KR20030095177A - Torsional-vibration decreasing device - Google Patents

Abstract

A torsional vibration reduction device according to the present invention comprises: an input side retaining plate having a spring receiving portion bent radially to have a substantially U-shaped cross section at an outer circumferential edge and a spring support wall disposed therein; A spring member housed in the spring receiving portion; And an output side transfer plate having a plurality of fixing claws which abut on the end face of the spring member. The center of gravity of the at least one spring contact of the spring support wall and the fixing claw is disposed at a position outside of the centerline of the end face of the spring member in the radial direction of rotation, wherein the centerline extends parallel to the axis of rotation of the device. .

Description

Torsional Vibration Reduction Device {TORSIONAL-VIBRATION DECREASING DEVICE}

The present invention relates to a torsional vibration reduction device, for example, arranged to reduce the torsional vibration of the system in a power transmission system between the engine and the transmission.

Torsional vibration reduction devices are disclosed in US Pat. No. 6,357,569, issued March 19, 2002 to Abe et al. This torsional vibration reduction device is interposed between the lockup piston and the turbine to reduce the torsional vibration during lockup. The lockup piston or input side rotation and the turbine or output side rotation are coupled in a rotational direction via a spring member.

In particular, the lock-up piston is arranged in the spring receptacle in the forward and rearward positions in the circumferential direction to support both the spring receptacle bent radially to have an approximately U-shaped cross section at the outer circumferential edge and both ends of the spring member accommodated in the spring receptacle. It has a retaining plate or spring support. On the other hand, the turbine or torque transmission member has a plurality of anchoring claws provided thereon to protrude axially, where each anchoring claw has side edges that abut on the end face of the spring member. Therefore, during the lockup, while compressing the spring member by the retaining plate and the fixing claw, torque is transmitted from the lockup piston to the turbine with the torsional vibration absorbed by the spring member's elasticity.

However, with the torsional vibration reducing device disclosed in US Pat. No. 6,357,569, the center of gravity of the spring contact portion of the retaining plate and the fixing claw is set to correspond to the center of the end face of the spring member. In this way, as the centrifugal force acting on the spring member is increased by the increase in the rotational speed of the lock-up piston, the spring member is deformed outward in the radial direction of rotation by being greatly subjected to the action of the centrifugal force. Therefore, the friction torque between the spring member and the spring receiving portion is increased by the increased centrifugal force, adversely affecting the vibration absorbing performance of the torsional vibration reducing device.

Therefore, it is an object of the present invention to provide a torsional vibration reduction device that contributes to the improvement of vibration absorption performance.

According to the present invention, there is provided a spring receiving portion provided in one of the input side rotating portion and the output side rotating portion, having a substantially disk-like shape, bent radially at the outer circumferential edge and having an approximately U-shaped cross section and an opening; And a retaining plate having a spring support wall disposed in the spring receiving portion in the second position; A spring member housed in the spring receiving portion and using the spring support wall as the support surface; A torque transmission member provided at another one of the input side rotating portion and the output side rotating portion, the torque transmitting member having an axially projecting end portion in the opening of the spring receiving portion and having a plurality of fixing claws which abuts on the end face of the spring member, Each fixed claw uses the side end face of the torque transmission member as a support surface, the torque transmission is performed between the retaining plate and the torque transmission plate while compressing the spring member by the spring support wall and the fixed claw, and the torsional vibration is carried out by the spring member. Absorbed by the elasticity of the spring support wall and the center of gravity of at least one of the spring abutment claws is disposed at a position external to the first centerline of the end face of the spring member in the radial direction of rotation of the device, A centerline is provided with a device that reduces torsional vibration extending parallel to the axis of rotation of the device.

1 is a longitudinal sectional view showing a first embodiment of a torsional vibration reduction device according to the present invention;

Fig. 2 is a partially broken partial front view showing the first embodiment as seen from arrow A of Fig. 1;

3 is a partially enlarged cross-sectional view of the first embodiment of the present invention.

4 is a partially broken partial front view similar to FIG. 2, showing a second embodiment of the present invention;

Fig. 5 is a partially enlarged sectional view similar to Fig. 3, showing a second embodiment of the present invention.

FIG. 6 is a partially broken front view showing a third embodiment of the present invention as seen from arrow A of FIG.

FIG. 7 is a longitudinal sectional view similar to FIG. 1, taken along line VIII-VIII in FIG.

8 is a front view showing the transfer plate;

Fig. 9 is an enlarged cross sectional view taken along the line VIII-VIII in Fig. 8;

<Explanation of symbols for the main parts of the drawings>

1: transducer housing

2: turbine jacket

3: turbine hub

4: lockup clutch

5: torsional vibration reduction device

6: external drum

7: inner drum

8: driving clutch plate

9: clutch plate

10: lock up piston

11: stop

12: cylindrical support wall

With reference to the drawings will be described a torsional vibration reduction device according to the present invention.

1 to 3, a first embodiment of the present invention is shown. Fig. 1 is a sectional view showing the lockup clutch portion of the torque converter arranged at the front end of the automatic transmission. The torque transducer comprises a transducer housing 1 and a turbine shell 2 which are integral with a torque transducer (not shown). The turbine hub 3 is integrally connected to the turbine shell 2. The transducer housing 1 is connected to the crankshaft (not shown) of the engine and the turbine hub 3 is splined to the input shaft (not shown) of the automatic transmission. The torque converter itself is a known form having a basic structure for transferring the torque provided from the crankshaft to the converter housing 1 to the turbine hub 3 by the action of a fluid between the pump and the turbine.

Referring to Fig. 1, the lockup clutch 4 is arranged to directly connect the transducer housing 1 and the turbine hub 3 during the high speed drive or the like. The torsional vibration reducing device 5 of the present invention is mounted to the lockup clutch 4.

The lockup clutch 4 is provided with an outer drum 6 protruding on the inner surface of the end wall of the transducer housing 1 and an inner drum coupled to the turbine hub 3 via a torsional vibration reducing device 5. 7) and a plurality of drive clutch plates 8 splined to the inner circumference of the outer drum 6 and alternately arranged between the drive clutch plates 8 in the state of splined to the outer circumference of the inner drum 7. And a plurality of driven clutch plates 9 and lock-up pistons 10 which are operated forward or backward by hydraulic pressure to appropriately press the driving clutch plate 8 against the driven clutch plate 9. The stop 11 is provided on the inner surface of the front end of the outer drum 6 to adjust the axial displacement of the drive clutch plate 8. The cylindrical support wall 12 protrudes on the inner surface of the end wall of the transducer housing 1 to slidably support the lock-up piston 10.

The torsional vibration reduction device 5 includes a substantially circular retaining plate 13 having an inner peripheral edge fixed to the inner drum 7 by rivets, and a plurality of spring members or coils held at the outer peripheral edge of the retaining plate 13. A transfer plate having a spring 14 and an inner circumferential edge fixed to the flange 3a of the turbine hub 3 by rivets and an outer circumferential edge coupled to the retaining plate 13 in a rotational direction through the spring member 14. Or torque transmission member 16.

1 and 2, a plurality of spring receiving portions 17 bent in a radial direction to have a substantially U-shaped cross section, and in the same manner to have a width substantially narrower than the diameter of the U-shaped cross section and the spring member 14. The plurality of bent spring support walls 18 are alternately formed in the circumferential direction at the outer circumferential edge of the retaining plate 13. Moreover, the reinforcing flange 19 is formed continuously in an annular shape on the outer circumference of the spring receiving portion 17 and the spring support wall 18 so as to extend outward in the radial direction. The spring receiving portion 17 is open to the turbine shell 2. The spring member 14 is inserted through this opening and mounted to the spring support wall 18 on both sides, which is used as the support surface. In this embodiment, the spring receptacle 17 has two parts, a long and a short part having a large and small circumferential length, in which the spring member 14 corresponding to the length of the spring receptacle is accommodated. Referring to Figure 2, a short spring receptacle (hereafter "short receptacle" for discrimination from other parts) 17 is approximately visible in the center of the upper part of Figure 2.

The spring receiving portion 17 has an inner wall 17a and an outer wall 17b which respectively guide the inner and outer sides of the spring member 14 in the radial direction of rotation. The inner wall 17a is formed linearly along the tangential direction of the retaining plate 13, so that the spring member 14 is kept substantially linear in the initial state in which the spring member is accommodated. On the other hand, the outer wall 17b is formed as a center of rotation and smooth arc of the holding plate 13 as a center, so that the outward displacement in the radial direction of the spring member 14 due to the shrinkage deformation of the spring member 14 or the like. Achieve regulation.

The spring support wall 18 has a radially inward first wall 18a and a radially outward second wall 18b, which refer to FIG. 3 where the walls 18a, 18b are generally spring members ( 14 is formed in such a way that it is offset outward in the radial direction of rotation with respect to the axis of rotation of the device, ie the centerline "p" parallel to the axis of rotation of the retaining plate 13. In particular, the first wall 18a is located at an inner position of the centerline "p" in the radial direction of rotation, and the two walls 18a, 18b have radial centers of gravity of their spring abutments with respect to the centerline "p". Are arranged in such a way that they are offset outward.

In the same manner as the retaining plate 13, the transfer plate 16 has a plurality of fixing claws 20 having a substantially L-shaped cross section which is formed as a whole, substantially like a disk, and separated and formed at the outer peripheral edge in the circumferential direction. The front end of the bend of each fixing claw 20 is inserted into the opening between the walls 18a and 18b of the spring support wall 18 of the retaining plate 13 along the axial direction, so as to support the wall 18a as a support surface. And an end face of the spring member 14 using the side end face of 18b). The spacing between adjacent fixing claws 20, 20 is set to be approximately the same length as the spring receptacle 17 except for the short receptacle as shown in FIG. In the spring receptacle 17 except for the short receptacle, each claw 20 abuts on the end face of the spring member 14 in its initial state.

With each fixed claw 20, as shown by the crosshatch of FIG. 3, the head and base regions of the bend have a centerline "q" therebetween in the radial direction. Abuts on the end face of the spring member 14 in the forward and rearward positions in the axial direction. Its spring abutment (exactly its center of gravity) is outwardly in the radial direction of rotation with respect to the centerline "p" of the end face of the spring member 14 in the same manner as the spring support wall 18 of the retaining plate 13. And are offset. In this embodiment, the offset size of the spring abutment portion of the fixing claw 20 with respect to the centerline "p" of the spring member 14 is greater than the offset size of the spring support wall 18, so that the spring fit of the fixing claw 20 is larger. The contact is located at the outer position of the center of the two walls 18a, 18b of the spring support wall 18 in the radial direction of rotation.

The retaining plate 13 and the conveying plate 16 in this manner abut the ends of the spring member 14 at positions that are outwardly offset in the radial direction of rotation, so that each spring member 14 is in the radial direction of rotation. Always receive a compressive load from a position that is slightly offset outward.

As shown in Fig. 2, the opposing spring support walls 18, 18 having the spring receiving portion 17 of the retaining plate 13 therebetween are radially outer second walls 18b, 18b. The spacing therebetween is set to be larger than the spacing between the inner first walls 18a, 18a in the radial direction. As a result, in this embodiment, the end of each spring member 14 is slightly separated from the second wall 18b in the initial state. Thus, when accommodating a compressive load by the relative movement of the holding plate 13 and the transmission plate 16, the edge part of each spring member 14 is inclined outwardly in the radial direction slightly, and this state was maintained In contact with the second wall 18b. However, when the spring member 14 is received in the spring receiving portion 17 by providing a relatively large preliminary compressive load, the end of the spring member 14 is in the same manner in the initial state to abut on the second wall 18b. Inclined to Moreover, the second wall 18b abuts on the end face of the spring member 14 near the outer end of the spring member 14 in the radial direction of its rotation, which is always the center of the spring wire of the spring member 14. Is set to extend over at least one half of the diameter of the spring wire of the spring member 14 to allow for the provision of contact loads to it.

On the outer circumferential edge of the transfer plate 16 at a position between adjacent fixing claws 20, 20, a spring adjustment piece 21 extending to cover the open side front face of the spring receiving portion 17 of the retaining plate 13. This is arranged to adjust the lateral protrusion of the spring member 14. Referring to Figure 1, a ring plate 22 is flanged 3a of the turbine hub 3 together with the transfer plate 16 to perform centering of the retaining plate 13 and adjustment of its axial displacement. Is fixed to.

With this structure, with the rotation of the crankshaft, the pump is rotated with the converter housing 1 to rotate the turbine, transferring its power from the turbine hub 3 to the automatic transmission. From this state, when the rotational speed or the like of the crankshaft reaches the set control condition, the hydraulic pressure flows from the oil hole 23 formed in the support wall 12 to the front face of the lockup piston 10, and the lockup piston Press (10) backwards. Next, the drive clutch plate 8 is pressed against the driven clutch plate 9 by the piston 10 so that the power of the transducer housing 1 is passed through the lockup clutch 4 and the torsional vibration reducing device 5. It is delivered directly to the turbine hub (3).

At this time, in the torsional vibration reduction device 5, both ends of the spring member 14 are supported by the spring support wall 18 and the fixing claw 20 of the retaining plate 13 and the transfer plate 16, respectively, The spring member 14 is elastically deformed in accordance with the torsion of the two plates 13 and 16 to absorb the torsional vibration of the power transmission system. When the rotational speed of the retaining plate 13 is high enough to increase the centrifugal force acting on the spring member 14, the spring member 14 is against the outer wall 17b of the spring receiving portion 17 under the influence of the centrifugal force. Is pressurized.

However, with the torsional vibration reducing device 5, the center of gravity of the spring abutment portion of the spring support wall 18 and the fixed claw 20 is the centerline "p" of the end face of the spring member 14 in the radial direction of rotation. Since it is located in an external position, the component of the pressing force acting from the spring support wall 18 and the fixing claw 20 on the end face of the spring member 14 acts inward in the radial direction of rotation, and the spring member 14 It is operated in such a way as to cancel the centrifugal force of the, thereby relieving the contact pressure of the spring member 14 and the outer wall 17b. Therefore, with this apparatus 5, even if the centrifugal force of the spring member 14 becomes large due to the increase in the rotational speed, large friction torque due to the violent contact of the spring member 14 and the outer wall 17b is prevented from occurring. It is possible to realize the stable vibration absorption performance at all times.

In this embodiment, the center of gravity of the spring abutment portion of both the spring support wall 18 and the fixed claw 20 is located at an outer position of the center line "p" of the end face of the spring member 14 in the radial direction of rotation. . Optionally, the center of gravity of any of the spring support wall 18 and the fixing claw 20 may be located at an external position in the radial direction of rotation, so that the effect can be obtained to some extent. Incidentally, when the fixing claw 20 with the single plate in contact with the end face of the spring member 14 is positioned at an external position in the radial direction of rotation as in this embodiment, the relatively small of the fixing claw 20 The offset magnitude allows the inward component force to act easily and surely in the radial direction of rotation on the end face of the spring member 14.

Moreover, with the torsional vibration reducing device 5, the head and base regions of the fixing claw 20 are substantially uniform with the end face of the spring member 14 in the axially forward and rearward positions with the centerline "q" therebetween. Contact, thereby allowing a small axial curvature deformation of the spring member 14 and a small contact friction in the axial and forward positions.

Furthermore, with the torsional vibration reducing device 5, the spacing between the second outer walls 18b, 18b in the radial direction of the spring support wall 18 is equal to the first inner walls 18a, 18a in the radial direction. It is set to be larger than the interval between. As such, when the spring member 14 is compressed by the relative rotation of the retaining plate 13 and the transfer plate 16, the end of the spring support wall 18 is inclined to open outward in the radial direction, and thus the spring member 14. Can be reliably prevented from slipping off the second wall 18b. Furthermore, with this device 5, the spring abutment of the second wall 18b is set to extend over at least one half of the diameter of the spring wire of the spring member 14, so that the spring wire of the spring member 14 Can be reliably pressed by the second wall 18b at all times, preventing slippage of the end of the spring member 14 from the second wall 18b and irregular deformation of the end of the spring member 14. It shows the advantages.

4 and 5, there is shown a second embodiment of the present invention, wherein like reference numerals are provided for parts similar to the parts in the first embodiment, and descriptions of duplicate parts will be omitted. .

In the second embodiment, in the same manner as in the first embodiment, the torsional vibration reducing device 105 is applied to the lockup clutch of the torque converter. The second embodiment is substantially the same as the first embodiment except for the structure of the fixing claw 120 of the transfer plate 116.

The fixing claw 120 is bent at the outer circumferential edge to have an approximately L-shaped cross section. The spring abutment portion of the fixing claw 120 extends in the axial direction from the bend 120a as well as the area extending radially inward from the bend 120a as indicated by the crosshatching of FIG. Is set to stretch over a portion of the. In this embodiment, a portion of the spring abutment portion of the fixing claw 120 is located at an inner position of the center line "p" of the end face of the spring member 214 in the radial direction of rotation as shown in FIG. The center of gravity of the abutment portion is located at an external position of the centerline "p" in the radial direction of the rotation as a whole.

Since the basic structure is the same as the first embodiment, the second embodiment can have a similar effect. In addition to this, the second embodiment provides the further advantage of being relievable of the stress acting on the extending base of the fixing claw 12, which is part of the abutting spring portion of the fixing claw 120 as described above. This is because it is set to extend over an area extending inwardly in the direction. In particular, the fixing claw 120 can receive a part of the reaction force of the spring member 214 at the inner position of the bend 120a in the radial direction of rotation, so that the fixing claw is driven by the reaction force of the spring member 214. The moment generated at the extension base of 120 is reduced, indicating a relaxation of the load acting on the extension base. Therefore, with the torsional vibration reducing device 105, deformation and deterioration of the transfer plate 116 can be prevented, thereby maintaining stable device performance for a long time.

6-9, a third embodiment of the present invention is shown. Fig. 7 is a sectional view showing the lockup clutch of the torque converter arranged at the front end of the automatic transmission. The torque converter includes a converter housing 201 and a turbine shell 202 integral with a torque converter pump (not shown). The turbine hub 203 is integrally connected to the turbine shell 202. The transducer housing 201 is connected to a crankshaft (not shown) of the engine and the turbine hub 203 is splined to an input shaft (not shown) of the automatic transmission. The torque converter itself is a known form having a basic structure for transferring the torque provided from the crankshaft to the converter housing 201 to the turbine hub 203 by the action of a fluid between the pump and the turbine.

Referring to Fig. 7, the lockup clutch 204 is arranged to be directly connected to the transducer housing 201 and the turbine hub 203 during the high speed drive or the like. Torsional vibration reducing device 205 of the present invention is mounted to lockup clutch 204.

The lockup clutch 204 has an outer drum 206 provided to protrude on the inner surface of the end wall of the transducer housing 201 and an inner drum coupled to the turbine hub 203 via a torsional vibration reducing device 205. 207, a plurality of drive clutch plates 208 splined to the inner circumference of the outer drum 206, and alternately arranged between the drive clutch plates 208 in a spline-engaged state with the outer circumference of the inner drum 207. And a plurality of driven clutch plates 209 and lock-up pistons 210 which are operated forward or backward by hydraulic pressure to appropriately press the driving clutch plate 208 against the driven clutch plate 209. A stop 211 is provided on the inner surface of the front end of the outer drum 206 to adjust the axial displacement of the drive clutch plate 208. The cylindrical support wall 212 protrudes on the inner surface of the end wall of the transducer housing 201 to slidably support the lock-up piston 210.

The torsional vibration reduction device 205 includes a substantially circular retaining plate 213 having an inner peripheral edge fixed to the inner drum 207 by rivets, and a plurality of spring members or coils held at the outer peripheral edge of the retaining plate 213. A transfer plate having a spring 214 and an inner circumferential edge fixed to the flange 203a of the turbine hub 203 by rivets and an outer circumferential edge coupled to the retaining plate 213 in a rotational direction through the spring member 214. Or torque transmission member 216.

6 and 7, in the same manner, a plurality of spring receiving portions 217 radially bent to have a substantially U-shaped cross section and a width narrower than the diameter of the approximately U-shaped cross section and the spring member 214. The plurality of bent spring support walls 218 are alternately formed in the circumferential direction at the outer circumferential edge of the retaining plate 213. Moreover, the reinforcing flange 219 is formed continuously in an annular shape on the outer periphery of the spring receiving portion 217 and the spring support wall 218 so as to extend outward in the radial direction.

The spring receptacle 217 is open to the turbine shell 202. The spring member 214 is inserted through this opening and mounted to the spring support wall 218 on both sides, which is used as the support surface. In this embodiment, the spring receptacle 217 has two parts, a long and a short part having a large and small circumferential length, in which a spring member 214 corresponding to the length of the spring receptacle is received. Referring to Figure 6, a short spring receptacle (hereinafter referred to as "short receptacle" for differentiation from other parts) 217 is approximately visible from the center of the top of Figure 6. The spring support wall 218 includes a pair of walls 218a and 218b arranged radially inward and outward and parallel to each other.

In the same manner as the retaining plate 213, the transfer plate 216 has a plurality of fixing claws 220 having a substantially L-shaped cross section that is generally formed like a disk and separated and formed at the outer circumferential edge in the circumferential direction. The front end of the bend of each fixing claw 220 is inserted into the opening between the walls 218a, 218b of the spring support wall 218 of the retaining plate 213 along the axial direction, so as to support the wall 218a. Abut the end face of the spring member 214 using the side end face of 218b.

6 and 8, on the outer circumferential edge of the transfer plate 216 at the position between adjacent fixing claws 220, 220, an open side front face of the spring receiving portion 217 of the retaining plate 213 is covered. Spring adjustment piece 221 extending so as to be arranged to adjust the lateral displacement of the spring member 214. The spring adjustment piece 221 is formed to extend from the base 221a to the head 221b like a sector. Referring to Fig. 9, both circumferential ends 221c and 221c of the head or wide area 221b are gently bent at the side opposite to the spring member 214. As shown in Figs. Further, a drawn portion 221d bent along the shape of the outer circumferential surface of the spring member 214 is arranged between the base 221a and the wide area 221b of the spring adjustment piece 221. A lightening hole 222 is formed in the lead portion 221d approximately centered circumferentially, such as an extension from the entire surface of the transfer plate 216.

Referring to FIG. 7, the ring plate 223 is fixed to the flange 203a of the turbine hub 203 together with the transfer plate 216 to perform centering of the retaining plate 213 and adjustment of its axial displacement.

With this structure, with the rotation of the crankshaft, the pump is rotated with the transducer housing 201 to rotate the turbine, transferring its power from the turbine hub 203 to the automatic transmission. From this state, when the rotational speed of the crankshaft or the like reaches the set control condition, the hydraulic pressure flows from the oil hole 223 formed in the support wall 212 to the front surface of the lockup piston 210, and the lockup piston Press 210 backwards. Next, the drive clutch plate 208 is pressed against the driven clutch plate 209 by the piston 210 so that the power of the transducer housing 201 is passed through the lockup clutch 204 and the torsional vibration reduction device 205. Directly to turbine hub 203.

At this time, in the torsional vibration reduction device 205, both ends of the spring member 214 are supported by the spring support wall 218 and the fixing claw 220 of the retaining plate 213 and the transfer plate 216, respectively, The spring member 214 is elastically deformed in accordance with the torsion of the two plates 213 and 216 to absorb the torsional vibration of the power transmission system.

When the retaining plate 213 and the conveying plate 216 generate torsional vibration or relative rotation, the spring member 214 is the spring retaining portion 217 on the side of the retaining plate 213 and the side of the conveying plate 216. The radial displacement controlled by the three walls of the upper spring adjustment piece 221. At this time, the end portion 221c of the spring adjustment piece 221 is bent to the side opposite to the spring member 214, so that the outer circumferential surface of the spring member 214, that is, the ring of the spring wire, expands and contracts the spring member 214. It is not possible to edge contact with the spring adjustment piece 221. In particular, since the end portion 221c of the spring adjustment piece 221 is separated from the outer circumferential surface of the spring member 214 by bending, and the bending portion is bent relatively gently, the spring member 214 adjusts the spring during its expansion and contraction. It cannot be in direct contact with the edge of the end 221c of the piece 221. And even if the spring member 214 is in contact with the bent portion, the spring member 214 may not be captured by the bent portion, and thus does not generate a large frictional resistance.

Therefore, with the torsional vibration reducing device 205, a large friction torque due to the edge contact of the spring member 214 with the spring adjusting piece 221 can be eliminated, so as to reliably prevent the resulting degradation of the absorption performance of the device. And deterioration of the spring member 214.

Moreover, with this device 205, the weighted hole 222 is formed in the transfer plate 216, so that the weight of the transfer plate 216 can be reduced by the hole as a whole. In particular, the weight reduction hole 222 of the transfer plate 216 is formed to extend over the lead portion 221d of the spring adjustment piece 221, so that the positional dispersion of the adjustment piece 221 is less.

In particular, when the lightweight hole 222 is formed in the area of the lead-out portion to perform the take-out press in a manner that extends over the hole 222, the lead-out area is reduced by the hole 222. As a result, accurate withdrawal can be provided to the transfer plate 216 with a relatively small pressure load. Further, the lightening hole 222 is located in the spring adjusting piece 221 at the outer peripheral edge of the transfer plate 216, when the heat transfer including the surface treatment such as carbonitriding after drawing out to the transfer plate 216 is applied. Residual stresses during pressurization and stresses due to tissue changes during heat treatment can be reliably removed from the holes 222. Therefore, transfer plate 216 may not experience torsion due to residual stress.

This enables reliable removal of the positional dispersion of the spring adjustment piece 221, leading to a sure prevention of the increase in contact friction between the spring member 214 and the spring adjustment piece 221.

Furthermore, since the torsional vibration reducing device 205 is used for the hydraulic oil in the torque converter, the hydraulic oil is transferred from the front face of the turbine shell 202 through the lightening hole 222 formed in the spring adjusting piece 221 of the transfer plate 216. It may smoothly flow into the outer circumferential region of the spring member 214. In particular, as the transfer plate 216, the lightening hole 222 is formed in a part of the spring adjustment piece 221 extending from the entire surface of the transfer plate 216 to the turbine shell 202, that is, in the lead-out portion 221d. By the centrifugal force of the transducer housing 201 due to the rotation thereof, it is possible to efficiently flow hydraulic oil in the housing 201 from the lightening hole 222 into the outer circumferential region of the spring member 214. Moreover, both ends 221c and 221c of the wide area 221b of the spring adjustment piece 221 are bent gently on the side opposite to the spring member 214, ie on the side of the turbine shell 202 as described above, The bend also acts as a fin for guiding the hydraulic oil to the outer circumferential region of the spring member 214.

Thus, with the torsional vibration reducing device 205, the hydraulic oil can be efficiently supplied to the peripheral region of the spring member 214 for the above reason, thereby providing efficient discharge of the wear powder attached on the spring member 214 and its peripheral member. Make it possible. This can prevent the acceleration of further wear of the spring member 214 and its peripheral members due to the attachment of the wear powder thereon.

While the invention has been described in connection with the preferred embodiments, it is to be understood that the invention is not so limited, and that various changes and modifications can be made without departing from the scope of the invention. By way of example, the retaining plate holding the spring member may be disposed on the output side, and the torque transmission member having the fixed claw may be disposed on the input side. Moreover, the torsional vibration reducing device can be applied to different power transmissions of a vehicle not only on the inside of the torque converter but also on the outside thereof or in which no torque converter is provided.

The entire disclosures of Japanese Patent Application No. 2002-166412, filed June 7, 2002, and Japanese Patent Application No. 2002-168112, filed June 10, 2002, are incorporated herein by reference.

According to the present invention, it is possible to provide a torsional vibration reduction device that contributes to the improvement of vibration absorption performance.

Claims (10)

Is a device to reduce torsional vibration, A spring receptacle provided in one of the input side rotation part and the output side rotation part, having a substantially disk-like shape, bent radially at the outer circumferential edge and having an approximately U-shaped cross section and an opening, in the first and second positions in the circumferential direction A holding plate having a spring support wall disposed in the spring receiving portion; A spring member housed in the spring receiving portion and using the spring support wall as the support surface; A torque transmission member provided at another one of the input side rotating portion and the output side rotating portion, the torque transmitting member having an axially projecting end portion in the opening of the spring receiving portion and having a plurality of fixing claws which abuts on the end face of the spring member, Each fixed claw uses the side end surface of the torque transmission member as a support surface, Torque transmission is carried out between the retaining plate and the torque transmission plate while compressing the spring member by the spring support wall and the fixing claw, Torsional vibration is absorbed by the elasticity of the spring member, The center of gravity of at least one of the spring contact portions of the spring support wall and the fixing claw is disposed at an outer position of the first center line of the end face of the spring member in the radial direction of the rotation of the device, the first center line being parallel to the axis of rotation of the device. And extend the device. The spring center of the spring engaging portion of the fixing claw is disposed at an outer position of the first center line, and an end and a base of each fixing claw are spring members at first and second positions in the axial direction of the fixing claw. Abuts on an end face of the first and second positions with a second center line of the end face of the spring member therebetween, the second center line extending along the radial direction of rotation. A device according to claim 2, wherein the base of each fixing claw is bent inwardly in the radial direction of rotation, and the base is integral with the body of the torque transmission member. 4. The device of claim 3, wherein the spring abutment of the base of each anchoring claw is set to extend over at least an area extending radially inward from the bend of the base. 2. The spring support wall of the retainer plate is bent in the same direction as the spring receiving portion, the spring support wall having a first wall radially located inside and a second wall located radially outward. And having a substantially U-shaped cross section so that the spacing between the first and second walls is less than the diameter of the spring member, the spring member being supported by the ends of the first and second walls. 6. The spring abutment of claim 2, wherein the spring abutment of the second wall of the spring support wall is offset relative to the spring abutment of the first wall of the spring support wall in the circumferential direction, the spacing between adjacent second walls being adjacent to the first abutment. Device characterized in that greater than the interval between. 6. The device according to claim 5, wherein the spring abutment of the second wall of the spring support wall is set to extend over at least one half of the diameter of the spring wire of the spring member. 2. The torque transmission member of claim 1 further comprising a spring adjustment piece extending between the claws circumferentially adjacent to the front of the opening of the spring receptacle, the spring adjustment piece adjusting the lateral displacement of the spring member. And circumferential ends bent at the side opposite the spring member. The device according to claim 8, wherein the spring adjustment piece has a lead portion formed along the shape of the outer circumferential surface of the spring member. 10. An apparatus according to claim 9, wherein the lightening holes are arranged to extend over the lead-out portion.