JP2017227317A - Torsional vibration attenuation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem that a conventional torsional vibration attenuation device into which an arc spring is assembled has not means for adjusting a hysteresis characteristic of the arc spring.SOLUTION: This torsional vibration attenuation device comprises: a rotatable spring holder 13 having a disc-plate shaped end plate part 13a and an annular cylinder part 13b erecting from an external peripheral edge of the end plate part; a coil spring 18 which is accommodated in the spring holder along an internal peripheral face of the cylinder part of the spring holder, and curved in an arc circular shape coaxial with a rotation center of the spring holder; a first rotating body 19 which is integrally arranged at the spring holder, and in which a spring receiving part 19a abutting on one end side along a center axial line of the coil spring is formed; a second rotating body 17 which opposes the first rotating body, and in which a spring receiving part 17a abutting on the other end side along the center axial line of the coil spring is formed; and an annular protrusion 22 or a groove which is formed at the internal peripheral face of the cylinder part of the spring holder, and regulates a contact state between the internal peripheral face of the cylinder part and the coil spring.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a torsional vibration damping device that can reduce torque fluctuation generated on the input side and transmit the torque fluctuation to the output side.

  In an internal combustion engine that obtains power by intermittently burning fuel, torque fluctuation inevitably occurs. For this reason, a torsional vibration damping device in which the input side and the output side are connected via an elastic body that can be elastically deformed is incorporated in the power transmission path, and torque fluctuations generated on the input side are alleviated and power is transferred to the output side. It is common to communicate.

  An example of such a torsional vibration damping device is disclosed in Patent Document 1. This torsional vibration damping device is mainly composed of a disk plate to which power from a drive source is transmitted, a hub plate on the output side facing the disk plate, and an arc spring incorporated between the disk plate and the disk plate. The part is composed. The disk plate and the hub plate are each provided with a pair of spring receiving portions that can be in contact with both end surfaces of the arc spring in the circumferential direction, and a receiving space for receiving the arc spring is formed between the pair of spring receiving portions. The The arc spring is a coil spring that is curved in an arc shape so that the center axis is concentric with the rotation axis of the disk plate and the hub plate. This arc spring can make the followability to torque fluctuation and the allowable load better than a general coil spring in which the central axis is linear.

  When the rotational force is transmitted from the drive source to the disk plate, the arc spring is compressed in the circumferential direction by the spring receiving portion of the disk plate that contacts the end surface of the arc spring facing the rotation direction. Then, the rotational force is transmitted to the hub plate through the spring receiving portion of the hub plate that is in contact with the opposite end surface of the arc spring. That is, the rotation of the disk plate is transmitted to the hub plate in a state where the arc spring is compressed according to the rotation torque of the disk plate. Torque fluctuations generated in the drive source are absorbed by further expansion and contraction of the arc spring accompanied by relative rotation between the disk plate and the arc spring.

JP 2014-114912 A

  In the torsional vibration damping device disclosed in Patent Document 1, the arc spring is displaced radially outward by the centrifugal force generated with the rotation of the disk plate, and the radially outer circumferential wall defining the accommodation space. Press firmly against. When the arc spring expands and contracts in such a state, a large friction is generated between the outer peripheral edge of the arc spring and the radially outer peripheral wall defining the accommodation space by the action of the centrifugal force described above, This contributes to increasing the hysteresis of the arc spring.

  However, in the conventional torsional vibration damping device, no particular attention has been paid to intentionally increasing or decreasing the hysteresis generated in the arc spring.

  An object of the present invention is to provide a torsional vibration damping device capable of previously controlling the hysteresis generated in an arc spring to a desired characteristic.

  A torsional vibration damping device according to the present invention includes a rotatable spring holder having a disc-shaped end plate portion and an annular cylindrical portion rising from the outer peripheral edge of the end plate portion, and an inner peripheral surface of the cylindrical portion of the spring holder A coil spring that is accommodated in the spring holder and curved in a circular arc concentric with the rotation center of the spring holder, and is provided integrally with the spring holder and contacts one end side along the central axis of the coil spring. A first rotating body formed with a spring receiving portion in contact with the second rotating body, and a second rotating support member formed opposite to the first rotating body and in contact with the other end side along the central axis of the coil spring. A rotating body and an annular protrusion or groove formed on the inner peripheral surface of the cylindrical portion of the spring holder for defining a contact state between the inner peripheral surface of the cylindrical portion and the coil spring are provided. And

  In the present invention, the coil spring expands and contracts with the relative rotation between the first rotating body and the second rotating body, and absorbs torque fluctuations between the first rotating body and the second rotating body. . At this time, the frictional force generated between the expanding and contracting coil spring and the inner peripheral surface of the cylindrical portion is defined by the annular protrusion or groove.

  The torsional vibration damping device according to the present invention may further comprise an annular protrusion or groove formed on the surface of the end plate portion of the spring holder and defining the contact state between the surface of the end plate portion and the coil spring. It is valid.

  According to the torsional vibration damping device of the present invention, by changing the number and shape of the annular protrusions or grooves formed on the inner peripheral surface of the cylindrical portion of the spring holder, the coil spring that expands and contracts, and the inner peripheral surface of the cylindrical portion It is possible to freely adjust the magnitude of the frictional resistance generated during the period. In other words, it is possible to control the hysteresis characteristics of the arc spring by defining the number and shape of the annular protrusions or grooves.

It is sectional drawing of one Embodiment which integrated the torsional vibration damping device by this invention in the torque converter with a lockup clutch. It is an extraction expanded sectional view of the part of the torsional vibration damping device in FIG. It is a front view of the part of the torsional vibration damping device in the embodiment shown in FIG. 1, and the lockup piston is drawn by a two-dot chain line. FIG. 4 is a three-dimensional projection view showing the external appearance of the torsional vibration damping device shown in FIG. 3, and shows the driven plate in an exploded state. FIG. 4 is an exploded perspective view of the torsional vibration damping device shown in FIG. 3. In the torsional vibration damping device shown in FIG. 3, it is a schematic diagram showing the relative positional relationship between the first rotating body, the second rotating body, and the arc spring in a state where rotational torque is not acting. In the torsional vibration damping device shown in FIG. 3, it is a schematic diagram showing the relative positional relationship between the first rotating body, the second rotating body, and the arc spring in a state where rotational torque is acting.

  DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment in which a torsional vibration damping device according to the present invention is incorporated in a torque converter with a lockup clutch will be described in detail with reference to FIGS. However, the present invention is not limited to such an embodiment, and the configuration thereof can be changed as appropriate according to the characteristics required for the power transmission mechanism in which the torsional vibration damping device is incorporated.

  FIG. 1 shows a cross-sectional structure of a torque converter with a lockup clutch in the present embodiment. The torsional vibration damping device in this embodiment is incorporated in a torque converter (hereinafter simply referred to as a torque converter) 10 with a lock-up clutch that connects an internal combustion engine (not shown) of the vehicle and an automatic transmission. A turbine runner 12 and a lockup piston 13 are assembled to an output shaft of a torque converter 10 connected to an input shaft of an automatic transmission (not shown), that is, a turbine hub 11. The turbine runner 12 is integrally connected to the turbine hub 11, and the lockup piston 13 is rotatably attached to the turbine hub 11. The damper A as the torsional vibration damping device of the present invention is assembled between the turbine runner 12 and the lockup piston 13.

  When the lockup clutch B is in a non-engaged state, the lockup piston 13 is in a non-contact state with respect to the front cover 14a of the torque converter case 14 to which power from the internal combustion engine is transmitted. For this reason, the rotation of the pump impeller 15 integral with the torque converter case 14 is transmitted to the turbine hub 11 integral with the turbine runner 12 via the automatic transmission oil interposed in the torque converter case 14. Torque fluctuations generated in the internal combustion engine are alleviated by the shear resistance of the automatic transmission oil interposed between the pump impeller 15 and the turbine runner 12.

  On the other hand, when the lockup clutch B is in the engaged state, the friction plate 16 joined to the lockup piston 13 is pressed against the front cover 14a of the torque converter case 14. Therefore, the rotation of the torque converter case 14 is transmitted to the turbine hub 11 via the damper A without passing through the automatic transmission oil. Accordingly, torque fluctuations generated in the internal combustion engine are alleviated by the damper A interposed between the lockup piston 13 and the turbine hub 11.

  FIG. 2 shows the portion of damper A extracted and enlarged in FIG. 1, the front shape of this damper A is schematically shown in FIG. 3, and the appearance of the damper A in a state where the driven plate 17 is cut away is shown in FIG. FIG. 5 shows the appearance of the damper A in a disassembled state. In FIG. 3, the lock-up piston 13 is drawn with a two-dot chain line for convenience. The previous lock-up piston 13 functions as a spring holder of the torsional vibration damping device in the present invention, and constitutes a part of the damper A in the present embodiment. The lock-up piston 13 has a disc-shaped end plate portion 13a and an annular cylindrical portion 13b that rises from the outer peripheral edge of the end plate portion 13a toward the pump impeller 15 side, and has an inner periphery of the end plate portion 13a. The end is rotatably supported by the turbine hub 11. The damper A in the present embodiment further includes an arc spring 18, a drive plate 19, and a driven plate 17 in addition to the lockup piston 13 described above.

  The arc spring 18 accommodated in the lockup piston 13 functions as a coil spring in the present invention, and a plurality (four in the illustrated example) are arranged in the circumferential direction along the inner peripheral surface of the cylindrical portion 13b of the lockup piston 13. ing. The center axis 18C of each arc spring 18 is curved in a circular arc shape concentric with the rotation center of the lockup piston 13, that is, the rotation axis 10C of the torque converter 10.

  An annular drive plate 19 that is integrally fixed to the lockup piston 13 via the rivet 20 functions as the first rotating body of the present invention. On the outer periphery of the drive plate 19, a plurality (four in the illustrated example) of spring receiving portions 19 a that can come into contact with the end surface in the circumferential direction of the arc spring 18 are protruded at equal intervals in the circumferential direction. The previous arc spring 18 is disposed between two spring receiving portions 19a adjacent to each other in the circumferential direction. The distance W along the circumferential direction between two circumferentially adjacent spring receiving portions 19a is substantially the same as or slightly smaller than the length along the central axis 18C of each arc spring 18 in an uncompressed state. It is set narrowly.

  The driven plate 17 disposed between the drive plate 19 and the turbine runner 12 so as to face the drive plate 19 functions as a second rotating body of the present invention that can rotate relative to the drive plate 19. The driven plate 17 is integrally fixed to the turbine hub 11 via the rivet 21 together with the turbine runner 12. A plurality (four in the illustrated example) of spring receiving portions 17a that can come into contact with the circumferential end surface of the arc spring 18 are provided on the outer periphery of the driven plate 17 so as to project at equal intervals in the circumferential direction. The spring receiving portions 17a are adjacent to each other in the circumferential direction. The distance along the circumferential direction between two circumferentially adjacent spring receiving portions 17a is substantially the same as or slightly narrower than the length along the central axis 18C of each arc spring 18 in an uncompressed state. Is set. In other words, the interval along the circumferential direction of the two spring receiving portions 17a adjacent in the circumferential direction of the driven plate 17, and the interval along the circumferential direction of the two spring receiving portions 19a adjacent in the circumferential direction of the drive plate 19 Are set to the same.

  Therefore, when the internal combustion engine is stopped and the driving torque is not transmitted to the torque converter case 14, the lockup clutch B is in a non-engaged state. The phases of the spring receiving portions 19a, 17a of the drive plate 19 and the driven plate 17 are matched by the spring force of the arc spring 18, and as shown in FIG.

  From this state, when the driving torque from the internal combustion engine is transmitted to the torque converter case 14 and the lockup clutch B is in the disengaged state, the driven plate 17 is moved to the turbine via the automatic transmission oil as the pump impeller 15 rotates. It rotates with the runner 12. Then, the rotational torque transmitted to the driven plate 17 is transmitted from the arc spring 18 to the drive plate 19, and the driven plate 17 and the drive plate 19 rotate integrally. At this time, the outer peripheral edge of the arc spring 18 is pressed against the inner peripheral surface of the cylindrical portion 13 b of the lockup piston 13 due to the influence of the centrifugal force generated with the rotation of the torque converter case 14. Further, the phase of the spring receiving portion 17 a of the driven plate 17 is shifted counterclockwise from the state shown in FIG. 6 with respect to the spring receiving portion 19 a of the drive plate 19, and the arc spring 18 is compressed according to the rotational resistance of the drive plate 19. Kept in a state.

  When the lockup clutch B is in the disengaged state, as described above, the torque fluctuation generated in the internal combustion engine is caused by the shear resistance of the automatic transmission oil interposed between the pump impeller 15 and the turbine runner 12. Will be alleviated.

  When the lockup clutch B is switched from this state to the engaged state, the drive torque from the internal combustion engine is directly transmitted to the drive plate 19 integrated with the lockup piston 13 via the torque converter case 14. As a result, drive torque is transmitted from the drive plate 19 to the turbine hub 11 integrated with the driven plate 17 via the arc spring 18, and the pump impeller 15 and the turbine runner 12 rotate integrally. For this reason, the arc spring 18 gradually returns from the compressed state to the original extended state. However, when a torque fluctuation occurs in the internal combustion engine, the arc spring 18 is displaced to the compressed state, and this torque fluctuation is alleviated. It has become.

  A plurality of (eight in the illustrated example) annular protrusions 22 projecting toward the arc spring 18 are parallel to the rotational axis 10 </ b> C of the torque converter 10 on the inner peripheral surface of the cylindrical portion 13 b of the lockup piston 13. It is formed at regular intervals along the direction. The individual annular protrusions 22 in the present embodiment have a mountain-shaped cross section, but are not limited thereto. For example, a trapezoidal cross section or a semicircular cross section may be used, and the annular protrusion 22 can be formed by pressing the cylindrical portion 13b.

  As described above, since the annular protrusions 22 protrude from the inner peripheral surface of the cylindrical portion 13b of the lockup piston 13, the arc spring 18 is caused to enter the individual annular protrusions 22 by the centrifugal force generated as the torque converter case 14 rotates. It pushes against the top, that is, the inner peripheral edge. This acts as a frictional resistance when the arc spring 18 expands and contracts in accordance with torque fluctuations of the internal combustion engine, and affects the hysteresis characteristics of the arc spring 18. Accordingly, by changing the contact area with the arc spring 18 by increasing or decreasing the number of the annular protrusions 22 or changing the cross-sectional shape thereof, etc., the hysteresis characteristics of the arc spring 18 according to the characteristics required for the damper A Can be controlled. For example, when it is desired to increase the hysteresis, the contact area between the annular protrusion 22 and the arc spring 18 is increased. When the hysteresis is desired to be decreased, the contact area between the annular protrusion 22 and the arc spring 18 is decreased. Is effective.

  In this embodiment, the shape of the inner peripheral surface on the tip side of the cylindrical portion 13b with which the arc sprink 18 abuts, that is, the side close to the turbine runner 12, is an arc-shaped cross section corresponding to the outer diameter of the arc spring 18. It is not limited to this. Even if the torque converter case 14 is not rotating, the arc spring 18 may be configured so that the arc spring 18 does not fall off from the cylindrical portion 13b of the lockup piston 13.

  A plurality of (four in this embodiment) annular projections 23 projecting toward the arc spring 18 are also provided on the surface of the end plate portion 13 a of the lockup piston 13 facing the drive plate 19. It is formed concentrically with the rotation axis 10C. Therefore, the hysteresis characteristics of the arc spring 18 can be controlled over a wider range by changing the contact area with the arc spring 18 by changing the number of the annular projections 23, the cross-sectional shape, etc., like the annular projection 22 described above. Is possible.

  In the above-described embodiment, it is necessary to make the plate thickness of the region where the annular protrusions 22 and 23 are formed thicker than other portions, but an annular groove complementary to the annular protrusions 22 and 23 is formed in the cylindrical portion 13b. This is not necessary when it is formed on the inner peripheral surface or the surface of the end plate portion 13a. That is, a region corresponding to the annular protrusion is formed between the adjacent annular grooves, and the contact area between the inner peripheral surface of the end plate portion 13a and the cylindrical portion 13b removed by the annular groove and the arc spring 18 is changed. As a result, the hysteresis characteristics of the arc spring 18 can be controlled in a wider range.

  Further, in the present embodiment, before the arc spring 18 enters the allowable maximum compression state due to the relative rotation of the drive plate 19 and the driven plate 17, the stopper means C is further provided for restricting the relative rotation of these. The stopper means in the present embodiment includes a plurality (four in the illustrated example) of coil springs 24 held between the lockup piston 13 and the drive plate 19. An opening 19b formed on the inner peripheral side of the drive plate 19 so as to accommodate each coil spring 24 and an arc-shaped opening 17b formed on the driven plate 17 so as to face the coil spring 24 are Include as a component. The coil spring 24 is accommodated in the opening 19b of the drive plate 19 in a compressed state. Therefore, both ends of the coil spring 24 are pressed against both ends in the circumferential direction of the opening 19b of the drive plate 19. The length along the circumferential direction of the opening 17 b formed in the driven plate 17 is longer than the length of the coil spring 24 and defines the relative rotation amount of the driven plate 17 with respect to the drive plate 19. That is, the amount of relative rotation between the drive plate 19 and the driven plate 17 is regulated by the collision of the end in the circumferential direction of the opening 17 b of the driven plate 17 with the end surface of the coil spring 24 held by the drive plate 19. At this time, the coil spring 24 is further compressed, so that the impact generated when the driven plate 17 collides against the coil spring 24 is reduced. The spring constant of the coil spring 24 that functions as a stopper needs to be set sufficiently higher than the spring constant of the arc spring 18.

  It should be noted that the present invention should be construed only from the matters described in the claims, and in the above-described embodiment, all the changes and modifications included in the concept of the present invention are other than those described. Is possible. That is, all matters in the above-described embodiments are not intended to limit the present invention, and can be arbitrarily changed according to its use, purpose, and the like, including configurations not directly related to the present invention. Is.

10 Torque converter with lock-up clutch (torque converter)
10C Torque converter rotation axis 13 Lock-up piston (spring holder)
13a End plate portion 13b Tube portion 17 Driven plate (second rotating body)
17a Spring receiving portion 18 Arc spring (coil spring)
18C Center axis of arc spring 19 Drive plate (first rotating body)
19a Spring receiving part 22, 23 Annular projection A Damper (torsional vibration damping device)

Claims (1)

A rotatable spring holder having a disc-shaped end plate portion and an annular cylindrical portion rising from the outer peripheral edge of the end plate portion;
A coil spring which is accommodated in the spring holder along the inner peripheral surface of the cylindrical portion of the spring holder and which is curved in an arc shape concentric with the rotation center of the spring holder;
A first rotating body provided integrally with the spring holder and formed with a spring receiving portion that abuts on one end side along the central axis of the coil spring;
A second rotating body formed with a spring receiving portion facing the first rotating body and contacting the other end side along the central axis of the coil spring;
Torsional vibration characterized by comprising an annular protrusion or groove formed on the inner peripheral surface of the cylindrical portion of the spring holder and defining the contact state between the inner peripheral surface of the cylindrical portion and the coil spring. Damping device.

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