JP5939686B2 - Torque damper of fluid transmission device - Google Patents

Description

  In the present invention, a plurality of first and second coil springs are alternately arranged along the circumferential direction of the clutch piston between the clutch piston of the lockup clutch and the turbine impeller, and some of the first and second coils are arranged. A drive claw and a driven claw respectively fixed to the clutch piston and the turbine impeller are inserted between the springs so as to be relatively rotatable, and the drive claw and the driven claw are inserted between the other first and second coil springs. The present invention relates to an improvement in a torque damper of a fluid transmission device, in which a third spring holding member that can rotate relative to the cylinder is inserted.

  A torque damper of such a fluid transmission device is already known as disclosed in Patent Document 1 below.

JP-A-10-196664

  By the way, in the torque damper disclosed in Patent Document 1, a cylindrical regulating member that regulates the bending due to the centrifugal force of each coil spring is disposed on the outer periphery of the first and second coil springs. Each coil spring comes into contact with its regulating member, and the frictional resistance causes hysteresis in the expansion and contraction of each coil spring, which slightly affects the torque buffering characteristics.

  The present invention has been made in view of such circumstances, and it is possible to eliminate the restriction member for restricting the bending of each coil spring by securely holding both ends of the first and second coil springs. An object of the present invention is to provide a torque damper of a fluid transmission device that can exhibit a good torque buffering characteristic while avoiding friction with other coil springs.

In order to achieve the above object, according to the present invention, a plurality of first and second coil springs are alternately arranged along the circumferential direction of the clutch piston between the clutch piston of the lockup clutch and the turbine impeller. A driving claw and a driven claw fixed to the clutch piston and the turbine impeller, respectively, are inserted between the first and second coil springs of the section so as to be relatively rotatable, and between the other first and second coil springs. Is a torque damper of a fluid transmission device in which a third spring holding member that is rotatable relative to the drive claw and the driven claw is inserted, and has a first annular plate having a plurality of first spring seats projecting on the outer periphery. A second spring plate having a first spring holding member and a plurality of second spring seats projecting on the outer periphery so as to sandwich the driving and driven claws along the circumferential direction of the clutch piston; Spring holding member and A third annular plate having a plurality of third spring seats projecting on the outer periphery is disposed between the first and second spring seats facing each other along the circumferential direction of the clutch piston without passing through the drive and driven pawls. The three spring holding members are arranged coaxially with the clutch piston so as to be rotatable relative to each other, and first and third connecting shafts are provided on the opposing surfaces of the first and third spring seats so that their tips are opposed to each other. In addition, second and fourth connecting shafts are provided on the opposing surfaces of the second and third spring seats so that their tips are opposed to each other, and the outer peripheral surfaces of the first and third connecting shafts are linear. the first to fit pressure of close winding portions formed on both ends of the coil spring, the outer peripheral surface of the second connecting shaft and the fourth connecting shaft, is formed on both ends of the straight said second coil spring contact fitted pressure winding section, each of said spring seat, mutually radially outer end And a pair of spring seat plates having elastic inner ends connected to corresponding annular plates and capable of being close to each other in the axial direction of the clutch piston. The pair of connecting shaft halves are coupled to the spring seat plates and face each other with a gap therebetween, and the pair of connecting shaft halves are contracted by the elastic mutual proximity of the pair of spring seat plates. The first characteristic is that each connecting shaft is provided with elasticity that enables diameter reduction in the radial direction .

According to the present invention , a plurality of first and second coil springs are alternately arranged along the circumferential direction of the clutch piston between the clutch piston of the lock-up clutch and the turbine impeller. A drive claw and a driven claw respectively fixed to the clutch piston and the turbine impeller are inserted between the coil springs so as to be relatively rotatable, and the drive claw and the driven claw are inserted between the other first and second coil springs. A first spring holding member having a first annular plate having a plurality of first spring seats projecting on the outer periphery thereof, and a clutch in a torque damper of a fluid transmission device, wherein a third spring holding member rotatable relative to a pawl is inserted. A second spring holding member having a second annular plate having a plurality of second spring seats projecting on the outer periphery so as to sandwich the drive and driven claws along the circumferential direction of the piston; Through a driven nail A third spring holding member having a third annular plate having a plurality of third spring seats disposed on the outer periphery thereof, which are arranged between the first and second spring seats facing each other along the circumferential direction of the clutch piston. The first and third connecting shafts are arranged coaxially with the clutch piston so as to be rotatable relative to each other, the front ends of the first and third spring seats face each other. Second and fourth connecting shafts having tips opposed to each other are provided on the opposing surface of the third spring seat, respectively, and the linear first coil spring is formed on the outer peripheral surface of the first connecting shaft and the third connecting shaft. The tightly wound portions formed at both end portions of the second connecting shaft and the fourth connecting shaft are press-fit to the tightly wound portions formed at both end portions of the linear coil spring. , The clutch piston, the first annular plate, the second annular plate and the first annular plate. A plurality of support shafts that rotatably support the annular plate via a rolling member are provided, and the rolling member is supported by the first annular plate, the second annular plate, and the third annular plate, respectively. The second feature is that the second and third ball bearings are used.

Further, according to the present invention , a plurality of first and second coil springs are alternately arranged along the circumferential direction of the clutch piston between the clutch piston of the lockup clutch and the turbine impeller, and some of the first and second coil springs are arranged. A drive claw and a driven claw respectively fixed to the clutch piston and the turbine impeller are inserted between the coil springs so as to be relatively rotatable, and the drive claw and the driven claw are inserted between the other first and second coil springs. A first spring holding member having a first annular plate having a plurality of first spring seats projecting on the outer periphery thereof, and a clutch in a torque damper of a fluid transmission device, wherein a third spring holding member rotatable relative to a pawl is inserted. A second spring holding member having a second annular plate having a plurality of second spring seats projecting on the outer periphery so as to sandwich the drive and driven claws along the circumferential direction of the piston; Via a driven nail A third spring holding member having a third annular plate projecting on the outer periphery of a plurality of third spring seats disposed between the first and second spring seats facing each other along the circumferential direction of the clutch piston without Are arranged coaxially with the clutch piston so as to be rotatable relative to each other, and first and third connecting shafts are provided on the opposing surfaces of the first and third spring seats so that their tips are opposed to each other. And second and fourth connecting shafts whose tips are opposed to each other on the opposing surfaces of the third spring seat, and the linear first coil on the outer peripheral surfaces of the first and third connecting shafts. The tightly wound portions formed at both ends of the spring are press-fitted, and the tightly wound portions formed at both ends of the linear second coil spring are press-fit to the outer peripheral surfaces of the second connecting shaft and the fourth connecting shaft. And the clutch piston includes the first annular plate, the second annular plate, and the A plurality of support shafts that rotatably support the three annular plates via a rolling member are provided, and the rolling member is a common roller that supports the first annular plate, the second annular plate, and the third annular plate. The configuration is the third feature.

In addition to the first feature, the present invention provides a plurality of support shafts that rotatably support the first annular plate, the second annular plate, and the third annular plate on a clutch piston via a rolling member. The fourth feature is that the above is provided.

The present invention, in addition to the second or third feature, the each connecting shaft is that it has granted elasticity that allows reduced diameter in the radial direction and the fifth aspect.

In addition to the fifth feature of the present invention, each of the spring seats has a radially outer end coupled to each other and a radially inner end coupled to a corresponding annular plate, and the axial direction of the clutch piston. And a pair of connecting shaft halves that are coupled to the pair of spring seat plates and face each other with a gap therebetween. in constructed, the pair of connecting shaft halves, and sixth aspect of that diameter by elastic mutual proximity of said pair of spring seat plate.

The present invention, in addition to any of the first to sixth features, and seventh aspect in that mutually made different spring constants of the first and second coil springs.

Is found in or present invention, in addition to any one of the first to seventh features, the a tip portion outer periphery of the connecting shaft, the said seal wear winding portion engages the inner end of the tightly wound portion corresponding An eighth feature is that a locking projection for preventing the corresponding connecting shaft from coming off is formed .

According to the first feature of the present invention, the first spring holding member having a first annular plate having a plurality of first spring seats provided on the outer periphery, and the drive and driven pawls are sandwiched along the circumferential direction of the clutch piston. A second spring holding member having a second annular plate having a plurality of second spring seats opposed to the first spring seat on the outer periphery, and along the circumferential direction of the clutch piston without intervening driving and driven pawls A third spring holding member having a third annular plate having a plurality of third spring seats arranged between the first and second spring seats facing each other and projecting on the outer periphery thereof is arranged coaxially with the clutch piston so as to be relatively rotatable. The first and third connecting shafts are provided on the opposing surfaces of the first and third spring seats so that the tips are opposed to each other, and the tips are opposed to the opposing surfaces of the second and third spring seats. A second connecting shaft and a fourth connecting shaft projecting from the first connecting shaft; The outer peripheral surface of the third connecting shaft, to fit pressure of close winding portions formed on both ends of the linear first coil spring, the outer peripheral surface of the second connecting shaft and the fourth connecting shaft, linear second coil spring the tightly wound portion formed at both ends since the fitting pressure of the first and second coil springs, the tightly wound portion of each of the two ends first and third connecting shaft, and the second and fourth connecting shaft by being fitted pressure on each outer peripheral surface, even if the centrifugal force to the first and second coil spring acts, the friction and backlash does not occur between the coupling shaft and the tightly wound portion, the close winding portion Can be prevented from coming off from each connecting shaft. Therefore, it is not necessary to provide a regulating member for restricting the bending due to the centrifugal force on the outer circumference of the first and second coil springs, and even when the torque converter is rotated at high speed, friction with other coil springs is not possible. Therefore, it is not necessary to generate hysteresis in the expansion and contraction of each coil spring, and a good torque buffering characteristic can be imparted to the torque damper. Moreover, both the first and second coil springs can contribute to the reduction of the cost of the torque damper by using inexpensive linear ones and eliminating the regulating member.

Each spring seat has a pair of spring seats whose outer ends in the radial direction are coupled to each other and whose inner ends in the radial direction are coupled to the corresponding annular plates, and which are close to each other in the axial direction of the clutch piston. Each connecting shaft is composed of a pair of connecting shaft halves that are coupled to a pair of spring seat plates and face each other with a gap therebetween. The diameter of the seat plate is reduced by the elastic proximity of each other so that each connecting shaft is elastic enough to reduce the diameter in the radial direction. The above-mentioned press fitting can be easily performed by elastically reducing the shaft, and not only the assembly is good, but also the stress generated by the reduced diameter of each connecting shaft is dispersed in each spring seat. The durability of the connecting shaft and the spring seat can be ensured.

According to the second feature of the present invention, the clutch piston is provided with a plurality of support shafts for rotatably supporting the first annular plate, the second annular plate and the third annular plate via the rolling member. The frictional force generated between the support shaft and the first, second and third annular plates accompanying the expansion and contraction of the first and second coil springs is extremely small, and there is almost no hysteresis on the expansion and contraction of each coil spring. In addition, since the rolling member is composed of the first, second, and third ball bearings that individually support the first annular plate, the second annular plate, and the third annular plate, respectively, the first and second coil springs are provided. The frictional force generated between the support shaft and the first, second, and third annular plates due to the expansion and contraction of the coil can be further reduced, and the generation of hysteresis is effectively suppressed when the coil springs expand and contract. Can do.

According to the third feature of the present invention, the clutch piston is provided with a plurality of support shafts for rotatably supporting the first annular plate, the second annular plate and the third annular plate via the rolling member. The frictional force generated between the support shaft and the first, second and third annular plates accompanying the expansion and contraction of the first and second coil springs is extremely small, and there is almost no hysteresis on the expansion and contraction of each coil spring. In addition, since the rolling member is composed of a common roller for supporting the first annular plate, the second annular plate, and the third annular plate, the first and second coil springs can be expanded and contracted with a simple structure. The frictional force generated between the support shaft and the first, second, and third annular plates can be suppressed as much as possible, and the cost can be reduced.

According to the fourth aspect of the present invention, the clutch piston is provided with a plurality of support shafts for rotatably supporting the first annular plate, the second annular plate and the third annular plate via the rolling member. The frictional force generated between the support shaft and the first, second and third annular plates accompanying the expansion and contraction of the first and second coil springs is extremely small, and there is almost no hysteresis on the expansion and contraction of each coil spring.

According to a fifth aspect of the present invention, each coupling shaft, since imparting elasticity to allow reduced diameter in the radial direction, sometimes fitting pressure of the tightly wound portion of the respective connecting shafts elastically connecting shaft compressed state makes it possible to easily fit the pressure, is good assemblability.

According to the sixth aspect of the present invention, the spring seats are connected to each other at their radially outer ends and to their corresponding annular plates at their radially inner ends and close to each other in the axial direction of the clutch piston. A pair of spring seat plates having elasticity to enable, and each coupling shaft is composed of a pair of coupling shaft halves that are respectively coupled to the pair of spring seat plates and face each other with a gap therebetween. stress coupling shaft halves. Thus reducing the diameter by elastic mutual proximity of a pair of spring seat plate, when fitted pressure on each connecting shaft of the tightly wound portion, which is generated by the diameter of the connecting shaft Is distributed to each spring seat, and the durability of each connecting shaft and spring seat can be ensured.

According to the seventh feature of the present invention, since the spring constants of the first and second coil springs are made different from each other, even a large torque shock generated between the pump impeller and the turbine impeller can be absorbed in stages. Therefore, the damper effect can be exhibited well.

According to the eighth feature of the present invention, the locking projection that engages with the inner end of the corresponding tightly wound portion on the outer periphery of the distal end portion of each connecting shaft and prevents the tightly wound portion from coming out of the corresponding connecting shaft. Therefore, even if centrifugal force acts on the first and second coil springs, each locking projection exerts strong resistance against centrifugal force, so that the tightly wound portions can be securely pulled out from the connecting shafts. Can be prevented.

FIG. 2 is a longitudinal side view of a torque converter with a torque damper according to an embodiment of the present invention (cross-sectional view taken along line 1-1 of FIG. 2). FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. FIG. 3 is an enlarged view of part 3 of FIG. 2. The principal part enlarged view of FIG. FIG. 5 is an enlarged sectional view taken along line 5-5 in FIG. FIG. 6 is an enlarged sectional view taken along line 6-6 of FIG. The exploded perspective view of the torque damper. FIG. 5 is a view corresponding to FIG. 4 showing a second embodiment of the present invention. FIG. 5 is a view corresponding to FIG. 4 showing a third embodiment of the present invention. FIG. 5 is a view corresponding to FIGS. 1 and 4 showing a fourth embodiment of the present invention.

  Embodiments of the present invention will be described below on the basis of preferred embodiments of the present invention shown in the accompanying drawings.

  First, the description starts with the description of the first embodiment of the present invention shown in FIGS. In FIG. 1, a torque converter T as a fluid transmission device includes a pump impeller 2, a turbine impeller 3 opposed to the pump impeller 2, and a stator impeller 4 disposed between the inner peripheral portions thereof. Between the impellers 2, 3 and 4, a circulation circuit 6 for power transmission by working oil is defined.

  A front cover 5 that covers the outer surface of the turbine impeller 3 is integrally connected to the pump impeller 2 by welding. A starting ring gear 7 is welded to the outer peripheral surface of the front cover 5, and a drive plate 8 coupled to the crankshaft 1 of the engine is fixed to the ring gear 7 with bolts 9. A thrust needle bearing 26 is interposed between the hub 3 h of the turbine impeller 3 and the front cover 5.

  An output shaft 10 arranged coaxially with the crankshaft 1 is disposed at the center of the torque converter T. The output shaft 10 is splined to the hub 3h of the turbine impeller 3 and is supported at the center of the front cover 5. 5a is rotatably supported via a bearing bush 18. The output shaft 10 is a main shaft of a multi-stage transmission (not shown).

  A cylindrical stator shaft 12 for supporting the hub 4h of the stator impeller 4 via a free wheel 11 is disposed on the outer periphery of the output shaft 10, and the relative rotation between the output shaft 10 and the stator shaft 12 is arranged. A bearing bush 13 that allows The outer end portion of the stator shaft 12 is supported by the transmission case 14 so as not to rotate.

  Thrust needle bearings 27 and 27 ′ are interposed between the hub 4 h of the stator impeller 4 and the hubs 2 h and 3 h of the pump impeller 2 and the turbine impeller 3 opposed to the hub 4 h.

  An auxiliary machine drive shaft 20 coupled to the pump impeller 2 is disposed on the outer periphery of the stator shaft 12 so as to be relatively rotatable. An oil pump 21 that supplies hydraulic oil to the torque converter T is provided by the auxiliary machine drive shaft 20. Driven.

  The turbine impeller 3 and the front cover 5 define a clutch chamber 22 therebetween, and a lockup clutch L that can directly connect the turbine impeller 3 and the front cover 5 is accommodated in the clutch chamber 22. The clutch chamber 22 is divided into an inner chamber 22a on the turbine impeller 3 side and an outer chamber 22b on the front cover 5 side by the clutch piston 25 that forms the main body of the lockup clutch L.

  A friction lining 28 facing the inner surface of the front cover 5 is attached to the clutch piston 25. The clutch piston 25 slidably supports a hub 25 h that is integrally bent at the inner peripheral end of the clutch piston 25 on the outer peripheral surface of the hub 3 h of the turbine impeller 3. It is possible to move in the axial direction between a connection position that is pressed against the inner wall and a non-connection position that is separated from the inner wall.

  The clutch chamber 22 is provided with a torque damper D according to the present invention that buffers the clutch piston 25 and the turbine impeller 3. The torque damper D will be described with reference to FIGS.

  In FIG. 1 to FIG. 3, the torque damper D is welded to a side surface of the clutch piston 25 opposite to the friction lining 28 and arranged at equal intervals in the circumferential direction, and on the rear surface of the turbine impeller 3. A first spring having welded pawls 31 that are welded and arranged in the radial direction of the drive pawl 30 and the clutch piston 25, and a first annular plate 32a projecting from the outer periphery of a plurality of first spring seats 32b. A second annular plate projecting from the holding member 32 and a plurality of second spring seats 33b facing the first spring seat 32b so as to sandwich the driving and driven claws 30 and 31 along the circumferential direction of the clutch piston 25 The second spring holding member 33 having 33a and the first and second spring seats 32b and 33b facing each other along the circumferential direction of the clutch piston 25 without the drive and driven claws 30 and 31 interposed therebetween. And a third spring holding member 34 having a third annular plate 34a projecting from the outer periphery of the plurality of third spring seat 34b to be.

  As shown in FIGS. 4 to 6, the first, second and third annular plates 32 a to 34 a are arranged coaxially with the clutch piston 25 between the clutch piston 25 and the turbine impeller 3. At that time, the first annular plate 32a, the third annular plate 34a, and the second annular plate 33a are arranged in order from the clutch piston 25 side.

  As shown in FIGS. 2, 3 and 7, a linear first coil spring 41 is contracted between the first and third spring seats 32b and 34b with a predetermined set load. Between the spring seats 33b and 34b, a second coil spring 42 which is also linear and has a larger spring constant than the first coil spring 41 is contracted with a predetermined set load.

The first to fourth spring seats 32b to 34b are provided with first to fourth connecting shafts 35 to 38, and an annular locking projection 43 is formed on the outer periphery of the tip of each connecting shaft 35 to 38. . On the other hand, at both end portions of the first and second coil springs 30, 31 are formed tightly wound portions 41a, 41a; 42a, 42a formed by winding the spring element wire several times, and the tightly wound portions 41a. , engaging as 42a is that while being fitted pressure on the outer periphery of the corresponding connecting shaft 35 to 38, the close winding portion 41a, the inner end of 42a is retained on the retaining projection 43 of the corresponding connecting shaft 35 to 38 Combined.

As shown in FIGS. 3 to 6, each of the spring seats 32b to 34b is welded to the annular plates 32a to 34a having the radially outer ends welded to each other and the radially inner ends corresponding to each other by rivets 46. A pair of spring seat plates 39, 39 'is formed, and both spring seat plates 39, 39' are opposed to each other with an interval 44 therebetween, and can be close to each other in the axial direction of the clutch piston 25. Elasticity is given. Each of the connecting shafts 35 to 38 is composed of a pair of connecting shaft halves 40 and 40 'having a semi-cylindrical cross section. , 39 'are joined by welding. At this time, the connecting shaft halves 40 and 40 'are arranged so as to face each other with a gap 45 therebetween, and the diameter of the connecting shaft halves 40 and 40' is reduced by the elastic mutual proximity of the pair of spring seat plates 39 and 39 '. It has become. Therefore, when the fitting pressure to the connecting shaft 35 to 38 which correspond to close winding portion 41a, 42a of the respective coil springs 30 and 31, accompanied each of the pair of spring seat plate 39, 39 'mutual elastic deformation The diameter of the connecting shafts 35 to 38 is reduced, and the tightly wound portions 41a and 42a can get over the locking projections 43, and the elastically repelling forces of the two spring seat plates 39 and 39 'allow the tightly wound portions 41a. , the connecting shaft 35 to 38 and the corresponding 42a, backlash-free pressure fitted state is ensured.

  The clutch piston 25 is fixedly provided with a plurality of support shafts 47a, 47... That protrude toward the turbine impeller 3 side and are arranged in the circumferential direction of the clutch piston 25. The clutch piston 25 is supported by a presser plate 48 that is riveted. These support shafts 47a, 47 ... have inner peripheral portions of the first, second and third annular plates 32a-34a through first, second and third roller bearings 55-57, which are individually operated. It is supported rotatably. On the outer peripheral surfaces of the outer races of the roller bearings 55 to 57, annular positioning grooves 55a to 57a for restricting the axial movement of the corresponding annular plates 32a to 34a are formed, whereby the annular plates 32a to 34a are mutually connected. Contact is avoided.

  In the above, the first, second and third annular plates 32a to 34a and the first, second and third spring seats 32b to 34b are formed of the first to fourth connecting shafts 35 to 38, and the first and second coils. The springs 30 and 31 are formed so as to be arranged on the same rotation plane P.

  Referring again to FIG. 1, a first oil passage 50 communicating with the outer chamber 22 b of the clutch chamber 22 through the lateral hole 29 and the thrust needle bearing 26 is provided at the center of the output shaft 10. A second oil passage 51 is defined between the auxiliary drive shaft 20 and the stator shaft 12 and communicates with the inner periphery of the circulation circuit 6 through the thrust needle bearings 27 and 27 ′ and the free wheel 11. The first oil passage 50 and the second oil passage 51 are alternately connected to the discharge side of the oil pump 21 and the oil reservoir 53 by a lock-up control valve 52.

  Next, the operation of this embodiment will be described.

  In the idling or extremely low speed operation region of the engine, the lockup control valve 52 connects the first oil passage 50 to the discharge side of the oil pump 21 as shown in FIG. It is controlled by an electronic control unit (not shown) so as to be connected to. Therefore, when the output torque of the crankshaft 1 of the engine is transmitted to the drive plate 8, the front cover 5, and the pump impeller 2 to rotate and drive the oil pump 21, the discharge operation of the oil pump 21 is performed. The oil sequentially flows from the lock-up control valve 52 into the circulation circuit 6 through the first oil passage 50, the lateral hole 29 and the thrust needle bearing 26, the outer chamber 22b of the clutch chamber 22, and the inner chamber 22a. Thereafter, the thrust needle bearings 27, 27 ′ and the free wheel 11 are sequentially transferred to the second oil passage 51, and then returned to the oil reservoir 53 from the lockup control valve 52.

  Thus, in the clutch chamber 22, the outer chamber 22 b has a higher pressure than the inner chamber 22 a due to the flow of the working oil as described above, and the clutch piston 25 is pulled away from the inner wall of the front cover 5 due to the pressure difference. Since it is pressed, the lock-up clutch L is in a disconnected state and allows relative rotation of the pump impeller 2 and the turbine impeller 3. Therefore, when the pump impeller 2 is driven to rotate from the crankshaft 1, the working oil filling the circulation circuit 6 circulates in the circulation circuit 6 as shown by the arrow, thereby reducing the rotational torque of the pump impeller 2 to the turbine blade. This is transmitted to the car 3 to drive the output shaft 10.

  At this time, if a torque amplifying action is generated between the pump impeller 2 and the turbine impeller 3, the accompanying reaction force is borne by the stator impeller 4, and the stator impeller 4 is caused by the locking action of the freewheel 11. Fixed.

  When the torque amplification operation is finished, the stator impeller 4 rotates in the same direction together with the pump impeller 2 and the turbine impeller 3 while idling the free wheel 11 due to the reversal of the torque direction received by the stator impeller 4.

  When the torque converter T is in such a coupling state, the lockup control valve 52 is switched by the electronic control unit. As a result, the oil discharged from the oil pump 21 flows into the circulation circuit 6 from the lock-up control valve 52 through the second oil passage 51 and fills the circuit 6, contrary to the previous operation, and then the clutch chamber 22. The inner chamber 22a is filled to fill the inner chamber 22a. On the other hand, the outer chamber 22b of the clutch chamber 22 is opened to the oil sump 53 via the first oil passage 50 and the lockup control valve 52. Therefore, in the clutch chamber 22, the inner chamber 22a is more than the outer chamber 22b. Due to the pressure difference, the clutch piston 25 is pressed toward the front cover 5 side, the friction lining 28 is pressed against the inner wall of the front cover 5, and the lockup clutch L is in a connected state. In this case, if the direction of rotation of the crankshaft 1 is the direction of arrow A in FIG. 2, the rotational torque transmitted from the crankshaft 1 to the pump impeller 2 is transmitted from the front cover 5 to the clutch piston 25, the drive claw 30, and the first spring. Since it is mechanically transmitted to the turbine impeller 3 via the seat 32b, the first coil spring 41, the third spring seat 34b, the second coil spring 42, the second spring seat 33b and the driven claw 31, the pump blade The vehicle 2 and the turbine impeller 3 are directly connected, and the output torque of the crankshaft 1 can be efficiently transmitted to the output shaft 10, thereby reducing fuel consumption.

  During this time, when torque fluctuation occurs between the pump impeller 2 and the turbine impeller 3, the first coil spring 41 having a low spring constant is first compressed between the first and third spring seats 32b and 34b, and the compression load is reduced. If it becomes more than a predetermined value, the 2nd coil spring 42 with a high spring constant will be compressed between the 2nd and 3rd spring seats 33b and 34b.

  By absorbing the torque shock in a stepwise manner, even a large torque shock generated between the pump impeller 2 and the turbine impeller 3 can be effectively absorbed.

By the way, the first and second coil springs 41 and 42 are connected to the tightly wound portions 41a and 42a at both ends of the first and third connecting shafts 35 and 37, and the second and fourth connecting shafts 36 and 38, respectively. pressure fit is the fact to the outer peripheral surface, close winding portion 41a of the locking projections 43 of the front end outer periphery of the connecting shaft 35 to 38 corresponding, by engaging the inner end of the 42a, first and second Even if a centrifugal force acts on the coil springs 41 and 42, friction and backlash do not occur between the connecting shafts 35 to 38 and the tightly wound portions 41a and 42a. A strong drag can be exerted to prevent the tightly wound portions 41a and 42a from coming out of the connecting shafts 35 to 38. For this reason, it is not necessary to provide a restricting member for restricting the bending due to the centrifugal force on the outer periphery of the first and second coil springs 41 and 42, and each coil spring can be operated even when the torque converter T rotates at a high speed. Thus, it is possible to avoid friction between the coil springs 41 and 42 and to generate hysteresis in the expansion and contraction of the coil springs 41 and 42, and the torque damper D can exhibit good torque buffering characteristics. In addition, since the first and second coil springs 41 and 42 are both inexpensive and linear, and the restriction member is eliminated, the cost of the torque damper D can be greatly reduced.

  The first, second and third annular plates 32a to 34a having the first, second and third spring seats 32b to 34b are arranged on the support shafts 47, 47. Since they are rotatably supported via the third ball bearings 55 to 57, they can smoothly rotate relative to each other as the first and second coil springs 42 expand and contract, and the shafts 47, 47. The frictional force generated between the first, second, and third annular plates 32a-34a is extremely small, and the first, second, and third annular plates 32a-34a are the outer races of the corresponding ball bearings 55-57. Since the guide grooves 55a to 57a are engaged with each other and do not come into contact with each other, the expansion and contraction of the coil springs 41 and 42 is hardly affected.

Incidentally, the respective connecting shafts 35 to 38, since the grant elasticity to allow reduced diameter in the radial direction, the tightly wound portion 41a of the respective connecting shafts 35 to 38, sometimes fitted pressure 42a, the connecting shaft 35 to 38 the elastic under compression can be performed easily fit the pressure, it is good assemblability.

Also, the spring seats 32b to 34b are coupled to each other at their radially outer ends, and their radially inner ends are coupled to the corresponding annular plates 32a to 34a, and can be close to each other in the axial direction of the clutch piston 25. A pair of spring seat plates 39 and 39 'having elasticity, and each of the connecting shafts 35 to 38 are coupled to the pair of spring seat plates 39 and 39' and face each other with a gap 45 therebetween. The shaft halves 40, 40 'are constituted by a pair of connecting shaft halves 40, 40' so that their diameter is reduced by the elastic mutual proximity of the pair of spring seat plates 39, 39 '. part 41a, when fitted pressure on each connecting shaft 35 to 38 of the 42a, will be stress generated by diameter of the connecting shaft 35 to 38 are dispersed in each spring seat 32B～34b, the connecting shaft 35 to 38 And stress on the spring seats 32b to 34b By avoiding middle, it is possible to ensure their durability.

  Next, a second embodiment of the present invention shown in FIG. 8 will be described.

  In the second embodiment, the pair of spring seat plates 39, 39 'constituting the spring seats 32b to 34b is formed by bending a single steel plate into a U shape, and the bent portion is a pair of springs. A connecting portion between the seat plates 39, 39 'is formed. Since other configurations are the same as those of the previous embodiment, portions corresponding to those of the previous embodiment in FIG. 8 are denoted by the same reference numerals, and redundant description is omitted.

  Next, a third embodiment of the present invention will be described.

  In the third embodiment, instead of the first, second and third ball bearings 55 to 57 in the first embodiment, the inner circumference of the first, second and third annular plates 34a is provided by a common roller 58. The guide groove 55a-57a with which the inner peripheral part of the 1st, 2nd and 3rd annular plate 34a engages is provided in the outer peripheral surface of the roller 58. As shown in FIG.

  According to the third embodiment, the first and second coil springs 42 are expanded and contracted by the simple structure between the support shafts 47, 47... And the first, second and third annular plates 32a to 34a. The generated frictional force can be reduced as much as possible, and the cost can be reduced.

  Finally, a fourth embodiment of the present invention shown in FIG. 10 will be described.

  In the fourth embodiment, a pair of drive pawls 30, 30 fixed to the clutch piston 25 are arranged at intervals in the radial direction of the clutch piston 25, and are a single follower fixed to the turbine impeller 3. The claw 31 is disposed so as to intervene between the pair of drive claws 30.

  According to the fourth embodiment, torque can be transmitted from the driving and driven claws 30, 31 to the first and second spring seats 32b, 33b in a well-balanced manner, and the first and second spring seats 32b, 33b Durability can be increased. Note that the same effect can be obtained even if a pair of driven claws 31 and a single drive claw 30 are used.

  The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention. For example, the present invention can be applied to a fluid coupling that does not have a stator impeller. Further, the spring constants of the first and second coil springs 41 and 42 can be made the same. Further, a plurality of third spring holding members 34 may be arranged, and other linear springs similar to the first and second coil springs 41 and 42 may be arranged between the third spring holding members. .

D ･ ･ ･ Torque damper L ･ ･ ･ Lockup clutch T ･ ･ ･ Hydraulic transmission (torque converter)
3 .... turbine impeller 25 ... clutch piston 30 ... driving claw 31 ... driven claw 32 ... first spring holding member 32a ... First annular plate 32b ... first spring seat 33 ... second spring holding member 33a ... second annular plate 33b ... second spring seat 34 ... third Spring holding member 34a ... third annular plate 34b ... third spring seat 35 ... first connecting shaft 36 ... second connecting shaft 37 ... third connecting Shaft 38 ... fourth connecting shaft 39, 39 '... spring seat plate 40, 40' ... connecting shaft half 41 ... first coil spring 42 ... second Coil spring 43 ··· Locking protrusion 45 ··· Gap 47 ··· Spindle 55 ··· Rolling member (first roller bearing)
56 ... Rolling member (second roller bearing)
57 Rolling member (third roller bearing)
58 ... Rolling member (roller)

Claims (8)

The first and second coil springs (41, 42) are alternately arranged along the circumferential direction of the clutch piston (25) between the clutch piston (25) of the lockup clutch (L) and the turbine impeller (3). There are a plurality of drive claws (30) and driven claws (1) fixed to the clutch piston (25) and the turbine impeller (3), respectively, between some of the first and second coil springs (41, 42). 31) is inserted so as to be relatively rotatable, and a third spring is held between the other first and second coil springs (41, 42) so as to be relatively rotatable with the drive claw (30) and the driven claw (31). In the torque damper of the fluid transmission device, in which the member (34) is inserted,
A first spring holding member (32) having a first annular plate (32a) having a plurality of first spring seats (32b) projecting on the outer periphery, and driving and driven pawls along the circumferential direction of the clutch piston (25) ( 30, 31) a second spring holding member (33) having a second annular plate (33 a) with a plurality of second spring seats (33 b) facing the first spring seat (32 b) protruding from the outer periphery. ) And the first and second spring seats (32b, 33b) facing each other along the circumferential direction of the clutch piston (25) without the drive and driven pawls (30, 31). A third spring holding member (34) having a third annular plate (34a) projecting from the outer periphery of a third spring seat (34b) is disposed coaxially with the clutch piston (25) so as to be relatively rotatable;
First and third connecting shafts (35, 37) projecting from each other on the opposing surfaces of the first and third spring seats (32b, 34b) respectively project, and the second and third spring seats. (33b, 34b) are provided with second and fourth connecting shafts (36, 38) projecting from each other, with their tips opposed to each other,
Wherein the outer peripheral surface of the first connecting shaft (35) and the third connecting shaft (37), to fit tightly wound portion formed at both ends of the straight said first coil spring (41) and (41a) pressure,
The outer peripheral surface of the second connecting shaft (36) and the fourth connecting shaft (38), to fit pressure close winding portions formed on both ends of the straight said second coil spring (42) and (42a),
Each of the spring seats (32b to 34b) is connected to the radially outer ends thereof and the radially inner ends to the corresponding annular plates (32a to 34a), and in the axial direction of the clutch piston (25). It is composed of a pair of spring seat plates (39, 39 ') having elasticity that allows them to be close to each other, and the coupling shafts (35-38) are coupled to the pair of spring seat plates (39, 39'), respectively. The pair of connecting shaft halves (40, 40 ') are opposed to each other with a gap (44) therebetween, and the pair of connecting shaft halves (40, 40') are the pair of spring seat plates. The fluid transmission device is characterized in that the diameter is reduced by the elastic proximity of (39, 39 '), and elasticity is provided to each connecting shaft (35-38) to enable diameter reduction in the radial direction. Torque damper. The first and second coil springs (41, 42) are alternately arranged along the circumferential direction of the clutch piston (25) between the clutch piston (25) of the lockup clutch (L) and the turbine impeller (3). There are a plurality of drive claws (30) and driven claws (1) fixed to the clutch piston (25) and the turbine impeller (3), respectively, between some of the first and second coil springs (41, 42). 31) is inserted so as to be relatively rotatable, and a third spring is held between the other first and second coil springs (41, 42) so as to be relatively rotatable with the drive claw (30) and the driven claw (31). In the torque damper of the fluid transmission device, in which the member (34) is inserted,
A first spring holding member (32) having a first annular plate (32a) having a plurality of first spring seats (32b) projecting on the outer periphery, and driving and driven pawls along the circumferential direction of the clutch piston (25) ( 30, 31) a second spring holding member (33) having a second annular plate (33 a) with a plurality of second spring seats (33 b) facing the first spring seat (32 b) protruding from the outer periphery. ) And the first and second spring seats (32b, 33b) facing each other along the circumferential direction of the clutch piston (25) without the drive and driven pawls (30, 31). A third spring holding member (34) having a third annular plate (34a) projecting from the outer periphery of a third spring seat (34b) is disposed coaxially with the clutch piston (25) so as to be relatively rotatable;
First and third connecting shafts (35, 37) projecting from each other on the opposing surfaces of the first and third spring seats (32b, 34b) respectively project, and the second and third spring seats. (33b, 34b) are provided with second and fourth connecting shafts (36, 38) projecting from each other, with their tips opposed to each other,
The tightly wound portions (41a) formed at both ends of the linear first coil spring (41) are press-fitted to the outer peripheral surfaces of the first connecting shaft (35) and the third connecting shaft (37),
A tightly wound portion (42a) formed at both ends of the linear second coil spring (42) is press-fitted to the outer peripheral surfaces of the second connecting shaft (36) and the fourth connecting shaft (38),
Plurally supporting the first annular plate (32a), the second annular plate (33a) and the third annular plate (34a) on the clutch piston (25) via rolling members (55 to 58). The support shaft (47) is provided,
First, second and third ball bearings (55-55) for supporting the rolling member individually on the first annular plate (32a), the second annular plate (33a) and the third annular plate (34a), respectively. 57) A torque damper for a fluid transmission device. The first and second coil springs (41, 42) are alternately arranged along the circumferential direction of the clutch piston (25) between the clutch piston (25) of the lockup clutch (L) and the turbine impeller (3). There are a plurality of drive claws (30) and driven claws (1) fixed to the clutch piston (25) and the turbine impeller (3), respectively, between some of the first and second coil springs (41, 42). 31) is inserted so as to be relatively rotatable, and a third spring is held between the other first and second coil springs (41, 42) so as to be relatively rotatable with the drive claw (30) and the driven claw (31). In the torque damper of the fluid transmission device, in which the member (34) is inserted,
A first spring holding member (32) having a first annular plate (32a) having a plurality of first spring seats (32b) projecting on the outer periphery, and driving and driven pawls along the circumferential direction of the clutch piston (25) ( 30, 31) a second spring holding member (33) having a second annular plate (33 a) with a plurality of second spring seats (33 b) facing the first spring seat (32 b) protruding from the outer periphery. ) And the first and second spring seats (32b, 33b) facing each other along the circumferential direction of the clutch piston (25) without the drive and driven pawls (30, 31). A third spring holding member (34) having a third annular plate (34a) projecting from the outer periphery of a third spring seat (34b) is disposed coaxially with the clutch piston (25) so as to be relatively rotatable;
First and third connecting shafts (35, 37) projecting from each other on the opposing surfaces of the first and third spring seats (32b, 34b) respectively project, and the second and third spring seats. (33b, 34b) are provided with second and fourth connecting shafts (36, 38) projecting from each other, with their tips opposed to each other,
The tightly wound portions (41a) formed at both ends of the linear first coil spring (41) are press-fitted to the outer peripheral surfaces of the first connecting shaft (35) and the third connecting shaft (37),
A tightly wound portion (42a) formed at both ends of the linear second coil spring (42) is press-fitted to the outer peripheral surfaces of the second connecting shaft (36) and the fourth connecting shaft (38),
Plurally supporting the first annular plate (32a), the second annular plate (33a) and the third annular plate (34a) on the clutch piston (25) via rolling members (55 to 58). The support shaft (47) is provided,
The rolling member is composed of a common roller (58) for supporting the first annular plate (32a), the second annular plate (33a), and the third annular plate (34a). Transmission device torque damper. The torque damper of the fluid transmission device according to claim 1 ,
Plurally supporting the first annular plate (32a), the second annular plate (33a) and the third annular plate (34a) on the clutch piston (25) via rolling members (55 to 58). A torque damper for a fluid transmission device, characterized in that a support shaft (47) is provided. In the torque damper of the fluid transmission device according to claim 2 or 3 ,
A torque damper for a fluid transmission device, wherein each of the connecting shafts (35 to 38) is provided with an elasticity that enables a radial diameter reduction. In the torque damper of the fluid transmission device according to claim 5 ,
Each of the spring seats (32b to 34b) is connected to the radially outer ends thereof and the radially inner ends to the corresponding annular plates (32a to 34a), and in the axial direction of the clutch piston (25). It is composed of a pair of spring seat plates (39, 39 ') having elasticity that allows them to be close to each other, and the coupling shafts (35-38) are coupled to the pair of spring seat plates (39, 39'), respectively. The pair of connecting shaft halves (40, 40 ') are opposed to each other with a gap (44) therebetween, and the pair of connecting shaft halves (40, 40') are formed of the pair of spring seat plates. A torque damper for a fluid transmission device, wherein the diameter is reduced by the elastic proximity of (39, 39 '). In the torque damper of the fluid transmission device according to any one of claims 1 to 6 ,
A torque damper for a fluid transmission device, wherein the first and second coil springs (41, 42) have different spring constants. In the torque damper of the fluid transmission device according to any one of claims 1 to 7 ,
The outer periphery of each of the connecting shafts (35 to 38) is engaged with the inner end of the corresponding tightly wound portion (41a, 42a) and the corresponding connecting shaft (35 to 35a) of the tightly wound portion (41a, 42a). characterized in that the formation of the locking projection (43) to prevent fastened securely out from 38), a torque damper for the hydraulic power transmission device.

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