JP2006250159A - Flywheel assembly - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress increase in hysteresis torque or abrasion of parts by a centrifugal force in operating a flywheel assembly, in a flywheel assembly provided with flywheel to which torque from a crankshaft of an engine is transmitted through a damper part. <P>SOLUTION: The flywheel assembly 1 comprises: an input side rotor 4; an output side rotor 5 disposed to the input side rotor 4 to be relatively rotatable and including the flywheel 51; a positive side spiral spring 82; and a negative side spiral spring 83. The positive side spiral spring 82 connects the input side rotor 4 with the output side rotor 5 in a rotation direction, and is operated in a tightening direction when the input side rotor 4 is twisted with respect to the output side rotor 5 on a rotation direction R1 side. The negative side spiral spring 83 connects the input side rotor 4 with the output side rotor 5 in the rotation direction, and is operated in the tightening direction when the input side rotor 4 is twisted with respect to the output side rotor 5 on a rotation direction R2 side. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a flywheel assembly, and more particularly to a flywheel assembly including a flywheel to which torque from an engine crankshaft is transmitted via a damper portion.

  A flywheel is mounted on the crankshaft of the engine in order to absorb vibrations caused by engine combustion fluctuations. Further, a clutch device is provided on the flywheel axial transmission side. The clutch device includes a clutch disk assembly coupled to an input shaft of the transmission, and a clutch cover assembly that biases a friction coupling portion of the clutch disk assembly to the flywheel. The clutch disk assembly has a damper portion for absorbing and damping torsional vibration. The damper part has an elastic member composed of a plurality of coil springs arranged so as to be compressed in the rotation direction.

On the other hand, a structure in which the damper portion is provided between the flywheel and the crankshaft instead of the clutch disk assembly is also known. In this case, the flywheel is positioned on the output side of the vibration system with the coil spring as a boundary, and the inertia on the output side is larger than in the conventional case. As a result, the resonance rotational speed can be set to be equal to or lower than the idle rotational speed, and a large damping performance can be realized. In this way, a structure configured by combining the flywheel and the damper portion is a flywheel assembly. The damper part of the flywheel assembly has an elastic member mainly composed of a plurality of coil springs arranged so as to be compressed in the rotational direction, like the damper part of the clutch disk assembly (for example, Patent Documents). 1).
JP-A-4-231757

  However, since the damper portion of the conventional flywheel assembly uses a plurality of coil springs, the plate members such as retaining plates for holding them and the plate members are fixed with the coil spring held. Therefore, a large number of fastening members such as rivets are required to increase the number of parts and the number of assembly steps.

  Further, when the conventional flywheel assembly is operated, centrifugal force acts on the coil spring. For this reason, since the coil spring moves outward in the radial direction and easily slides on the plate member for holding the coil spring, an increase in hysteresis torque, a plate member for holding the coil spring and the coil spring, etc. Wear of parts cannot be avoided.

  An object of the present invention is to provide an increase in hysteresis torque due to centrifugal force during operation of a flywheel assembly in a flywheel assembly including a flywheel in which torque from an engine crankshaft is transmitted via a damper portion. It is to suppress wear of parts.

  The flywheel assembly according to claim 1 is for transmitting torque from a crankshaft of an engine, and includes an input side rotating body, an output side rotating body, a positive side spiral spring, and a negative side spiral. And a spring. The input side rotating body receives torque from the crankshaft. The output-side rotator is disposed so as to be rotatable relative to the input-side rotator, and includes a flywheel. The positive-side spiral spring connects the input-side rotator and the output-side rotator in the rotational direction. When the input-side rotator is twisted in the rotational direction drive side with respect to the output-side rotator, Operate. The negative spiral spring connects the input-side rotator and the output-side rotator in the rotational direction. When the input-side rotator is twisted to the opposite side of the rotational direction drive side with respect to the output-side rotator. Operates in the winding direction.

  In this flywheel assembly, torque from the crankshaft of the engine is transmitted in the order of the input side rotary body, the positive side spiral spring, the negative side spiral spring, and the output side rotary body. When the combustion fluctuation from the engine is input to the flywheel assembly, the input side rotating body and the output side rotating body rotate relative to each other, and the positive side spiral spring and the negative side spiral spring operate between them. Torsional vibration is absorbed and attenuated.

  In this flywheel assembly, a spiral spring is used as an elastic member for connecting the input-side rotator and the output-side rotator in the rotational direction, so that when the input-side rotator and the output-side rotator rotate. It is less susceptible to centrifugal force. In addition, in this flywheel assembly, as the spiral spring, a positive spiral spring that operates in the tightening direction when the input-side rotator is twisted in the rotational direction drive side with respect to the output-side rotator, and the input-side rotator Is used with a negative spiral spring that operates in the tightening direction when twisted in the direction opposite to the rotation direction drive side with respect to the output side rotating body, when twisting to the positive side and twisting to the negative side In both cases, it is possible to obtain the torsional characteristics when the spiral spring is operated in the tightening direction, so that the structure of the spiral spring basically used in the direction of tightening is considered.

  As described above, in this flywheel assembly, the elastic member for connecting the input-side rotator and the output-side rotator in the rotation direction corresponds to the positive member corresponding to the case of twisting to the positive side and the case of twisting to the negative side. Since the side spiral spring and the negative spiral spring are used, it is possible to suppress an increase in hysteresis torque and wear of the elastic member due to centrifugal force when the input side rotating body and the output side rotating body rotate.

  A flywheel assembly according to a second aspect is the flywheel assembly according to the first aspect, in which the input-side rotating body is positively rotated during the positive-side twisting operation in which the input-side rotating body is twisted from the neutral state to the rotational direction drive side. A spring operation mechanism that operates only the spiral spring and operates only the negative spiral spring during the negative twisting operation in which the output side rotating body is twisted from the neutral state to the rotation direction drive side. Have.

  In this flywheel assembly, the torsional characteristics of only the positive spiral spring can be obtained during the positive side twisting operation by the spring operating mechanism that constitutes the input side rotating body, and the negative side torsional operation can be performed under the negative side torsional operation. It is possible to obtain torsional characteristics using only the side spiral spring.

  A flywheel assembly according to a third aspect is the flywheel assembly according to the second aspect, wherein the spring operating mechanism includes a drive plate, a positive side hub, and a negative side hub. Torque from the crankshaft is input to the drive plate. The positive side hub is connected to the positive side spiral spring, and is rotated by the drive plate during the positive side twisting operation, but is not driven by the drive plate during the negative side twisting operation. The negative hub is connected to a negative spiral spring, and is rotated by the drive plate during the negative twisting operation, but is not rotated by the drive plate during the positive twisting operation.

  In this flywheel assembly, the torque from the crankshaft of the engine is transmitted from the drive plate to the positive side hub or the negative side hub in accordance with the direction of twisting operation of the drive plate constituting the spring operating mechanism, and the positive side spiral It is transmitted to the output side rotator via a spring or a negative spiral spring.

A flywheel assembly according to a fourth aspect is the flywheel assembly according to the third aspect, wherein the first spiral spring and the second spiral spring are arranged side by side in the axial direction.
In this flywheel assembly, interference between the first spiral spring and the second spiral spring can be prevented. Further, the positive side hub and the negative side hub can also be arranged side by side in the axial direction according to the arrangement of the first spiral spring and the second spiral spring.

  According to a fifth aspect of the present invention, in the flywheel assembly according to the fourth aspect, the drive plate has a drive claw extending in the axial direction. The positive side hub has a positive side driving claw guide portion that abuts the circumferential end of the driving claw during the positive side twisting operation and guides the driving claw rotatably during the negative side twisting operation. The negative side hub has a negative side drive claw guide portion that abuts the circumferential end of the drive claw during the negative side twist operation and guides the drive claw rotatably during the positive side twist operation. .

  In this flywheel assembly, during the positive side twisting operation, the drive claw of the drive plate contacts the positive side drive claw guide portion of the positive side hub to drive the positive side hub. Then, the driving claw rotates with respect to the negative side hub by the negative side driving claw guide portion of the negative side hub. As a result, the positive hub is rotated by the drive plate and the negative hub is not rotated by the drive plate, and only the positive spiral spring is operated during the positive twisting operation. be able to. Further, during the negative side twisting operation, the drive claw of the drive plate contacts the negative side drive claw guide portion of the negative side hub to drive the negative side hub. Then, the driving claw is rotated with respect to the positive side hub by the positive side driving claw guide portion of the positive side hub. As a result, the negative hub is rotationally driven by the drive plate and the positive hub is not rotationally driven by the drive plate, and only the negative spiral spring is activated during the negative torsion operation. be able to.

  A flywheel assembly according to a sixth aspect is the flywheel assembly according to the fifth aspect, wherein the drive pawl is formed by cutting and raising a part of the drive plate.

  In the flywheel assembly according to the present invention, as an elastic member for connecting the input-side rotator and the output-side rotator in the rotational direction, the positive side corresponding to each of when twisting to the positive side and twisting to the negative side Since the spiral spring and the negative spiral spring are used, it is possible to suppress an increase in hysteresis torque and wear of the elastic member due to a centrifugal force when the input side rotating body and the output side rotating body rotate.

Hereinafter, embodiments of a flywheel assembly according to the present invention will be described with reference to the drawings.
(1) Overall Configuration of Flywheel Assembly FIGS. 1 to 6 show a flywheel assembly 1 as an embodiment of the present invention. The flywheel assembly 1 uses torque from a crankshaft 11 of an engine (not shown) disposed on the left side of FIG. 1 as a clutch (specifically, a clutch disk assembly 2 and a clutch cover assembly 3). Is a mechanism for transmitting to the input shaft 12 of a transmission (not shown) arranged on the right side of FIG. The flywheel assembly 1 has a damper function for absorbing and attenuating torsional vibrations, and mainly includes an input-side rotating body 4, an output-side rotating body 5, an input-side rotating body 4, and an output-side rotating body. 5, a first damper portion 6, a friction generating mechanism 7, and a second damper portion 8.

  Here, FIG. 1 is a schematic vertical cross-sectional view (E-O-F cross-sectional view of FIG. 3) of the flywheel assembly 1. FIG. 2 is a plan view of the flywheel assembly 1 (a cross-sectional view taken along the line CD in FIG. 1). FIG. 3 is a plan view of the flywheel assembly 1 (cross-sectional view taken along the line AB in FIG. 1). FIG. 4 is an enlarged view of FIG. FIG. 5 is an enlarged view of FIG. FIG. 6 is an enlarged view of FIG. Note that OO in FIGS. 1 and 6 is a rotation axis of the flywheel assembly 1. In the following description, when the axial position of the flywheel assembly 1 is described, the left side in FIGS. 1 and 6 is the axial engine side, and the right side is the axial transmission side. Furthermore, when the rotation direction of the flywheel assembly 1 is described, the direction of the arrow R1 in FIGS. 2 to 5 is the driving side or the positive side, and the direction of the arrow R2 in FIGS. Negative side.

(2) Configuration of Input-side Rotator The input-side rotator 4 is a member to which torque from the crankshaft 11 is input, and mainly includes a drive plate 41, a positive-side hub 42, a negative-side hub 43, and a driven And plate 44.

<Drive plate>
The drive plate 41 is a plate-like plate member made of sheet metal having a center hole, and has a function of transmitting torque from the crankshaft 11 to the positive side hub 42, the negative side hub 43 and the driven plate 44. ing.

  The inner peripheral portion of the drive plate 41 is fixed to the tip of the crankshaft 11 by a plurality of bolts 13. Bolt holes 41 a are formed in the drive plate 41 at positions corresponding to the bolts 13.

  The inner peripheral end of the drive plate 41 is provided with an inner peripheral cylindrical portion 41b extending toward the axial transmission side formed by press bending the inner peripheral portion of the drive plate 41 or the like. A bearing 14 (specifically, an inner race 14a of the bearing 14) is fitted to the outer peripheral surface of the inner peripheral cylindrical portion 41b. The axial end of the bearing 14 on the engine side is locked to a stepped portion 41c formed on the inner cylindrical portion 41b, and the end surface on the axial transmission side is locked by a snap ring 15, so that the axial direction The inner circumferential tubular portion 41b is fitted in a state in which the inner circumferential tubular portion 41b cannot move.

  A first driving claw portion 41d and a second driving portion extending toward the axial transmission side formed by cutting and machining a part of the radial central portion of the drive plate 41 at the radial central portion of the drive plate 41. A claw portion 41e is provided. A plurality of first drive claws 41d are provided side by side in the circumferential direction. In the present embodiment, two first drive claw portions 41d are provided side by side at equal intervals in the circumferential direction. A plurality of second drive claws 41e are provided side by side in the circumferential direction. In the present embodiment, two second driving claws 41e are provided side by side between the circumferential directions of the first driving claws 41d at a position radially inward of the first driving claws 41d. .

  An arc-shaped slit hole 41 f is formed on the outer periphery of the drive plate 41. The slit holes 41f are provided so as to correspond to the circumferential positions of the first drive claws 41d. In the present embodiment, the circumferential center position of the slit hole 41f is provided so as to coincide with the circumferential center position of the first drive claw portion 41d.

  An engine starting ring gear 16 is fixed to the outer peripheral end of the drive plate 41 by welding or the like. The engine starting ring gear 16 is a member thicker than the plate thickness of the drive plate 41, and also has a function as an inertia member of the flywheel assembly 1.

Thus, the drive plate 41 rotates integrally with the crankshaft 11.
<Positive hub>
The positive side hub 42 is a disk-shaped member in which a center hole 42a is formed, and functions to be driven to rotate when the drive plate 41 is twisted at least in the rotational direction R1 side. The positive side hub 42 is disposed on the axial transmission side of the drive plate 41.

  The center hole 42a has a diameter that allows each second drive claw portion 41e to be fitted from the axial direction. In addition, an arcuate positive side drive claw guide portion formed by notching the peripheral edge portion of the center hole 42a to a radial position where each first drive claw portion 41d can be fitted from the axial direction. 42b is provided. The positive drive claw guide portion 42b is cut out to a circumferential width larger than the circumferential width of the first drive claw portion 41d, and the circle of the first drive claw portion 41d is provided at both ends in the circumferential direction. Drive claw abutting portions 42c and 42d with which circumferential ends can abut are formed. The positive side hub 42 is provided in a state of being fitted to the drive claws 41 d and 41 e of the drive plate 41 from the axial direction. Further, since the outer diameter of the positive side hub 42 is substantially half of the outer diameter of the drive plate 41, a relatively large space is formed on the outer peripheral side of the positive side hub 42. Here, of the drive claw contact portions 42c and 42d, the drive claw contact portion that can contact when the first drive claw portion 41d is twisted in the rotation direction R1 side is referred to as a drive claw contact portion 42c. A drive claw contact portion that can contact when the first drive claw portion 41d is twisted in the rotation direction R2 side is referred to as a drive claw contact portion 42d.

  On the outer peripheral edge of the positive side hub 42, fixing portions 42e for fixing an input side end portion 82a of a positive side spiral spring 82 to be described later are provided in the number (specifically, two) of the positive side spiral springs 82. Correspondingly formed. In the present embodiment, the fixed portion 42e has a concave shape that allows the input-side end portion 82a of the positive spiral spring 82 to be fitted from the axial direction and prevents it from coming out in the radial direction. More specifically, the fixing portion 42e has a hole that penetrates the positive side hub 42 in the axial direction and a groove that is notched so that the outer peripheral edge of the positive side hub 42 communicates with the through hole. It has a different shape. In addition, the fixing portion 42e is disposed at a position where its circumferential position is shifted from the central position in the circumferential direction of each positive drive claw guide portion 42b toward the rotation direction R1, and each other is equally spaced in the circumferential direction. Are arranged side by side.

  Thus, when the drive plate 41 is twisted at least in the rotational direction R1, the positive side hub 42 has the circumferential end of the first drive claw portion 41d of the drive plate 41 driven by the positive side drive claw guide portion 42b. By rotating relative to the drive plate 41 until contacting the claw contact portion 42c, the circumferential end of the first drive claw portion 41d is then contacted to the drive claw contact portion 42c and is driven to rotate. The torque from the crankshaft 11 is input by rotating integrally with the drive plate 41. At this time, the second drive claw portion 41e of the drive plate 41 is disposed on the radially inner side with respect to the first drive claw portion 41d and the positive drive claw guide portion 42b. It can be rotated without hindering relative rotation with the drive plate 41.

<Negative hub>
The negative side hub 43 is a disk-shaped member having a center hole 43a formed therein, and functions to be driven to rotate when the drive plate 41 is twisted at least in the rotational direction R2. The negative side hub 43 is disposed on the axial transmission side of the drive plate 41. In the present embodiment, the negative hub 43 is disposed on the axial transmission side of the positive hub 42.

  The center hole 43a has a diameter capable of fitting each second drive claw portion 41e from the axial direction. In addition, an arc-shaped negative drive claw guide portion formed by cutting out the peripheral portion of the center hole 43a to a radial position where each first drive claw portion 41d can be fitted from the axial direction. 43b is provided. The negative drive claw guide portion 43b is cut out to a circumferential width larger than the circumferential width of the first drive claw portion 41d, and the circle of the first drive claw portion 41d is provided at both ends in the circumferential direction. Drive claw abutting portions 43c and 43d that can abut on the circumferential ends are formed. And the negative side hub 43 is provided along with the positive side hub 42 and the axial direction in the state fitted by the drive nail | claw part 41d, 41e of the drive plate 41 from the axial direction. Further, since the outer diameter of the negative side hub 43 is substantially half of the outer diameter of the drive plate 41, a relatively large space is formed on the outer peripheral side of the negative side hub 43. Here, of the drive claw contact portions 43c and 43d, a drive claw contact portion that can contact when the first drive claw portion 41d is twisted in the rotation direction R1 side is referred to as a drive claw contact portion 43c. The drive claw contact portion 43d is a drive claw contact portion that can come into contact when the first drive claw portion 41d is twisted in the rotation direction R2 side.

  Fixing portions 43e for fixing an input side end 83a of a negative spiral spring 83, which will be described later, are provided on the outer peripheral edge of the negative hub 43 in accordance with the number (specifically, two) of the negative spiral springs 83. Correspondingly formed. In the present embodiment, the fixing portion 43e has a concave shape that allows the input side end portion 83a of the negative spiral spring 83 to be fitted from the axial direction and prevents it from coming out in the radial direction. More specifically, the fixing portion 43e has a hole that penetrates the negative side hub 43 in the axial direction and a groove that is notched so that the outer peripheral edge of the negative side hub 43 communicates with the through hole. It has a different shape. Moreover, the fixing | fixed part 43e is arrange | positioned in the position where the circumferential direction position shifted | deviated to the rotation direction R2 side from the circumferential direction center position of each negative side drive nail | claw guide part 43b, and mutually is equidistantly spaced in the circumferential direction Are arranged side by side.

  Thus, when the drive plate 41 is twisted at least in the rotational direction R2, the negative side hub 43 has the circumferential end of the first drive claw portion 41d of the drive plate 41 driven by the negative side drive claw guide portion 43b. Until the contact with the claw contact portion 43d, it rotates relative to the drive plate 41, and then the circumferential end of the first drive claw portion 41d contacts the drive claw contact portion 43c and is driven to rotate. The torque from the crankshaft 11 is input by rotating integrally with the drive plate 41. At this time, the second drive claw portion 41e of the drive plate 41 is disposed on the radially inner peripheral side with respect to the first drive claw portion 41d and the negative side drive claw guide portion 43b. It can be rotated without hindering relative rotation with the drive plate 41.

In the present embodiment, the positive side hub 42 and the negative side hub 43 are members having the same shape and the same size.
<Driven plate>
The driven plate 44 is a disk-shaped member made of sheet metal in which a center hole 44a is formed, and functions so as to be rotationally driven when the drive plate 41 is twisted in the rotational direction. The driven plate 44 is disposed on the axial transmission side of the drive plate 41 and on the radially inner peripheral side of the hubs 42 and 43.

  A spring driving portion 44b formed by cutting out in the radial direction is provided at the peripheral portion of the center hole 44a. A plurality of spring drive portions 44b are provided side by side in the circumferential direction. In the present embodiment, two spring drive portions 44b are provided side by side at equal intervals in the circumferential direction. Both ends in the circumferential direction of the spring drive portion 44b are spring abutting portions 44c and 44d with which both ends in the circumferential direction of a coil spring 62 described later can abut.

  The outer peripheral edge of the driven plate 44 is a position on the inner peripheral side with respect to the peripheral positions of the center holes 42a, 43a of the hubs 42, 43 and the radial position of the first drive claw portion 41d of the drive plate 41, and the drive plate 41 extends to a position on the outer peripheral side with respect to the radial position of the second drive claw portion 41e. Then, an arc-shaped second drive claw guide portion formed by notching the outer peripheral edge of the driven plate 44 to a radial position where each second drive claw portion 41e can be fitted from the axial direction. 44e is provided. The second drive claw guide portion 44e is cut out to a circumferential width that is substantially the same as the circumferential width of the second drive claw portion 41e, and both ends in the circumferential direction are circumferential with respect to the second drive claw portion 41e. It is in contact with the direction end. In the present embodiment, two second drive claw guide portions 44e are provided side by side at equal intervals in the circumferential direction so as to correspond to each second drive claw portion 41e. Moreover, the spring drive part 44b is arrange | positioned between the circumferential directions of the 2nd drive nail | claw guide part 44e.

  Thus, when the drive plate 41 is twisted in the rotation direction R1 side and the R2 side, the driven plate 44 has the circumferential end of the second drive claw portion 41e of the drive plate 41 at the second drive claw guide portion 44e. Is rotated in contact with the end in the circumferential direction so as to rotate integrally with the drive plate 41 and the torque from the crankshaft 11 is inputted.

(3) Configuration of Output-side Rotator The output-side rotator 5 is a member that is disposed on the input-side rotator 4 so as to be relatively rotatable, and mainly includes a flywheel 51.

<Flywheel>
The flywheel 51 is a disk-shaped member in which a central hole is formed, and is arranged on the drive plate 41 on the axial transmission side.

  The flywheel 51 is provided on the drive plate 41 via the bearing 14 so as to be relatively rotatable. More specifically, the inner peripheral end of the flywheel 51 is provided with an inner peripheral cylindrical portion 51a extending toward the axial engine side, and a bearing 14 (specifically, a bearing 14) is provided on the inner peripheral surface thereof. 14 outer races 14b) are fitted. The inner peripheral cylindrical portion 51 a is formed with a protruding portion 51 b that protrudes further to the inner peripheral side than the outer peripheral surface of the bearing 14. When the inner peripheral cylindrical portion 51 a is fitted to the bearing 14, the drive plate 41. The movement of the flywheel 51 to the axial direction engine side is limited. Further, a spline 51c for providing a friction plate 71 described later is formed on the outer peripheral surface of the inner peripheral cylindrical portion 51a.

  The portion from the radially inner periphery of the flywheel 51 to the radially central portion is a portion having a relatively small plate thickness. And this part is provided in the state which left the clearance gap in the axial direction so that it may not contact the axial direction transmission side edge part of the drive claw parts 41d and 41e of the drive plate 41. FIG. And in the part from the radial direction inner peripheral part of the flywheel 51 to the radial direction center part, in the position of the radial direction inner peripheral side rather than the axial direction transmission side edge part of the drive claw parts 41d and 41e of the drive plate 41, A bush friction surface 51i is formed on the axial engine side. The bush friction surface 51i is an annular and flat surface, and is a portion with which a bush 61 described later comes into contact with and slides.

  A clutch friction surface 51e is formed on the axial transmission side at a portion from the radial center of the flywheel 51 to the radially outer periphery. The clutch friction surface 51e is an annular and flat surface and is a portion to which a clutch disk assembly 3 described later is connected. In addition, a portion having a relatively large thickness is formed in a portion from the center in the radial direction to the outer peripheral portion in the radial direction of the flywheel 51. That is, a protrusion 51 d extending toward the axial engine side is formed on the radially outer periphery of the flywheel 51.

  A positive side fixing portion 51f for fixing an output side end portion 82b of a positive spiral spring 82, which will be described later, is provided on the inner peripheral edge of the protruding portion 51d so as to correspond to the axial position of the positive side hub 42. It is formed corresponding to the number of spiral springs 82 (specifically, two). In the present embodiment, the positive-side fixing portion 51f has a concave shape that allows the output-side end portion 82b of the positive-side spiral spring 82 to be fitted from the axial direction and not to come out in the radial direction. Yes. More specifically, the positive side fixing portion 51f seems to have a hole that penetrates the protruding portion 51d in the axial direction and a groove that is notched so that the inner peripheral edge of the protruding portion 51d communicates with the through hole. It has a different shape. In the present embodiment, the positive side fixing portions 51f are arranged side by side at equal intervals in the circumferential direction.

  Further, a negative side fixing portion 51g for fixing an output side end portion 83b of a negative spiral spring 83 to be described later is provided on the inner peripheral edge of the protruding portion 51d so as to correspond to the axial position of the negative side hub 43. It is formed corresponding to the number of negative spiral springs 83 (specifically, two). In the present embodiment, the negative-side fixing portion 51g has a concave shape that allows the output-side end portion 83b of the negative-side spiral spring 83 to be fitted from the axial direction and prevents it from coming out in the radial direction. Yes. More specifically, the negative-side fixing portion 51g has a hole that penetrates the protruding portion 51d in the axial direction and a groove that is cut out so as to allow the inner peripheral edge of the protruding portion 51d to communicate with the through-hole. It has a different shape. In the present embodiment, the negative side fixing portions 51g are arranged side by side at equal intervals in the circumferential direction. In the present embodiment, the positive side fixing part 51f and the negative side fixing part 51g are arranged at the same circumferential position, and constitute an integral concave part.

  Further, a disc-shaped back plate 53 is fixed to the axially engine side surface of the protruding portion 51d by a stopper bolt 52. Note that a bolt hole 51 h is formed in the protrusion 51 d at a position corresponding to the stopper bolt 52. In the present embodiment, the circumferential center position of the bolt hole 51h (that is, the circumferential center position of the stopper bolt 52) is provided so as to coincide with the circumferential center position of the fixing portions 51f and 51g. .

<Stopper bolt>
The stopper bolt 52 is disposed so as to correspond to the radial position of each slit hole 41 f of the drive plate 41. In the present embodiment, the stopper bolts 52 are arranged at equal intervals in the circumferential direction. The head 52a of the stopper bolt 52 has a size that can be inserted into the slit hole 41f, and penetrates the slit hole 41f in the axial direction. Thus, when the flywheel 51 and the drive plate 41 rotate relative to each other, the head 52a comes into contact with the circumferential end of the slit hole 41f, and the twist angle of the drive plate 41 with respect to the flywheel 51 is set to a predetermined angle. Can be limited to within range.

<Back plate>
The back plate 53 is a member that is formed with a center hole having a diameter that allows the first drive claw portion 41 d of the drive plate 41 to be inserted from the axial direction, and rotates integrally with the flywheel 51. The outer peripheral edge of the back plate 53 extends to the vicinity of the outer peripheral edge of the flywheel 51. The back plate 53 is provided on the axial transmission side of the drive plate 41 with a gap in the axial direction so as not to contact the drive plate 41. Further, hubs 42 and 43 are disposed between the axial direction between the back plate 53 and the radial center of the flywheel 51. For this reason, an annular spring accommodating space S in which spiral springs 82 and 83 to be described later are arranged is formed by the projecting portion 51d and the radial center portion of the flywheel 51, the hubs 42 and 43, and the back plate 53. A bolt through hole 53a is formed in the outer peripheral portion of the back plate 53 at a position corresponding to the stopper bolt 52 and the bolt 51h.

  Thus, the flywheel 51 is disposed so as to be relatively rotatable with respect to the drive plate 41 via the bearing 14, and the twist angle thereof is within a predetermined angle range by the stopper bolt 52 and the slit hole 41 f of the drive plate 41. It has come to be restricted.

(4) Configuration of First Damper Unit The first damper unit 6 includes a driven plate 44 that constitutes the input side rotating body 4 and a bush 61 that functions as the output side rotating body 5 in a range where the input torque is small by the friction generating mechanism 7. Is a member that constitutes a damper mechanism that functions in a range in which the torsion angle of the input-side rotator 4 with respect to the output-side rotator 5 is small, and is mainly composed of a coil spring 62. .

<Coil spring>
The coil springs 62 are arranged so as to correspond to the respective spring drive portions 44 b of the driven plate 44. The coil spring 62 is held by the bush 61.

<Bush>
The bush 61 includes a first portion 63 and a second portion 64 disposed on the axial transmission side of the first portion 63.

  The first portion 63 and the second portion 64 are resin-made disk-shaped members in which a center hole is formed, on the inner peripheral side of the first drive claw portion 41 d of the drive plate 41, and on the flywheel 51. It arrange | positions at the outer peripheral side of the inner peripheral cylindrical part 51a. A surface 63f on the axial direction engine side of the first portion 63 is in contact with a friction plate 71 described later. A surface 64 f of the second portion 64 on the axial direction engine side is in contact with a bush friction surface 51 i of the flywheel 51.

  A spring holding portion 63 a for holding a portion of each coil spring 62 on the axial direction engine side is formed on the outer peripheral portion of the first portion 63. The spring holding portion 63a holds portions of the coil spring 62 on the axial engine side, the radially inner peripheral side, and both ends in the circumferential direction. A spring holding portion 64 a for holding a portion of each coil spring 62 on the axial transmission side is formed on the outer peripheral portion of the second portion 64. The spring holding portion 64a holds the portions of the coil spring 62 on the axial transmission side, the radial inner peripheral side, and both ends in the circumferential direction. The spring holding portions 63 a and 64 a are arranged at circumferential positions corresponding to the arrangement of the coil springs 62.

  In addition, the driven plate 44, together with the coil spring 62, the first portion 63, the second portion 64, and the first portion 63 and the second portion 64 at the circumferential position where the spring holding portions 63a, 64a are not formed. Driven plate guides 63b and 64b are formed so as to ensure a gap for sandwiching between the driven plates 44 and 64, and the driven plate 44 and the bush 61 are relatively rotatable. Thus, when the driven plate 44 and the bush 61 rotate relative to each other, the coil spring 62 is compressed between the circumferential end of the spring drive portion 44b of the driven plate 44 and the circumferential end of the spring holding portions 63a and 64a. Will be.

  In addition, an arc-shaped first portion formed by notching the outer peripheral edge of the first portion 63 to a radial position where each second driving claw portion 41e of the drive plate 41 can be fitted from the axial direction. A two-drive claw guide 63c is provided. The second drive claw guide portion 63c is notched to a circumferential width larger than the circumferential width of the second drive claw portion 41e, and the second drive claw portion 41e has a circular shape at both ends in the circumferential direction. Drive claw contact portions 63d and 63e with which circumferential ends can be contacted are formed. And the 1st part 63 is provided in the state fitted by the 2nd drive nail | claw part 41e of the drive plate 41 from the axial direction. Further, like the first portion 63, the outer peripheral edge of the second portion 64 is notched to a radial position where each second drive claw portion 41e of the drive plate 41 can be fitted from the axial direction. The formed arcuate second driving claw guide portion 64c is provided. The second drive claw guide portion 64c is notched to a circumferential width larger than the circumferential width of the second drive claw portion 41e, and the circle of the second drive claw portion 41e is provided at both ends in the circumferential direction. Drive claw abutting portions 64d and 64e with which circumferential ends can abut are formed. And the 2nd part 64 is provided in the state fitted by the 2nd drive nail | claw part 41e of the drive plate 41 from the axial direction. Here, among the drive claw contact portions 63d, 63e, 64d, and 64e, the drive claw contact portion that can come into contact when the second drive claw portion 41e is twisted in the rotation direction R1 side is the drive claw contact. The drive claw contact portions 63e and 64e are the drive claw contact portions that can contact when the second drive claw portion 41e is twisted in the rotation direction R2 side.

  Thus, when the driven plate 44 is twisted in the rotational directions R1 and R2 by the drive plate 41, the coil spring 62 has the second end of the second drive claw portion 41e of the drive plate 41 at the circumferential end of the bush 61. The circumferential end of the spring drive portion 44b of the driven plate 44 is the circumferential end of the spring holding portions 63a and 64a of the bush 61 until the drive pawl guide portions 63c and 64c come into contact with the drive claw contact portions 63d and 64d. , The driven plate 44 and the bush 61 can be connected in the rotational direction. That is, the first damper portion 6 functions as a damper mechanism that elastically connects the input-side rotator 4 and the output-side rotator 5 within a predetermined operating angle range.

  In the present embodiment, the first portion 63 and the second portion 64 are members of the same shape and the same size, and are arranged such that the spring holding portions 63a and 64a face each other.

(5) Configuration of Friction Generation Mechanism The friction generation mechanism 7 is provided between the rotation direction of the bush 61 and the flywheel 51, and the bush 61 and the flywheel are within a large torsional angle range that is greater than the operating angle of the first damper portion 6. 51 is a member that generates a predetermined hysteresis torque when it rotates relative to 51, and mainly includes a friction plate 71, a cone spring 72, and a snap ring 73.

<Friction plate>
The friction plate 71 is an annular member that rotates integrally with the flywheel 51 and contacts and slides on the bush 61 (specifically, the surface 63 f of the first portion 63). Between the portion 51 a and the second drive claw portion 41 e of the drive plate 41, the bush 61 is disposed on the axial engine side. A plurality of teeth that mesh with the splines 51c of the flywheel 51 are formed on the inner peripheral edge of the friction plate 71, and are not relatively rotatable with respect to the flywheel 51 (specifically, the inner peripheral cylindrical portion 51a). It can move in the axial direction.

<Corn spring>
The cone spring 72 is a conical or disc-shaped spring having a central hole that biases the friction plate 71 toward the axial transmission side, and is a second drive of the inner peripheral cylindrical portion 51 a of the flywheel 51 and the drive plate 41. Between the claw portion 41e and the radial direction, the friction plate 71 is disposed on the axial direction engine side. The bush 61 is sandwiched between the friction plate 71 and the flywheel 51 (specifically, the bush friction surface 51i) by the urging force of the cone spring 72.

<Snap ring>
The snap ring 73 is an annular member that locks the cone spring 72 to the axial engine side in a state in which the cone spring 72 urges the friction plate 71 toward the axial transmission side. It is disposed between the circumferential cylindrical portion 51 a and the second drive claw portion 41 e of the drive plate 41 in the radial direction and on the axial engine side of the cone spring 72. The snap ring 73 is fitted in the vicinity of the end on the axial direction engine side of the inner peripheral cylindrical portion 51 a of the flywheel 51.

  As described above, when the bush 61 is sandwiched between the axial direction of the friction plate 71 and the flywheel 51 by the urging force of the cone spring 72, the bush 61 is in contact with the flywheel 51 until a predetermined torque is input. When the input torque increases as a result of the integral rotation, the rotation relative to the flywheel 51 occurs, and the bush 61 (specifically, the surface 63f of the first portion 63) and the friction plate 71 and the bush 61 ( Specifically, a predetermined hysteresis torque is generated between the surface 64f) of the second portion 64 and the flywheel 51 (specifically, the bush friction surface 51i).

(6) Configuration of Second Damper Part The second damper part 8 includes a positive side hub 42 and a negative side hub 43 that constitute the input side rotating body 4, and a flywheel 51 that is a part of the output side rotating body 5. A member that constitutes a damper mechanism that functions in a range in which the torsion angle of the input-side rotator 4 with respect to the output-side rotator 5 is larger than the operating angle of the first damper portion 6. A positive spiral spring 82 and a negative spiral spring 83 are included.

<Positive spiral spring>
The positive spiral spring 82 is a spiral spring that connects the positive hub 42 and the flywheel 51 in the rotational direction, and is disposed in the annular spring accommodating space S. In the present embodiment, two positive spiral springs 82 are provided. An end portion on the inner peripheral side of each positive spiral spring 82 is an input-side end portion 82a that is rounded so as to be fitted to the fixing portion 42e of the positive hub 42. Further, the outer end of the positive spiral spring 82 is an output end 82b that is rounded so as to be fitted to the positive fixing portion 51f of the flywheel 51. The positive spiral spring 82 has a spiral shape that operates in the winding direction when the positive hub 42 is twisted in the rotational direction R <b> 1 with respect to the flywheel 51. In the present embodiment, the two positive spiral springs 82 are fixed in a state where they are shifted by a half circumference in the circumferential direction. Further, in this embodiment, the number of turns of each positive spiral spring 82 is such that the positive hub 42 and the negative hub 43 are not twisted with respect to the flywheel 51 in either the rotational direction R1 side or the rotational direction R2 side. In the following (neutral state, the state shown in FIGS. 2 to 5), there are 1.5 turns.

  In such a neutral state, the positive side hub 42 and the flywheel 51 have a relative positional relationship such that the circumferential position of the fixing portion 42e and the circumferential position of the positive side fixing portion 51f coincide. Become. Further, since the fixing portion 42e is disposed at a position shifted from the circumferential center position of the positive drive claw guide portion 42b toward the rotation direction R1, the circumference of the positive drive claw guide portion 42b of the positive hub 42 is determined. The direction center position is disposed at a position shifted from the fixed portion 42e toward the rotation direction R2. Thereby, the clearance between the rotation direction R2 side end of the first drive claw portion 41d and the drive claw contact portion 42d of the positive side drive claw guide portion 42b is the same as the rotation direction R1 side end of the first drive claw portion 41d and the positive side. The clearance between the driving claw guide portion 42b and the driving claw abutting portion 42c is larger than that between the circumferential directions.

In the neutral state, the drive plate 41 is disposed so that the circumferential center position of the first drive claw portion 41d coincides with the circumferential position of the fixed portion 42e and the positive side fixed portion 51f. In addition, a gap is formed between the end of the first drive claw portion 41d on the rotation direction R1 side and the circumferential direction between the drive claw contact portion 42c of the positive drive claw guide portion 42b. In addition, since the second drive claw portion 41e is arranged side by side in the circumferential direction of the first drive claw portion 41d, the circumferential center position of the second drive claw portion 41e is the first drive claw portion 41d. It is arrange | positioned in the position which shifted | deviated 90 degrees in the circumferential direction from the circumferential direction center position. Then, the second drive claw guide portion 44e of the driven plate 44 is disposed at the same circumferential position as the second drive claw portion 41e, and as a result, the spring drive portion 44b is connected to the first drive claw portion 41d. Arranged at the same circumferential position. As a result, the coil spring 62 and the spring holding portions 63a and 64a of the bush 61 whose both ends in the circumferential direction abut on the spring drive portion 44b are also arranged at the same circumferential position as the first drive claw portion 41d. A clearance between the end of the second drive claw portion 41e of the drive plate 41 on the rotation direction R1 side and the drive claw contact portions 63d and 64d of the second drive claw guide portions 63c and 64c of the bush 61 in the circumferential direction. The clearance angle corresponding to (α _1p ) corresponds to the clearance between the end of the first drive claw portion 41d on the rotation direction R1 side and the drive claw contact portion 42c of the positive drive claw guide portion 42b in the circumferential direction. It is the same as or smaller than the clearance angle (α _2p ). Further, the circumferential center position of the slit hole 41 f of the drive plate 41 coincides with the circumferential position of the stopper bolt 52. When the drive plate 41 is twisted in the rotation direction R2, the slit hole 41f has an end on the rotation direction R2 side of the first drive claw portion 41d that is a drive claw of the positive side drive claw guide portion 42b of the positive side hub 42. The dimension is set such that the stopper bolt 52 contacts the end of the slit hole 41f on the rotation direction R1 side before contacting the contact part 42d.

<Negative spiral spring>
The negative spiral spring 83 is a spiral spring that connects the negative hub 43 and the flywheel 51 in the rotational direction, and is disposed in the annular spring accommodating space S. In the present embodiment, two negative spiral springs 83 are provided. An end portion on the inner peripheral side of each negative spiral spring 83 is an input end portion 83a that is rounded in an annular shape so as to be fitted to the fixing portion 43e of the negative hub 43. Further, the end on the outer peripheral side of the negative spiral spring 83 is an output end 83b that is rounded so as to be fitted to the negative fixing portion 51g of the flywheel 51. The negative spiral spring 83 has a spiral shape that operates in the tightening direction when the negative hub 43 is twisted in the rotational direction R <b> 1 with respect to the flywheel 51. In the present embodiment, the two negative spiral springs 83 are fixed in a state where they are shifted by a half circumference in the circumferential direction. Further, in the present embodiment, the number of turns of each negative spiral spring 83 is such that the positive hub 42 and the negative hub 43 are not twisted with respect to the flywheel 51 in either the rotational direction R1 side or the rotational direction R2 side. In the following (neutral state, the state shown in FIGS. 2 to 5), there are 1.5 turns. A separate plate 85 is arranged between the positive spiral spring 82 and the negative spiral spring 83 in the axial direction to divide the spring housing space S into two in the axial direction.

  In such a neutral state, the negative hub 43 and the flywheel 51 have a relative positional relationship such that the circumferential position of the fixing portion 43e and the circumferential position of the negative fixing portion 51g coincide. Become. Further, since the fixing portion 43e is disposed at a position shifted from the circumferential center position of the negative drive claw guide portion 43b toward the rotation direction R2, the circumference of the negative drive claw guide portion 43b of the negative hub 43 is determined. The direction center position is disposed at a position shifted from the fixed portion 43e toward the rotation direction R1. Thereby, the clearance between the rotation direction R1 side end of the first drive claw portion 41d and the drive claw contact portion 43c of the negative side drive claw guide portion 43b is the same as the rotation direction R2 side end of the first drive claw portion 41d and the negative side. It is larger than the clearance between the drive claw guide portion 43b and the drive claw contact portion 43d in the circumferential direction.

In the neutral state, the drive plate 41 is disposed so that the circumferential center position of the first drive claw portion 41d coincides with the circumferential position of the fixed portion 43e and the negative side fixed portion 51g. In addition, a gap is formed between the end in the rotation direction R2 side of the first drive claw portion 41d and the circumferential direction between the drive claw contact portion 43d of the negative drive claw guide portion 43b. A clearance between the end of the second drive claw portion 41e of the drive plate 41 on the rotation direction R2 side and the drive claw contact portions 63d and 64d of the second drive claw guide portions 63c and 64c of the bush 61 in the circumferential direction. The clearance angle corresponding to (α _1n ) corresponds to the clearance between the end of the first drive claw portion 41d on the rotation direction R2 side and the drive claw contact portion 42d of the negative drive claw guide portion 43b in the circumferential direction. It is the same as or smaller than the gap angle (α _2n ). Further, the circumferential center position of the slit hole 41 f of the drive plate 41 coincides with the circumferential position of the stopper bolt 52. When the drive plate 41 is twisted in the rotation direction R1, the slit hole 41f is such that the end on the rotation direction R1 side of the first drive claw portion 41d is the drive claw of the negative side drive claw guide portion 43b of the negative side hub 43. The dimension is set such that the stopper bolt 52 contacts the end of the slit hole 41f on the rotation direction R2 side before contacting the contact part 43c.

  Thus, when the drive plate 41 is twisted from the neutral state to the rotational direction R1, the positive side spiral spring 82 is actuated in the tightening direction as the positive side hub 42 is rotationally driven by the drive plate 41. The positive side hub 42 as the input side rotating body 4 and the flywheel 51 can be elastically connected in the rotation direction. The negative drive claw guide 43b of the negative hub 43 can be rotated relative to the negative hub 43 only until the stopper bolt 52 contacts the end of the slit hole 41f on the rotation direction R2 side. It has become. Further, when the drive plate 41 is in the negative twisting operation in which the drive plate 41 is twisted in the rotational direction R2 from the neutral state, the negative hub 43 is rotated by the drive plate 41 so that the negative spiral spring 83 is in the tightening direction. By operating, the negative side hub 43 as the input side rotating body 4 and the flywheel 51 can be elastically connected in the rotation direction. The positive drive claw guide 42b of the positive hub 42 can be rotated relative to the positive hub 42 only until the stopper bolt 52 contacts the end of the slit hole 41f on the rotation direction R1 side. It has become. For this reason, the input side rotating body 4 includes a driven plate 41 (specifically, the first driving claw portion 41d), a positive side hub 42 (specifically, the positive side driving claw guide portion 42b), and a negative side hub 43. (Specifically, the negative drive pawl guide 43b) operates only the positive spiral spring 82 during the positive twisting operation that is twisted from the neutral state to the positive side in the rotation direction, and the neutral state. And a spring actuating mechanism that actuates only the negative spiral spring 83 during a negative twisting operation that is twisted in the negative direction of rotation.

In the present embodiment, in the neutral state, the circumferential direction between the rotation direction R1 side end of the first drive claw portion 41d of the drive plate 41 and the drive claw contact portion 42c of the positive side drive claw guide portion 42b and the first The clearance angle (α _2p , α _2n ) between the rotation direction R2 side end of the one drive claw portion 41d and the drive claw contact portion 43d of the negative side drive claw guide portion 43b is the second angle of the drive plate 41. Is it the same as the clearance angle (α _1p , α _1n ) between the circumferential end of the drive claw portion 41e and the second drive claw guide portions 63c, 64c of the bush 61 between the drive claw contact portions 63d, 64d? Alternatively, the coil spring 62 serving as the first damper portion 6 is disposed at the circumferential end of the second drive claw portion 41e of the drive plate 41 at the second end of the bush 61 during the positive side twisting operation and the negative side twisting operation. Driving claw guides 63c and 64 The circumferential end of the spring drive part 44b of the driven plate 44 is compressed between the end of the bush 61 in the rotational direction of the spring holding parts 63a and 64a until it comes into contact with the drive claw contact parts 63d and 64d of c. As a result, the driven plate 44 and the bush 61 are connected in the rotational direction. At this time, the bush 61 is integrated with the flywheel 51 by the friction generating mechanism 7 (specifically, by being sandwiched between the axial direction of the friction plate 71 and the flywheel 51 by the urging force of the cone spring 72). It rotates and functions as the output side rotating body 5. When the circumferential end of the second drive claw portion 41e of the drive plate 41 contacts the drive claw contact portions 63d and 64d of the second drive claw guide portions 63c and 64c of the bush 61, the second of the drive plate 41 is moved. The torque input to the bush 61 from the drive claw portion 41e increases, and the bush 61 rotates relative to the flywheel 51 while generating hysteresis torque. As described above, the positive spiral spring 82 and the negative spiral spring 83 as the second damper portion 8 are operated between the hubs 42 and 43 and the flywheel 51, whereby the drive plate 41 and the flywheel 51 are operated. Are connected in the rotational direction.

  Thus, in the flywheel assembly 1 of the present embodiment, the coil spring 62 constituting the first damper portion 6, the positive spiral spring 82 and the negative spiral spring 83 constituting the second damper portion 8 are input. Although it is configured to operate in parallel between the side rotator 4 and the output side rotator 5, the torsional characteristics are obtained by the first damper portion 6 in the range where the torsion angle is small, and the second damper is in the range where the torsion angle is large. A two-stage torsional characteristic of obtaining a torsional characteristic by the portion 8 is realized.

(7) Clutch disc assembly The clutch disc assembly 2 of the clutch includes a friction facing 21 disposed in proximity to the clutch friction surface 51e of the flywheel 51, and a hub 22 that is spline-engaged with the input shaft 12 of the transmission. Have.

(8) Clutch cover assembly The clutch cover assembly 3 includes a clutch cover 31, a diaphragm spring 32, and a pressure plate 33. The clutch cover 31 is a disk-like and annular member fixed to the flywheel 51. The pressure plate 33 is an annular member having a pressing surface close to the friction facing 21, and rotates integrally with the clutch cover 31. The diaphragm spring 32 is a member for elastically urging the pressure plate 33 toward the axial engine side while being supported by the clutch cover 31. When a release device (not shown) pushes the inner peripheral end of the diaphragm spring 32 toward the axial engine side, the diaphragm spring 32 releases the bias to the pressure plate 33.

(9) Operation of flywheel assembly <Torque transmission>
In this flywheel assembly 1, the torque from the crankshaft 11 of the engine is applied to the output side rotator 5 including the flywheel 51, the input side rotator 4, the first damper portion 6, the friction generating mechanism 7, 2 is transmitted via the damper portion 8. Further, when the clutch is engaged, torque is transmitted from the flywheel 51 to the clutch disc assembly 2 and finally output to the input shaft 12.

<Absorption and damping of torsional vibration>
When combustion fluctuations from the engine are input to the drive plate 41 constituting the input-side rotator 4, the input-side rotator 4 including the drive plate 41 and the output-side rotator 5 including the flywheel 51 rotate relative to each other, Meanwhile, the coil spring 62, the positive spiral spring 82, and the negative spiral spring 83 operate in parallel. Further, the friction generating mechanism 7 generates a predetermined hysteresis torque. By the above action, torsional vibration is absorbed and damped.

  Next, the absorption / damping operation of torsional vibration in the flywheel assembly 1 will be described in detail with reference to FIGS. 4, 5, and 7. Here, FIG. 7 is a torsional characteristic diagram of the flywheel assembly 1.

First, the positive side twisting operation in which the drive plate 41 is twisted in the rotational direction R1 from the neutral state will be described.
When the drive plate 41 is twisted in the rotation direction R1 side, the rotation direction R1 side end of the second drive claw portion 41e of the drive plate 41 is aligned with the rotation direction R1 side end of the second drive claw guide portion 44e of the driven plate 44. In order to rotationally drive, the coil spring 62 as the first damper portion 6 is between the spring contact portion 44c of the spring drive portion 44b of the driven plate 44 and the rotation direction ends of the spring holding portions 63a and 64a of the bush 61. Compressed. Here, the bush 61 that holds the coil spring 62 is sandwiched between the axial direction of the friction plate 71 and the flywheel 51 by the urging force of the cone spring 72, and has a predetermined torque (torque T _{1p in} FIG. 7). Until the reference is input, the friction plate 71 and the flywheel 51 rotate together to function as the output-side rotating body 5.

Subsequently, when the drive plate 41 is further twisted in the rotation direction R1 side and the drive plate 41 is increased to the twist angle _α1p , the second drive claw portion 41e of the drive plate 41 is moved to the second drive claw guide portion of the bush 61. The bush 61 is driven to rotate by the drive plate 41 in contact with the drive claw contact portions 63d and 64d of 63c and 64c. Then, when the torque input to the bush 61 from the drive plate 41 exceeds a predetermined value (see torque _{T1p in} FIG. 7), the friction torque sandwiched between the axial direction of the friction plate 71 and the flywheel 51 is overcome, The friction generating mechanism 7 is operated by the rotation of the bush 61 relative to the flywheel 51, and a predetermined hysteresis torque (in this embodiment, the torque is determined according to the frictional resistance between the bush 61, the friction plate 71, and the flywheel 51. (Substantially the same as _T1p ).

As described above, in the region where the twist angle of the drive plate 41 is small (the twist angle is from zero to _α1p ), only the coil spring 62 constituting the first damper portion 6 is operated to obtain a linear torsion characteristic. (See FIG. 7).

Subsequently, when the drive plate 41 is further twisted in the rotational direction R1 side and the drive plate 41 is increased to the twist angle α _{2p, the} end in the rotational direction R1 side of the first drive claw portion 41d of the drive plate 41 is the positive hub. Since the positive side hub 42 is rotated by the drive plate 41 in contact with the drive claw contact part 42c of the positive side drive claw guide part 42b of the 42, the positive side spiral spring 82 as the second damper part 8 is It is operated in the winding direction between the hub 42 and the flywheel 51. Here, since the negative side hub 43 is not rotationally driven by the drive plate 41, the negative side spiral spring 83 is maintained in a neutral state. The first drive claw portion 41 d of the drive plate 41 rotates relative to the negative side hub 43 by the negative side drive claw guide portion 43 b of the negative side hub 43. In the present embodiment, since the twist angle α _2p is set to the same angle as the twist angle α _1p , the coil spring 62 as the first damper portion 6 is operated, and hysteresis torque is generated by the friction generating mechanism 7. Almost at the same time, the positive spiral spring 82 as the second damper portion 8 starts to operate (see FIG. 7).

Subsequently, when the drive plate 41 is further twisted in the rotational direction R1 side and the drive plate 41 is increased to the twisting angle _α3p , the stopper bolt 52 comes into contact with the rotational direction R2 side end of the slit hole 41f of the drive plate 41. Therefore, the tightening operation of the positive spiral spring 82 is finished, and the stopper torque is generated.

Thus, in the region where the twist angle of the drive plate 41 is large (the twist angle is from α _2p to α _3p ), the positive spiral spring 82 constituting the second damper portion 8 operates in the tightening direction. Curved torsional characteristics are obtained according to the torque characteristics of the spiral spring shown in FIG. 8 (see FIG. 7).

Next, an operation when the drive plate 41 returns from the state twisted to the rotation direction R1 side to the angle _α3p to the neutral state will be described.
When the drive plate 41 returns to the torsion angle _α2p from the state in which the drive plate 41 is twisted to the rotation direction R1 side to the torsion angle _α3p, the positive-side spiral once wound between the positive side hub 42 and the flywheel 51 The spring 82 is rewound. Here, as shown in FIG. 8, the spiral spring has a torque characteristic that causes hysteresis between the torque when the winding operation is performed and the torque when the winding is rewinded from the wound state. . For this reason, in the flywheel assembly 1, curvilinear torsional characteristics having hysteresis are obtained both when the winding operation is performed and when the winding wheel is rewound from the wound state (see FIG. 7). Even when the positive spiral spring 82 is rewound, the negative hub 43 is not rotationally driven by the drive plate 41, so the neutral state of the negative spiral spring 83 is maintained, and the first drive of the drive plate 41 is performed. The claw portion 41 d is rotated relative to the negative side hub 43 by the negative side drive claw guide portion 43 b of the negative side hub 43.

Subsequently, when the torsion angle _α2p returns to zero, torque is not input from the drive plate 41 to the positive side hub 42, and torque is input from the drive plate 41 only to the driven plate 44, thereby generating friction. Hysteresis torque is not generated by the mechanism 7, and the compression of the compressed coil spring 62 is released, and a linear torsional characteristic corresponding to this is obtained (see FIG. 7).

Next, the negative side twisting operation in which the drive plate 41 is twisted in the rotation direction R2 side from the neutral state will be described.
When the drive plate 41 is twisted in the rotation direction R2 side, the rotation direction R2 side end of the second drive claw portion 41e of the drive plate 41 is aligned with the rotation direction R2 side end of the second drive claw guide portion 44e of the driven plate 44. In order to drive the rotation, the coil spring 62 as the first damper portion 6 is between the spring contact portion 44d of the spring drive portion 44b of the driven plate 44 and the rotation direction ends of the spring holding portions 63a and 64a of the bush 61. Compressed. Here, the bush 61 holding the coil spring 62 is sandwiched between the axial direction of the friction plate 71 and the flywheel 51 by the urging force of the cone spring 72, and a predetermined torque (torque T _{1n in} FIG. 7). Until the reference (in this embodiment, the same as T _1p ) is input, the friction plate 71 and the flywheel 51 rotate together to function as the output-side rotating body 5.

Subsequently, when the drive plate 41 is further twisted in the rotational direction R1 side and the drive plate 41 is increased to the twist angle α _1n , the second drive claw portion 41e of the drive plate 41 becomes the second drive claw guide portion of the bush 61. The bush 61 is driven to rotate by the drive plate 41 in contact with the drive claw contact portions 63e and 64e of 63c and 64c. Then, when the torque input from the drive plate 41 to the bush 61 exceeds a predetermined value (see torque T _{1n in} FIG. 7), the friction torque sandwiched between the axial direction of the friction plate 71 and the flywheel 51 is overcome, The friction generating mechanism 7 is operated by the rotation of the bush 61 relative to the flywheel 51, and a predetermined hysteresis torque (in this embodiment, the torque is determined according to the frictional resistance between the bush 61, the friction plate 71, and the flywheel 51. (Substantially the same as T _1n ).

As described above, in the region where the twist angle of the drive plate 41 is small (the twist angle is from zero to α _1n ), only the coil spring 62 constituting the first damper portion 6 is operated to obtain a linear torsion characteristic. (See FIG. 7).

Then, it will further twisted in the rotation direction R2 side drive plate 41, drive the plate 41 increases until the torsion angle alpha _2n, the first rotary direction R2 side end of the drive pawl portion 41d is the positive side hub of the drive plate 41 42, the positive side spiral spring 82 as the second damper portion 8 is positively contacted with the drive claw contact portion 43 c of the negative side drive claw guide portion 43 b and rotationally drives the negative side hub 43 by the drive plate 41. It is operated in the winding direction between the hub 42 and the flywheel 51. Here, since the negative side hub 43 is not rotationally driven by the drive plate 41, the negative side spiral spring 83 is maintained in a neutral state. The first drive claw portion 41 d of the drive plate 41 is rotated relative to the positive side hub 42 by the positive side drive claw guide portion 42 b of the positive side hub 42. In the present embodiment, since the twist angle α _2n is set to the same angle as the twist angle α _1n , the coil spring 62 serving as the first damper portion 6 operates and hysteresis torque is generated by the friction generating mechanism 7. Almost at the same time, the negative spiral spring 83 as the second damper portion 8 starts to operate (see FIG. 7).

Subsequently, when the drive plate 41 is further twisted in the rotation direction R2 side and the drive plate 41 is increased to the twist angle _α3n , the stopper bolt 52 comes into contact with the rotation direction R1 side end of the slit hole 41f of the drive plate 41. For this reason, the tightening operation of the negative spiral spring 83 is completed, and a stopper torque is generated.

Thus, in the region where the torsion angle of the drive plate 41 is large (the torsion angle is α _2n to α _3n ), the negative spiral spring 83 constituting the second damper portion 8 operates in the tightening direction. Similar to the case of the side twisting operation, a curved twist characteristic is obtained (see FIG. 7).

Next, an operation when the drive plate 41 returns from the state twisted to the rotation direction R2 side to the angle α _3n to the neutral state will be described.
When the drive plate 41 returns to the torsion angle α _2n from the state in which the drive plate 41 is twisted to the rotation direction R 2 side to the torsion angle α _{3 n,} the negative side spiral once wound between the negative hub 43 and the flywheel 51 The spring 83 is rewound. Here, as in the case of the positive side twisting operation, a curved torsional characteristic having hysteresis is obtained (see FIG. 7). Even when the negative spiral spring 83 is rewound, since the positive hub 42 is not driven to rotate by the drive plate 41, the neutral state of the positive spiral spring 82 is maintained, and the first drive of the drive plate 41 is performed. The claw portion 41 d is rotated relative to the positive side hub 42 by the positive side drive claw guide portion 42 b of the positive side hub 42.

Then, when returning to zero from torsion angle alpha _2n, the torque is not inputted to the negative side the hub 43 from the drive plate 41, becomes the torque from the drive plate 41 only in the driven plate 44 is inputted, the friction generating Hysteresis torque is not generated by the mechanism 7, and the compression of the compressed coil spring 62 is released, and a linear torsional characteristic corresponding to this is obtained (see FIG. 7).

  As described above, in the flywheel assembly 1, only the positive spiral spring 82 that constitutes the second damper portion 8 is obtained when the drive plate 41 is twisted in the rotational direction R <b> 1 with respect to the neutral state (positive twisting operation). And only the negative spiral spring 83 constituting the second damper portion 8 is operated in a state where the drive plate 41 is twisted in the rotational direction R2 side with respect to the neutral state (negative side twisting operation). Is possible.

(10) Features of Flywheel Assembly The flywheel assembly 1 of the present embodiment has the following features.
(A)
In the flywheel assembly 1 of this embodiment, the spiral springs 82 and 83 are used as elastic members for connecting the input side rotating body 4 and the output side rotating body 5 in the rotational direction. 4 and the output side rotator 5 are less susceptible to the centrifugal force when rotating. In addition, in the flywheel assembly 1, as the spiral spring, the input side rotating body 4 operates in the tightening direction when the input side rotating body 4 is twisted in the rotational direction driving side (that is, the rotational direction positive side) with respect to the output side rotating body 5. The positive spiral spring 82 and the negative side that operates in the tightening direction when the input side rotator 4 is twisted to the opposite side of the rotational direction drive side with respect to the output side rotator 5 (ie, the negative side in the rotational direction). Since the spiral spring 83 is used, the torsional characteristics when the spiral spring is operated in the tightening direction can be obtained both when twisting to the positive side and when twisting to the negative side. It has a configuration in consideration of the characteristics of the spiral spring used in the direction of tightening. Thus, in the flywheel assembly 1 of this embodiment, when twisting to the positive side and twisting to the negative side as an elastic member for connecting the input side rotating body 4 and the output side rotating body 5 in the rotational direction. Since the positive spiral spring 82 and the negative spiral spring 83 corresponding to each of these are used, the centrifugal force when the input side rotary body 4 and the output side rotary body 5 rotate is compared with the case where the coil spring is used. An increase in hysteresis torque due to force and wear of the elastic member can be suppressed.

(B)
In addition, it is possible to omit a plate member such as a retaining plate for holding the coil spring and a fastening member such as a rivet for fixing the plate members while holding the coil spring. Can be reduced. In addition, the spring housing space S can be made relatively small as compared with the case where a coil spring is used, and a compact structure can be realized.

(C)
Further, in the flywheel assembly 1 of the present embodiment, the drive plate 41, the positive side hub 42 and the negative side hub 43 constituting the input side rotator 4 are in a neutral state with respect to the output side rotator 5 with respect to the input side rotator 4. Only the positive spiral spring 82 was actuated during the positive twisting operation, which is a state twisted from the rotational direction drive side to the rotational direction drive side, and twisted from the neutral state with respect to the output side rotating body 5 to the opposite side to the rotational direction drive side A spring actuating mechanism is configured to actuate only the negative spiral spring 83 during the negative torsional operation. Thus, in this flywheel assembly 1, only the torsional characteristics of the positive spiral spring 82 can be reliably obtained during the positive twisting operation, and the negative spiral spring can be obtained during the negative twisting operation. Only 83 torsional characteristics can be reliably obtained.

(D)
In this embodiment, the number of spiral springs 82 and 83 is two on the positive side and two on the negative side, but the torsional characteristics can be adjusted by increasing or decreasing these numbers, It is easy to adjust the positive side and the negative side to different characteristics by changing the number of spiral springs, the number of turns, and the like between the positive side and the negative side.

It is a longitudinal cross-sectional schematic diagram (EOF sectional drawing of FIG. 3) of the flywheel assembly as one Embodiment of this invention. It is a top view (C-D sectional view of Drawing 1) of a flywheel assembly. It is a top view (AB sectional drawing of FIG. 1) of a flywheel assembly. FIG. 3 is an enlarged view of FIG. 2. FIG. 4 is an enlarged view of FIG. 3. It is an enlarged view of FIG. It is a torsional characteristic diagram of a flywheel assembly. It is a torque characteristic diagram of a spiral spring.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Flywheel assembly 4 Input side rotary body 5 Output side rotary body 41 Drive plate 42 Positive side hub 43 Negative side hub 51 Flywheel 82 Positive side spiral spring 83 Negative side spiral spring

Claims (6)

A flywheel assembly for transmitting torque from an engine crankshaft,
An input-side rotating body to which torque is input from the crankshaft;
The input side rotator is disposed so as to be relatively rotatable, and an output side rotator including a flywheel;
The input-side rotator and the output-side rotator are connected in the rotation direction, and the input-side rotator operates in the winding direction when the input-side rotator is twisted in the rotation direction drive side with respect to the output-side rotator. A positive spiral spring,
The input-side rotator and the output-side rotator are coupled in a rotational direction, and the input-side rotator is tightened when twisted in the direction opposite to the rotational direction drive side with respect to the output-side rotator. A negative spiral spring that operates in a direction,
Flywheel assembly with   The input-side rotator operates only the positive-side spiral spring during a positive-side twisting operation in which the output-side rotator is twisted from a neutral state to a rotational direction drive side, and the output-side rotator 2. The fly according to claim 1, further comprising a spring actuation mechanism that actuates only the negative spiral spring during a negative twisting operation in a state twisted from a neutral state to a rotational direction drive side. Wheel assembly. The spring operating mechanism is
The drive plate to which torque from the crankshaft is input;
The positive spiral spring is connected, and is rotated by the drive plate during the positive twisting operation, but is not rotated by the drive plate during the negative twisting operation. ,
The negative spiral spring is connected, and is rotated by the drive plate during the negative twisting operation, but is not rotated by the drive plate during the positive twisting operation; ,
have,
The flywheel assembly according to claim 2.   The flywheel assembly according to claim 3, wherein the first spiral spring and the second spiral spring are arranged side by side in the axial direction. The drive plate has a drive claw extending in the axial direction;
The positive side hub has a positive side driving claw guide portion that abuts the circumferential end of the driving claw during the positive side twisting operation and rotatably guides the driving claw during the negative side twisting operation. Have
The negative side hub has a negative side driving claw guide portion that abuts the circumferential end of the driving claw during the negative side twisting operation, and rotatably guides the driving claw during the positive side twisting operation. Have
The flywheel assembly according to claim 4.   The flywheel assembly according to claim 5, wherein the drive claw is formed by cutting and raising a part of the drive plate.

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