JP5497703B2 - Torque damper of fluid transmission device - Google Patents

Description

  In the present invention, a cylindrical housing connected to one of them is disposed between a clutch piston of a lock-up clutch and a rear surface of a turbine impeller facing the clutch piston. A plurality of spring assemblies composed of a plurality of linear coil springs that are arranged in the circumferential direction of the cylindrical housing with a set load of are arranged, and a clutch piston is disposed between opposing ends of adjacent spring assemblies. And a drive member and a follower member fixed to the turbine impeller and capable of rotating relative to each other, and between the coil springs adjacent to each other in each spring assembly, radially outward from the coil springs. The present invention relates to a torque damper for a fluid transmission device, in which an intermediate spring seat member that receives an urging force is interposed, and a roller that can roll the inner peripheral surface of the cylindrical housing is provided on the intermediate spring seat member.

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

JP 2008-106855 A

  Conventionally, in the torque damper of such a fluid transmission device, a concave portion that opens toward the inner peripheral surface of the cylindrical housing is formed in the intermediate spring seat member, and the roller is rotatably fitted in the concave portion. During rotation, a relatively large friction is generated between the outer peripheral surface of the large-diameter roller and the inner peripheral surface of the recess, and the friction resistance causes hysteresis in the expansion and contraction of each coil spring, which adversely affects the torque buffering characteristics. Become.

  The present invention has been made in view of such circumstances, and suppresses friction generated between the roller and the intermediate spring seat member as much as possible, and at the same time, prevents the roller from tilting. An object of the present invention is to provide a torque damper of a fluid transmission device that can roll on an inner peripheral surface and can stabilize torque buffering characteristics.

In order to achieve the above object, according to the present invention, a cylindrical housing connected to one of them is disposed between a clutch piston of a lock-up clutch and a rear surface of a turbine impeller opposed thereto. A plurality of spring assemblies comprising a plurality of linear coil springs arranged in the circumferential direction of the cylindrical housing by applying a set load in the compression direction are arranged in the cylindrical housing, and the adjacent spring assemblies are arranged. A driving member and a driven member, which are fixed to the clutch piston and the turbine impeller and are rotatable relative to each other, are interposed between the opposed ends, and between the adjacent coil springs in each of the spring assemblies. An intermediate spring seat member that receives a biasing force radially outward from both coil springs is interposed, and a fluid that is provided on the intermediate spring seat member with a roller that can roll the inner peripheral surface of the cylindrical housing. Transmission In the torque damper, the intermediate spring seat member is provided with a roller receiving recess that opens toward the inner peripheral surface of the cylindrical housing, and a pair of bearing holes that open on both side surfaces of the roller receiving recess, and the roller receiving recess The support shaft that protrudes from both side surfaces of the roller is rotatably supported in the bearing hole so that the roller floats from the inner peripheral surface of the roller receiving recess, and the cylindrical housing The first feature is that side walls opposed to both side surfaces of the intermediate spring seat member are continuously provided, and slide ribs slidably contacting the side walls protrude from both side surfaces of the intermediate spring seat member. . In addition, the said side wall respond | corresponds to the clutch piston 21 and the spring holder 38 in embodiment of this invention mentioned later.
This is the first feature.

Further, according to the present invention, a cylindrical housing connected to one of the clutch piston of the lockup clutch and the rear surface of the turbine impeller facing the clutch piston is disposed, and the cylindrical housing is compressed in the cylindrical housing. A plurality of linear spring assemblies, each of which is provided with a set load in the direction and arranged in the circumferential direction of the cylindrical housing, and between the opposing ends of the adjacent spring assemblies, the clutch A drive member and a follower member, which are fixed to the piston and the turbine impeller and are rotatable relative to each other, are interposed, and between the adjacent coil springs in each of the spring assemblies, radially outward from both coil springs. In a torque damper of a fluid transmission device, comprising an intermediate spring seat member that receives a biasing force toward the direction, and a roller capable of rolling the inner peripheral surface of the cylindrical housing is provided on the intermediate spring seat member. The intermediate spring seat member is provided with a roller receiving recess that opens toward the inner peripheral surface of the cylindrical housing, and a pair of bearing holes that open on both side surfaces of the roller receiving recess, and the roller receiving recess is provided with the roller And a support shaft projecting from both side surfaces of the roller is rotatably supported in the bearing hole so that the roller floats from the inner peripheral surface of the roller housing recess, and the outermost coil of the spring assembly is An outer spring seat member that contacts the drive and driven members in a separable manner is connected to the outer end portion of the spring. When the outer spring seat member is in a contact position with the drive member, the outer spring seat member A first restricting portion for restricting the outward movement of the outer spring seat is provided in the cylindrical housing, and the outer spring seat member is engaged with the driven member in the radially outer direction of the outer spring seat member. Restricted movement to That was provided second restricting portion and the second feature that. The first restricting portion and the second restricting portion respectively correspond to a restricting wall 31a and a positioning groove 44d in an embodiment of the present invention described later.

According to the present invention, in addition to the first or second feature, the intermediate spring seat member protrudes from a spring seat with which the opposing end surfaces of the two coil springs contact the intermediate spring seat member. A third feature is that a connecting shaft that is fitted to the inner peripheral surface of the opposite end of the projection is provided.

In addition to the third feature of the present invention, the roller receiving recess is formed so as to fit within a region connecting the connecting shafts of the intermediate spring seat member in plan view from the outer peripheral side of the cylindrical housing. that were you with the fourth aspect.

According to the onset bright, to absorb the torque fluctuation between the clutch piston and the turbine impeller, when the coil springs in a spring assembly expands and contracts, the circumferential intermediate spring seat member for connecting the coil spring to each other of the cylindrical housing Although the roller moves along the direction, the roller supported by the intermediate spring seat member rolls on the inner peripheral surface of the cylindrical housing, so that the intermediate spring seat member moves smoothly. In particular, the roller has a smaller-diameter support shaft projecting from both end faces thereof rotatably supported in the bearing hole of the intermediate spring seat member, and floats from the inner peripheral surface of the roller housing recess of the intermediate spring seat member. Therefore, the outer peripheral surface of the roller does not come into contact with the intermediate spring seat member, and the frictional resistance that the roller receives during its rotation is a small frictional resistance generated between the small-diameter support shaft and the bearing hole. Therefore, the roller can roll on the inner peripheral surface of the cylindrical housing very smoothly, so that almost no hysteresis is generated in the expansion and contraction of each coil spring, and the torque damper exhibits a good torque buffering characteristic. Can do.

In particular, according to the first feature of the present invention, the movement of the intermediate spring seat member in the axial direction is restrained by the slide ribs formed on both side surfaces thereof coming into contact with the side wall. At this time, the thrust load acting on the intermediate spring seat member is extremely small, and the slide rib can smoothly slide on the side wall, so that the frictional resistance against the movement of the intermediate spring seat member can be kept small.

Further, particularly according to the second feature of the present invention, the movement of the outer member in the radial direction is always restricted by the restriction by the first and second restricting portions, even when the driving and driven members are relatively rotated. The non-contact state with the cylindrical housing inner peripheral surface of the coil spring supported by the spring seat member can be maintained.

In particular , according to the third feature of the present invention, the end surface of the coil spring is brought into contact with the spring seat of the intermediate spring seat member, and the inner peripheral surface of the end portion of the coil spring is fitted to the connecting shaft of the intermediate spring seat member. By combining, the support of the coil spring by the intermediate spring seat member is stabilized, and the contact of the coil spring with the inner peripheral surface of the cylindrical housing can be reliably prevented.

In particular , according to the fourth feature of the present invention , even if the inner diameter of the roller accommodating recess is set large so as to accommodate a large-diameter roller, the thickness of each part of the intermediate spring seat member around the roller accommodating recess is sufficiently obtained. it can, Ru can ensure the strength of the intermediate spring seat member.

The half longitudinal section side view of the torque converter with a torque damper concerning the embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line 2-2 of FIG. 1 showing the torque damper in a free state. FIG. 3 is an enlarged vertical sectional view of a part 3 in FIG. 2. FIG. 4 is a sectional view taken along line 4-4 of FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. The disassembled perspective view of an intermediate spring seat member and a roller. FIG. 3 is a view corresponding to FIG. 2 showing an operating state of a torque damper accompanying acceleration or deceleration operation of the engine.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  First, in FIG. 1, a torque converter T as a fluid transmission device includes a pump impeller 2, a turbine impeller 3 opposed thereto, and a stator impeller 4 disposed between the inner peripheral portions thereof, Between these three impellers 2, 3 and 4, a circulation circuit 6 for power transmission by the working oil is defined.

  A transmission cover 5 that covers the outer surface of the turbine impeller 3 is integrally connected to the pump impeller 2 by welding. A mounting boss 7 is welded to the outer peripheral surface of the transmission cover 5, and a drive plate 8 coupled to the crankshaft 1 of the engine is fixed to the mounting boss 7 with a bolt 9. A thrust needle bearing 10 is interposed between the hub 3 h of the turbine impeller 3 and the transmission cover 5.

  An output shaft 11 arranged coaxially with the crankshaft 1 is disposed at the center of the torque converter T. The output shaft 11 is splined to the hub 3h of the turbine impeller 3 and at the same time a hub 5h at the center of the transmission cover 5 The bearing bush 12 is rotatably supported. The output shaft 11 is a main shaft of a multi-stage transmission (not shown).

  A cylindrical stator shaft 14 for supporting the hub 4h of the stator impeller 4 via the one-way clutch 13 is disposed on the outer periphery of the output shaft 11, and the relative relationship between the output shaft 11 and the stator shaft 14 is relative to the output shaft 11. A bearing bush 15 that allows rotation is interposed. The outer end portion of the stator shaft 14 is supported by the mission case 16 so as not to rotate.

  Thrust needle bearings 17 and 17 ′ 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 18 coupled to the pump impeller 2 is disposed on the outer periphery of the stator shaft 14 so as to be relatively rotatable. An oil pump 19 that supplies hydraulic oil to the torque converter T is provided by the auxiliary machine drive shaft 18. Driven.

  The turbine impeller 3 and the transmission cover 5 define a clutch chamber 20 therebetween, and a lockup clutch L that can directly connect the turbine impeller 3 and the transmission cover 5 is accommodated in the clutch chamber 20. The clutch chamber 21 is divided into an inner chamber 20a on the turbine impeller 3 side and an outer chamber 20b on the transmission cover 5 side by the clutch piston 21 that forms the main body of the lockup clutch L.

  A friction lining 23 is attached to the side surface of the clutch piston 21 that faces the inner surface of the transmission cover 5. The clutch piston 21 is slidably supported on the outer peripheral surface of the hub 3h of the turbine impeller 3, and a clutch-on position where the friction lining 23 is pressed against the inner surface of the transmission cover 5 and a clutch separated from the inner wall. It can move in the axial direction between the off positions.

  A first oil passage 26 is provided in the central portion of the output shaft 11, and the first oil passage is formed in the outer chamber 20 b of the clutch chamber 20 through the lateral hole 24 and a through groove 25 on the side of the thrust needle bearing 10. Communicate. A second oil passage 27 is defined between the auxiliary machine drive shaft 18 and the stator shaft 14, and this second oil passage 27 is connected to the circulation circuit through the thrust needle bearings 17 and 17 ′ and the one-way clutch 13. 6 communicates with the inner periphery. The first oil passage 26 and the second oil passage 27 are alternately connected to the discharge side of the oil pump 19 and the oil reservoir 30 by a lock-up control valve 28.

  The clutch chamber 20 is provided with a torque damper D according to the present invention that buffers the clutch piston 21 and the turbine impeller 3. The torque damper D will be described next.

  1 and 2, the torque damper D includes a cylindrical housing 31, a plurality of sets (three sets in the illustrated example) spring assemblies 34, 34..., And the same number of drive members 36 as the spring assemblies 34, 34. , 36... And driven members 37, 37.

  As shown in FIGS. 1 and 4, the cylindrical housing 31 is formed to bend from the outer peripheral edge of the clutch piston 21 toward the turbine impeller 3 side. A plurality of spring holders 38, 38... Are secured to the clutch piston 21 by rivets 41 so as to cover the open end of the cylindrical housing 31 with a certain interval in the circumferential direction. Thus, an annular spring chamber 33 is defined by the clutch piston 21, the cylindrical housing 31 and the spring holders 38, 38..., And a plurality of sets of spring assemblies 34, 34.

  Each drive member 36 includes a base portion 36a fixed to the clutch piston 21 by a rivet 42 between spring holders 38, 38... Arranged in the circumferential direction of the cylindrical housing 31, and an inner periphery of the cylindrical housing 31 protruding from the base portion 36a. The U-shaped portion 36b is disposed close to the surface, and the U-shaped portion 36b opens the side opposite to the clutch piston 21.

  Each driven member 37 is fixed to the rear surface of the turbine impeller 3 by welding, and the tip portion thereof is disposed in the U-shaped portion 36b of the driving member 36 in a non-contact state, and the tip portion is rotated. Both ends in the direction protrude from the U-shaped portion 36b. These driving and driven members 36 and 37 are adapted to rotate relative to the clutch piston 21 and the turbine impeller 3 relative to each other.

  As shown in FIGS. 2 to 5, each spring assembly 34 includes a plurality of (three in the illustrated example) linear coil springs 43, 43... Arranged along the inner peripheral surface of the cylindrical housing 31. And an outer spring seat member 44 that contacts the driving member 36 and the driven member 37 while supporting the outer end portion of the outermost coil spring 43, and the adjacent coil springs 43, 43. And a predetermined compression set load is applied to each coil spring 43. A short auxiliary coil spring 46 is accommodated in the hollow portion of each coil spring 43.

  The outer spring seat member 44 is made of synthetic resin, and at one end thereof, a spring seat 44a that supports the outer end surface of the coil spring 43 at the outermost position, and a projection of the coil spring 43 protruding from the spring seat 44a. A connecting shaft 44b that is lightly press-fitted into the inner peripheral surface of the outer end is provided at one end, and a contact surface 44c that contacts the U-shaped portion 36b of the drive member 36 is provided at the other end.

  When the outer spring seat member 44 is in a contact position with the drive member 36, the cylindrical housing 31 has an arc-shaped regulating wall 31 a that restricts the outward movement of the outer spring seat member 44 in the radial direction. It is formed by recessing a part of the housing 31 inward in the radial direction. Further, the driven member 37 receives a portion protruding to the outside of the U-shaped portion 36b, and a general surface on the inner periphery of the cylindrical housing 31 of the outer spring seat member 44 (that is, an inner peripheral surface other than the restriction wall 31a). A positioning groove 44d is provided to prevent contact with the positioning groove 44d.

  On the other hand, the intermediate spring seat member 45 is also made of synthetic resin, and a pair of spring seats 45a and 45a for supporting opposite end surfaces of the two coil springs 43 and 43 disposed on both sides of the intermediate spring seat member 45, respectively. A pair of connecting shafts 45b and 45b are provided which protrude from the spring seats 45a and 45a and are lightly press-fitted into the inner peripheral surfaces of the opposing ends of the two coil springs 43 and 43, respectively.

  Further, a central portion of the intermediate spring seat member 45 has a roller receiving recess 47 that opens toward the inner peripheral surface of the cylindrical housing 31, and penetrates both side walls of the roller receiving recess 47, and the inside of the cylindrical housing 31. A pair of bearing holes 48, 48 that open toward the circumferential surface and also have a semi-cylindrical bottom surface are provided. At that time, as shown in FIG. 5, the roller accommodating recess 47 is accommodated in a region S (shaded portion in FIG. 5) connecting the pair of connecting shafts 45b and 45b in a plan view from the outer peripheral side of the cylindrical housing 31. Formed.

  As shown in FIGS. 3 to 5, the roller 50 is accommodated in the roller accommodating recess 47. The roller 50 has a support shaft 51 protruding from both axial end surfaces thereof, and the support shaft 51 is rotatably supported on the bottoms of the bearing holes 48 and 48. By this support, the roller 50 is floated from the inner peripheral surface of the roller accommodating recess 47 and is disposed so that a part is exposed from the roller accommodating recess 47 and is in contact with the inner peripheral surface of the cylindrical housing 31. Thus, the roller 50 can roll on the inner peripheral surface of the cylindrical housing 31. The support shaft 51 is formed integrally with the roller 50 or formed as a single continuous metal rod-shaped support shaft that is separate from the roller 50 and attached to the roller 50 in a skewered manner.

  The pair of connecting shafts 45b and 45b form an obtuse angle .theta. Along the central axes Y and Y of the two coil springs 43 and 43 fitted therein, and the two coil springs 43 and 43. The intermediate spring seat member 45 is urged radially outward by the compression set load, and the roller 50 is pressed against the inner peripheral surface of the cylindrical housing 31.

  Thus, the coil spring 43 supported by the outer spring seat member 44 and the intermediate spring seat member 45 is prevented from contacting the inner peripheral surface of the cylindrical housing 31.

  Further, on both side surfaces of the intermediate spring seat member 45 aligned in the axial direction of the cylindrical housing 31, a slide that slidably contacts the inner surface of the spring chamber 33, that is, the clutch piston 21 and the spring holders 38, 38. The rib 52 is integrally formed. The slide rib 52 is slidably brought into contact with the clutch piston 21 and the spring holders 38, 38... To prevent the coil springs 43, 43 from contacting the clutch piston 21 and the spring holders 38, 38. It has become.

  Each of the spring holders 38 is provided with a guide groove 38a that can receive the end of the drive member 36 when the drive member 36 and the driven member 37 are relatively rotated.

  Next, the operation of this embodiment will be described.

  In the engine idling or extremely low speed operation region, the lockup control valve 28 connects the first oil passage 26 to the discharge side of the oil pump 19 and the second oil passage 27 as an oil reservoir 30 as shown in FIG. It is controlled by an electronic control unit (not shown) so as to be connected to. Therefore, the output torque of the crankshaft 1 of the engine is transmitted to the drive plate 8, the transmission cover 5, and the pump impeller 2 to rotate and further drive the oil pump 19. After the discharged working oil flows into the circulation circuit 6 from the lockup control valve 28 through the first oil passage 26, the lateral hole 24 and the through hole 25, and the outer chamber 20b of the clutch chamber 20 in order, the circuit 6 is filled. Then, the thrust needle bearings 17 and 17 ′ and the one-way clutch 13 are sequentially passed to the second oil passage 27, and return to the oil reservoir 30 from the lockup control valve 28.

  Thus, in the clutch chamber 20, the outer chamber 20 b has a higher pressure than the inner chamber 20 a due to the flow of the working oil as described above, and the clutch piston 21 is pulled away from the inner wall of the transmission cover 5 due to the pressure difference. Since it is pressed, the lock-up clutch L is in an OFF state, and the relative rotation of the pump impeller 2 and the turbine impeller 3 is allowed. Therefore, when the pump impeller 2 is rotationally driven from the crankshaft 1, the working oil that fills the circulation circuit 6 circulates in the circulation circuit 6 as indicated by an arrow, so that the rotational torque of the pump impeller 2 is reduced to the turbine blade. This is transmitted to the car 3 to drive the output shaft 11.

  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 locks the one-way clutch 13. It is fixed by.

  When the torque amplifying 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 one-way clutch 13 by reversing the torque direction received by the stator impeller 4.

  When the torque converter T enters such a coupling state, the lockup control valve 28 is switched by the electronic control unit. As a result, the discharge hydraulic oil of the oil pump 19 flows into the circulation circuit 6 from the lockup control valve 28 via the second oil passage 27 and fills the circuit 6, contrary to the previous time, and then the clutch chamber 20. The inner chamber 20a is filled with the inner chamber 20a. On the other hand, since the outer chamber 20b of the clutch chamber 20 is opened to the oil sump 30 via the first oil passage 26 and the lockup control valve 28, in the clutch chamber 20, the inner chamber 20a is more than the outer chamber 20b. Due to the pressure difference, the clutch piston 21 is pressed to the transmission cover 5 side, the friction lining 23 is pressed against the inner wall of the transmission cover 5, and the lockup clutch L is turned on. Therefore, the rotational torque transmitted from the crankshaft 1 to the pump impeller 2 is mechanically transmitted from the transmission cover 5 to the turbine impeller 3 via the clutch piston 21, the drive member 36, the spring assembly 34 and the driven member 37. As a result, the pump impeller 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 11, thereby reducing fuel consumption.

  When torque fluctuation occurs between the pump impeller 2 and the turbine impeller 3 with the acceleration or deceleration operation of the engine in such an on state of the lockup clutch, the clutch piston 21 is connected as shown in FIG. The drive member 36 and the driven member 37 connected to the turbine impeller 3 rotate relatively, and the plurality of coil springs 43, 43... Of each spring assembly 34 are composed of an outer spring seat member 44 and an intermediate spring seat member. 45, or between the intermediate spring seat members 45.

  When the relative rotation of the drive member 36 and the driven member 37 proceeds beyond a predetermined angle, the auxiliary coil spring 46 in each coil spring 43 is moved between the outer spring seat member 44 and the intermediate spring seat member 45 or the intermediate spring. The auxiliary coil spring 46 is also compressed between the seat members 45.

  As described above, the stepwise compression deformation of the coil spring 43 and the auxiliary coil spring 46 increases the total repulsive force of the spring in a non-linear manner, thereby effectively preventing the torque shock generated between the pump impeller 2 and the turbine impeller 3. Can be absorbed.

  By the way, in each spring assembly 34, each coil spring 43 is supported at both ends by the outer spring seat member 44 and the intermediate spring seat member 45, or between the intermediate spring seat members 45, and inside the cylindrical housing 31 during expansion and contraction. There is no contact with the peripheral surface. As the coil spring 43 expands and contracts, the intermediate spring seat member 45 that connects the coil springs 43, 43 moves along the circumferential direction of the cylindrical housing 31, but is supported by the intermediate spring seat member 45. As the roller 50 rolls on the inner peripheral surface of the cylindrical housing 31, the intermediate spring seat member 45 moves smoothly.

  In particular, the roller 50 is rotatably supported by a pair of bearing holes 48 of the intermediate spring seat member 45 with a support shaft 51 having a smaller diameter projecting from both end surfaces thereof. Since it floats from the inner peripheral surface, the outer peripheral surface of the roller 50 does not come into contact with the intermediate spring seat member 45. The axial movement of the roller 50 is constrained by both inner side surfaces of the roller receiving recess 47, but the thrust load acting on the roller 50 is extremely small. The resulting frictional resistance is negligibly small.

  After all, the frictional resistance that the roller 50 receives during the rotation becomes a small frictional resistance generated between the small-diameter support shaft 51 and the bearing hole 48, and the roller 50 extremely smoothly moves the inner peripheral surface of the cylindrical housing 31. Thus, almost no hysteresis is generated in the expansion and contraction of each coil spring 43, and the torque damper D can exhibit a good torque buffering characteristic.

  In addition, since the support shaft 51 protruding from both end faces of the roller 50 is supported by the pair of bearing holes 48 of the intermediate spring seat member 45, the support type of the roller 50 is a double-supported type, so that the roller 50 is always inclined. It is possible to smoothly roll the inner peripheral surface of the cylindrical housing 31 with a stable posture, so that it rides on an arcuate inner corner between the cylindrical housing 31 and the clutch piston 21 or opens the cylindrical housing 31. There is no movement that causes the wheel to come off the edge.

  Further, the axial movement of the intermediate spring seat member 45 is restricted by the slide ribs 52 formed on both side surfaces of the intermediate spring seat member 45 coming into contact with both inner side surfaces of the spring chamber 33, that is, the inner side surfaces of the clutch piston 21 and the spring holder 38. . At this time, the thrust load acting on the intermediate spring seat member 45 is extremely small, and the slide rib 52 can slide smoothly on the inner surface of the spring chamber 33, so that the frictional resistance against the movement of the intermediate spring seat member 45 is also kept small. be able to.

  In addition, the roller accommodating recess 47 is formed so as to be within a region S (see FIG. 4) connecting the pair of connecting shafts 45a and 45a in a plan view of the intermediate spring seat member 45 from the outer peripheral side of the cylindrical housing 31. Therefore, even if the inner diameter of the roller accommodating recess 47 is set large so as to accommodate the large-diameter roller 50, the thickness of each part of the intermediate spring seat member 45 around the roller accommodating recess 47 can be sufficiently obtained. The strength of the member 45 can be ensured.

  Further, when the driving and driven members 36 and 37 are rotated relative to each other, the outer spring seat member 44 that maintains the contact position with the driving member 36 is moved outward in the radial direction by the restriction wall 31 a of the cylindrical housing 31. The other outer spring seat member 44 receives the follower member 37 in its positioning groove 44d and restricts its outward movement in the radial direction. Therefore, any of the outer spring seat members 44, 44 has a cylindrical housing. 31 is maintained in a non-contact state with the general surface of the inner periphery.

  The present invention is not limited to the above-described embodiment, and various design changes can be made without departing from the gist thereof. For example, the number of coil springs of each spring assembly 34 may be three or more, and the spring assembly 34 may be two sets or four sets or more, and the cylindrical housing 31 is disposed on the turbine impeller 3 side. It can also be formed. Further, the roller 50 and the support shaft 51 can be relatively rotated. Furthermore, the present invention can also be applied to a fluid coupling that does not have a stator impeller.

D ･ ･ ･ Torque damper L ･ ･ ･ Lockup clutch T ･ ･ ･ Hydraulic transmission (torque converter)
3... Turbine impeller 21... Clutch piston 31... Cylindrical housing 31 a.
34... Spring assembly 36... Drive member 37 .. driven member 38... Spring holder 43. Member 44a ... Spring seat 44b ... Connection shaft 44c ... Contact surface 44d ... Second restricting portion (positioning groove)
45... Intermediate spring seat member 45 a... Spring seat 45 b... Connecting shaft 47. .... Spindle 52 ... Slide rib

Claims (4)

Between the clutch piston (21) of the lock-up clutch (L) and the rear surface of the turbine impeller (3) opposed to the clutch piston (21), a cylindrical housing (31) connected to one of them is disposed. A spring assembly comprising a plurality of linear coil springs (43, 43...) Arranged in the circumferential direction of the cylindrical housing (31) by applying a set load in the compression direction in the cylindrical housing (31). 34), a plurality of sets are provided, and the clutch piston (21) and the turbine impeller (3) are fixed between the opposing ends of the adjacent spring assemblies (34, 34), respectively, and can be driven relative to each other. A member (36) and a follower member (37) are interposed, and between the coil springs (43, 43) adjacent to each other in each spring assembly (34), a radius is greater than both the coil springs (43, 43). Intermediate receiving urging force outward A fluid transmission device comprising a seat member (45) and a roller (50) capable of rolling the inner peripheral surface of the cylindrical housing (31) is provided on the intermediate spring seat member (45). A torque damper,
The intermediate spring seat member (45) has a roller receiving recess (47) that opens toward the inner peripheral surface of the cylindrical housing (31), and a pair of bearings that open on both sides of the roller receiving recess (47). Holes (48, 48), the roller (50) is accommodated in the roller accommodating recess (47), and the roller (50) is floated from the inner peripheral surface of the roller accommodating recess (47). A support shaft (51) protruding from both side surfaces of the roller (50) is rotatably supported in the bearing holes (48, 48), and both sides of the intermediate spring seat member (45) are supported on the cylindrical housing (31). Side walls (21, 38) facing the surface are continuously provided, and slide ribs (52) slidably contacting the side walls (21, 38) are provided on both side surfaces of the intermediate spring seat member (45). and wherein the a, a hydraulic power transmission device Rukudanpa. Between the clutch piston (21) of the lock-up clutch (L) and the rear surface of the turbine impeller (3) opposed to the clutch piston (21), a cylindrical housing (31) connected to one of them is disposed. A spring assembly comprising a plurality of linear coil springs (43, 43...) Arranged in the circumferential direction of the cylindrical housing (31) by applying a set load in the compression direction in the cylindrical housing (31). 34), a plurality of sets are provided, and the clutch piston (21) and the turbine impeller (3) are fixed between the opposing ends of the adjacent spring assemblies (34, 34), respectively, and can be driven relative to each other. A member (36) and a follower member (37) are interposed, and between the coil springs (43, 43) adjacent to each other in each spring assembly (34), a radius is greater than both the coil springs (43, 43). Intermediate receiving urging force outward A fluid transmission device comprising a seat member (45) and a roller (50) capable of rolling the inner peripheral surface of the cylindrical housing (31) is provided on the intermediate spring seat member (45). A torque damper,
The intermediate spring seat member (45) has a roller receiving recess (47) that opens toward the inner peripheral surface of the cylindrical housing (31), and a pair of bearings that open on both sides of the roller receiving recess (47). Holes (48, 48), the roller (50) is accommodated in the roller accommodating recess (47), and the roller (50) is floated from the inner peripheral surface of the roller accommodating recess (47). A support shaft (51) protruding from both side surfaces of the roller (50) is rotatably supported in the bearing holes (48, 48), and the outer end of the outermost coil spring (43) of the spring assembly (34). An outer spring seat member (44) that contacts the drive and driven members (36, 37) in a separable manner is connected to the portion, and the outer spring seat member (44) contacts the drive member (36). Of the outer spring seat member (44) when in position. The tubular housing (31) is provided with a first restricting portion (31a) for restricting the radially outward movement, and the outer spring seat member (44) is engaged with the driven member (37). A torque damper for a fluid transmission device is provided with a second restricting portion (44d) for restricting the outward movement of the outer spring seat member (44) in the radial direction. In the torque damper of the fluid transmission device according to claim 1 or 2 ,
The intermediate spring seat member (45) protrudes from the spring seats (45a, 45a) with which the opposing end faces of the coil springs (43, 43) abut on the intermediate spring seat member (45). (43, 43) A torque damper for a fluid transmission device, characterized in that a connecting shaft (45b, 45b) fitted to the inner peripheral surface of the opposite end of (43, 43) is projected. In the torque damper of the fluid transmission device according to claim 3 ,
The roller receiving recess (47) is located in a region (S) connecting the connecting shafts (45b, 45b) of the intermediate spring seat member (45) in a plan view from the outer peripheral side of the cylindrical housing (31). characterized the formed it to fit, Torukudan path for the hydraulic power transmission device.

Images