A on the drive side. The cross-sectional area of the portion between the long hole 14b and the long hole 14b of the output member 14 can be increased in the circumferential direction, and a high torque torsional characteristic can be accommodated. Further, when the strength of the output member 14 is sufficient, the drive-side clearance dimension A can be increased so that the drive-side torsional characteristics of the damper 4 are ensured up to a high torque.

In the present embodiment, since the projecting portion 12d and the long hole 14b are arranged on the inner peripheral side of the torque converter device, the axial force transmitted to the turbine hub 21 via the projecting portion 12d is the shortest distance in the radial direction. Therefore, the bending of each part can be kept small. Since the plate thickness dimension t in the radial direction of the protrusion 12d is substantially the same as the plate thickness of the clutch side input member 12, the radial dimension of the long hole 14b is also reduced, and the radial layout of the torque converter device is reduced. Do not regulate.
(B) Embodiment 2
Next, Embodiment 2 is shown in FIG. Since this embodiment is obtained by changing a part of the first embodiment, the same parts are denoted by the same reference numerals, description thereof is omitted, and only different parts are described.

  As can be seen from comparison with FIG. 1, the fluid coupling side input member 13 is not connected to the turbine 10 and does not function as an input member. The outer peripheral portion of the output hub 16 is engaged with the inner peripheral portion of the output member 14 via the spline engaging portion 30. The inner peripheral portion of the turbine 10 that is the output member of the fluid coupling 3 is directly coupled to the right end surface on the outer peripheral side of the output hub 16.

  In this embodiment, a groove 31 as a restriction frame is formed on the surface of the output member 14 on the lockup clutch 2 side. The groove 31 is formed along an arc centered on the axis of the output member 14 as in the case of the long hole 14b in FIG. The leading end of the protruding portion 12 d is fitted in the groove 31, and the leading end of the protruding portion 12 d can come into contact with the bottom surface of the groove 31. The output member 14 with which the front end of the projecting portion 12d can come into contact is not integral with the clutch-side input member 12, but is a member that rotates relatively as much as the spring 15 is compressed, but rotates substantially together.

According to this invention, both the member that supports the inner peripheral portion of the clutch-side input member 12 in the axial direction via the protruding portion 12d and the member that restricts the protruding portion 12d of the clutch-side input member 12 in the circumferential direction Becomes the output hub 16.
(C) Embodiment 3
Next, Embodiment 3 is shown in FIG. Since this embodiment is obtained by changing a part of the first embodiment, the same parts are denoted by the same reference numerals, description thereof is omitted, and only different parts are described.

  In this embodiment, the radial positions of the projecting portions 12d and the long holes 14b are the radial positions of the thrust bearings 18b disposed between the turbine 10 and the stator 11 provided adjacent to the turbine 10. And correspond. Moreover, the spring 15 has a parallel arrangement configuration in which the spring 15 is arranged in parallel on the outer side and the inner side in the radial direction.

  According to the present invention, since the radial positions of the projecting portion 12d and the long hole 14b correspond to the radial positions of the thrust bearing 18b, the axial load generated in the output-side spline 6 of the lockup clutch 2 is achieved. Is supported by the thrust bearing 18b through the clutch-side input member 12 and its protruding portion 12d. Therefore, deformation of the turbine hub 21 is suppressed.

  Since other configurations and operations are the same as those of the first embodiment, description thereof is omitted.

  In Embodiments 1 to 3, three sets of protrusions and long holes are formed along the circumferential direction, but one set may be formed, or two sets or four or more sets may be formed. And “to be able to contact” may be in a state of contact, but also includes a state of being in a neutral state and having a slight gap. Further, in the first embodiment, the tip of the projecting portion can be brought into contact with the side surface of the turbine hub 21, but may be able to come into direct contact with the side surface of the fluid coupling side input member 13. In the second embodiment, a groove is formed in the output hub 16, but a groove may be formed directly in the output member 14. In addition to FIG. 1, FIG. 5 shows a protrusion 12d arranged at a position corresponding to the thrust bearing 18b in the radial direction, but protrudes to a position corresponding to the thrust bearing 18b in the radial direction with respect to FIG. A configuration in which the portion 12d is arranged can also be adopted.

Sectional drawing which shows a torque converter apparatus (Embodiment 1). The front view which looked at the clutch side input member from the fluid coupling side (Embodiment 1). The front view of the fluid coupling side input member (Embodiment 1). Sectional drawing which shows a torque converter apparatus (Embodiment 2). Sectional drawing which shows a torque converter apparatus (Embodiment 3).

Explanation of symbols

DESCRIPTION OF SYMBOLS 2 ... Lock-up clutch 3 ... Fluid coupling 4 ... Damper 12 ... Clutch side input member 13 ... Fluid coupling side input member 14 ... Output member 15 ... Spring (elastic member)
12d ... Projection 14b ... Long hole (regulation frame)
14c, 14d ... end wall 16 ... output hub 21 ... turbine hub 31 ... groove (regulation frame)

Claims (6)

A lockup clutch connected to the crankshaft of the engine is connected to the transmission via a damper, and a fluid coupling connected to the crankshaft is connected to the transmission directly or via the damper;
The damper includes an input member coupled to only the lockup clutch or both the lockup clutch and the fluid coupling, an output member coupled to the transmission, and the input member and the output member in a rotational direction. In a torque converter device comprising an elastic member interposed therebetween,
The clutch-side input member connected to the lock-up clutch has a protruding portion that protrudes in the axial direction along the circumferential direction, and a restriction frame into which the protruding portion fits is formed on the output member. A torque converter device, wherein the torque converter device is formed along an arc centered on an axial center, and the tip of the protruding portion can be brought into contact with a member that rotates together with the clutch-side input member. The torque converter device according to claim 1,
The input member includes the clutch-side input member, and a fluid coupling-side input member that is integrally coupled to the clutch-side input member and connected to the fluid coupling.
A torque converter device, wherein a long hole is formed as the restriction frame, and a tip end of the projecting portion inserted through the long hole can contact the fluid coupling side input member. The torque converter device according to claim 1,
The input member is constituted only by the clutch side input member, and the fluid coupling is directly connected to the output member,
A torque converter device, wherein a groove is formed as the restriction frame, and a tip of the projecting portion loosely fitted in the groove can abut against a bottom surface of the groove. In the torque converter device in any one of Claims 1-3,
The torque converter device according to claim 1, wherein a width dimension in a circumferential direction of the projecting portion is set larger than a thickness dimension in a radial direction of the projecting portion. In the torque converter device according to any one of claims 1 to 4,
The torque converter device characterized in that a gap dimension between the end face of the protruding portion and the end wall surface of the restriction frame in the neutral state of the damper is set smaller on the coast side than on the drive side. In the torque converter device according to any one of claims 1 to 5,
The radial positions of the protrusions and the restriction frame correspond to the radial positions of thrust bearings arranged between the turbine constituting the fluid coupling and a stator provided adjacent to the turbine. A torque converter device characterized by that.

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