JP4950776B2 - Torsional vibration reduction device - Google Patents

Description

  The present invention relates to a torsional vibration reduction device, and is a device that can stably support a pair of springs by improving a connecting portion interposed between the pair of springs.

A torsional vibration reducing device is provided between the crankshaft of the engine mounted on the vehicle and the turbine of the torque converter. The torsional vibration reducing device elastically connects an input side member connected to a crankshaft of an engine, an output side member connected to a turbine of a torque converter, and the input side member and the output side member in a rotational direction. It is comprised with the spring arrange | positioned along the circumferential direction while connecting. An annular holding member is provided in order to restrict this deformation when the spring arranged along the circumferential direction is compressed and centrifugal force acts to bend in a convex shape in the outer circumferential direction. There is. This holding member is free without being pressed against other constituent members and does not cause hysteresis. As a conventional torsional vibration reducing device provided with such a holding member, there is one disclosed in Patent Document 1. . In this torsional vibration reducing device, a spring holder is provided as a holding member that covers the entire outer circumference of the spring, and a claw portion formed inside the spring holder is inserted between a pair of springs.
JP 2002-089657 A

  However, since the claw portion is configured to abut against the element wire of the spring wound along a circle along the radial direction, the claw portion stabilizes the end portions of the spring when the pair of springs are compressed. Therefore, there is a possibility that the spring and the member holding the spring may be worn or damaged.

  In recent years, the material used has been made thinner for the purpose of reducing the cost and weight of parts. For this reason, a retainer is interposed between the spring and the claw portion.

  Therefore, an object of the present invention is to provide a torsional vibration reduction device that solves the above-described problems.

According to a first aspect of the present invention, there is provided a lockup piston that is provided between an engine crankshaft and a transmission and that can be connected to and disconnected from the crankshaft, an input-side member coupled to the lockup piston, A plurality of first pressing parts arranged along the circumferential direction on the outer peripheral part of the input side member, a pair of springs arranged between the first pressing parts, and the outer side of the spring covering the outer side of the input side member An annular holding member which is relatively rotatable with respect to the holding member, a connecting portion projecting radially inward from the holding member between the pair of springs, an output side member connected to the transmission, and the output In the torsional vibration reduction device having a second pressing portion provided on the side member at substantially the same interval as the first pressing portion and compressing the spring between the first pressing portion,
The holding member is formed in a cylindrical shape, and both ends of the cylinder are formed to project radially inward to form a pair of contact surfaces, and the pair of contact surfaces allow the respective springs to be connected to the connecting portion. It is characterized by a spring receiving surface .

According to the present invention, both ends of the cylinder constituting the holding member are formed to project radially inward to form a pair of contact surfaces, so that only one side protrudes radially inward as in the case of forming the spring. The spring is stably supported by the connecting portion without being deformed by being twisted by the urging force. Further, since there is no notch, there is no portion where stress is concentrated, and the strength of the holding member can be maintained.

The invention according to claim 2 is the torsional vibration damping system according to claim 1, wherein the protruding portion is formed by bending, characterized in that to increase the contact area between the spring.

  According to the present invention, since the projecting portion is bent and the contact area with the spring is large, the spring is prevented from popping out, and the spring is stably supported by the connecting portion.

The invention according to claim 3 is the torsional vibration reduction device according to claim 2 , wherein a retainer is interposed only at an end portion of the spring that contacts the first pressing portion and the second pressing portion. To do.

  According to the present invention, since the spring is stably supported at the connecting portion, there is no need to interpose a retainer for preventing the spring from jumping out between the spring and the connecting portion, and the number of parts is reduced.

According to the torsional vibration reducing device of the first aspect , since both end portions of the cylinder constituting the holding portion are formed to protrude radially inward to form a pair of contact surfaces, only one side protrudes radially inward. Unlike the case where it is formed, it is not twisted and deformed by the urging force of the spring, and the spring is stably supported by the connecting portion. Further, since there is no notch, there is no portion where stress is concentrated, and the strength of the holding member can be maintained.

According to the torsional vibration reducing device of the second aspect , since the protruding portion is bent and the contact area with the spring is large, the spring is prevented from popping out and the spring is stably supported by the connecting portion. .

According to the torsional vibration reducing device of the third aspect , since the spring is stably supported at the connecting portion, there is no need to interpose a retainer for preventing the spring from jumping out between the spring and the connecting portion. Points are reduced.

Embodiments of a torsional vibration reducing device according to the present invention will be described below.
(A) Embodiment 1
First, the first embodiment will be described with reference to FIGS. A torque converter is disposed between a crankshaft of an engine (not shown) and a transmission (not shown). The torque converter is provided with a torsional vibration reducing device 1 shown in FIG. The torsional vibration reducing device 1 includes a lockup piston 2 that can be connected to and disconnected from a cover (not shown) of a torque converter that is connected to a crankshaft (not shown) on the left in FIG. 1 (b), and the lockup piston. 2, an input side member 3 coupled to a turbine of a torque converter (not shown) on the right side in FIG. 1B, an input side member 3 disposed along the circumferential direction and the input side A spring 5 that elastically couples the member 3 and the output side member 4 in the rotational direction, and is arranged so as to cover the outer periphery of the spring 5, restricts both axial sides of the spring 5, and lockup piston 2 and input The ring-shaped holding member 6 is rotatable relative to the side member 3. In addition, the lower left 1/4 of FIG. 1 is a figure in the state in which the output side member 4 exists, and the other part is a figure which abbreviate | omitted the output side member 4. FIG.

  The lock-up piston 2 has a hole 2a for supporting the lock-up piston 2 in the axial direction so as to be movable in the axial direction, and a friction lining 2b is coupled to the vicinity of the outer peripheral surface. The friction lining 2b causes the lock-up piston 2 to move to the left in the axial direction, frictionally connect with a cover (not shown) of the torque converter that rotates integrally with the crankshaft of the engine, and rotate integrally with the cover. A cylindrical cylindrical portion 2 c is formed on the outer peripheral portion of the lockup piston 2.

  The input side member 3 is provided so as to be coupled to the transmission side surface of the lockup piston 2, and a large hole 3e is formed in the center as shown in FIG. As shown in FIG. 2A, four first pressing portions 3 b that press the end portion of the spring 5 are formed on the outer peripheral portion of the input side member 3 at substantially equal intervals along the circumferential direction. . The cross-sectional shape of the first pressing portion 3b is a substantially U-shaped cross section as shown in the upper part of FIG. In FIG. 1, in the circumferential direction, a pressing portion position where the first pressing portion 3b and the second pressing portion 4b are present is indicated by P, and a connecting portion position where a connecting portion 6c described later is present is indicated by Q. In addition, an arcuate throttle portion 3c is formed inside the first pressing portion 3b for the purpose of reinforcement. Further, the first pressing portion 3b is extended to the transmission side and further extended outward in the radial direction, thereby forming a restriction portion 3f that restricts the holding member 6 from moving to the transmission side. Between the four first pressing portions 3b in the circumferential direction, as shown in the lower part of FIG. 2B, a regulating portion 3d that regulates the inner side of the spring 5 and the axial transmission side is provided in the circumferential direction. It is formed in an arc shape along. A mounting hole 3a is formed slightly on the center side from the both end positions of the first pressing portion 3b in the circumferential direction in FIG. 2A, and the input side member 3 is connected via the rivet 7 inserted into the mounting hole 3a. Coupled to the lock-up piston 2. Since the input side member 3 compresses the spring 5 and slides with the spring 5 and the holding member 6, high strength and hardness are required, and carbonitriding is performed.

  As shown in FIG. 3A, the holding member 6 has an annular shape that covers the outer periphery of the spring 5. The cross-sectional shape is cylindrical as shown in the upper part of FIG. 3B, and a pair of side surface restricting portions 6a and 6b for restricting both axial sides of the spring 5 are formed at both ends of the cylinder. As shown in the cross-sectional shape in the lower part of FIG. 3B, the holding member 6 is formed with four connecting portions 6c projecting between the pair of springs 5 inward in the radial direction at substantially equal intervals in the circumferential direction. ing. The connecting portion 6c is provided to connect the pair of springs 5 in the circumferential direction, and the connecting portion 6c includes a pair of projecting portions 6d and 6e as shown in the lower part of FIG. Has been. That is, a pair of projecting portions 6d and 6e are formed so as to project both ends of the cylinder inward in the radial direction and come into contact with the upper left portion and the lower right portion of the end face of the spring 5. The protrusion 6d is formed such that the side surface restricting portion 6a is bent inwardly in the radial direction, axially on the transmission side, and radially inward to increase the contact area with the spring 5, while the protrusion 6e is formed on the side surface restricting portion 6b. Is bent inward in the radial direction. By configuring the connecting portion 6c with a pair of projecting portions 6d and 6e, the spring receiving surface for receiving each spring 5 has a contact area as shown by a mesh line as shown in FIG. It is comprised by a pair of contact surfaces 6f and 6g with large. The holding member 6 is obtained by drawing a flat plate into a ring shape and drawing it. Since the holding member 6 slides in contact with the spring 5 on which centrifugal force acts, high strength and durability are required, and a carbonitriding process or the like is performed. A lubricating film coating may be applied to a portion that slides with the spring 5.

  The movement of the holding member 6 toward the engine in the axial direction is restricted by the lockup piston 2, and the movement toward the transmission side is restricted by the restriction portion 3 f of the input side member 3. On the other hand, the restriction of the holding member 6 in the radial direction is basically performed by the presence of the outer spring portion of the inner spring 5 and the first pressing portion 3 b of the input side member 3.

  The output side member 4 will be described. As shown in FIG. 4A, the second pressing portions 4b that press the end portions of the springs 5 are provided at substantially the same intervals as the first pressing portions 3b, and the second side of the input side member 3 is arranged in the circumferential direction. It arrange | positions in the press part position P corresponding to the 1 press part 3b, and compresses the spring 5 between the 1st press parts 3b. The second pressing portion 4b protrudes in the form of a single character toward the axial engine side as shown in the upper part of FIG. 4B. As shown in FIG. 1B, the output side member 4 extends from the transmission side to the input side. It is assembled toward the member 3. 4B, the outer peripheral portion between the first pressing portions 3b in the circumferential direction is a restricting portion for restricting the radially inner side and the axial transmission side with respect to the spring 5. As shown in FIG. 4a is formed at a position corresponding to the restriction portion 3d of the input side member 3 in the circumferential direction. A mounting hole 4c for connecting to the turbine of the torque converter is formed on the radially inner peripheral side of the output side member 4.

  As shown in FIG. 1B, the spring 5 is constituted by a parent-child spring comprising a large-diameter parent spring 5a and a child spring 5b accommodated in the parent spring 5a. A pair of the springs 5 configured in this way is disposed between the first pressing portions 3 b of the input side member 3. A retainer 8 is interposed at the end of the spring 5 that contacts the first pressing portion 3b and the second pressing portion 4b, but the retainer 8 is provided between the connecting portion 6c and the spring 5. Absent. The reason why the retainer 8 is not provided between the connecting portion 6c and the spring 5 is that the end portion of the spring 5 is received by the pair of contact surfaces 6f and 6g having a large contact area, so that the end portion of the spring 5 is supported stably. This is because there is no need to provide the retainer 8.

  Next, the operation of the torsional vibration reducing device will be described.

  When the engine rotates and its rotational speed reaches a predetermined value, the lock-up piston 2 is pressed to the engine side by hydraulic pressure, and the friction lining 2b is pressed and connected to the cover of the torque converter (not shown). Is transmitted to the input side member 3 through the lock-up piston 2. When the input side member 3 rotates relative to the output side member 4, the pair of springs 5 is the first of the input side member 3 even when the input side member 3 rotates relatively in any direction. Compression is performed by the pressing portion 3b and the second pressing portion 4b of the output side member 4, and the spring 5 has an elastic property, so that torsional vibration is reduced. Then, due to the compression of the pair of springs 5, the connecting portion 6 c moves in the circumferential direction together with the holding member 6. Since the spring 5 is compressed, a force acts in the outer circumferential direction. Further, since the spring 5 rotates, a centrifugal force is applied, and all the force in the outer circumferential direction and the centrifugal force are applied to the holding member 6. These forces are strongest at the position of the connecting portion 6 c located at the center of the pair of springs 5, and this position has the largest relative movement amount of the spring 5 and the holding member 6 in the circumferential direction. There are few positions. Since the relative movement amount between the spring 5 and the holding member 6 in the radially outward direction is the smallest, the occurrence of hysteresis is suppressed to a minimum.

  According to the present invention, since the springs 5 are received by the pair of contact surfaces 6f and 6g on both sides of the connecting portion 6c interposed between the pair of springs 5, the spring 5 is supported by the connecting portion 6c. It is performed stably.

  According to the present invention, both ends of the cylinder constituting the holding member 6 are formed to project radially inward to form the pair of contact surfaces 6f and 6g, so that only one side projects radially inward. Thus, the spring 5 is stably deformed without being twisted and deformed by the biasing force of the spring 5 as described above. Moreover, since there is no notch, there is no stress concentration, and the strength of the holding member 6 can be maintained.

  According to the present invention, the protruding portion is bent and formed so that the contact area with the spring 5 is large, so that the spring 5 is prevented from popping out and the spring 5 is stably supported by the connecting portion 6c.

According to this invention, since the spring 5 is stably supported by the presence of the pair of contact surfaces 6f and 6g having a large contact area in the connecting portion 6c, the spring is interposed between the spring 5 and the connecting portion 6c. There is no need to intervene a retainer for preventing 5 from popping out, and the number of parts is reduced.
(B) Embodiment 2
Next, a second embodiment will be described. Since this embodiment is obtained by changing a part of the first embodiment, the same portions are denoted by the same reference numerals, description thereof is omitted, and only different portions are described.

  As shown in the lower part of FIG. 6, the shape of the protruding portion 6 d of the pair of protruding portions 6 d and 6 e constituting the connecting portion 6 c of the holding member 6 is formed in an inverted U shape in the present embodiment. In this case, there is no portion corresponding to the protruding portion 6e in FIG.

  Since other configurations and operations are the same as those of the first embodiment, description thereof is omitted.

  In addition, although the shape shown in FIG. 5 or the inverted U-shape shown in FIG. 6 is shown as the shape of the contact surface of the connecting portion, it may be L-shaped, S-shaped or crank-shaped.

FIG. 5A is a front view of the torsional vibration reduction device, with partly omitted, and FIG. 5B is a view taken along the line A-0-A in FIG. It is related with an input member, (a) is a front view, (b) is a B-0-B arrow view of (a) (Embodiment 1). It is related with a holding member, (a) is a front view, (b) is the C-0-C arrow line view of (a) (Embodiment 1). It is related with an output member, (a) is a front view, (b) is the E-0-E arrow line view of (a) (Embodiment 1). DD arrow view of FIG. 3 (Embodiment 1). Sectional drawing of a torsional vibration reducing device (Embodiment 2).

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Torsional vibration reduction apparatus 2 ... Lock-up piston 3 ... Input side member 3b ... 1st press part 4 ... Output side member 4b ... 2nd press part 5 ... Spring 6 ... Holding member 6c ... Connection part 6f, 6g ... Contact surface

Claims (3)

A lockup piston that is provided between the crankshaft of the engine and the transmission and that can be connected to and disconnected from the crankshaft, an input side member coupled to the lockup piston, and a circle on the outer periphery of the input side member A plurality of first pressing portions disposed along the circumferential direction, a pair of springs disposed between the first pressing portions, an outer periphery of the springs, and relatively rotatable with respect to the input side member An annular holding member, a connecting portion projecting radially inward from the holding member between the pair of springs, an output side member connected to the transmission, and the first pressing portion on the output side member And a torsional vibration reducing device having a second pressing portion that is provided at substantially the same interval and compresses the spring between the first pressing portion,
The holding member is formed in a cylindrical shape, and both ends of the cylinder are formed to project radially inward to form a pair of contact surfaces, and the pair of contact surfaces allow the respective springs to be connected to the connecting portion. A torsional vibration reduction device characterized by a spring receiving surface . The torsional vibration reducing device according to claim 1 ,
The torsional vibration reducing device according to claim 1, wherein the protruding portion is bent to increase a contact area with the spring. The torsional vibration reduction device according to claim 2 ,
A torsional vibration reduction device, wherein a retainer is interposed only at an end portion of the spring contacting the first pressing portion and the second pressing portion.

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