JP4941201B2 - Damper device - Google Patents

Description

  The present invention relates to a damper device provided in, for example, a fluid torque transmission device.

  In general, a vehicular automatic transmission is provided with a fluid torque transmission device for transmitting engine torque to an input shaft of a transmission mechanism. The hydrodynamic torque transmission device includes a front cover coupled to an output shaft of an engine, a pump impeller coupled to the front cover, a turbine runner coupled to an input shaft of a transmission mechanism in a manner facing the pump impeller, and the like The rotation member is provided. The rotational force transmitted from the engine side to the pump impeller is transmitted to the turbine runner via an ATF (automatic transmission fluid) that is a fluid, so that the rotational force is transmitted to the transmission mechanism side. .

  In addition, when power is transmitted to such a fluid torque transmission mechanism through ATF, power loss occurs and fuel consumption is deteriorated. Therefore, when the vehicle speed reaches a certain level, A lock-up clutch is provided that mechanically connects the front cover to the input shaft of the transmission mechanism. When the lock-up clutch is engaged, the rotational force from the engine side is mechanically transmitted to the transmission mechanism that is in the directly connected state.

  On the other hand, however, when the lock-up clutch is in the engaged state, vibrations based on the explosion of fuel in the engine may be transmitted as torque fluctuations to the input shaft of the transmission mechanism. Therefore, recently, as a device for absorbing such torque fluctuation in the fluid torque transmission device, for example, a damper device described in Patent Document 1 has been proposed.

  The damper device described in Patent Document 1 is transmitted to a drive plate (first flywheel) that rotates integrally with a lockup clutch, a driven plate (second flywheel) that rotates together with a turbine runner, and the drive plate. Torque transmitting means for transmitting the generated torque to the driven plate. The torque transmission means is arranged in a plurality of damper springs arranged in series so as to be along the circumferential direction centering on the rotation axis of each plate, and arranged on the radially inner side of each damper spring. And a disk-shaped intermediate member arranged so as to be rotatable around the center.

Each of the drive plate and the driven plate is provided with a torque transmission portion that comes into contact with the corresponding damper spring so as to be able to transmit torque in the circumferential direction around the rotation axis. Further, the intermediate member includes a torque transmission portion that is interposed between the damper springs and contacts the damper springs so as to be able to transmit torque in a circumferential direction centering on the rotation axis. It is installed. When the lockup clutch is in the engaged state, torque fluctuations are absorbed by the expansion / contraction operation of each damper spring and the loose movement of the intermediate member around the rotation axis.
JP-A-11-141617

  Incidentally, in the damper device described in Patent Document 1, each torque transmission portion provided on each plate and intermediate member normally abuts against a portion corresponding to the central axis of the damper spring and torque between the damper spring. It comes to communicate. Therefore, the damper spring is deformed into a convex curve toward the rotating member in the direction along the rotation axis when the damper spring expands and contracts along the circumferential direction around the rotation axis along with torque transmission with each torque transmission portion. There was something to do. Therefore, conventionally, even when the damper spring is deformed in a convex curve in a direction of another peripheral member, the damper spring has conventionally been provided between the damper spring and the peripheral member so that the damper spring does not contact the peripheral member. There is a problem that it is necessary to secure a displacement allowable space of the damper spring, and in this respect, it is not possible to contribute to downsizing of the apparatus.

  This invention is made | formed in view of such a situation, The objective is to provide the damper apparatus which can contribute to size reduction of an apparatus.

In order to achieve the above object, a damper device according to a first aspect of the present invention includes a first flywheel that is rotatable about a predetermined axis and connected to the engine side, and the first flywheel. A second flywheel disposed coaxially with respect to the wheel and connected to the speed change mechanism side; and provided between the first flywheel and the second flywheel; and In a damper device comprising: torque transmission means for transmitting the rotational force of the first flywheel to the second flywheel; and a displacement regulating member for regulating displacement of the torque transmission means in one direction in the axial direction. The torque transmission means includes a damper spring that is arranged to be stretchable along a circumferential direction centering on the axis, and the first flywheel includes the damper. The first flywheel is provided in contact with the spring to be able to transmit torque in the circumferential direction centered on the axis, and the second flywheel is centered on the axis with respect to the damper spring. A second torque transmission portion that is in contact with the damper spring so as to be able to transmit torque in a circumferential direction, and the load center position at the time of torque transmission with the damper spring in at least one of the torque transmission portions is the axis line A torque transmission portion provided in a region farther from the displacement regulating member than the center axis of the damper spring in the direction, and among the torque transmission portions, the torque transmission portion provided in a region far from the displacement regulating member is the load center position. The portion that comes into contact with the damper spring during torque transmission with the damper spring is a circumference around the axis. And summarized in that is formed so as to extend at an increasingly away slant from the displacement regulating member nears to the damper spring in the direction.

According to this configuration, da damper springs, the torque is transmitted from the opposite side of the displacement-regulating members from the central axis of the damper spring in the axial direction, deforming the displacement regulating member side in the axial direction in a convex curved shape . That is, unlike the conventional damper device, it is necessary to provide a space allowing the displacement of the damper spring between the peripheral member and the damper spring arranged in the direction away from the displacement regulating member in the axial direction than the damper spring. There is no. Therefore, it is possible to contribute to downsizing of the device in which the damper device is disposed.
Further, in the torque transmission portion provided in the region where the load center position is far from the displacement regulating member, the portion that contacts the damper spring at the time of torque transmission is an oblique shape that gradually moves away from the displacement regulating member in the circumferential direction as it approaches the damper spring. Is formed. Therefore, the torque transmission unit can reliably apply a pressing force toward the displacement regulating member to the damper spring, and can reliably displace the damper spring toward the displacement regulating member during torque transmission.

The invention according to claim 2 is the damper device according to claim 1 , wherein the torque transmission means includes a plurality of damper springs arranged in series along a circumferential direction centering on the axis. A third arm which is interposed between the respective damper springs and moves along a circumferential direction centered on the axis so as to contact the damper springs so that torque can be transmitted in the circumferential direction centered on the axis. An intermediate member having a torque transmission portion, and the load center position at the time of torque transmission with the damper spring in the third torque transmission portion is more in the axial direction than the central axis in the displacement regulating member. The main point is that it is provided in a region far from the center.

According to this configuration, the damper springs adjacent to each other in the circumferential direction of the third torque transmitting portion can be deformed in a convex curve toward the displacement regulating member in the axial direction.

According to a third aspect of the present invention, in the damper device according to the second aspect , the intermediate member is provided with a sliding contact portion with respect to the displacement regulating member on a side facing the displacement regulating member. Is the gist.

If the intermediate member is given a pressing force in the direction of approaching the displacement regulating member in the axial direction from the damper spring, the sliding contact portion and the displacement regulating member when the intermediate member moves along the circumferential direction There is a possibility that the frictional force between the two becomes larger and the torque fluctuation generated on the engine side cannot be absorbed appropriately. In this regard, in the present invention, the pressing force in the direction away from the displacement restricting member in the axial direction is applied from the damper spring to the third torque transmitting portion at the time of torque transmission. The frictional force between the sliding contact portion and the displacement restricting member when moving along is not increased. Therefore, unlike the case where the pressing force in the direction in which the intermediate member approaches the displacement regulating member in the axial direction is applied from the damper spring, it is possible to appropriately absorb the generated torque fluctuation stopped on the engine side.
According to a fourth aspect of the present invention, in the damper device according to any one of the first to third aspects, the load center position is located in a region far from the displacement regulating member among the torque transmitting portions. The provided torque transmitting portion is arranged such that both end portions in the circumferential direction centering on the axis line are disposed on the opposite side of the displacement regulating member side from the center axis line of the damper spring in the axial direction, and the axis line is the center. The gist is that the center portion in the circumferential direction is arranged closer to the displacement regulating member than the both end portions.

  Hereinafter, an embodiment in which the present invention is embodied in a damper device for a starting device will be described with reference to FIGS. In the following description of the present specification, the “front-rear direction” refers to the front-rear direction indicated by the arrows in the figure.

  As shown in FIG. 1, the starting device 10 according to the present embodiment includes a front cover 12 connected to an engine output shaft 11 and a pump cover 13 fixed to the outer peripheral side end of the front cover 12 by welding. A housing 14 is configured. The converter housing 14 contains a torque converter 15, a lock-up clutch 16, and a damper device 17 which is a main part of the present invention, and is filled with ATF (automatic transmission fluid) as hydraulic oil. Yes.

  The front cover 12 has a substantially cylindrical shape with a bottom closed at the front end and opened at the rear end, and an engine output shaft 11 is connected to a substantially central portion in the radial direction of the bottom wall to thereby output the engine. The shaft 11 is rotated based on the rotational drive of the shaft 11. The pump cover 13 has a substantially annular shape so as to close the opening on the rear end side of the front cover 12, and the inner peripheral edge thereof is connected to a drive shaft of an oil pump of an automatic transmission (not shown). A support cover 18 is fixed. That is, the rotation of the output shaft 11 of the engine is transmitted to the oil pump through the front cover 12, the pump cover 13, and the support cover 18. In the present embodiment, the front cover 12, the pump cover 13, and the support cover 18 are formed so as to rotate about a rotation axis (predetermined axis) S of the output shaft 11 of the engine.

  The torque converter 15 includes a pump impeller 19, a turbine runner 20, and a stator 21. The pump impeller 19 is integrally disposed on the front side of the pump cover 13 fixed to the front cover 12 (the relative surface side facing the front cover), and is configured to rotate integrally with the front cover 12. ing.

  The turbine runner 20 is disposed so as to face the pump impeller 19 in the internal space between the front cover 12 and the pump cover 13. The inner peripheral side of the turbine runner 20 is connected to a flanged turbine hub 24 via a first pin 23, and the inner peripheral side of the turbine hub 24 is spline-engaged with an input shaft 25 of the automatic transmission. . That is, the turbine runner 20 is connected to rotate integrally with the input shaft 25 of the automatic transmission.

  The stator 21 is disposed between the pump impeller 19 and the turbine runner 20, and a one-way clutch 26 that functions to prevent rotation in one direction is provided therein. The stator 21 adjusts the flow direction of the ATF in the torque converter 15 by the one-way clutch 26 based on the speed difference between the pump impeller 19 and the turbine runner 20.

  Between the front cover 12 and the turbine runner 20, there is provided a lockup clutch 16 capable of directly connecting the engine output shaft 11 and the input shaft 25 of the automatic transmission mechanism by operating a clutch. The lock-up clutch 16 includes a piston 27 (also referred to as a “clutch plate”) as a metal displacement regulating member having a substantially cylindrical shape with a closed front end and an open rear end. The piston 27 is engaged with the turbine hub 24 so as to be movable in the axial direction (front-rear direction).

  Further, a seal ring 28 is disposed between the piston 27 and the turbine hub 24. Further, a friction member 29 is fixed to the front surface of the bottom 27a of the piston 27 in the radial direction centering on the rotation axis S so as to face the back surface of the front cover 12, and the front cover 12 is provided as necessary. It is possible to make frictional contact. The piston 27 moves in the axial direction according to the hydraulic pressure difference between the front side (front cover 12 side) hydraulic pressure and the rear side (pump cover 13 side) hydraulic pressure of the bottom 27a of the piston 27 by the sealing function of the seal ring 28. It is supposed to be free.

  Specifically, when ATF is supplied via an oil passage (not shown) to the front space 2a when viewed from the bottom 27a of the piston 27, the front space 2a when viewed from the bottom 27a of the piston 27 is located in the piston. The hydraulic pressure is higher than the space 2b on the rear side as viewed from 27. Therefore, the piston 27 is pressed rearward in the axial direction, so that the friction member 29 and the front cover 12 are dissociated. That is, the lock-up clutch 16 is disengaged.

  On the other hand, when ATF is supplied to the rear space 2b as viewed from the bottom portion 27a of the piston 27 via the inside 15a of the torque converter 15, a differential pressure between the front space 2a and the rear space 2b. Produce. The friction member 29 and the front cover 12 are brought into an engaged state by the piston 27 being gradually pressed forward in the axial direction by the differential pressure. That is, the lockup clutch 16 is engaged.

  Next, the damper device 17 which is a main part of the present invention will be described in detail with reference to FIGS. 4 (a) and 4 (b) are schematic views of the damper device when viewed obliquely from the rotation axis S in FIG.

  As shown in FIGS. 1 and 2, the damper device 17 includes a first flywheel 30 connected to the engine side, a second flywheel 31 connected to the transmission mechanism side (not shown), and both flywheels. Torque transmission means 32 for transmitting the rotational force (torque) of the first flywheel 30 between the wheels 30 and 31 to the second flywheel 31 is provided.

  The first flywheel 30 includes a wheel body 33 having a substantially annular shape. The first flywheel 30 is supported by the bottom 27a of the piston 27 via a plurality of second pins 34 (only nine are shown in FIG. 2) in the radial direction around the rotation axis S. This is connected to the piston 27. That is, when the piston 27 is engaged with the front cover 12 via the friction member 29, the first flywheel 30 is shown in FIG. 2 around the rotational axis S together with the front cover 12 and the piston 27. It rotates integrally along the arrow R direction. That is, the first flywheel 30 rotates in the counterclockwise direction in FIG. 2, which is the same direction as the rotation direction of the output shaft 11 of the engine.

  In the wheel main body 33, a plurality (four in this embodiment) of receiving holes 35 are formed through the inner peripheral edge side of the second pins 34 at regular intervals in the circumferential direction around the rotation axis S. ing. Each of the accommodation holes 35 accommodates an inner spring 36 that can expand and contract along the circumferential direction around the rotation axis S. In the wheel main body 33, a restricting portion 37 for restricting the inner spring 36 from dropping from the accommodation hole 35 to the rear side (that is, the turbine runner 20 side) is provided in the vicinity of each accommodation hole 35. ing.

  Further, the first flywheel 30 includes a plurality of (four in this embodiment) first torque transmitting portions protruding outward in the radial direction around the rotation axis S from the outer peripheral edge of the wheel body 33. 38 are arranged at regular intervals in the circumferential direction around the rotation axis S. The first torque transmission portions 38 are arranged at the same positions in the circumferential direction around the inner springs 36 and the rotation axis S.

  Each first torque transmission portion 38 is formed so as to have a substantially U-shaped cross section. Specifically, each first torque transmission portion 38 has a radially central portion centered on the rotation axis S located closest to the bottom 27a side (ie, the front side) of the piston 27 and the rotation axis S centered. The radially outer portion is formed so as to be positioned on the rear side in the axial direction with respect to the inner portion. That is, the radially outer ends of the first torque transmitting portions 38 around the rotational axis S are located at substantially the same position as the rear end of the peripheral wall 27b of the piston 27 in the axial direction. In addition, as shown in FIG. 1, the wheel main body 33 is located at each part between the first torque transmission portions 38 adjacent to each other in the circumferential direction around the rotation axis S in the outer peripheral edge of the wheel main body 33. Ridges 39 projecting from the rear side to the rear side are formed along the circumferential direction with the rotation axis S as the center.

  Further, both end portions 40 in the circumferential direction around the rotation axis S of each first torque transmitting portion 38 constitute torque transmitting means 32 in the axial direction as will be described later, as shown in FIGS. 4 (a) and 4 (b). The outer spring 44 is positioned on the rear side of the center axis Y. Further, both end portions 40 of each first torque transmission portion 38 gradually become the bottom portion of the piston 27 as it approaches the torque transmission means 32 (more specifically, an outer spring 44 described later) in the circumferential direction around the rotation axis S. Each of them is formed so as to extend obliquely away from 27a.

  The second flywheel 31 includes an annular wheel body 41 disposed on the rear side in the axial direction with respect to the first flywheel 30, and the wheel body 41 is interposed via the first pin 23. The turbine runner 20 and the turbine hub 24 are connected. That is, when the first flywheel 30 rotates as the output shaft 11 of the engine rotates, the rotational force of the first flywheel 30 is transmitted to the second flywheel 31 via the torque transmission means 32. Thus, the second flywheel 31 rotates together with the turbine runner 20 and the turbine hub 24 around the rotation axis S.

  Further, as shown in FIGS. 1 and 2, the second flywheel 31 includes a plurality of (in this embodiment) protruding outward in the radial direction from the outer peripheral edge of the wheel body 41 around the rotation axis S. Four) second torque transmission portions 42 are arranged at regular intervals in the circumferential direction around the rotation axis S. Each of these second torque transmission portions 42 is disposed at the same position as each of the first torque transmission portions 38 in the radial direction and the circumferential direction around the rotation axis S. Therefore, when the damper device 17 of the present embodiment is viewed from the rear side in the axial direction, each of the first torque transmission portions 38 is in a state where most of each is covered with each second torque transmission portion 42. Yes.

  As shown in FIGS. 4 (a) and 4 (b), both end portions 43 in the circumferential direction centering on the rotation axis S of each second torque transmitting portion 42 are more than the center axis Y of the outer spring 44 in the axial direction. Each is located on the back side. In addition, both end portions 43 of each second torque transmission portion 42 gradually become the bottom portion of the piston 27 as it approaches the torque transmission means 32 (more specifically, an outer spring 44 described later) in the circumferential direction around the rotation axis S. Each of them is formed so as to extend obliquely away from 27a.

  As shown in FIGS. 1 and 2, the torque transmission means 32 includes a plurality (eight in the present embodiment) of outer springs 44 as damper springs, a bottom 27 a of the piston 27, and the first flywheel 30. And an intermediate member 45 that is rotatable about the rotation axis S. The intermediate member 45 includes an intermediate member main body 46 having a substantially annular shape in a plan view, and the intermediate member main body 46 has an inner peripheral edge centered on the rotation axis S rather than the arrangement position of the second pin 34. The outer peripheral edge portion is located on the radially outer side centering on the rotation axis S with respect to each first torque transmission portion 38 while being located on the radially outer side.

  The intermediate member 45 has a plurality of (four in this embodiment) third torque transmitting portions 47 that protrude outward in the radial direction around the rotation axis S from the outer peripheral edge of the intermediate member main body 46. They are arranged at regular intervals in the circumferential direction around the rotation axis S. Each of these third torque transmission portions 47 is disposed at the same position as each of the first torque transmission portions 38 and each of the second torque transmission portions 42 in the radial direction around the rotation axis S. In addition, each third torque transmission portion 47 is located at the approximate center between the first torque transmission portions 38 (each second torque transmission portion 42) adjacent to each other in the circumferential direction about the rotation axis S. ing. An outer spring 44 is provided between the first torque transmission unit 38 (second torque transmission unit 42) and the third torque transmission unit 47 that are adjacent to each other in the circumferential direction about the rotation axis S. They are arranged so as to be stretchable along the direction.

  Further, most of the midway portion in the circumferential direction around the rotation axis S of each third torque transmission portion 47 is the outer spring 44 in the axial direction as shown in FIGS. 2 and 3A and 3B. Center axis Y (shown by a one-dot chain line in FIGS. 3A and 3B). Further, both end portions 48 in the circumferential direction centering on the rotation axis S of each third torque transmitting portion 47 are located rearward of the center axis Y of the outer spring 44 in the axial direction. Then, as shown in FIGS. 4 (a) and 4 (b), both end portions 48 of each third torque transmission portion 47 have an oblique shape that gradually moves away from the bottom portion 27a of the piston 27 as the outer spring 44 is approached. Each is formed to extend.

  Further, as shown in FIG. 3B, in the intermediate member 45, the connection portion between the intermediate member main body 46 and each third torque transmission portion 47 protrudes from the connection portion toward the bottom portion 27 a of the piston 27. A sliding contact portion 49 is provided, and each sliding contact portion 49 is in sliding contact with the bottom portion 27 a of the piston 27. When torque is transmitted to the first flywheel 30 from the piston 27 side, each sliding contact portion 49 of the intermediate member 45 slides along the bottom portion 27a of the piston 27. .

  Next, the operation of the damper device 17 will be described below with reference to FIGS. 4 and 5, the configuration of the third torque transmission unit 47 is illustrated in a simplified manner for the convenience of understanding the description.

  When the piston 27 moves forward in the axial direction while the output shaft 11 of the engine is driven to rotate, the friction member 29 provided on the piston 27 engages with the front cover 12. Then, the rotational force of the engine is directly transmitted to the turbine runner 20 via the piston 27 and the damper device 17.

  That is, when the piston 27 rotates in the R direction (the arrow direction shown in FIG. 2), the first flywheel 30 receives the rotational force Pe of the engine via the piston 27 as shown in FIGS. Therefore, it rotates integrally with the piston 27 in the R direction. At this time, both end portions 40 of each first torque transmitting portion 38 are located on the rear side of the central axis Y of the outer spring 44 in the axial direction, and from the front side to the rear side in the axial direction. It is formed in an oblique shape that gradually approaches the outer spring 44. In other words, the load center position 50 when the rotational force is transmitted to the outer spring 44 in each first torque transmission portion 38 (at the time of torque transmission) is lower than the center axis Y of the outer spring 44 in the axial direction than the bottom portion 27a of the piston 27. It is provided in the area far from.

  As a result, when the rotational force P1 of each first torque transmission portion 38 (a force comparable to the rotational force Pe of the engine) is transmitted to the adjacent outer springs 44 in the R direction, the outer springs 44 are The pressing force in the direction and the pressing force in the direction approaching the bottom portion 27a of the piston 27 are applied. Note that, when the rotational force P <b> 1 is transmitted to the outer spring 44, a repulsive force P <b> 2 in the direction opposite to the rotational force P <b> 1 is applied to each first torque transmission portion 38 from the outer spring 44.

  On the other hand, each of the outer springs 44 to which the rotational force P1 is transmitted from the first torque transmitting unit 38 is adjacent to the third torque transmitting unit adjacent to the rotational force P3 having the same magnitude as the rotational force P1 in the R direction. 47 respectively. At this time, both end portions 48 of each third torque transmitting portion 47 are positioned rearward of the central axis Y of the outer spring 44 in the axial direction, and as they move from the front side to the rear side in the axial direction. It is formed in an oblique shape that gradually approaches the outer spring 44. In other words, the load center position 51 when the rotational force is transmitted to the outer spring 44 in each third torque transmission portion 47 is provided in a region farther from the bottom portion 27a of the piston 27 than the center axis Y of the outer spring 44 in the axial direction. It has been.

  Therefore, when the rotational force P3 is transmitted from the outer spring 44 to each third torque transmission portion 47, each third torque transmission portion 47 is pressed in the R direction and away from the bottom portion 27a of the piston 27. It will be in the state where the pressing force to was applied. Each of the third torque transmission portions 47 applies a repulsive force P4 in the direction opposite to the rotational force P3 to the outer spring 44 when the rotational force P3 is transmitted from the outer spring 44.

  Further, each third torque transmission portion 47 to which the rotational force P3 is transmitted from the outer spring 44 transmits the rotational force P5 having the same magnitude as the rotational force P3 to the adjacent outer springs 44 in the R direction. Then, each outer spring 44 is in a state where a pressing force in the R direction and a pressing force in a direction approaching the bottom 27a of the piston 27 are applied. In addition, when the rotational force P5 is transmitted to the outer spring 44, the repulsive force P6 in the direction opposite to the rotational force P5 is applied from the outer spring 44 to each third torque transmission portion 47. Therefore, each third torque transmission portion 47 tends to be displaced in a direction away from the bottom portion 27 a of the piston 27.

  On the other hand, each outer spring 44 to which the rotational force P5 is transmitted from the third torque transmission unit 47 applies a rotational force P7 of the same magnitude as the rotational force P5 to the second torque transmission unit 42 adjacent in the R direction. Communicate each. At this time, both end portions 43 of each second torque transmitting portion 42 are located on the rear side of the central axis Y of the outer spring 44 in the axial direction, and from the front side to the rear side in the axial direction. It is formed in an oblique shape that gradually approaches the outer spring 44. In other words, the load center position 52 of each second torque transmission portion 42 when transmitting the rotational force with the outer spring 44 is provided in a region farther from the bottom portion 27a of the piston 27 than the center axis Y of the outer spring 44 in the axial direction. It has been.

  Therefore, when the rotational force P <b> 7 is transmitted from the outer spring 44 to each second torque transmission unit 42, each second torque transmission unit 42 is pressed in the R direction and away from the bottom 27 a of the piston 27. It will be in the state where the pressing force to was applied. When the rotational force P7 is transmitted to each second torque transmission unit 42, the second flywheel 31 rotates together with the turbine runner 20 and the turbine hub 24 in the R direction, and as a result, the rotational force of the engine. Is transmitted to the transmission mechanism side. Each of the second torque transmitting portions 42 applies a repulsive force P8 in the direction opposite to the rotational force P7 to the outer spring 44 when the rotational force P7 is transmitted from the outer spring 44.

  As described above, while the rotational force is transmitted to the damper device 17, the circumferential end portions of the outer springs 44 around the rotational axis S are pushed toward the bottom 27 a side of the piston 27 in the axial direction. Each pressure is applied. Here, suppose that the load center positions of the torque transmitting portions 38, 42, and 47 adjacent to the outer spring 44 in the circumferential direction about the rotation axis S as in the prior art shown in FIGS. Assuming that 50 to 52 are provided at positions closer to the bottom 27a of the piston 27 than the center axis Y of the outer spring 44 in the axial direction, there are axial directions at both ends in the circumferential direction around the rotation axis S of the outer spring 44. , A pressing force in a direction away from the bottom 27a of the piston 27 is applied. As a result, the outer spring 44 is deformed into a convex curve in a direction away from the bottom 27 a of the piston 27.

  In this respect, in this embodiment, the direction of the pressing force in the axial direction applied to both ends in the circumferential direction around the rotation axis S of each outer spring 44 is opposite to the conventional case. . Therefore, each of these outer springs 44 is deformed into a convex curve on the bottom 27a side of the piston 27 in the axial direction. In addition, when the amount of displacement of each outer spring 44 toward the bottom 27a side of the piston 27 is large, the portion of each outer spring 44 that is closest to the bottom 27a (that is, the central portion in the circumferential direction) is the bottom 27a of the piston 27. To touch. At this time, to each outer spring 44 that presses the piston 27 forward in the axial direction, a repulsive force P10 in the rearward direction in the axial direction that repels the pressing force P9 that each outer spring 44 applies to the piston 27 is applied from the piston 27. The Therefore, further displacement of each outer spring 44 toward the bottom 27a side (front side in the axial direction) of the piston 27 is restricted.

  Also, assuming that each torque transmitting portion 38, 42, 47 has the conventional configuration shown in FIGS. 5 (a) and 5 (b), the pistons 27 are disposed in both end portions 48 of each third torque transmitting portion 47 in the axial direction. A pressing force in a direction approaching the bottom portion 27a is applied. Then, each third torque transmission portion 47 is displaced toward the bottom portion 27 a of the piston 27, so that each sliding contact portion 49 provided on the intermediate member 45 is pressed against the bottom portion 27 a of the piston 27. As a result, the frictional force between each sliding contact portion 49 and the bottom portion 27a of the piston 27 becomes too large, hindering the loose movement of the intermediate member 45 around the rotation axis S, and the rotational force generated on the engine side. The fluctuation (torque fluctuation) may not be absorbed well.

  In this regard, in the present embodiment, the direction of the pressing force in the axial direction applied to both end portions 48 of each third torque transmission portion 47 is opposite to the conventional case. Therefore, each third torque transmission portion 47 is slightly displaced in the direction away from the bottom portion 27a of the piston 27 in the axial direction, and as a result, between each sliding contact portion 49 of the intermediate member 45 and the bottom portion 27a of the piston 27. Increase in frictional force is regulated. Therefore, in this embodiment, even if each outer spring 44 is displaced in the axial direction, fluctuations in rotational force generated on the engine side are absorbed well.

According to the damper device of the above embodiment, the following effects can be obtained.
(1) When the first flywheel 30 rotates based on the rotation of the piston 27, the rotational force P1 is transmitted from each first torque transmission section 38 to the outer spring 44 adjacent in the R direction. Then, since the load center position 50 at the time of transmission of the rotational force with the outer spring 44 in each first torque transmission portion 38 is provided in a region on the rear side of the central axis Y of the outer spring 44, the outer spring 44. Is deformed in a convex curve toward the bottom 27a side of the piston 27 in the axial direction. That is, unlike the conventional damper device, the outer spring 44 is disposed between a peripheral member (such as the turbine runner 20) and the outer spring 44 disposed in a direction away from the bottom 27 a of the piston 27 in the axial direction than the outer spring 44. It is not necessary to provide a space that allows the spring 44 to be displaced. Therefore, it is possible to contribute to downsizing of the starting device 10 in which the damper device 17 is disposed.

  (2) The load center position 52 when the rotational force is transmitted to the outer spring 44 in each second torque transmission portion 42 is provided in a region on the rear side of the central axis Y of the outer spring 44. Therefore, the outer spring 44 that has transmitted the rotational force P7 to the second torque transmitting portion 42 is applied with the repulsive force P8 from the second torque transmitting portion 42, thereby causing the piston 27 to move toward the bottom 27a side in the axial direction. Deforms into a convex curve. That is, the outer spring 44 that transmits the rotational force P7 to the second torque transmitting portion 42 can be displaced toward the bottom 27a side of the piston 27 in the axial direction.

  (3) The load center position 51 when the rotational force is transmitted to the outer spring 44 in each third torque transmission portion 47 is provided in a region on the rear side of the central axis Y of the outer spring 44. Therefore, the outer spring 44 adjacent to the third torque transmitting portion 47 in the circumferential direction around the rotation axis S has a pressing force from the third torque transmitting portion 47 to the bottom 27a side of the piston 27 in the axial direction. Therefore, it is deformed into a convex curve toward the bottom 27a side of the piston 27. That is, the outer spring 44 adjacent to the third torque transmission portion 47 in the circumferential direction around the rotation axis S can be displaced toward the bottom 27a side of the piston 27 in the axial direction.

  (4) Further, the outer spring 44 deformed in a convex curve toward the bottom 27 a side of the piston 27 in the axial direction is further deformed by contacting the bottom 27 a of the piston 27. That is, unlike the case where the outer spring 44 is deformed in the direction away from the bottom 27a of the piston 27 in the axial direction, an increase in the amount of displacement of the outer spring 44 can be suppressed. Therefore, it is possible to reduce the size of the damper device 17 in the axial direction.

  (5) The end portions 40, 43, 48 of the torque transmission portions 38, 42, 47 are inclined so as to gradually move away from the bottom portion 27 a of the piston 27 as they approach the outer spring 44 in the circumferential direction around the rotation axis S. Are formed respectively. Therefore, the end portions 40, 43, and 48 of the torque transmission portions 38, 42, and 47 are axial with respect to the outer spring 44 when the rotational force is transmitted to the outer spring 44 that is adjacent in the circumferential direction around the rotational axis S. A pressing force can be reliably applied to the bottom 27a side of the piston 27 in the direction. Accordingly, the outer springs 44 can be reliably deformed in a convex curve toward the bottom 27a side of the piston 27 in the axial direction when the rotational force is transmitted.

  (6) The end portions 40, 43, and 48 of the torque transmission portions 38, 42, and 47 are configured to deform the outer spring 44 into a convex curve toward the bottom portion 27a side of the piston 27 in the axial direction when transmitting the rotational force. Has been. Therefore, the frictional force between each sliding contact portion 49 provided on the intermediate member 45 and the bottom portion 27a of the piston 27 decreases as the deformation amount of the outer spring 44 increases. Therefore, unlike the conventional case where the outer spring 44 is deformed in the direction away from the bottom 27a of the piston 27 in the axial direction when the rotational force is transmitted, the fluctuation of the rotational force generated on the engine side can be appropriately absorbed.

  (7) Further, when the lockup clutch 16 is in the disengaged state, the rotation of the turbine runner 20 is transmitted to the piston 27 via the damper device 17. That is, the transmission path of the rotational force is in a state reverse to that in the case where the lockup clutch 16 is in the engaged state. Even in such a case, the load center positions 50, 51, 52 at the time of transmission of the rotational force with the outer spring 44 in each of the torque transmission portions 38, 42, 47 are regions behind the central axis Y of the outer spring 44. Therefore, the outer spring 44 can be deformed toward the bottom 27a of the piston 27 in the axial direction.

In addition, you may change this embodiment into another embodiment as follows.
The sliding contact portion 49 may be disposed at a position different from the third torque transmission portion 47 in the circumferential direction around the rotation axis S.

The intermediate member 45 may not be provided with the sliding contact portion 49.
The end portions 40, 43, and 48 of the torque transmitting portions 38, 42, and 47 have an oblique shape that gradually moves away from the bottom portion 27a of the piston 27 as the outer spring 44 is approached in the circumferential direction about the rotation axis S. If it is a configuration, it may be a curved surface.

  The both end portions 48 of the third torque transmission portion 47 may be surfaces that are orthogonal to the central axis Y of the outer spring 44. Further, both end portions 43 of the second torque transmission portion 42 may be surfaces orthogonal to the central axis Y of the outer spring 44. Further, both end portions 40 of the first torque transmitting portion 38 may be surfaces orthogonal to the central axis Y of the outer spring 44.

The damper device 17 may have a configuration in which the intermediate member 45 is not provided.
The first flywheel 30 may be configured to include an arbitrary number (for example, six) of first torque transmission units 38 other than four. In this case, it is desirable that the second flywheel 31 has the same number of second torque transmission units 42 as the first torque transmission units 38.

  The intermediate member 45 includes a plurality of (for example, two) third intermediate members between the first torque transmission unit 38 and the second torque transmission unit 42 that are adjacent to each other in the circumferential direction about the rotation axis S. A configuration in which the torque transmission unit 47 is arranged may be employed. And it is desirable to arrange | position the outer spring 44 between the torque transmission parts 38, 42, and 47 mutually adjacent | abutted in the circumferential direction centering on the rotating shaft S, respectively.

  The damper device 17 may be provided with a displacement restricting member that is configured separately from the piston 27. In addition, the displacement regulating member may be disposed on the rear side in the axial direction with respect to each outer spring 44. In this case, the load center positions 50, 51, 52 at the time of transmission of the rotational force with the outer spring 44 in each torque transmission portion 38, 42, 47 may be arranged in front of the central axis Y of the outer spring 44 in the axial direction. desirable. If comprised in this way, each outer spring 44 can suppress the deformation | transformation to the bottom part 27a side of piston 27 in an axial direction at the time of rotational force transmission.

  -The 1st flywheel 30 does not need to be provided. In this case, it is desirable to dispose the first torque transmitting portion 38 on the peripheral wall 27b of the piston 27 at a constant interval in the circumferential direction around the rotation axis S. In this case, the piston 27 functions as the first torque transmission unit 38.

  The outer spring 44 may be arranged so as to form a polygonal ring (for example, a decagonal ring) in the circumferential direction around the rotation axis S. Further, if the torque transmission means is arranged between the first torque transmission unit 38 and the second torque transmission unit 42, the damper device 17 has a configuration in which the outer spring 44 is arranged non-annularly. There may be.

The partial cross section figure of the starting device of this embodiment. The schematic plan view which shows the principal part of the damper apparatus of this embodiment. (A) is AA arrow sectional drawing in FIG. 2, (b) is BB arrow sectional drawing in FIG. (A) is a schematic diagram which shows the mode at the time of non-rotational force transmission in this embodiment, (b) is a schematic diagram which shows the mode at the time of rotational force transmission in this embodiment. (A) is a schematic diagram which shows the mode at the time of the conventional non-rotational force transmission, (b) is a schematic diagram which shows the mode at the time of rotational force transmission in the conventional damper apparatus.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 23 ... Piston, 17 ... Damper apparatus, 27 ... Piston as a displacement control member, 30 ... 1st flywheel, 31 ... 2nd flywheel, 32 ... Torque transmission means, 38 ... 1st torque transmission part, 42 ... 2nd torque transmission part, 44 ... Outer spring as damper spring, 45 ... Intermediate member, 47 ... 3rd torque transmission part, 49 ... Sliding contact part, 50, 51, 52 ... Load center position, Pe, P1 , P3, P5, P7 ... rotational force, S ... rotational axis as a predetermined axis, Y ... central axis.

Claims (4)

A first flywheel that is rotatable about a predetermined axis and connected to the engine side, and is disposed so as to be relatively rotatable coaxially with the first flywheel and connected to the transmission mechanism side. Torque transmitting means provided between the second flywheel and the first flywheel and the second flywheel and transmitting the rotational force of the first flywheel to the second flywheel. And a damper device comprising a displacement restricting member that restricts displacement of the torque transmitting means in one direction in the axial direction,
The torque transmission means includes a damper spring arranged to be stretchable along a circumferential direction around the axis,
The first flywheel is provided with a first torque transmission portion that comes into contact with the damper spring so as to be able to transmit torque in a circumferential direction around the axis, and
The second flywheel is provided with a second torque transmission portion that comes into contact with the damper spring so that torque can be transmitted in a circumferential direction centered on the axis.
The load center position at the time of torque transmission between the damper spring in at least one of the torque transmitting portion of the torque transmitting portion is provided in a region far from the displacement regulating member than the center axis of the damper spring in the axial direction And
Among the torque transmission portions, the torque transmission portion provided in a region where the load center position is far from the displacement regulating member is such that a portion that contacts the damper spring at the time of torque transmission with the damper spring is centered on the axis. A damper device, wherein the damper device is formed so as to extend obliquely away from the displacement restricting member as it approaches the damper spring in a circumferential direction . The damper device according to claim 1 ,
The torque transmitting means includes a plurality of damper springs arranged in series along a circumferential direction centered on the axis, and a circumferential direction centered on the axis interposed between the damper springs. An intermediate member having a third torque transmitting portion that contacts the damper springs so as to be able to transmit torque in a circumferential direction centered on the axis.
The load center position at the time of torque transmission with the damper spring in the third torque transmission portion is provided in a region farther from the displacement regulating member than the center axis in the axial direction. . The damper device according to claim 2 , wherein
The damper device according to claim 1, wherein the intermediate member is provided with a sliding contact portion with respect to the displacement regulating member on a side facing the displacement regulating member. In the damper device according to any one of claims 1 to 3,
Among the torque transmitting portions, the torque transmitting portion provided in a region where the load center position is far from the displacement regulating member is such that both end portions in the circumferential direction centering on the axis are center axes of the damper springs in the axial direction. The damper device is characterized in that it is arranged on the opposite side to the displacement regulating member side, and a central portion in the circumferential direction centering on the axis is arranged on the displacement regulating member side with respect to the both end portions .

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