JP2022053636A - Torque fluctuation absorber - Google Patents

Abstract

To provide a torque fluctuation absorber capable of improving vibration attenuation performance and making the entire device compact, while reducing the number of components and suppressing an increase in cost.SOLUTION: A torque fluctuation absorber absorbing torque fluctuations between an engine and an input shaft of a transmission, includes: a damper mechanism that includes an input element coupled to an output shaft of the engine, an output element, and an elastic body transmitting torque between the input element and the output element; and a limiter mechanism that has a first friction engagement plate spline-fitted with an inner peripheral portion of the output element of the damper mechanism, a second friction engagement plate spline-fitted with an outer peripheral portion of the input shaft of the transmission, and an energizing member that energizes the first friction engagement plate and the second friction engagement plate so as to friction-engage with each other.SELECTED DRAWING: Figure 2

Description

The present disclosure relates to a torque fluctuation absorber that absorbs torque fluctuations between an engine and an input shaft of a transmission.

Conventionally, a torsion damper (torque fluctuation absorbing device) that connects an output shaft of an internal combustion engine and an input shaft of a transmission is known (see, for example, Patent Document 1). This torsion damper includes a damper mechanism that absorbs torsional vibration due to fluctuations in input torque by elastic deformation of a coil spring, and a friction type torque limiter arranged inside the damper mechanism in the radial direction. The torque limiter is spline-fitted to the outer peripheral portion of the input shaft of the transmission, the first and second support members connected to the hub, and the inner peripheral portion of the disc member which is the output element of the damper mechanism. A fixed intermediate member, a plurality of first friction plates spline-fitted to the outer peripheral portion of the second support member, and a spline fit to the inner peripheral portion of the intermediate member so as to be alternately arranged with the plurality of first friction plates. It includes a second friction plate to be formed and a countersunk spring arranged between the second support member and the first friction plate in the vicinity thereof. In such a torque limiter, the magnitude of the slip generation torque, which is the minimum torque that causes the torque limiter to slip, is adjusted by the urging force of the disc spring. When the input torque is less than the slip generation torque, the frictional force generated between the first and second friction plates causes the intermediate member, the disk member, and the hub to rotate integrally, and the output shaft of the internal combustion engine and the transmission. It becomes possible to transmit torque to and from the input shaft. Further, when the input torque becomes equal to or higher than the slip generation torque, slippage of the first and second friction plates occurs, and it is possible to suppress an excessive load from acting on each part of the transmission and the internal combustion engine. Further, when the relative rotation phase difference with the disk member (output element) becomes a predetermined amount or more at the inner peripheral side end portions of the first and second accommodating members which are the input elements of the damper mechanism, the relative rotation position is concerned. A hysteresis mechanism is provided as a brake that suppresses an increase in the phase difference.

Further, conventionally, a torque fluctuation absorbing device having a damper mechanism and a torque limiter arranged in a power transmission path from a flywheel (input side rotating member) to an inner peripheral hub member (output side rotating member) is known (for example). , Patent Document 2). The damper mechanism of this torque fluctuation absorber consists of two disc plates connected to the outer peripheral portion of the flywheel, a spring that damps the vibration caused by the relative rotation between the disc plate and the outer peripheral hub member, and the flywheel and the inner peripheral hub. It includes a hysteresis part that applies a brake to the relative rotation with the member to suppress noise and vibration. Further, the torque limiter is connected to the inner peripheral hub member via a spline and a friction plate (lining plate and friction material) spline-fitted to the inner peripheral portion of the outer peripheral hub member that transfers torque to and from the spring. Includes a plate that is spline-fitted to the outer periphery of the holding member. As a result, the torque limiter is arranged radially inside the spring and the hysteresis portion of the damper mechanism.

Japanese Patent No. 5384290 Japanese Unexamined Patent Publication No. 2011-247425

In the torque fluctuation absorbing device described in Patent Document 1, a plurality of first friction plates are spline-fitted to the outer peripheral portion of a second support member connected to a hub to which the plurality of first friction plates are spline-fitted to the outer peripheral portion of the input shaft of the transmission. Will be combined. Further, the plurality of second friction plates are spline-fitted to the inner peripheral portion of the intermediate member fixed to the inner peripheral portion of the disc member (output element) of the damper mechanism. Further, in the torque fluctuation absorbing device described in Patent Document 2, a plurality of friction plates are spline-fitted to the inner peripheral portion of the outer peripheral hub member, and the plurality of plates are connected to the inner peripheral hub member via the spline. The spline is fitted to the outer peripheral portion of the holding member. Therefore, in the torque fluctuation absorbers described in Patent Documents 1 and 2, the outer diameter of the damper mechanism becomes large, so that the accommodation space of the flywheel connected to the damper mechanism becomes narrow, and the mass of the flywheel becomes large. It becomes difficult to increase the (inertial mass) to improve the vibration damping performance or to make the entire device compact. Further, in the torque fluctuation absorbing device described in Patent Documents 1 and 2, the number of parts increases, and it is necessary to form splines on a large number of members, so that it is difficult to suppress the cost increase.

Therefore, the main object of the present disclosure is to provide a torque fluctuation absorbing device capable of improving the vibration damping performance and making the entire device compact while reducing the number of parts and suppressing the cost increase.

The torque fluctuation absorber of the present disclosure is a torque fluctuation absorber that absorbs torque fluctuations between an engine and an input shaft of a transmission, and includes an input element, an output element, and the input element connected to the output shaft of the engine. A damper mechanism including an elastic body that transmits torque to and from the output element, a first friction engaging plate spline-fitted to the inner peripheral portion of the output element of the damper mechanism, and the input shaft of the transmission. A limiter mechanism including a second friction engagement plate spline-fitted to the outer peripheral portion, and an urging member for urging the first friction engagement plate and the second friction engagement plate so as to be frictionally engaged. Is included.

In the torque fluctuation absorber of the present disclosure, the first friction engagement plate of the limiter mechanism is spline-fitted to the inner peripheral portion of the output element of the damper mechanism. Further, the second friction engagement plate of the limiter mechanism is spline-fitted directly to the outer peripheral portion of the input shaft of the transmission, and is urged by the urging member so as to be frictionally engaged with the first friction engagement plate. As a result, the hub that is spline-fitted to the input shaft of the transmission can be omitted, so that the outer diameter of the damper mechanism can be reduced. In addition, the yield of both can be improved by reducing the diameter of the first and second friction engagement plates. As a result, the vibration damping performance is increased by increasing the mass (inertial mass) of the member connecting the engine and the damper mechanism while reducing the number of parts and the number of members to be spline-processed to suppress cost increase. It is possible to improve the performance and make the entire device compact.

It is a schematic block diagram which shows the vehicle which includes the torque fluctuation absorption apparatus of this disclosure. It is sectional drawing which shows the torque fluctuation absorption apparatus of this disclosure. It is sectional drawing which shows the torque fluctuation absorption apparatus of this disclosure. It is sectional drawing which shows the other torque fluctuation absorption apparatus of this disclosure. It is sectional drawing which shows the other torque fluctuation absorption apparatus of this disclosure. It is sectional drawing which shows the other torque fluctuation absorption apparatus of this disclosure.

Next, a mode for carrying out the invention of the present disclosure will be described with reference to the drawings.

FIG. 1 is a schematic configuration diagram showing a vehicle V including the torque fluctuation absorbing device 10 of the present disclosure. Vehicle V uses an engine (internal combustion engine) EG that generates power by exploding and burning a mixture of hydrocarbon fuels such as gasoline, light oil, and LPG and air, and wheels (torque) from the engine EG. It includes a transmission TM transmitted to the drive wheel) W. The transmission TM is attached to the input shaft (input member) IS connected to the crankshaft (output shaft) CS of the engine EG via the torque fluctuation absorber 10, and the left and right drive shaft DS and wheels W via the differential gear DF. Includes an output shaft (output member) OS to be connected. The transmission TM may include a fluid transmission (torque converter), a lockup clutch and a stepped or continuously variable transmission mechanism, including a starting clutch and a stepped or continuously variable transmission mechanism. It may include one motor generator, at least one clutch and a transmission mechanism, and may include two motor generators and a power distribution mechanism.

As shown in FIG. 2, the torque fluctuation absorbing device 10 has a damper mechanism 11 that absorbs torque fluctuations, that is, vibrations between the engine EG and the transmission TM, and an input shaft IS between the damper mechanism 11 and the transmission TM. It includes a limiter mechanism 20 provided. In the following description, the "axial direction" basically refers to the extending direction of the central axis of the torque fluctuation absorbing device 10 (axial center, refer to the alternate long and short dash line in FIG. 2, etc.), unless otherwise specified. show. Further, the "radial direction" is basically the radial direction of the rotating element of the torque fluctuation absorbing device 10, that is, the direction orthogonal to the central axis from the central axis of the torque fluctuation absorbing device 10 (unless otherwise specified. Indicates the extending direction of a straight line extending in the radial direction). Further, the "circumferential direction" basically indicates the circumferential direction of a rotating element such as the torque fluctuation absorbing device 10, that is, the direction along the rotating direction of the rotating element, unless otherwise specified.

The damper mechanism 11 of the torque fluctuation absorber 10 is a so-called dry damper, and has a drive member (input element) 12 connected to the crankshaft CS of the engine EG via a flywheel FW as a connecting member as a rotating element. It includes a driven member (output element) 15 connected to the input shaft IS of the transmission TM via the limiter mechanism 20. Further, the damper mechanism 11 acts in parallel between the drive member 12 and the driven member 15 as a torque transmission element (torque transmission elastic body) to transmit torque (for example, 2-6 in this embodiment). ), And a plurality of spring (first elastic body) SPs that can act in parallel between the drive member 12 and the driven member 15 to transmit torque (in the present embodiment, the same number as the spring SPs, for example 2- 6) elastic member (second elastic body) EM.

As shown in FIG. 2, the drive member 12 of the damper mechanism 11 is fixed (connected) to the first plate member 121 fixed to the flywheel FW and the first plate member 121 via a plurality of rivets. Includes plate member 122. The first plate member 121 is an annular plate body formed by pressing a steel plate or the like, and a plurality of bolt holes are arranged at intervals (equally spaced) in the circumferential direction on the outer peripheral portion thereof. Has been done. The first plate member 121 is fixed to the crankshaft CS via a plurality of bolts B that are inserted into the corresponding bolt holes and screwed into the flywheel FW. Further, the first plate member 121 includes a plurality of (same number as the spring SP) spring accommodating windows 121w formed at intervals (equally spaced) in the circumferential direction, and a plurality of (same number as the spring SP) torque transfer portions (the same number as the spring SP). The elastic body contact portion) 121c and the like are included. Each spring accommodating window 121w has a peripheral length corresponding to the natural length of the spring SP, and each torque transfer portion 121c is formed one by one between adjacent spring accommodating windows 121w in the circumferential direction.

The second plate member 122 is formed by pressing a steel plate or the like so as to have an inner diameter slightly larger than the inner diameter of the first plate member 121 and an outer diameter smaller than the outer diameter of the first plate member 121. It is an annular pressed product. Further, the second plate member 122 is formed with a plurality of springs (the same number as the spring SP) formed at intervals (equally spaced) in the circumferential direction so as to face the corresponding spring accommodating window 121w of the first plate member 121. The accommodation window 122w and a plurality of torque transfer portions (elastic body contact portions) 122c (the same number as the spring SP) are included. Each spring accommodating window 122w also has a peripheral length corresponding to the natural length of the spring SP, and each torque transfer portion 122c is formed one by one between adjacent spring accommodating windows 122w in the circumferential direction.

The driven member 15 of the damper mechanism 11 includes first and second hub members 151 and 152. The first and second hub members 151 and 152 are both annular pressed products formed by pressing a steel plate or the like, and are radially outward from the tubular portion C and one end of the tubular portion C. Each includes an annular flange portion F extending to the surface. Further, spline SLs are formed in the tubular portions C of the first and second hub members 151 and 152 by press working, and spline teeth and splines are formed on the inner peripheral portion and the outer peripheral portion of each tubular portion C. The grooves are arranged alternately. Further, from at least one of the flange portions F of the first and second hub members 151 and 152, a plurality of torque transfer portions (elastic body contact portions) (the same number as the spring SP), which are not shown, are the natural lengths of the spring SP. It extends outward in the radial direction at intervals in the circumferential direction according to the above. Further, as shown in FIG. 2, the flange portions F of the first and second hub members 151 and 152 are connected to each other via a plurality of rivets R so that the tubular portions C extend in opposite directions to each other (as shown in FIG. 2). (Fixed).

One spring SP is arranged in each spring accommodating window 121w of the first plate member 121 and in each spring accommodating window 122w of the second plate member 122. Further, as shown in FIG. 2, a spring seat SS is attached to each spring SP prior to the arrangement of the spring accommodating windows 121w and 122w. The spring seat SS is formed so as to be fitted to one end of the corresponding spring SP and to cover the radial outer region of the outer peripheral surface of the spring SP. Further, a spring seat (not shown) is fitted to the other end of each spring SP. The spring SP to which the spring seat SS or the like is mounted is arranged in the spring accommodating windows 121w, 122w so as to be in sliding contact with the inner wall surface or the like of the spring accommodating windows 121w, 122w corresponding to the spring seat SS.

Then, in the mounted state of the damper mechanism 11, the torque transfer portions 121c and 122c of the drive member 12 are attached to the spring seat SS or the like on one end side or the other end side of the spring SP arranged in the corresponding spring accommodating windows 121w and 122w. Contact. Further, each torque transfer portion of the driven member 15 comes into contact with the spring seat SS or the like on one end side or the other end side of the corresponding spring SP. As a result, the drive member 12 and the driven member 15 are connected via the plurality of springs SP.

In the present embodiment, as the spring SP, a linear coil spring made of a metal material spirally wound so as to have an axial center extending straight when no load is applied is adopted. As a result, the spring SP can be expanded and contracted more appropriately along the axis as compared with the case where the arc coil spring is used. As a result, the torque transmitted from the spring SP to the driven member 15 when the relative displacement between the drive member 12 (input element) and the driven member 15 (output element) increases, and the drive member 12 and the driven member 15 It is possible to reduce the difference from the torque transmitted from the spring SP to the driven member 15, that is, the hysteresis as the relative displacement of the spring SP decreases. However, an arc coil spring may be adopted as the spring SP.

Further, the elastic member EM is formed of a short columnar shape by resin, and one elastic member EM is coaxially arranged inside each spring SP. In the plurality of elastic member EMs, the input torque (driving torque) to the drive member 12 or the torque (driven torque) applied to the driven member 15 from the drive shaft DS side corresponds to the maximum twist angle θmax of the damper mechanism 11. A plurality of predetermined torques (first threshold value) T1 or more, which are smaller than T2 (second threshold value), and when the relative twist angle between the drive member 12 and the driven member 15 is the angle θref or more. It acts in parallel with the spring SP. This makes it possible to increase the torsional rigidity of the damper mechanism 11 when a large torque is transmitted to the damper mechanism 11. In addition, the damper mechanism 11 includes a stopper (not shown) that regulates the relative rotation between the drive member 12 and the driven member 15. When the input torque to the drive member 12 reaches the torque T2 corresponding to the maximum twist angle θmax of the damper mechanism 11, the stopper regulates the relative rotation between the drive member 12 and the driven member 15, and the spring is accompanied by the relative rotation. All deflections of the SP and elastic member EM are regulated. In the damper mechanism 11, the number of elastic member EMs does not necessarily have to be the same as the number of spring SPs, and a smaller number of elastic member EMs than the spring SPs are equal to the plurality of springs SP in the circumferential direction. It may be assembled at intervals.

The limiter mechanism 20 of the torque fluctuation absorbing device 10 includes a plurality of first friction engaging plates 21 spline-fitted to the inner peripheral portions of the driven member 15, that is, the first and second hub members 151 and 152 of the damper mechanism 11. Encouragement to urge the first and second friction engagement plates 21 and 22 to be frictionally engaged with a plurality of second friction engagement plates 22 spline-fitted to the outer peripheral portion of the input shaft IS of the transmission TM. It includes a plurality of (two in this embodiment) disc springs 25 which are members. Each first friction engagement plate 21 is an annular member formed of a steel plate or the like whose both sides are flat and extend in parallel, and a first or second hub is formed on the outer peripheral portion of each first friction engagement plate 21. Splines SL formed on the tubular portions C of the members 151 and 152, that is, splines (spline teeth and spline grooves) fitted to the spline teeth and spline grooves on the inner peripheral side are formed. Each second friction engagement plate 22 is also an annular member formed of a steel plate or the like having both sides flat and extending in parallel, and the inner peripheral portion of each second friction engagement plate 22 has an outer periphery of the input shaft IS. Splines (spline teeth and spline grooves) fitted to splines (spline teeth and spline grooves) formed on the surface are formed.

In the present embodiment, as shown in FIG. 2, a plurality of first friction engaging plates 21 are fitted to the spline SL of the first hub member 151, and the input shaft IS is fitted to the first hub member 151. The number of second friction engagement plates is one less than that of the first friction engagement plate 21 fitted to the first hub member 151 so as to be located between two adjacent first friction engagement plates 21. The plate 22 is fitted. Further, a snap ring 23 for restricting the axial movement of the first friction engaging plate 21 located on the end side opposite to the flange portion F is attached to the tubular portion C of the first hub member 151. To. Further, a plurality of first friction engaging plates 21 are fitted to the spline SL of the second hub member 152, and two adjacent first friction plates fitted to the second hub member 152 are fitted to the input shaft IS. The number of second friction engagement plates 22 fitted to the input shaft IS is one less than that of the first friction engagement plate 21 fitted to the second hub member 152 so as to be located between the engagement plates 21. Will be done. Further, a snap ring 23 for restricting the axial movement of the first friction engaging plate 21 located on the end side opposite to the flange portion F is attached to the tubular portion C of the second hub member 152. To.

Then, the first friction engaging plate 21 that is closest to the second hub member 152 that is spline-fitted to the first hub member 151, and the first hub member 151 that is spline-fitted to the second hub member 152. Two disc springs 25 are arranged in parallel with one friction engagement plate 21. As a result, the plurality of first friction engaging plates 21 fitted to the first hub member 151 correspond to a plurality (at least one) fitted to the input shaft IS by the urging force from the two disc springs 25. Friction engages with the second friction engagement plate 22 of. Similarly, the plurality of first friction engaging plates 21 fitted to the second hub member 152 also correspond to a plurality (at least one) fitted to the input shaft IS by the urging force from the two disc springs 25. Friction engages with the second friction engagement plate 22 of.

Further, the damper mechanism 11 of the torque fluctuation absorbing device 10 includes a friction generating mechanism 30 that generates a frictional force between the drive member 12 and the driven member 15. The friction generation mechanism 30 has a first pressing member 31 whose inner peripheral portion is spline-fitted to the first hub member 151 of the driven member 15 and rotates integrally with the driven member 15, and a third inner peripheral portion of the driven member 15. 2 The first urging member 32 that is spline-fitted to the hub member 152 and rotates integrally with the driven member 15 and the first pressing member 31 are urged so as to be in sliding contact with a part of the drive member 12. It includes a first disc spring 33 as a member and a second disc spring 34 as a second discouraging member that urges the second pressing member 32 so as to be in sliding contact with a portion other than the part of the drive member 12. ..

The first pressing member 31 of the friction generating mechanism 30 is formed from a cylindrical portion 31c fitted to a spline tooth and a spline groove on the outer peripheral side of the tubular portion C of the first hub member 151 and one end of the tubular portion 31c. It is an annular member including a flange portion 31f extending radially outward. As shown in FIG. 2, the outer peripheral surface of the tubular portion 31c of the first pressing member 31 rotatably supports (aligns) the inner peripheral portion 121i of the first plate member 121 of the drive member 12. Further, the first disc spring 33 is arranged between the flange portion F of the first hub member 151 and the flange portion 31f of the first pressing member 31, and the flange portion 31f is used as the inner peripheral portion 121i of the first plate member 121. It is urged to slide on the inner surface of the. As a result, a frictional force can be generated between the first hub member 151 of the driven member 15 and the first plate member 121 of the drive member 12.

The second pressing member 32 of the friction generating mechanism 30 is formed from a cylindrical portion 32c fitted to the spline teeth and the spline groove on the outer peripheral side of the tubular portion C of the second hub member 152, and from one end of the tubular portion 32c. It is an annular member including a flange portion 32f extending outward in the radial direction. As shown in FIG. 2, the outer peripheral surface of the tubular portion 32c of the second pressing member 32 rotatably supports (aligns) the inner peripheral portion 122i of the second plate member 122 of the drive member 12. Further, the second disc spring 34 is arranged between the flange portion F of the second hub member 152 and the flange portion 32f of the second pressing member 32, and the flange portion 32f is arranged with the flange portion 31f of the first pressing member 31. The first plate member 121 is urged so as to be in sliding contact with the inner surface of the inner peripheral portion 122i of the second plate member 122 on the radial outer side of the sliding contact portion with the inner peripheral portion 121i. As a result, a frictional force larger than the frictional force between the first hub member 151 and the first plate member 121 between the second hub member 152 of the driven member 15 and the second plate member 122 of the drive member 12 is applied. It is possible to generate it.

Further, in the friction generation mechanism 30, the first and second disc springs 33 and 34 are arranged in series in the axial direction so as to reduce the overall spring rigidity, so that the first and second disc springs are sliding members. The amount of change in the urging force (load) of the first and second disc springs 33 and 34 according to the amount of wear of the pressing members 31 and 32 can be reduced. Further, in the present embodiment, the first pressing member 31 and the first disc spring 33 of the friction generating mechanism 30 are torqued when torque is transmitted from the engine EG side to the transmission TM side and from the transmission TM side to the engine side EG. Is transmitted, a relatively small frictional force is constantly applied to the first plate member 121 of the drive member 12. Further, in the second pressing member 32 and the second disc spring 34 of the friction generating mechanism 30, torque is transmitted from the transmission TM side to the engine side EG, and the twist angle of the driven member 15 with respect to the drive member 12 is equal to or larger than a predetermined angle. Only occasionally, it is configured to apply a frictional force greater than the frictional force applied to the first plate member 121 from the first pressing member 31 and the first disc spring 33 to the second plate member 122 of the drive member 12. There is.

In the vehicle V including the torque fluctuation absorbing device 10 configured as described above, the torque from the engine EG (crankshaft CS) is transmitted to the drive member 12 of the damper mechanism 11 via the flywheel FW, and the drive member 12 is transmitted. The torque transmitted to the transmission is transmitted via a plurality of springs SP (and a plurality of elastic bodies), a driven member 15, and a plurality of first and second friction engagement plates 21 and 22 of a frictionally engaged limiter mechanism 20. It is transmitted to the input axis IS of TM. At this time, the fluctuation of the torque from the engine EG, that is, the vibration is damped by the plurality of springs SP (and the plurality of elastic member EMs) of the damper mechanism 11.

Further, when torque is transmitted from the engine EG to the input shaft IS of the transmission TM, a relatively small frictional force is driven from the first pressing member 31 and the first disc spring 33 (driven member 15) of the friction generating mechanism 30. It is always applied to the first plate member 121 of the member 12. As a result, when torque is transmitted from the engine EG to the input shaft IS of the transmission TM, the vibration of the drive member 12 can be appropriately attenuated to satisfactorily suppress the generation of noise and vibration in the torque fluctuation absorber 10. It will be possible.

Further, in the vehicle V including the torque fluctuation absorbing device 10, when the torque from the wheel W (transmission TM) side is transmitted to the input shaft IS, the torque transmitted to the input shaft IS is frictionally engaged with the limiter mechanism. It is transmitted to the engine EG side via a plurality of first and second friction engagement plates 21 and 22, a plurality of driven members 15, a plurality of spring SPs (and a plurality of elastic bodies), a drive member 12, and a flywheel FW of 20. .. At this time, the fluctuation of the torque from the input shaft IS, that is, the vibration is damped by the plurality of springs SP (and the plurality of elastic member EMs) of the damper mechanism 11.

Further, when torque is transmitted from the input shaft IS of the transmission TM to the engine EG side, a relatively small frictional force is generated from the first pressing member 31 and the first disc spring 33 (driven member 15) of the friction generating mechanism 30. It is always applied to the first plate member 121 of the drive member 12. In addition, when the twist angle of the driven member 15 with respect to the drive member 12 becomes equal to or greater than the predetermined angle, a frictional force larger than the frictional force applied to the first plate member 121 by the first pressing member 31 and the first disc spring 33 is generated. The second pressing member 32 and the second disc spring 34 (driven member 15) are applied to the second plate member 122 of the drive member 12. As a result, when torque is transmitted from the input shaft IS of the transmission TM to the engine EG side, the vibration of the drive member 12 is appropriately attenuated, and the generation of noise and vibration in the torque fluctuation absorber 10 is satisfactorily suppressed. Is possible.

Further, the torque transmitted from the engine EG to the driven member 15 of the damper mechanism 11 or the torque transmitted from the wheel W (transmission TM) side to the input shaft IS is the dynamic friction between the first and second friction engagement plates 21 and 22. When the limiter torque (slip generation torque) Tlim of the limiter mechanism 20 determined by the coefficient, the working radius of the first and second friction engagement plates 21 and 22, the rigidity (spring constant) of the countersunk spring 25, etc. is exceeded, the first and first 2 Slip occurs between the friction engagement plates 21 and 22. This makes it possible to satisfactorily suppress the transmission of excessive torque from the engine EG to the transmission TM side and the transmission of excessive torque from the transmission TM to the engine EG side.

Then, in the torque fluctuation absorbing device 10, the plurality of first friction engaging plates 21 of the limiter mechanism 20 are the inner peripheral portions of the driven member 15 (first and second hub members 151, 152) which is an output element of the damper mechanism 11. Spline fits into. Further, the plurality of second friction engagement plates 22 of the limiter mechanism 20 are spline-fitted directly to the outer peripheral portion of the input shaft IS of the transmission TM, and the plates are so as to be frictionally engaged with the plurality of first friction engagement plates 21. It is urged by the spring 25. As a result, the hub spline-fitted to the input shaft IS of the transmission TM can be omitted, so that the outer diameter of the damper mechanism 11 can be reduced. In addition, the yields of the first and second friction engagement plates 21 and 22 can be improved by reducing the diameters of the plates 21 and 22. As a result, the mass (inertia) of the flywheel FW that connects the engine EG and the damper mechanism 11 (drive member 12) is suppressed while reducing the number of parts and the number of members to be spline-processed to suppress cost increase. It is possible to increase the mass) (see the two-dot chain line in FIG. 2) to improve the vibration damping performance.

Further, in the torque fluctuation absorbing device 10, the outer diameter of the first plate member 121 of the damper mechanism 11, that is, the drive member 12 can be reduced. Therefore, as shown in FIG. 3, the diameter of the flywheel FW is reduced to absorb the torque fluctuation. The device 10 can be made compact as a whole in the radial direction. This makes it possible to further improve the space efficiency of the vehicle V.

Further, the driven member 15 of the damper mechanism 11 extends radially outward from one end of the tubular portion C and the tubular portion C having a spline SL to which the outer peripheral portion of the first friction engagement plate 21 is fitted. Includes first and second hub members 151 and 152, which are stamped products having a flange portion F to be formed. As a result, as compared with the case where the driven member 15 of the damper mechanism 11 is manufactured by cutting, the manufacturing cost of the driven member 15 is significantly reduced, the yield is improved, and the torque fluctuation absorbing device 10 is further reduced in cost. It becomes possible to plan.

Further, the flange portions F of the first and second hub members 151 and 152 constituting the driven member 15 are connected to each other so that the tubular portions C extend in opposite directions to each other. By forming the driven member 15 into two parts in this way, the axial length of the tubular portion C (spline SL) can be shortened as compared with the case where the driven member 15 is a single member. As a result, it becomes possible to further improve the molding accuracy and workability of the spline SL in the first and second hub members 151 and 152. In addition, the two disc springs 25 as urging members are the first friction engaging plate 21 closest to the second hub member 152 spline-fitted to the first hub member 151, which is one of the stamped products. It is arranged between the first friction engaging plate 21 closest to the first hub member 151 spline-fitted to the second hub member 152, which is the other pressed product. This makes it possible to further improve the space efficiency of the torque fluctuation absorbing device 10.

However, depending on the configuration of the limiter mechanism 20, the two countersunk springs 25 as urging members are frictionally engaged with the first friction engaging plate 21 spline-fitted to the first hub member 151, which is one of the pressed products. The matching second friction engagement plate 22 and the second friction engagement plate 22 that is frictionally engaged with the first friction engagement plate 21 spline-fitted to the second hub member 152 which is the other pressed product. It may be placed in between. Further, by arranging them in parallel on two (plurality) disc springs 25 as described above, it is possible to secure a sufficiently large limiter torque Tlim, but the required size of the limiter torque Tlim. Depending on the situation, a single disc spring 25 may be arranged between the two first friction engagement plates 21 or the like.

Further, the damper mechanism 11 of the torque fluctuation absorbing device 10 includes a friction generating mechanism 30 that generates a frictional force between the drive member 12 and the driven member 15, and the friction generating mechanism 30 torques the torque from the engine EG to the transmission TM. The frictional force is changed depending on whether the torque is transmitted from the transmission TM to the engine EG. This makes it possible to satisfactorily suppress the generation of noise and vibration in the torque fluctuation absorbing device 10.

Further, in the above embodiment, the friction generation mechanism 30 includes a first pressing member 31 spline-fitted to the outer peripheral portion of the driven member 15 (cylindrical portion C of the first hub member 151) and a first pressing member 31. The first disc spring 33 that is urged so as to be in sliding contact with the inner peripheral portion 121i of the first plate member 121 that is a part of the drive member 12, and the outer circumference of the driven member 15 (cylindrical portion C of the second hub member 152). The second pressing member 32 spline-fitted to the portion and the second pressing member 32 are urged so as to be in sliding contact with the inner peripheral portion 122i of the second plate member 122 which is a portion other than the part of the drive member 12. Further, the second pressing member 32 including the second disc spring 34 is in sliding contact with the drive member 12 (inner peripheral portion 122i) on the radial outer side of the first pressing member 31. This makes it possible to configure the friction generation mechanism 30 that can satisfactorily suppress the generation of noise and vibration in the torque fluctuation absorbing device 10 while suppressing the cost increase.

FIG. 4 is a cross-sectional view showing another torque fluctuation absorbing device 10B of the present disclosure. Of the components of the torque fluctuation absorbing device 10B, the same elements as those of the torque fluctuation absorbing device 10 are designated by the same reference numerals, and duplicate description will be omitted.

The damper mechanism 11B of the torque fluctuation absorbing device 10B shown in FIG. 4 includes a driven member 15B corresponding to the driven member 15 in which the first hub member 151 is replaced with an annular member 153 which is a pressed product. The annular member 153 has an annular outer peripheral portion O connected (fixed) to the flange portion F of the second hub member 152 via a plurality of rivets R, and is offset axially from the outer peripheral portion O and is radially inward. It includes an extended annular inner peripheral portion I and an annular bent portion M formed by press working between the outer peripheral portion O and the inner peripheral portion I. In the damper mechanism 11B, the first pressing member 31B of the friction generating mechanism 30B is sandwiched between the bent portion M of the annular member 153 and the inner peripheral portion 121i of the first plate member 121 of the drive member 12, and the outer peripheral portion of the annular member 153. The flange portion 31f is urged so as to be in sliding contact with the inner peripheral portion 121i by the first disc spring 33 arranged between O and the flange portion 31f of the first pressing member 31B.

Further, the inner circumference of the inner peripheral portion I of the annular member 153 is located radially inside the inner circumference of the tubular portion C of the second hub member 152, and is located on the inner peripheral portion I and the second hub member 152. Two disc springs 25 are arranged in parallel with the first friction engaging plate 21 on the most annular member 153 side to which the spline is fitted. In the torque fluctuation absorbing device 10B, the number of members to be splined can be further reduced by omitting the first hub member 151, and the cost of the entire device can be reduced. The driven member 15B may be composed of the first hub member 151 of the driven member 15 and the annular member 153.

FIG. 5 is a cross-sectional view showing still another torque fluctuation absorbing device 10C of the present disclosure. Of the components of the torque fluctuation absorbing device 10C, the same elements as those of the torque fluctuation absorbing device 10 and the like are designated by the same reference numerals, and duplicate description will be omitted.

In the damper mechanism 11C of the torque fluctuation absorbing device 10C shown in FIG. 5, the second pressing member 32, the second disc spring 34 and one snap ring 23 are omitted from the friction generating mechanism 30, and an annular plate member 35 is added. Includes a friction generating mechanism 30C corresponding to that. As shown in FIG. 5, the plate member 35 is spline-fitted to the outer peripheral portion of the input shaft IS of the transmission TM, and the flange portion 31f of the first pressing member 31 and the inner peripheral portion 121i of the first plate member 121. On the radial side of the sliding contact portion of the above, the sliding contact (contact) with the inner peripheral portion 122i of the second plate member 122 constituting the drive member 12 of the damper mechanism 11C. Further, the plate member 35 abuts on the first friction engagement plate 21 separated from the first hub member 151 spline-fitted to the tubular portion C of the second hub member 152, and the first friction engagement plate is in contact with the first friction engagement plate 21. 21 Axial movement is restricted.

In the torque fluctuation absorbing device 10C, the torque transmitted from the engine EG to the driven member 15 of the damper mechanism 11C or the torque transmitted from the wheel W (transmission TM) side to the input shaft IS is equal to or less than the limiter torque Tlim of the limiter mechanism 20. At one point, the plate member 35 rotates integrally with the input shaft IS together with the driven member 15. Therefore, in the torque fluctuation absorbing device 10C, a frictional force can be generated between the driven member 15 and the second plate member 122 of the drive member 12 via the plate member 35. Further, in the torque fluctuation absorbing device 10C, the number of parts of the friction generating mechanism 30C is reduced by omitting the second pressing member 32, the second disc spring 34 and one snap ring 23, and the cost of the entire device is further reduced. Is possible. The friction generation mechanism 30C is in sliding contact with the second pressing member 32 and the second disc spring 34 in the friction generation mechanism 30 and the inner peripheral portion 121i of the first plate member 121 constituting the drive member 12 of the damper mechanism 11C. It may include the plate member 35.

FIG. 6 is a cross-sectional view showing another torque fluctuation absorbing device 10D of the present disclosure. Of the components of the torque fluctuation absorbing device 10D, the same elements as those of the torque fluctuation absorbing device 10 and the like are designated by the same reference numerals, and duplicate description will be omitted.

The damper mechanism 11D of the torque fluctuation absorbing device 10D shown in FIG. 6 omits the second pressing member 32, the second disc spring 34 and one snap ring 23 in the friction generating mechanism 30, and is a second plate member of the drive member 12. It includes a friction generation mechanism 30D corresponding to a reduced inner diameter of 122. That is, in the torque fluctuation absorbing device 10D, the inner diameter of the second plate member 122 of the drive member 12 is set to be slightly larger than the outer diameter of the input shaft IS of the transmission TM. Then, the inner peripheral portion 122i of the second plate member 122 abuts on the first friction engaging plate 21 separated from the first hub member 151 spline-fitted to the tubular portion C of the second hub member 152. (Sliding contact) is performed to regulate the movement of the first friction engagement plate 21 in the axial direction.

In such a torque fluctuation absorbing device 10D, when torque is transmitted between the engine EG and the transmission TM, a plurality of first friction engaging plates 21 are constantly urged by two disc springs 25 with the driven member 15. It rotates in one piece. Therefore, the inner peripheral portion 122i of the second plate member 122 abuts (slides) on the first friction engaging plate 21 separated from the first hub member 151 spline-fitted to the tubular portion C of the second hub member 152. By contacting), it is possible to generate a relatively large frictional force between the first friction engagement plate 21 (driven member 15) and the drive member 12. Further, also in the torque fluctuation absorbing device 10D, the number of parts of the friction generating mechanism 30D is reduced by omitting the second pressing member 32, the second disc spring 34 and one snap ring 23, and the cost of the entire device is further reduced. be able to. In the torque fluctuation absorbing device 10D, the inner peripheral portion 122i of the second plate member 122 may abut (sliding) with the second friction engaging plate 22 depending on the configuration of the limiter mechanism 20. Further, in the friction generation mechanism 30D, the second pressing member 32 and the second disc spring 34 in the friction generation mechanism 30 and the inner peripheral portion 121i are brought into contact (sliding contact) with the first friction engagement plate 21 and the like. It may include the formed first plate member 121. Further, the inner peripheral portions 121i, 122i of the first or second plate members 121, 122 may be in direct contact (sliding contact) with the driven member 15.

As described above, the torque fluctuation absorber of the present disclosure is a torque fluctuation absorber (10, 10B, 10C,) that absorbs torque fluctuation between the input shaft (IS) of the engine (EG) and the transmission (TM). In 10D), the input element (12), the output element (15), and the torque between the input element (12) and the output element (15) connected to the output shaft (CS) of the engine (EG). Splines on the inner peripheral portion of the damper mechanism (11, 11B, 11C, 11D) including the elastic body (SP, EM) that transmits the above and the output element (15) of the damper mechanism (11, 11B, 11C, 11D). The first friction engagement plate (21) to be fitted, the second friction engagement plate (22) spline-fitted to the outer peripheral portion of the input shaft (IS) of the transmission (TM), and the first friction. It includes a limiter mechanism (20) including an urging member (25) that urges the engagement plate (21) and the second friction engagement plate (22) to be frictionally engaged.

In the torque fluctuation absorber of the present disclosure, the first friction engagement plate of the limiter mechanism is spline-fitted to the inner peripheral portion of the output element of the damper mechanism. Further, the second friction engagement plate of the limiter mechanism is spline-fitted directly to the outer peripheral portion of the input shaft of the transmission, and is urged by the urging member so as to be frictionally engaged with the first friction engagement plate. As a result, the hub that is spline-fitted to the input shaft of the transmission can be omitted, so that the outer diameter of the damper mechanism can be reduced. In addition, the yield of both can be improved by reducing the diameter of the first and second friction engagement plates. As a result, the vibration damping performance is increased by increasing the mass (inertial mass) of the member connecting the engine and the damper mechanism while reducing the number of parts and the number of members to be spline-processed to suppress cost increase. It is possible to improve the performance and make the entire device compact.

Further, the output element (15, 15B) of the damper mechanism (11, 11B, 11C, 11D) is a cylinder having a spline (SL) to which the outer peripheral portion of the first friction engagement plate (21) is fitted. It may include a stamped product (151, 152) having a shaped portion (C) and a flange portion (F) extending radially outward from one end of the tubular portion (C). As a result, compared to the case where the output element of the damper mechanism is manufactured by cutting, it is possible to reduce the manufacturing cost of the output element, improve the yield, and further reduce the cost of the torque fluctuation absorber. Become.

Further, in the output element (15) of the damper mechanism (11, 11C, 11D), the flange portions (F) are connected to each other so that the tubular portions (C) extend in opposite directions. The stamped product (151, 152) may be included, and the urging member (25) is spline-fitted to one of the stamped products (151). It may be arranged between (21) and the first friction engaging plate (21) spline-fitted to the other stamped product (152). By dividing the output element into two in this way, the axial length of the cylindrical portion (spline) can be shortened as compared with the case where the output element is a single member, so that the spline can be formed in each stamped product. It is possible to further improve the accuracy and workability. In addition, an urging member shall be placed between the first friction engagement plate spline-fitted to one stamped product and the first friction engagement plate spline-fitted to the other stamped product. Therefore, the space efficiency of the torque fluctuation absorber can be further improved.

Further, the output element (15B) of the damper mechanism (11B) may include an annular member (153) connected to the flange portion (F) of the pressed product (152). The urging member (25) may be arranged between the first friction engaging plate (21) spline-fitted to the stamped product (152) and the annular member (153). This makes it possible to further reduce the number of members to be splined and reduce the cost of the entire torque fluctuation absorbing device.

Further, the damper mechanism (11, 11B, 11C, 11D) is a friction generating mechanism (30, 30B, 30C,) that generates a frictional force between the input element (12) and the output element (15, 15B). 30D) may be included, and the friction generating mechanism (30, 30B, 30C, 30D) is used when torque is transmitted from the engine (EG) to the transmission (TM) and when the transmission (TM) is transmitted. ) When the torque is transmitted to the engine (EG), the frictional force may be changed. This makes it possible to satisfactorily suppress the generation of noise and vibration in the torque fluctuation absorber.

Further, the friction generating mechanism (30) includes a first pressing member (31) in which an inner peripheral portion (31c) is spline-fitted to the output element (15, 151) of the damper mechanism (11), and the first pressing member (31). The first urging member (33) for urging the pressing member (31) so as to be in sliding contact with a part (121i) of the input element (12, 121), and the inner peripheral portion (32c) are the damper mechanism (12c). The second pressing member (32) spline-fitted to the output element (15, 152) of 11) and the second pressing member (32) other than the part (121i) of the input element (12). The second pressing member (32) may include a second urging member (34) that urges the portion (122, 122i) so as to be in sliding contact with the portion (122, 122i). It may be in sliding contact with the input element (12,122i) on the outer side in the radial direction. This makes it possible to configure a friction generation mechanism that can satisfactorily suppress the generation of noise and vibration in the torque fluctuation absorbing device while suppressing the cost increase.

Further, the friction generating mechanism (30C) is spline-fitted to the outer peripheral portion of the input shaft (IS) of the transmission (TM) and is a part of the input element (12) of the damper mechanism (11C). It may include a plate member (35) that is in sliding contact with (122, 122i). This makes it possible to reduce the number of parts of the friction generating mechanism and further reduce the cost of the entire torque fluctuation absorbing device.

Further, a part of the input element (12) of the damper mechanism (11D) may be in sliding contact with the first friction engagement plate (21) or the second friction engagement plate (22). In such a torque fluctuation absorber, a relatively large frictional force is applied between the input element and the first or second friction engagement plate that rotates integrally with the input shaft of the output element or the transmission because it is not urged by the urging member. At the same time, it is possible to reduce the number of parts of the friction generating mechanism and reduce the cost of the entire torque fluctuation absorbing device.

It goes without saying that the invention of the present disclosure is not limited to the above-described embodiment, and various changes can be made within the scope of the extension of the present disclosure. Further, the above embodiment is merely a specific embodiment of the invention described in the column of the outline of the invention, and does not limit the elements of the invention described in the column of the outline of the invention.

The invention of the present disclosure can be used in the manufacturing field of a torque fluctuation absorber.

10,10B, 10C, 10D torque fluctuation absorber, 11, 11B, 11C, 11D damper mechanism, 12 drive member, 121 first plate member, 121c torque transfer part, 121i inner circumference part, 121w spring accommodating window, 122 second Plate member, 122c torque transfer part, 122i inner peripheral part, 122w spring accommodating window, 15,15B driven member, 151 1st hub member, 152 2nd hub member, 153 annular member, 20 limiter mechanism, 21 1st friction engagement Plate, 22 2nd friction engagement plate, 23 snap ring, 25 flat spring, 30, 30B, 30C, 30D friction generation mechanism, 31, 31B 1st pressing member, 31c tubular part, 31f flange part, 32 2nd pressing Member, 32c tubular part, 32f flange part, 33 1st flat spring, 34 2nd flat spring, 35 plate member, C tubular part, B bolt, C tubular part, CS crankshaft, DF differential gear, DS drive Shaft, EG engine, EM elastic member, F flange part, FW fly wheel, I inner circumference part, IS input shaft, M bending part, O outer circumference part, OS output shaft, R rivet, SL spline, SP spring, SS spring seat , T1, T2 torque, TM transmission, Tlim limiter torque, V vehicle, W wheel.

Claims (8)

In a torque fluctuation absorber that absorbs torque fluctuations between the engine and the input shaft of the transmission
An input element connected to the output shaft of the engine, an output element, and a damper mechanism including an elastic body for transmitting torque between the input element and the output element.
A first friction engagement plate spline-fitted to the inner peripheral portion of the output element of the damper mechanism, a second friction engagement plate spline-fitted to the outer peripheral portion of the input shaft of the transmission, and the first friction engagement plate. A limiter mechanism including a urging member that urges the friction engagement plate and the second friction engagement plate to be frictionally engaged, and a limiter mechanism.
A torque fluctuation absorber equipped with. In the torque fluctuation absorbing device according to claim 1,
The output element of the damper mechanism includes a tubular portion having a spline to which an outer peripheral portion of the first friction engagement plate is fitted, and a flange portion extending radially outward from one end of the tubular portion. Torque fluctuation absorber including stamped products. In the torque fluctuation absorbing device according to claim 2,
The output element of the damper mechanism includes two stamped products in which the flange portions are connected to each other so that the tubular portions extend in opposite directions to each other.
The urging member is between the first friction engaging plate spline-fitted to one of the stamped products and the first friction engaging plate spline-fitted to the other pressed product. Arranged torque fluctuation absorber. In the torque fluctuation absorbing device according to claim 2,
The output element of the damper mechanism includes an annular member connected to the flange portion of the stamped product.
The urging member is a torque fluctuation absorbing device arranged between the first friction engaging plate spline-fitted to the pressed product and the annular member. In the torque fluctuation absorbing device according to any one of claims 1 to 3.
The damper mechanism includes a friction generating mechanism that generates a frictional force between the input element and the output element.
The friction generating mechanism is a torque fluctuation absorbing device that changes the frictional force between when torque is transmitted from the engine to the transmission and when torque is transmitted from the transmission to the engine. In the torque fluctuation absorbing device according to claim 5,
The friction generating mechanism urges a first pressing member whose inner peripheral portion is spline-fitted to the output element of the damper mechanism and the first pressing member so as to be in sliding contact with a part of the input element. 1 The urging member, the second pressing member whose inner peripheral portion is spline-fitted to the output element of the damper mechanism, and the second pressing member so as to be in sliding contact with a portion other than the part of the input element. Including the second urging member to urge
The second pressing member is a torque fluctuation absorbing device that is in sliding contact with the input element on the radial side of the first pressing member. In the torque fluctuation absorbing device according to claim 5,
The friction generating mechanism is a torque fluctuation absorbing device including a plate member that is spline-fitted to the outer peripheral portion of the input shaft of the transmission and is in sliding contact with a part of the input element of the damper mechanism. In the torque fluctuation absorbing device according to claim 5,
A part of the input element of the damper mechanism is a torque fluctuation absorbing device that is in sliding contact with the first friction engaging plate or the second friction engaging plate.

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