JP6247524B2 - Torque converter lockup device - Google Patents

Description

  The present invention relates to a lockup device, in particular, a lockup which is disposed between a front cover connected to a member on an engine side and a torque converter main body and directly transmits torque from the front cover to a turbine of the torque converter main body. Relates to the device.

  In the torque converter, a lockup device is provided to reduce fuel consumption. The lockup device is disposed between the front cover and the turbine, and mechanically connects the front cover and the turbine to directly transmit torque therebetween.

  Generally, the lockup device has a piston and a damper mechanism. The piston has a friction member, is pressed against the front cover by the action of hydraulic pressure, and torque is transmitted from the front cover. The damper mechanism also has a plurality of torsion springs, and the plurality of torsion springs elastically connect the piston and the output-side member connected to the turbine. In such a lockup device, the torque transmitted to the piston is transmitted to the output side member via a plurality of torsion springs and further transmitted to the turbine.

  As disclosed in Patent Document 1, there is also provided a lockup device that suppresses fluctuations in the rotational speed of an engine by attaching an inertia member to an output-side member.

JP 2009-293671 A

  In a conventional lockup device, a stop pin is provided to restrict the relative rotation angle between the input side plate and the output side plate or inertia member within a predetermined range. More specifically, for example, in the apparatus of Patent Document 1, the pair of plates and the inertia member arranged so as to be sandwiched between them are arranged so as to be relatively rotatable, and these are rotated in the rotation direction by a torsion spring. It is elastically connected.

  Here, in order to regulate the relative rotation angle between the pair of plates and the inertia member, there is a method in which the torsion spring is brought into close contact, but in this case, excessive stress is easily applied to the torsion spring, and the life of the torsion spring is increased. Becomes shorter.

  Therefore, a stopper mechanism for restricting the relative rotation angle between the pair of plates and the inertia member is necessary. The stopper mechanism disclosed in Patent Document 1 fixes a pair of plates to each other with a stop pin, and causes the inertia member to abut on the stop pin when the inertia member rotates a predetermined angle with respect to the pair of plates. The torsion spring is prevented from sticking.

  However, when the stop pin is provided, it is necessary to avoid interference between the head or the caulked portion of the stop pin and other members, which hinders shortening in the axial direction.

  An object of the present invention is to shorten the axial space of the stopper mechanism in the lockup device of the torque converter, and to suppress the axial space of the entire device.

  A torque converter lock-up device according to a first aspect of the present invention is disposed between a front cover coupled to an engine-side member and a torque converter main body, and directly transmits torque from the front cover to a turbine of the torque converter main body. A device for transmitting. This lock-up device includes a clutch portion, a damper mechanism, and a stopper mechanism. The clutch portion transmits torque from the front cover to the output side. The damper mechanism is rotatable relative to the first and second plates between the axial direction of the first and second plates, and the first and second plates provided in the axial direction so as to receive torque from the clutch portion. And a plurality of elastic members elastically connecting the first and second plates and the third plate in the rotational direction and held by the first and second plates. The stopper mechanism includes a first engagement portion formed on at least one of the first and second plates, and a first plate, a second plate, and a third plate formed on the third plate and engaged with the first engagement portion. And a second engaging portion that regulates a relative rotation angle within a predetermined angle range.

  In this device, when the clutch portion is on (power transmission state), power from the front cover is transmitted from the clutch portion to the turbine via the damper mechanism. At this time, fluctuations in rotational speed can be suppressed by the damper mechanism.

  Here, the first and second plates and the third plate rotate relative to each other by expansion and contraction of the plurality of elastic members. This relative rotational angle range is regulated by the engagement of the first engagement portion formed on at least one of the first and second plates and the second engagement portion of the third plate. Therefore, the stopper mechanism can be realized with a simple configuration, and the axial space occupied by the stopper mechanism is shorter than that of the conventional stopper mechanism.

  In the torque converter lock-up device according to the second aspect of the present invention, the third plate is rotatable relative to the clutch portion and is connected to the turbine.

  In the torque converter lockup device according to the third aspect of the present invention, the damper mechanism further includes a plurality of outer peripheral side elastic members arranged on the outer peripheral side of the elastic member. The plurality of outer peripheral elastic members elastically connect the clutch portion and the first and second plates in the rotational direction.

  Here, since the axial space of the stopper mechanism is short, the stopper mechanism and the outer peripheral elastic member are unlikely to interfere with each other. Therefore, the coil diameter of the outer peripheral side elastic member can be increased, and the rigidity of the damper mechanism can be reduced to contribute to the improvement of fuel consumption.

  In the torque converter lockup device according to the fourth aspect of the present invention, the first and second plates are formed by bending the first and second plates so as to contact each other's plates. At predetermined intervals in the circumferential direction. The damper mechanism further includes a fixing member that fastens the first contact portion and the second contact portion so that the first plate and the second plate cannot be rotated relative to each other and cannot move in the axial direction. And the 1st engaging part is formed of the 1st and 2nd contact part.

  In the torque converter lockup device according to the fifth aspect of the present invention, the third plate is formed in a disc shape. The second engaging portion has a plurality of stopper projections formed to protrude from the outer peripheral surface of the third plate to the outer peripheral side. The plurality of stopper projections are arranged at positions overlapping the first and second contact portions in the axial direction and the radial direction between the circumferential directions of the plurality of first and second contact portions.

  Here, when the first and second plates and the third plate rotate relative to each other by a predetermined angle, the stopper projections of the third plate abut against the abutting portions of the first and second plates. Thereby, the relative rotation of the first and second plates and the third plate is restricted.

  In the torque converter lock-up device according to the sixth aspect of the present invention, the first plate has a disk-shaped main body, a plurality of protrusions, and a plurality of locking portions. The plurality of projecting portions project from the main body portion to the outer peripheral side, and are formed at predetermined intervals in the circumferential direction. The plurality of locking portions are provided at the tip of the protruding portion, and both ends in the circumferential direction can be locked to both ends of the outer peripheral side elastic member. j The first engaging portion is formed by cutting and raising the circumferential central portion of the plurality of protruding portions toward the second plate.

  The torque converter lockup device according to the seventh aspect of the present invention includes an inertia member provided on one of the first and second plates so as to be relatively rotatable with respect to the first and second plates. And a dynamic damper device for damping the vibration.

  In the torque converter lockup device according to the eighth aspect of the present invention, the dynamic damper device further includes a plurality of dynamic damper elastic members that elastically connect the first and second plates and the inertia member in the rotational direction. .

  According to the present invention as described above, in the lockup device of the torque converter, the axial space of the stopper mechanism can be shortened, and the axial space of the entire device can be suppressed. In addition, the damper mechanism can be reduced in rigidity in the same space as in the prior art.

The cross-sectional block diagram of the torque converter provided with the lockup apparatus by one Embodiment of this invention. The figure which extracts and shows the lockup apparatus of FIG. The figure which extracts and shows the intermediate member and dynamic damper apparatus of FIG. The front fragmentary view of a dynamic damper apparatus. The perspective view which shows a part of stopper mechanism. The front fragmentary view of the inertia ring of a dynamic damper apparatus. The figure which shows the stop pin of a dynamic damper apparatus. FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation.

  FIG. 1 is a partial sectional view of a torque converter 1 having a lock-up device according to an embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure. Note that OO shown in FIG. 1 is a rotation axis of the torque converter and the lockup device.

[Overall Configuration of Torque Converter 1]
The torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to an input shaft of a transmission, and includes a front cover 2 fixed to an input-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5) and a lockup device 7 are included.

  The front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the transmission is formed on the outer peripheral portion thereof. The impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape provided on the inner peripheral side of the impeller shell 12. And the impeller hub 14.

  The turbine 4 is disposed to face the impeller 3 in the fluid chamber. The turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15. The turbine hub 17 has a flange 17 a extending to the outer peripheral side, and an inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18. An input shaft of a transmission (not shown) is splined to the inner peripheral portion of the turbine hub 17.

  The stator 5 is a mechanism for rectifying hydraulic fluid that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3. The stator 5 mainly includes a stator carrier 20 and a plurality of stator blades 21 provided on the outer peripheral surface thereof. The stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22. Thrust bearings 24 and 25 are provided on both axial sides of the stator carrier 20.

[Lock-up device 7]
FIG. 2 shows the lock-up device 7 extracted from FIG. The lockup device 7 is disposed in a space between the front cover 2 and the turbine 4. The lock-up device 7 includes a piston 30, a drive plate 31, an outer periphery side torsion spring 32, a float member 33, an intermediate member 34, an inner periphery side torsion spring 35, a hub flange (third plate) 36, A stopper mechanism 39 and a dynamic damper device 37 are provided.

  The drive plate 31, the outer peripheral side torsion spring 32, the float member 33, the intermediate member 34, the inner peripheral side torsion spring 35, and the hub flange 36 constitute a damper mechanism.

<Piston 30>
The piston 30 is formed in an annular shape and is disposed on the transmission side of the front cover 2. A cylindrical portion 30 a extending to the transmission side is formed on the inner peripheral portion of the piston 30. The cylindrical portion 30a is supported on the outer peripheral surface of the turbine hub 17 so as to be axially movable and relatively rotatable. Further, an annular friction material 38 is fixed to the surface on the front cover 2 side in the outer peripheral portion of the piston 30. When the friction material 38 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the piston 30.

  A stepped portion including a small-diameter portion 17b on the engine side and a large-diameter portion 17c on the transmission side is formed on the outer peripheral surface of the turbine hub 17. The piston 30 is supported by the small diameter portion 17b, and the axial movement toward the transmission side is restricted by the side surface of the large diameter portion 17c. Further, a seal member 40 is attached to the small diameter portion 17b, and the space between the inner peripheral surface of the piston 30 and the turbine hub 17 is thereby sealed.

<Drive plate 31>
The drive plate 31 is fixed to the side surface on the transmission side on the outer peripheral side of the piston 30. Specifically, the drive plate 31 is formed in an annular shape, and the inner peripheral portion 31a is fixed to the transmission side surface of the piston 30 by a rivet (not shown). A plurality of engaging portions 31 b are formed on the outer peripheral portion of the drive plate 31. The engaging portion 31 b is bent at the outer peripheral end toward the transmission side and is engaged with both ends of the outer peripheral side torsion spring 32 in the circumferential direction.

<Outer peripheral side torsion spring 32 and float member 33>
The plurality of outer peripheral side torsion springs 32 are composed of, for example, a total of six springs in one set, and the float member 33 is provided so that the two outer peripheral side torsion springs 32 of each set act in series. Yes.

  The float member 33 is an annular member having a C-shaped cross section, and is disposed between the outer peripheral portion of the piston 30 and the outer peripheral portion of the drive plate 31 in the axial direction. The float member 33 is disposed so as to be rotatable relative to the drive plate 31, the outer peripheral portion 33 a supports the outer peripheral portion of the outer peripheral torsion spring 32, and the side portion 33 b supports the side of the outer peripheral side torsion spring 32 on the engine side. I support it.

  The tip 33c of the float member 33 on the transmission side in the axial direction is bent on the inner peripheral side and the engine side. The bent portion 33c of the tip is inserted between the pair of outer peripheral torsion springs 32. ing. That is, both end surfaces of the bent portion 33 c in the circumferential direction are in contact with the corresponding end surfaces of the outer peripheral torsion springs 32.

  The inner peripheral end 33 d of the float member 33 can abut on the piston side surface of the drive plate 31. Further, the inner peripheral end surface of the float member 33 is supported on the outer peripheral surface of a support portion 31 c formed on a part of the drive plate 31. That is, the float member 33 is restricted from moving in the axial direction by the piston 30 and the drive plate 31, and is positioned in the radial direction by the support portion 31 c of the drive plate 31.

  As described above, both ends in the circumferential direction of the set of outer peripheral side torsion springs 32 arranged so as to act in series engage with the engaging portions 31b of the drive plate 31, and the one set of outer peripheral side torsion springs 32 A bent portion 33c of the float member 33 is inserted in the intermediate portion.

<Intermediate member 34>
FIG. 3 shows the intermediate member 34 and the dynamic damper device 37 extracted from FIG. The intermediate member 34 is a member for connecting the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 35 in series, and has a function of holding the inner peripheral side torsion spring 35. Yes. The intermediate member 34 includes a first plate 41 and a second plate 42, and is rotatable relative to the drive plate 31 and the hub flange 36.

  The first and second plates 41 and 42 are annular and disk-shaped members disposed between the piston 3 and the turbine shell 15. The first plate 41 and the second plate 42 are arranged with a gap in the axial direction. The first plate 41 is disposed on the engine side, and the second plate 42 is disposed on the transmission side.

  The first plate 41 includes a disk-shaped main body 41a and a plurality of protrusions 41b protruding from the main body 41a to the outer peripheral side. The plurality of protruding portions 41b are formed at predetermined intervals in the circumferential direction. A plurality of locking portions 41 c extending to the outer peripheral torsion spring 32 are formed at the tip (outer peripheral end) of the protruding portion 41 b. The locking portion 41c is formed by bending the tip of the protruding portion 41b toward the axial engine side. A pair of outer peripheral torsion springs 32 that act in series are disposed between the two locking portions 41c. Further, as is apparent from FIG. 5, a first abutting portion 41d formed by being cut and raised toward the second plate 42 is provided at the circumferential central portion of the protruding portion 41b.

  5 is a view of the outer peripheral portion (the protruding portion 41b and the locking portion 41c) of the first plate 41 as viewed from the front cover 2 side.

  The second plate 42 has a disc-shaped main body portion 42a, and a plurality of second contact portions as a second abutting portion are arranged on the outer peripheral portion of the main body portion 42a at predetermined intervals in the circumferential direction as shown in FIG. A protruding portion (hereinafter, referred to as a “second contact portion”) 42 d is formed. The plurality of second contact portions 42d are formed by protruding the outer peripheral portion of the second plate 42 further outward in the radial direction and offset from the main body portion 42a to the first plate 41 side. The second contact portion 42 d of the second plate 42 and the first contact portion 41 d of the first plate 41 are in contact with each other, and the contacted portion of both is a plurality of rivets (fixing members) 43. Are connected so as not to be relatively rotatable and axially immovable. That is, it functions as a first engaging portion.

  Moreover, the outer peripheral part of the main-body part 42a has the inlay part 45b formed by once bending the outer peripheral part of the main-body part 42a to the turbine 4 side. The inlay portion 45b is formed in a cylindrical shape.

  The first plate 41 and the second plate 42 are formed with window portions 41e and 42e penetrating in the axial direction, respectively. The window portions 41e and 42e are formed to extend in the circumferential direction, and cut and raised portions that are cut and raised in the axial direction are formed on the inner peripheral portion and the outer peripheral portion.

  The intermediate member 34 as described above allows the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 35 to act in series.

<Inner circumference torsion spring 35>
As shown in FIGS. 3 and 4, each of the plurality of inner peripheral side torsion springs 35 is inserted into the large coil spring 35a and the small coil having the same length as the spring length of the large coil spring 35a. It consists of a combination with a coil spring 35b. Each inner peripheral torsion spring 35 is disposed in the window portions 41 e and 42 e of both plates 41 and 42 of the intermediate member 34. Each inner torsion spring 35 is supported at both ends in the circumferential direction and both sides in the radial direction by window portions 41e and 42e. Further, each inner torsion spring 35 is restricted from projecting in the axial direction by the cut-and-raised portions of the window portions 41e and 42e.

<Hub flange 36>
The hub flange 36 is an annular and disk-shaped member, and an inner peripheral portion thereof is fixed to the flange 17 a of the turbine hub 17 by a rivet 18 together with the turbine shell 15. The hub flange 36 is disposed between the first plate 41 and the second plate 42 so as to be rotatable relative to the plates 41 and 42. A window hole 36 a is formed in the outer peripheral portion of the hub flange 36 corresponding to the window portions 41 e and 42 e of the first and second plates 41 and 42. The window hole 36a is a hole penetrating in the axial direction, and an inner peripheral torsion spring 35 is disposed in the window hole 36a.

<Stopper mechanism 39>
The stopper mechanism 39 is constituted by a part of the first plate 41 and the second plate 42 and a part of the hub flange 36. Specifically, as shown in FIGS. 3 to 5, the first contact portion 41 d of the first plate 41 and the second contact portion 42 d of the second plate 42 are in contact with each other and fixed by a rivet 43. ing. And the 1st engaging part is formed as mentioned above.

  On the other hand, a plurality of stopper projections 36b (see FIG. 4) projecting to the outer peripheral side are formed on the outer peripheral portion of the hub flange 36. The stopper projection 36b is disposed at a position overlapping the contact portions 41d and 42d of the first and second plates 41 and 42 in the axial direction. As shown in FIG. 4, the stopper projection 36b is disposed between the two contact portions 41d and 42d in the circumferential direction, and is disposed at a position overlapping the both contact portions 41d and 42d in the radial direction. Has been. As described above, the stopper projection 36b functions as a second engagement portion.

  Therefore, when the relative rotation between the first and second plates 41 and 42 and the hub flange 36 increases, the circumferential side surface of the stopper projection 36b (second engaging portion) and the first and second plates The side surfaces in the circumferential direction of the contact portions 41d and 42d (first engagement portions) are in contact with each other, and the relative rotation of both is restricted.

[Dynamic damper device 37]
As shown in FIGS. 3 and 4, the dynamic damper device 37 includes a damper plate portion 45 that is an outer peripheral extension portion of the second plate 42 of the intermediate member 34, a pair of inertia rings 46, and a pair of lid members 47. And a spring unit (elastic damper elastic member) 48 and a stop pin 49. FIG. 4 is a partial view of the dynamic damper device 34 viewed from the turbine 4 side.

<Damper plate 45>
As described above, the damper plate portion 45 is a portion formed by extending the outer peripheral portion of the second plate 42 constituting the intermediate member 34 further outward in the radial direction. As shown in FIG. 4, the damper plate part 45 is arrange | positioned between the circumferential directions of the 2nd contact part 42d. That is, the damper plate part 45 and the second contact part 42d provided with the rivets 43 are provided at different positions in the circumferential direction. For this reason, the radial dimension of the second plate 42 can be suppressed.

  Further, the damper plate portion 45 extends further outward than the second contact portion 42d. The damper plate portion 45 is formed with a spring storage portion 45a. The spring accommodating portion 45a is formed to extend in the circumferential direction and penetrates in the axial direction.

<Inertia ring 46>
The pair of inertia rings 46 is formed by pressing a sheet metal member, and is disposed on both axial sides of the damper plate portion 45. The two inertia rings 46 have the same configuration. As shown in FIG. 6, the inertia ring 46 has a plurality of spring accommodating portions 46a at predetermined intervals in the circumferential direction. The spring accommodating portion 46 a is formed at a position corresponding to the spring accommodating portion 45 a of the damper plate portion 45. The inertia ring 46 has a plurality of through holes 46b. The plurality of through holes 46 b are holes to which the stop pins 49 are attached, and are formed between the circumferential directions of the plurality of damper plate portions 45. Furthermore, a notch 46c that is recessed on the outer peripheral side is formed on the inner peripheral edge of the inertia ring 46 in order to avoid interference with the protrusions 42a of the second plate 42 during assembly.

  The pair of lid members 47 are disposed on the outer side in the axial direction of the pair of inertia rings 46. Specifically, one lid member 47 is further disposed on the front cover 2 side of the inertia ring 46 disposed on the front cover 2 side, and the other lid member 47 is further disposed on the inertia ring 46 disposed on the turbine 4 side. It is arranged on the turbine 4 side.

<Lid member 47>
As shown in FIG. 4, the lid member 47 is formed in an annular shape, the outer diameter is the same as the outer diameter of the inertia ring 46, and the inner diameter is larger than the outer diameter of the protruding portion 42 d of the second plate 42. is there. A through hole 47 b is formed in the lid member 47 at a position corresponding to the through hole 46 b of the inertia ring 46.

<Spring unit 48>
As shown in FIG. 4, the spring unit 48 includes large and small coil springs 48a and 48b housed in a plurality of spring housing portions 45a. The large coil spring 48a has substantially the same length as the circumferential length of the spring storage portion 45a. Therefore, both end portions of the large coil spring 48 a are in contact with the end portions in the circumferential direction of the spring accommodating portions 45 a and 46 a of the damper plate portion 45 and the inertia ring 46. The small coil spring 48b is disposed on the inner peripheral portion of the large coil spring 48a, and is set shorter by the length of the large coil spring 48a. For this reason, the small coil spring 48b operates later than the operation of the large coil spring 48a.

<Stop pin 49>
The stop pin 49 is attached to the inertia ring 46 and the through holes 46 b and 47 b of the lid member 47. That is, the stop pin 49 is disposed between the circumferential directions of the plurality of damper plate portions 45. As shown in FIG. 7, the stop pin 49 has a large-diameter barrel portion 49a at the center in the axial direction and small-diameter barrel portions 49b on both sides thereof. The large diameter body 49 a has a larger diameter than the through hole 46 b of the inertia ring 46. Further, the large-diameter trunk portion 49 a is formed to be slightly thicker than the damper plate portion 45.

  The small diameter barrel portion 49 b is inserted through the through hole 46 b of the inertia ring 46 and the through hole 47 b of the lid member 47. And the inertia ring 46 and the cover member 47 are being fixed to the axial direction both sides of the damper plate part 45 by crimping the head of the small diameter trunk | drum 49b.

  With the above-described configuration, the damper plate 45, the inertia ring 46, and the lid member 47 can be relatively rotated within a range in which the stop pin 49 can move between the adjacent damper plate portions 45. Then, when the large-diameter body portion 49a of the stop pin 49 abuts on the circumferential end surface of the damper plate portion 45, the relative rotation of both is restricted.

  Further, in a state where the inertia ring 46 and the lid member 47 are fixed by the stop pin 49, the inner peripheral surface of the inertia ring 46 abuts on the outer peripheral surface of the spigot part 45 b of the damper plate portion 45, thereby the inertia ring 46 and the lid The member 47 and the large and small coil springs 48a and 48b are positioned in the radial direction.

[Operation]
First, the operation of the torque converter body will be briefly described. In a state where the front cover 2 and the impeller 3 are rotating, hydraulic oil flows from the impeller 3 to the turbine 4, and torque is transmitted from the impeller 3 to the turbine 4 through the hydraulic oil. Torque transmitted to the turbine 4 is transmitted to an input shaft (not shown) of the transmission via the turbine hub 17.

  When the speed ratio of the torque converter 1 increases and the input shaft reaches a constant rotational speed, the hydraulic oil between the front cover 2 and the piston 30 is drained, and the hydraulic oil is supplied to the turbine 4 side of the piston 30. Then, the piston 30 is moved to the front cover 2 side. As a result, the friction member 38 fixed to the piston 30 is pressed against the front cover 2, and the lockup clutch is turned on.

  In the clutch-on state as described above, torque is transmitted through the path of the front cover 2 → piston 30 → drive plate 31 → outer side torsion spring 32 → intermediate member 34 → inner side torsion spring 35 → hub flange 36. It is output to the hub 17.

  The lockup device 7 transmits torque and absorbs and attenuates torque fluctuations input from the front cover 2. Specifically, when torsional vibration occurs in the lockup device 7, the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 35 are compressed in series between the drive plate 31 and the hub flange 36. Furthermore, also in the outer peripheral side torsion spring 32, one set of outer peripheral side torsion springs 32 is compressed in series. For this reason, the twist angle can be widened.

[Operation of Dynamic Damper Device 37]
The torque transmitted to the intermediate member 34 is transmitted to the hub flange 36 via the inner peripheral side torsion spring 35, and further transmitted to the transmission side member via the turbine hub 17. At this time, since the dynamic damper device 37 is provided in the intermediate member 34, fluctuations in the rotational speed of the engine can be effectively suppressed. That is, the rotation of the damper plate portion 45 and the rotation of the inertia ring 46 and the lid member 47 cause a phase shift due to the action of the damper mechanism 48. Specifically, the inertia ring 46 and the lid member 47 fluctuate at a phase that cancels out the rotational speed fluctuation of the damper plate portion 45 at a predetermined engine speed. Due to this phase shift, the rotational speed fluctuation of the transmission can be absorbed.

  In this embodiment, the dynamic damper device 37 is fixed to the intermediate member 34, and the inner peripheral torsion spring 35 for suppressing vibration is disposed between the dynamic damper device 37 and the turbine hub 17. Due to the action of the inner periphery side torsion spring 35, as shown in FIG. 8, it is possible to more effectively suppress the rotational speed fluctuation. In FIG. 8, the characteristic C1 shows the rotational speed fluctuation in the conventional lockup device. Characteristic C2 shows the fluctuation when the dynamic damper device is mounted on the turbine hub and there is no torsion spring on the output side of the dynamic damper device. Further, the characteristic C3 shows the fluctuation when the dynamic damper device 37 is attached to the intermediate member 34 and the inner periphery side torsion spring 35 is provided on the output side of the dynamic damper device 37 as in the present embodiment.

  As is clear by comparing the characteristics C2 and C3 in FIG. 8, when the inner peripheral torsion spring 35 is provided on the output side of the dynamic damper device 37, the peak of the rotational speed fluctuation is reduced, and the engine speed is reduced. The rotational speed fluctuation can be suppressed even in the normal number range.

  Here, the spring unit 48 has two-stage torsional characteristics. Specifically, when relative rotation occurs between the damper plate portion 45, the inertia ring 46, and the lid member 47, only the large coil spring 48a is first compressed in the low torsion angle region, and the low rigidity torsion is performed. The spring unit 48 is actuated by the rotation characteristics (first stage torsion characteristics). In this case, the inertia ring 46 and the lid member 47 rotate relative to the damper plate portion 45 with a relatively small resistance, and the rotational speed fluctuation can be effectively suppressed.

  When a larger rotational fluctuation occurs and a larger relative rotation occurs between the damper plate portion 45 and the inertia ring 46 and the lid member 47, the small coil spring 48b is also compressed in addition to the large coil spring 48a. become. For this reason, the spring unit 48 operates with higher torsional characteristics (second stage torsional characteristics) compared to low rigidity torsional characteristics.

  When such a large rotational fluctuation occurs, the spring unit 48 is operated with the second-stage torsion characteristic through the first-stage torsion characteristic. In this case, the inertia ring 46 and the lid member 47 are less likely to rotate with respect to the damper plate portion 45 and the relative rotational speed of both is reduced compared to the case where the first stage torsion characteristic is operated. To do. For this reason, even if the circumferential end surface of the damper plate portion 45 collides with the stop pin 49, the impact is suppressed as compared with the conventional dynamic damper device having only one-stage torsional characteristics.

[Feature]
(1) The stopper mechanism 39 is configured by bringing the stopper protrusions 36b of the hub flange 36 into contact with the contact portions 41d and 42d formed on the first plate 41 and the second plate 42. For this reason, it is not necessary to use the stop pin used in the conventional stopper mechanism. Therefore, a space for avoiding interference between the stopper mechanism and other members becomes unnecessary, and the axial space of the entire apparatus can be shortened. Further, the number of parts constituting the stopper mechanism is reduced.

  (2) The first contact portion 41d (first engagement portion) constituting the stopper mechanism 39 by cutting and raising the circumferential center portion of the protrusion 41b and the locking portion 41c that receive torque from the outer peripheral torsion spring 32. Is forming. For this reason, the 1st contact part 41d for the stopper mechanism 39 can be formed, ensuring the width | variety of the circumferential direction of the protrusion part 41b and the latching | locking part 41c enough, and maintaining intensity | strength.

  (3) For the same reason as described above, the coil diameter of the outer peripheral torsion spring can be increased when the same axial space as in the prior art is secured. For this reason, a damper mechanism can be made more rigid and the fuel-saving of the vehicle which employ | adopted this lockup apparatus can be achieved.

  (4) A damper plate portion 45 of the dynamic damper device 37 is constituted by a part of the second plate 42 constituting the intermediate member 34. For this reason, the number of parts of the whole apparatus can be suppressed. In particular, even when the dynamic damper device 37 is provided together with the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 35, it is possible to avoid an increase in the size of the entire device.

  (5) In the second plate 42, the second contact portion 42d with the first plate 41 and the damper plate portion 45 are provided at different positions in the circumferential direction. For this reason, it can suppress that the 2nd plate 42 becomes large in radial direction.

  (6) Since the pair of inertia rings 46 are arranged on both sides of the damper plate portion 45 to constitute the dynamic damper device 37, the pair of inertia rings 46 can be formed of plate members. Therefore, the manufacturing cost can be reduced as compared with the case where the inertia ring is formed of a cast product or a forged product.

  (7) Since the damper mechanism 48 is accommodated in the damper plate portion 45 and the inertia ring 46, the space occupied by the dynamic damper device in the axial direction can be made particularly compact.

  (8) Since the inertia ring 46 is divided in the axial direction, the insertion of the damper plate portion 45 and the assembly of the damper mechanism 48 are facilitated.

  (9) Since the dynamic damper device 37 is mounted on the intermediate member 34 and the inner peripheral side torsion spring 35 is provided on the output side of the dynamic damper device 37, the rotational speed fluctuation can be more effectively suppressed.

[Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

  (A) In the above embodiment, the present invention is applied to a lockup device having an outer periphery side torsion spring in addition to an inner periphery side torsion spring. However, the device is provided with a torsion spring only on one side. The present invention can be similarly applied.

  (B) In the above-described embodiment, the present invention is applied to the configuration in which the first and second plates 41 and 42 are provided so as to be rotatable relative to the drive plate 31 and the hub flange 36. The present invention is not limited to the embodiment. For example, the present invention can be applied to a configuration in which first and second plates are fixed to a turbine, and an inertia member (third plate) is provided on the first and second plates so as to be relatively rotatable.

DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 4 Turbine 6 Torque converter main body 7 Lockup apparatus 30 Piston 32 Outer peripheral side torsion spring 35 Inner peripheral side torsion spring 36 Hub flange 36b Stopper projection 37 Dynamic damper apparatus 39 Stopper mechanism 41 First plate 41d First 1 contact portion 42 second plate 42d second contact portion 46 inertia ring 48 spring unit

Claims (8)

A lockup device disposed between a front cover coupled to a member on an engine side and a torque converter main body, for directly transmitting torque from the front cover to a turbine of the torque converter main body,
A clutch portion for transmitting torque from the front cover to the output side;
Torque from the clutch portion is input and the first and second plates provided opposite to each other in the axial direction, and the first and second plates are rotatable relative to each other between the axial directions of the first and second plates. A third plate disposed; and a plurality of elastic members that elastically connect the first and second plates and the third plate in a rotational direction and are held by the first and second plates. A damper mechanism,
A first engagement portion formed on at least one of the first and second plates and an engagement between the first engagement portion formed on the third plate and the first engagement portion. A stopper mechanism having a second engagement portion that regulates a relative rotation angle with the plate within a predetermined angle range;
Equipped with a,
The first plate is
A disc-shaped body,
A plurality of protrusions protruding from the main body part toward the outer peripheral side and formed at predetermined intervals in the circumferential direction;
Have
A part of the first engaging portion is formed by cutting and raising a circumferential central portion of the plurality of protruding portions toward the second plate.
Torque converter lockup device.   The torque converter lockup device according to claim 1, wherein the third plate is rotatable relative to the clutch portion and is connected to the turbine.   The damper mechanism further includes a plurality of outer peripheral side elastic members disposed on the outer peripheral side of the elastic member, and the plurality of outer peripheral side elastic members move the clutch portion and the first and second plates in the rotation direction. The lockup device for a torque converter according to claim 1, wherein the lockup device is elastically connected. The first and second plates have a plurality of first and second contact portions formed by bending so as to contact each other's plates at predetermined intervals in the circumferential direction;
A part of the first engagement portion is the first contact portion,
The damper mechanism includes a fixing member that fixes the first plate and the second plate so as not to be relatively rotatable and to be axially movable by fastening the first contact portion and the second contact portion. In addition,
The first engagement portion is formed by the first and second contact portions,
The torque converter lockup device according to any one of claims 1 to 3. The third plate is formed in a disc shape,
The second engaging portion has a plurality of stopper protrusions formed to protrude from the outer peripheral surface of the third plate to the outer peripheral side, and the plurality of stopper protrusions are the first and second plurality of stoppers. The first and second contact portions are arranged at positions overlapping in the axial direction and the radial direction between the circumferential directions of the contact portions.
The torque converter lockup device according to claim 4. Said first plate, said plurality of opposite ends in the circumferential direction is provided at the tip of the protrusion has further a plurality of locking portions can be engaged with both ends of the outer peripheral side elastic member, in claim 3 The torque converter lockup device described.
  2. A dynamic damper device that is provided on one of the first and second plates and has an inertia member that is rotatably provided relative to the first and second plates, further comprising a dynamic damper device that attenuates rotational speed fluctuations. To 6. The torque converter lockup device according to any one of items 1 to 6. 8. The lockup device for a torque converter according to claim 7, wherein the dynamic damper device further includes a plurality of dynamic damper elastic members that elastically connect the first and second plates and the inertia member in a rotation direction. .

Images