JP3521012B2 - Vibration damping device for torsional damper - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toe used for the purpose of damping in a transmission system between a prime mover and a transmission, such as an engine, having a torque fluctuation and having a torque fluctuation. The present invention relates to a vibration damping device for a positional damper. 2. Description of the Related Art A conventional example of this kind of torsional damper is disclosed in, for example, Japanese Patent Application No. Hei.
There is one described in FIG.
This torsion damper is conceptually shown in FIGS.
And a hub plate 2 connected to one of two rotating bodies (for example, an engine output shaft and a torque converter) to be drivingly connected to each other (for example, a torque converter) by bolts 1 and coaxially adjacent to the hub plate. Side plates 4 and 5 connected to the other rotating body (for example, an engine output shaft) by bolts 3, and circumferentially arranged to transmit power between the hub plate 2 and the side plates 4 and 5. And a torsion spring 6. A torsion spring 6 is accommodated in a rectangular window 2a formed to penetrate the hub plate 2 in the axial direction so as to extend in the circumferential direction, and a wire loop portion of the torsion spring 6 protruding from the rectangular window. The side plate 4,
5 are received in the rectangular windows 4a, 5a. As a result, both ends of the torsion spring 6 are seated at the circumferential ends of the rectangular windows 2a, 4a, 5a to elastically support the hub plate 2 and the side plates 4, 5 at the relative rotation neutral position. 6 can transmit power between the hub plate 2 and the side plates 4 and 5. Thus, the rotation of the engine output shaft is controlled by the bolt 3, the side plates 4, 5, the torsion spring 6,
The torque is transmitted to the torque converter via the hub plate 2 and the bolt 1 sequentially, and during this power transmission, the torque deformation can be absorbed by the elastic deformation of the torsion spring 6 and a predetermined buffer function can be achieved. [0005] When rotational vibration is generated by resonance at the time of starting the engine or the like, this causes a large relative rotation between the hub plate 2 and the side plates 4 and 5, and the rotational vibration is generated by the following mechanism. Attenuate. That is, this conventional vibration damping device for a torsional damper includes retaining plates 7, 8 which are rotationally engaged with the inner surfaces of the side plates 4, 5, facing each other. The friction block 9 is interposed. Then, the disc spring 10 is contracted between the side plate 5 and the retaining plate 8 to urge the retaining plate 8 toward the retaining plate 7, thereby causing the friction block 9 to retain the friction block 9, and thus the friction block 9. A frictional contact is made with the side plates 4 and 5. The friction block 9 is inserted through a circumferentially elongated hole 2b formed to penetrate the hub plate 2 in the axial direction,
The elongated hole 2b restrains the friction block 9 in the radial direction, but forms the friction block 9 in such a shape that the friction block 9 can be moved relative to the hub plate 2 by a gap α in both circumferential directions. Further, low rigid bodies 11 are provided at both ends of a circumferentially long hole 2b for the friction block 9 formed on the hub plate 2 connected to the torque converter with the bolt 1. [0008] Such a vibration damping device operates as follows. In other words, under a small torsion angle of the torsional damper smaller than the gap α, the friction block 9 does not come into contact with both ends of the circumferential elongated hole 2b, and the friction block 9 is sandwiched between the retaining plates 7, 8. With these, that is, with the side plates 4 and 5, it is displaced relatively to the hub plate 2. Therefore, the friction block 9 has no influence on the buffer function of the torsional damper, and can reliably absorb the torque fluctuation. When rotational vibration is generated due to resonance at the time of starting the engine or the like, this causes a large relative rotation of α or more between the hub plate 2 and the side plates 4 and 5 (a large torsional displacement of the torsional damper). As a result, the friction block 9 comes into contact with the low rigid body 11 provided at the end of the circumferentially long hole 2b and engages with the hub plate 2. Due to the engagement with the hub plate 2, the friction block 9 cannot be displaced together with the side plates 4 and 5, and the friction block 9 applies frictional resistance to the side plates 4 and 5, and as shown in FIG. A large hysteresis torque is generated in the torsional displacement region of the torsion damper described above. Due to this hysteresis torque, the above-described rotational vibration is attenuated, and the vibration can be suppressed. At this time, when the friction block 9 is displaced relative to the hub plate 2 by the circumferential limited range α together with the side plate 4, the friction block 9 does not directly collide with the hub plate 2 but contacts the hub plate 2 via the low-rigid body 11. Therefore, it is possible to eliminate the problem that a loud metallic sound is generated due to the collision and a vibration is generated due to the rebound. However, in the above-mentioned conventional vibration damping device for a torsional damper, low rigidity members are provided at the contact portions at both ends of the circumferentially long hole of the hub plate. The structure that suppresses the sound and vibration caused by the impact requires a low-rigid body at all the contact parts of the hub plate. As a result, it is necessary to arrange a low-rigid body twice as many as the number of friction blocks as a whole. However, the number of parts is increased, the workability of assembly is reduced, and the cost is increased. Also,
Since the low-rigid body provided in the abutting portion requires a certain thickness or more in order to secure the effect as the collision buffer member, when providing the low-rigid body, it is necessary to secure the thickness of the low-rigid body. If the clearance (play angle) α is reduced or the friction block is reduced in size in the circumferential direction, the frictional force generation area is reduced.
The increase in the major axis b causes a decrease in the rigidity of the neck portion of the hub plate, and the degree of freedom in designing the cushioning effect is reduced. An object of the present invention is to solve the above-mentioned problem by providing a low-rigid body at an abutting portion of a friction block so as not to affect the frictional force generating area of the friction block. [0012] To this end, an arrangement according to claim 1 of the present invention comprises a hub plate connected to one of two rotating bodies to be drivingly connected to each other and a hub plate connected to the hub plate. A side plate coaxially arranged and coupled to the other rotating body, a torsion spring circumferentially arranged to transmit power between the hub plate and the side plate, and one of the hub plate and the side plate is pressed to frictionally contact the torsional damper and the other to have a friction block engages collides after the relative movement in the circumferential direction limits the
The friction block is axially mounted on the hub plate and the hub plate.
Force generating surface that comes into frictional contact with one of the side plate and side plate
Both sides including the friction material, the hub plate and
Intermediate part including abutment that abuts against the other side plate
The part is a low-rigid body that is a member having a lower rigidity than the friction material.
It is characterized in that the. According to the first aspect of the present invention, the power transmission between the rotating body connected to the hub plate and the rotating body connected to the side plate uses the torsion spring. During this time, the fluctuation in torque is absorbed by the elastic deformation of the torsion spring, and a predetermined buffer function is performed. Here, when a rotational vibration of the torsional damper is generated by resonance, the friction block initially has a large relative rotation between the hub plate and the side plate, together with the hub plate or the side plate in frictional contact. Then, it moves in the circumferential direction relatively to the side plate or the hub plate, but engages with the latter side plate or the hub plate after the relative movement within the limited range in the circumferential direction. Therefore, after the relative movement within the above-mentioned circumferential limit range, frictional resistance (hysteresis torque) is generated between the friction block and the hub plate or the side plate, thereby attenuating the rotational vibration. it can. The contact portion of the friction block comes into contact with the contact portion of the side plate or the hub plate after the relative movement of the friction block within the limited range in the circumferential direction. The contact part of the friction block is
Direction of the hub plate and side plate
Friction on both sides including the frictional force generating surface that comes into frictional contact with one side
The other of the hub plate and the side plate
An intermediate portion including an abutting portion that abuts against
Since the low-rigidity member is a low-rigidity member, the engagement is performed through the low-rigidity member, which causes a problem that a loud metal sound is generated by the engagement and a problem that a vibration is generated by the rebound. In addition, the friction block and the low-rigid body are integrated, so that the number of parts is reduced and the cost is reduced. Further, the friction block and the low-rigid body can be laid out in the same limited space as in the conventional example under the same design conditions as in the conventional example, and the degree of freedom in design is improved. Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1A is a diagram showing a configuration of a main part of a first embodiment of a vibration damping device for a torsional damper according to the present invention, and FIGS. 1B and 1C are respectively diagrams of FIG. It is AA sectional drawing and arrow B view. In FIG. 1A, the same parts as those in FIGS. 4 and 5 showing the above-described conventional example (Japanese Patent Application No. 5-222358) are denoted by the same reference numerals. The first embodiment is configured in the same manner as the above-described conventional example, except for the following changes. The first embodiment is an improvement proposal for the vibration damping device of the conventional torsional damper shown in FIGS. 4 and 5. That is, in FIG. 4 and FIG. 5, of the engine output shaft and the torque converter (both not shown) to be mutually drive-coupled via the torsional damper, the hub plate 2 coupled to the torque converter by the bolt 1 is provided. A circumferential slot 2b for the formed friction block 9
Are provided at both ends of the low-rigid body 11, which is a member having a lower rigidity than the friction block 9 , but in the present embodiment, the low-rigid body is embedded in the friction block 9 as described below, and the two are joined together. It is integrated. That is, in FIG. 1A, the friction block 9 is arranged in the circumferentially long hole 2b having the same shape and the same size as the conventional example so as to occupy the same angle as the conventional example. And the play angle becomes the same angle α as in the conventional example.
Therefore, the relative positions of the friction blocks 9 with respect to the retaining plates 7, 8 and the hub plate 2 and the side plates 4, 5 are not changed at all, and the layout is the same as that of the conventional example. Further, the friction block 9, FIGS. 1 (a)
As shown in FIG. 1B, which is a cross-sectional view taken along the line A-A, a low-rigid body 21 is buried only in the vicinity of the abutting portion 9a of the friction block 9 with the hub plate 2 in order to exhibit a buffering effect. . At this time, an intermediate portion in the axial direction including a contact portion 9a with the hub plate 2 (a hatched portion in the drawing) so as not to affect an area of a frictional force generating surface which is a contact surface with the retaining plates 7, 8. Is a low-rigid body (cushioning member),
Both side surfaces in the axial direction including the frictional force generating surfaces 9b and 9c and intermediate portions in the circumferential direction (portions not hatched) are friction materials. Note that the low-rigid body 21 is a view B in FIG.
It is buried as shown. In the present embodiment having the above-described structure, when the vibration damping action is performed in the same manner as in the conventional example, when the friction block 9 is displaced relative to the hub plate 2 by the circumferential limit range α together with the side plate 4. Instead of directly colliding with the hub plate 2, it comes into contact via the low-rigid body 21 buried in the vicinity of the contact portion of the friction block 9. The problem of occurrence of vibration is prevented. In the first embodiment, the cost is reduced due to the reduction in the number of parts associated with the integration of the friction block and the low-rigid body. In addition, by arbitrarily designing the X dimension (thickness of the low-rigid body 21 embedded in the friction block 9) of the low-rigid body (cushioning material) in FIG. In addition, the degree of freedom in designing the cushioning material is improved. Further, by using a member having a low thermal conductivity as the low-rigid body (cushioning material), the durability of the low-rigidity body as the cushioning material can be improved. Further, the same layout as the above-described conventional example allows the hub plate 2
The rigidity of the neck portion (the portion between the two circumferential elongated holes 2b) is maintained at the same level as that of the conventional example, and the generation of abnormal noise due to the decrease in the play angle and the decrease in the durability due to the reduction in the frictional force generation area of the friction block. Can be prevented. FIG. 2A is a view showing the structure of a main part of a vibration damping device for a torsional damper according to a second embodiment of the present invention, and FIGS. 2B and 2C respectively show FIGS. It is CC sectional drawing and D arrow view of a). In FIG. 2A, the same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted. The second embodiment is different from the first embodiment in that the shape of the low-rigid body embedded in the friction block 9 is changed, and the other parts are configured in the same manner as the first embodiment. That is, in the first embodiment, the low-rigid body 21 is divided into two members because the low-rigid body 21 is buried only in the vicinity of the contact portion 9a of the friction block 9 in the circumferential direction. In the second embodiment, as shown in FIG. 2C, one low-rigid body 31 having the same cross-sectional shape as that of the first embodiment is subjected to friction to exert a cushioning effect as shown in FIG. Abutting portion 9a of block 9 with hub plate 2
And is buried in the whole area in the circumferential direction including the vicinity of. At this time, an intermediate portion in the axial direction including a contact portion 9a with the hub plate 2 (a hatched portion in the drawing) so as not to affect an area of a frictional force generating surface which is a contact surface with the retaining plates 7, 8. Is a low-rigid body (cushioning member),
Both side surfaces in the axial direction including the frictional force generating surfaces 9b and 9c (portions not hatched) are made of friction material. In the second embodiment, the same function and effect as those of the first embodiment are obtained, and the friction member 9 and the low-rigid body 21 are integrated by changing the embedding method of the low-rigid body. This has the effect of facilitating the creation of a finished part. FIG. 3A is a diagram showing the configuration of a main part of a vibration damping device for a torsional damper according to a third embodiment of the present invention, and FIGS. 3B and 3C respectively show FIGS. It is EE sectional drawing and arrow F figure of a). In FIG. 3A, the same parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted. The third embodiment is different from the first embodiment in that the circumferential dimension of the friction block is reduced so that the low-rigid body 21 is not embedded and is connected to both end faces (contact portions) of the friction block. The other parts are configured in the same manner as in the first embodiment. That is, in the third embodiment, FIG.
As shown in FIGS. 3A and 3C, two low-rigid bodies 21 having the same shape as in the first embodiment are combined with each other in a circumferential direction of the friction block 19 as shown in FIGS. 3A and 3B. Since the friction block 19 is shortened by the thickness of the two low-rigid bodies 21 (= twice the X dimension) and is bonded to both end faces of the friction block 19 by, for example, bonding, the circumferential dimension after the two are integrated is the first dimension. This is the same as in the first embodiment. In this embodiment, since the end face of the low-rigid body 21 directly contacts the hub plate 2, the low-rigid body 2
One end is chamfered. In the third embodiment, the number of parts is reduced due to the integration of the friction block and the low-rigid body, so that an effect of cost reduction as compared with the conventional example can be obtained, and a low-rigid body is provided inside the friction member. The effect of facilitating the production of the integrated part compared to the first and second embodiments can be obtained by the non-embedded structure.
By adding a buffering action due to sliding deformation at the joint between the low-rigid body 21 and the friction member 19 to the original buffering action of 1, the impact force can be more effectively absorbed. The low-rigid bodies (low-rigid bodies 21 and 31) used in each of the above embodiments are preferably made of, for example, a shock-absorbing material made of a felt-woven structure of para-aromatic polyamide fibers. . In this case, the addition of the low-rigid body does not cause adverse effects such as deterioration of the thermal stability of the vibration damping device, and thus the thermal stability of the torsional damper, reduction in strength, and reduction in wear resistance. . As described above, according to the structure of claim 1 of the vibration damping device for the torsional damper of the present invention,
Predetermined damping function against torque fluctuation, damping action against rotational vibration of torsional damper due to resonance, loud metal noise generated at the time of collision between friction block and side plate or hub plate, or vibration generated due to rebound It can solve the problem, of course,
The hub plate and the side plate in the axial direction.
Both sides including the frictional force generating surface that comes into frictional contact with one of the rates
The hub plate and the side play
The intermediate part including the contact part that makes contact with the other
Since the low rigid body is a member having lower rigidity than the material, the engagement is performed through the low rigid body, and a problem that a loud metal noise is generated due to the engagement and a vibration is generated due to repulsion Problem can be solved. Further, since a low-rigid body is provided at the contact portion of the friction block to integrate the friction block and the low-rigid body,
The number of parts is reduced and the cost is reduced. Furthermore, the friction block and the low-rigidity body can be laid out in the same limited space as in the conventional example under the same design conditions as in the conventional example, and the degree of freedom in design is improved.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1A is a diagram showing a configuration of a main part of a first embodiment of a vibration damping device for a torsional damper according to the present invention;
FIG. 1B is a cross-sectional view taken along the line AA of FIG. 1A, and FIG. 1C is a view taken along the arrow B of FIG. FIG. 2A is a diagram showing a configuration of a main part of a second embodiment of a vibration damping device for a torsional damper according to the present invention;
FIG. 2B is a cross-sectional view taken along line CC of FIG. 2A, and FIG. 2C is a view taken along arrow D of FIG. 2A. FIG. 3A is a diagram showing a configuration of a main part of a third embodiment of a vibration damping device for a torsional damper according to the present invention;
FIG. 3B is a cross-sectional view taken along the line E-E of FIG. 3A, and FIG. 3C is a view taken along the arrow F of FIG. FIG. 4 is a diagram showing a conventional vibration damping device for a torsional damper. FIG. 5 is a diagram showing a conventional vibration damping device for a torsional damper. FIG. 6 is a diagram showing hysteresis torque characteristics in the conventional example. [Description of Signs] 2 Hub plate 2b Circumferential slot 4 Side plate 5 Side plate 6 Torsion spring 7 Retaining plate 8 Retaining plate 9 Friction block 9a Contact parts 9b, 9c Friction force generating surface 10 Disc spring 19 Friction Block 21, 31 Low rigidity body

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Atsuhiro Mori 2 Takara-cho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan Motor Co., Ltd. (72) Inventor Taku Murasugi 2 Takara-cho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan Motor (56) References JP-A-6-129490 (JP, A) JP-A-2-105613 (JP, U) JP-A-63-150135 (JP, U) (58) Fields investigated (Int. ⁷ , DB name) F16F 15/121-15/139

Claims (1)

(57) [Claim 1] A hub plate connected to one of two rotating bodies to be drive-coupled to each other, and coaxially adjacent to the hub plate and connected to the other rotating body. Side plate, a torsion spring circumferentially arranged to transmit power between the hub plate and the side plate, and pressed against one of the hub plate and the side plate in frictional contact with the other, and a circumferential direction against the other. A friction block that abuts and engages after relative movement within a limited range, wherein the friction block is axially aligned with the hub play.
Frictional force that comes into frictional contact with one of the
Both sides including the raw surface are made friction materials and the hub plate and
And abutment against the other side plate
A low-rigid body whose intermediate portion is a member having lower rigidity than the friction material
And then, characterized in that the vibration damping device of the torsional damper.