JPH07243481A - Vibration damping device for torsional damper - Google Patents

Abstract

PURPOSE:To reduce the size of a low rigidity body by a method wherein a load during collision of a friction block is absorbed by the resilient force of a low rigidity body and a damping force during deformation of a resin layer arranged in series to the low rigidity body. CONSTITUTION:A resin layer 20 and a low rigidity body 11 are arranged peripherally in series to the two ends of a peripheral oblong hole 2b for a friction block 9 formed in a hub plate 2 coupled to a torque converter. The friction block 9 is brought into contact with the end face of the peripheral oblong 2b through a low rigidity body 11 arranged in series to the resin layer 20 coupled with the end face of the peripheral oblong hole 2b of the hub plate 2 when the friction block is relatively displaced from the hub plate 2 by a peripheral direction limit range alpha togetherwith a side plate 4. Thereby, a load during collision of the friction block 9 is absorbed by the resilient force of the low rigidity body 11 and a damping force during the resin layer 20 is deformed along the end face of the peripheral oblong hole 2b. Thus, compared with a case wherein a load during collision is absorbed only by the low rigidity body, the size of the low rigidity body 11 itself is reduced.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping device for a torsional damper, which is used by being inserted into a transmission system of a prime mover such as an engine which is subject to torque fluctuations for the purpose of cushioning.

[0002]

2. Description of the Related Art As a conventional example of such a torsional damper, for example, the Japanese Patent Application No. 5 (1994) filed previously by the applicant of the present application is given.
-222358 specification. This torsional damper is conceptually as shown in FIGS. 7 and 8, and one of the two rotating bodies (for example, the engine output shaft and the torque converter) (for example, the torque converter) to be drivingly coupled to each other (for example, the torque converter) is provided with the bolt 1. Hub plate 2 and side plates 4, 5 arranged coaxially adjacent to the hub plate and connected to the other rotating body (for example, an engine output shaft) with bolts 3, and the hub plate 2 and the side plate 4 , 5, and a torsion spring 6 arranged in the circumferential direction so as to transmit power between them.

The torsion spring 6 is housed in a rectangular window 2a formed by penetrating the hub plate 2 in the axial direction so as to extend in the circumferential direction, and the coil portion of the torsion spring 6 protruding from the rectangular window. The side plate 4,
5 in the rectangular windows 4a, 5a. As a result, both ends of the torsion spring 6 are seated on both ends of the rectangular windows 2a, 4a, 5a in the circumferential direction, and the hub plate 2 and the side plates 4, 5 are elastically supported in the relative rotation neutral position, and the torsion springs are also combined. 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,
It is transmitted to the torque converter through the hub plate 2 and the bolt 1 in order, and during the transmission of the power, the torque fluctuation can be absorbed by the elastic deformation of the torsion spring 6 and a predetermined cushioning function can be fulfilled.

When rotational vibration occurs due to resonance when the engine is started, this causes a large relative rotation between the hub plate 2 and the side plates 4 and 5. Such rotational vibration is caused by the following mechanism. Attenuate.

That is, the conventional vibration damping device for the torsional damper includes the retaining plates 7 and 8 which are rotatably engaged with the inner surfaces of the side plates 4 and 5 and face each other, and the retaining plates 7 and 8 are disposed between the retaining plates 7 and 8. The friction block 9 is interposed. Then, the disc spring 10 is contracted between the side plate 5 and the retaining plate 8,
The retaining plate 8 is biased towards the retaining plate 7, which causes the friction block 9 to frictionally contact the retaining plates 7, 8 and thus the side plates 4, 5.

The friction block 9 is inserted into a circumferential elongated hole 2b formed by penetrating the hub plate 2 in the axial direction,
The elongated hole 2b restrains the friction block 9 in the radial direction, but has a shape capable of moving the friction block 9 relative to the hub plate 2 in both circumferential directions by a gap α. Further, low-rigidity bodies 11 are provided at both ends of the circumferentially elongated hole 2b for the friction block 9 formed in the hub plate 2 connected to the torque converter with the bolt 1.

The vibration damping device operates as follows. That is, under a small torsion angle of the torsion damper less than the clearance 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 and 8. Together with these, that is, with the side plates 4 and 5, they are displaced relative to the hub plate 2. Therefore, the friction block 9 does not have any influence on the buffer function of the torsional damper and can reliably absorb the torque fluctuation.

When rotational vibration occurs due to resonance when the engine is started, this causes a large relative rotation of α or more (a large torsional displacement of the torsional damper) between the hub plate 2 and the side plates 4 and 5. As a result, the friction block 9 abuts against the low-rigidity body 11 provided at the end of the circumferential elongated 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 imparts 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 torsional damper described above. Due to this hysteresis torque, the above-mentioned rotational vibration is attenuated and the vibration can be suppressed. At that time, when the friction block 9 is displaced together with the side plate 4 by the circumferential direction limited range α with respect to the hub plate 2, the friction block 9 does not directly collide with the hub plate 2 but contact with the low rigidity body 11. Therefore, it is possible to solve the problem that a loud metal sound is generated due to the collision, or vibration is generated due to the repulsion.

[0010]

However, in the vibration damping device for the conventional torsional damper described above, when the torsional damper undergoes a torsional displacement of α, the friction block 9 causes the end portion of the circumferential elongated hole 2b to move. And a large hysteresis torque is suddenly generated as shown in FIG.
In order to solve the problem that a large metal sound is generated at the time of collision or vibration is generated due to repulsion, low rigidity bodies 11 are provided at both ends of the circumferential elongated hole 2b for the friction block 9, so that low rigidity is achieved. The body 11 needs to be able to absorb the load at the time of a collision only by its elastic force, and is inevitably sized to a certain extent or more, and it is difficult to lay out a low-rigid body in a limited space. become.

According to the present invention, in addition to absorbing the load at the time of collision by the elastic force of the low rigidity body, the friction block and
It is possible to solve the above problems by downsizing the low-rigidity body itself so that it is also absorbed by the damping force at the time of deformation of the resin layer provided in series with the low-rigidity body between both ends of the circumferential long hole. To aim.

[0012]

To this end, the invention provides, as claimed in claim 1, a hub plate which is connected to one of the two rotating bodies which are to be drivingly connected to each other, and a coaxial plate to the hub plate. Side plates that are arranged next to each other and connected to the other rotating body, a torsion spring that is circumferentially arranged to transmit power between these hub plates and side plates, and friction on one of the hub plates and side plates A torsional damper having a friction block that is pressed to come into contact with the other and abuts and engages with the other after relative movement within the circumferential limit range, and the friction block and the friction block are within the circumferential limit range. Having a low-rigidity body interposed in an abutting portion with a hub plate or a side plate that abuts and engages after relative movement in the In the vibration damping device of the damper, between the friction block and abutment portion and is characterized in that a resin layer in the low rigid member and circumferentially in series.

[0013]

In the structure of claim 1 of the present invention, torque fluctuation occurs while power is transmitted between the rotating body connected to the hub plate and the rotating body connected to the side plate through the torsion spring. It is absorbed by the elastic deformation of the torsion spring and fulfills a predetermined cushioning function.

When the rotational vibration of the torsional damper occurs due to the resonance, the friction block causes a large relative rotation between the hub plate and the side plate, so that the friction block is initially frictionally contacted with the hub plate or the side plate. Then, it moves in the circumferential direction relative to the side plate or the hub plate, but after the relative movement within the circumferential direction limited range, it abuts and engages with the latter side plate or hub plate. Therefore, after the relative movement within the circumferential direction limited range, a frictional resistance (hysteresis torque) is generated between the friction block and the former hub plate or side plate, which can damp the rotational vibration. it can.

By the way, since the friction block and the side plate or the hub plate, which abuts and engages after the relative movement within the circumferential direction restricted range, engages the low rigidity body, the engagement is concerned. Therefore, it is possible to solve the problem that a large metal sound is generated due to the engagement and the problem that vibration is generated due to repulsion. Further, at that time, since the resin layer is arranged in series in the circumferential direction in series with the low-rigidity body between the friction block and the contact portion, the load at the time of collision of the friction block is absorbed by the elastic force of the low-rigidity body. In addition to this, the low-rigidity body and the resin layer provided in series between both ends of the circumferential long hole are also absorbed by the damping force when the resin layer is deformed, so that the low-rigidity body itself can be downsized. Therefore, layout of the low-rigidity body in the limited space does not become difficult.

According to the second aspect of the present invention, since the end of the friction block on the abutting side has a predetermined convex curvature, the amount of deformation of the central portion becomes maximum when the friction block is pressed. As described above, the deformation amount and the damping force due to the deformation when the low-rigidity body is compressed and deformed and the resin layer is deformed along the end face of the abutting portion of the hub plate are larger than those in claim 1, and Since the load at the time of collision to be absorbed is reduced, the low-rigidity body itself can be made smaller than in the first aspect.

Further, in the structure of claim 3, since the end face of the abutting portion of the hub plate is provided with a predetermined gradient, when the low-rigidity body is compressed and deformed by the collision with the friction block, the resin layer is formed. The component force of the applied load in the direction along the end face of the abutting portion becomes large, and the amount of deformation and the damping force due to the deformation when the resin layer deforms along the end face of the abutting portion become larger than those in claim 1. Since the load at the time of a collision that should be absorbed by the low-rigidity body is reduced, the low-rigidity body itself can be made smaller than in claim 1.

In the structure of claim 4, since the low-rigidity body is divided in the radial direction and the resin layer is sandwiched between the frictional block and the low-rigidity body in the first or second aspect. At the time of collision with, the resin layer is deformed along the opposing end faces of the two low-rigidity bodies, so that the same function and effect as in claim 1 can be obtained, and the resin layer is sandwiched between the low-rigidity bodies. Thereby, the assembling property and durability of the resin layer are improved as compared with the first embodiment.

According to the fifth aspect of the invention, since the surfaces of the low-rigidity body sandwiching the resin layer are provided with predetermined gradients, the damping force when the resin layer 20 is deformed is provided. However, the structure of the third embodiment or the fourth embodiment is larger than that when it is used alone, and the low-rigidity body itself can be further downsized.

The low-rigidity member in each of the above claims is
As described in claim 6, it is preferable that the shock absorbing material is made of a para-aromatic polyamide fiber felt weave structure.

[0021]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a diagram showing the configuration of a first embodiment of a vibration damping device for a torsional damper according to the present invention. In the figure, the same parts as those in FIGS. 7 and 8 described above are designated by the same reference numerals. The first embodiment has the same configuration as that of FIG. 1 of the above-mentioned Japanese Patent Application No. 5-222358, except for the following modifications.

This embodiment is an improvement proposal for the vibration damping device of the torsional damper shown in FIGS. 7 and 8.
That is, in FIG. 7 and FIG. 8, of the engine output shaft and the torque converter (both not shown) to be drivingly connected to each other via the torsional damper, the hub plate 2 connected to the torque converter by the bolt 1 is connected. The low-rigidity bodies 11 were provided at both ends of the formed circumferential elongated hole 2b for the friction block 9, but in the present embodiment, the friction block 9 and the circumferential direction limited range of the friction block 9 are further provided. Between the friction block 9 and the end face (abutting portion) of the circumferentially elongated hole 2b of the hub plate 2 that abuts and engages with the friction block 9 in series with the low-rigidity body 11 in the circumferential direction. It is arranged. In the circumferential direction, the resin layer 20 is located on the center side,
The low-rigidity body 11 may be arranged on the end face side of the circumferential elongated hole 2b.

In the construction of the present embodiment, the friction block 9 together with the side plate 4 is limited to the hub plate 2 by the circumferential limit range α in the vibration damping action of the torsional damper described with reference to FIGS. 7 and 8. When relatively displaced, do not directly collide with the hub plate 2, but contact through the resin layer 20 coupled to the end face of the circumferential elongated hole 2b of the hub plate 2 and the low-rigidity body 11 arranged in series therewith. Therefore, the problem that a loud metallic noise is generated due to the engagement or the vibration is generated due to the repulsion is solved. At that time, the load of the friction block 9 at the time of collision is due to the elastic force of the low-rigidity body 11 and the resin layer 20 in the circumferential elongated hole 2b.
Since it is absorbed by the damping force when it is deformed along the end face of the vehicle, compared to the case of absorbing the load at the time of collision with only a low-rigid body as shown in FIG. 1 of Japanese Patent Application No. 5-222358.
The low-rigidity body 11 itself can be downsized, and the layout of the low-rigidity body does not become difficult even in a limited space.

FIGS. 2 (a) and 2 (b) are views showing the construction of the essential parts of a vibration damping device for torsional dampers according to a second embodiment of the present invention. In this embodiment, the friction block 9 having the linear shape in the first embodiment is provided with the contact side end 9a shown in FIG.
A predetermined curvature in the convex direction is given as shown in (a), and the other portions are configured in the same manner as in the first embodiment (FIG. 1). Needless to say, the resin layer 20 and the low-rigidity body 11 may be interchanged in the circumferential direction, as in the first embodiment.

In the structure of this embodiment, since the low-rigidity body 11 is pressed by the friction block 9 and is compressed and deformed so that the deformation amount of the central portion becomes maximum as shown in FIG. 2B, The amount of deformation when the resin layer 20 is deformed along the end face of the circumferential elongated hole 2b and the damping force due to the deformation are larger than in the first embodiment. Therefore, the low-rigidity body 11
Since the load at the time of collision to be absorbed is reduced and the durability is improved, the low-rigidity body 11 itself can be made smaller than in the first embodiment.

FIGS. 3 (a) and 3 (b) are views showing the construction of the essential parts of a vibration damping device for torsional dampers according to a third embodiment of the present invention. In this embodiment, in the first embodiment, the end face 11 of the linearly shaped low-rigidity member 11 that is connected to the resin layer 20 is connected.
3a is a trapezoidal shape of the low-rigidity body 11 given a predetermined gradient as shown in FIG.
The configuration is similar to that of the embodiment (FIG. 1). It should be noted that the shape of the end face of the circumferential elongated hole 2b is changed as shown in FIG. 3A in response to the change of the low-rigidity body, and the resin layer 20 is circumferentially changed in the same manner as in the first embodiment. Needless to say, the low rigidity body 11 may be replaced with the low rigidity body 11.

In the structure of this embodiment, when the low-rigidity body 11 is compressed and deformed by the collision with the friction block 9, the load F1 applied to the resin layer 20 in the circumferential direction as shown in FIG. 3B. The component F2 in the direction along the end face of the elongated hole 2b becomes large, and the amount of deformation when the resin layer 20 is deformed along the end face of the elongated hole 2b in the circumferential direction and the damping force due to the deformation are larger than those in the first embodiment. Also grows. Therefore, since the load at the time of a collision that should be absorbed by the low-rigidity body 11 is reduced and the durability is improved, the low-rigidity body 1 is further improved than in the first embodiment.
It becomes possible to miniaturize 1 itself.

FIGS. 4 (a) and 4 (b) are diagrams showing the construction of the essential parts of a vibration damping device for torsional dampers according to a fourth embodiment of the present invention. In this embodiment, the low-rigidity body, which was one member in the first embodiment, is radially divided into two low-rigidity bodies 30a and 30b, and the resin layer 20 is arranged between them. The other parts are configured similarly to the first embodiment (FIG. 1).

In the structure of this embodiment, when the friction block 9 and the low-rigidity body 30a collide, the resin layer 20
Along the opposing end faces of the low-rigidity bodies 30a and 30b.
Since the deformation occurs as shown in (b), the load at the time of collision is absorbed by the elastic force of the low-rigidity body 11 and the damping force at the time of deformation of the resin layer 20, and the same operation as that of the first embodiment. The effect is obtained. In addition, as described above, the low rigidity body 30
Since the resin layer is sandwiched between a and 30b, the resin layer 2
Assembling property and durability of 0 are improved as compared with the first embodiment.

In the above embodiment, the example in which the low-rigidity body is divided into two is shown, but it may be divided into three or more and a resin layer may be provided between the divided surfaces. In that case, as in the case of the first embodiment, it is provided between the end faces of the low-rigidity member (low-rigidity member 30b) and the circumferential elongated hole 2b, and the resin layer is also provided on the end face of the lowest-rigidity member at the center side. However, in that case, the damping effect of the resin layer is further increased.

FIGS. 5 (a) and 5 (b) are views showing the structure of the essential parts of a vibration damping device for torsional dampers according to a fifth embodiment of the present invention. The present embodiment is a combination of the configurations of the above-described second and fourth embodiments, and the other parts are configured in the same manner as the second and fourth embodiments.

In the structure of the present embodiment, the damping force when the resin layer 20 is deformed is larger than that when the structure of the second embodiment or the fourth embodiment is used alone.
The low-rigidity body itself can be further downsized. In addition,
Needless to say, the number of divisions of the low-rigidity body and the arrangement of the low-rigidity body and the resin layer may be changed as in the third embodiment.

FIGS. 6 (a) and 6 (b) are views showing the construction of the essential parts of a sixth embodiment of the vibration damping device for torsional dampers of the present invention. The present embodiment is a combination of the ideas of the above-described third and fourth embodiments. That is,
The low-rigidity body is divided into two in the radial direction to divide the low-rigidity body 40a, 4 into
0b and the resin layer 20 is disposed between them, the concept of the fourth embodiment is adopted, and the low rigidity bodies 40a, 4a,
The idea of the third embodiment is adopted in that the surfaces having the resin layer 20 of 0b (the mating surfaces) are each provided with a predetermined gradient. The other parts are configured in the same manner as in the third and fourth embodiments.

In the structure of this embodiment, the damping force when the resin layer 20 is deformed is larger than that when the structure of the third embodiment or the fourth embodiment is used alone.
The low-rigidity body itself can be further downsized. In addition,
Needless to say, the number of divisions of the low-rigidity body and the arrangement of the low-rigidity body and the resin layer may be changed as in the third embodiment.

In each of the above-mentioned embodiments, the above-mentioned low rigidity body (low rigidity body 11, 30a, 30b, 40a, 40) is used.
It is preferable that b) is composed of, for example, a shock absorbing material made of a para-aromatic polyamide fiber felt weave structure. In this case, the addition of the low-rigidity body does not cause adverse effects such as deterioration of the thermal stability of the vibration damping device and eventually the torsional damper, reduction of strength, and reduction of wear resistance. .

[0036]

As described above, the vibration damping device for a torsional damper according to the present invention has a predetermined damping function for torque fluctuation, a damping action for rotational vibration of the torsional damper due to resonance, and a friction. It is of course possible to solve the problem that a large metallic noise is generated at the time of contact between the block and the side plate or the hub plate, or vibration is generated due to repulsion, and of course, a resin layer is provided between the friction block and the contact portion. By arranging in series with the low-rigidity body, the load at the time of collision of the friction block is reduced by the elastic force of the low-rigidity body and the resin layer provided in series in the circumferential direction between both ends of the friction block and the circumferentially elongated hole. Since it is absorbed by the damping force at the time of deformation, the low-rigidity body itself can be downsized. Therefore, layout of the low-rigidity body in the limited space does not become difficult.

According to the second aspect of the present invention, since the end of the friction block on the abutting side has a predetermined curvature in the convex direction, the deformation amount of the central portion becomes maximum when the friction block is pressed. As described above, the deformation amount and the damping force due to the deformation when the low-rigidity body is compressed and deformed and the resin layer is deformed along the end face of the abutting portion of the hub plate are larger than those in claim 1, and Since the load at the time of collision to be absorbed is reduced, the low-rigidity body itself can be made smaller than in the first aspect.

According to the third aspect of the present invention, since the end face of the abutting portion of the hub plate is provided with a predetermined inclination, when the low-rigidity body is compressed and deformed by the collision with the friction block, the resin layer is formed. The component force of the applied load in the direction along the end face of the abutting portion becomes large, and the amount of deformation and the damping force due to the deformation when the resin layer deforms along the end face of the abutting portion become larger than those in claim 1. Since the load at the time of a collision that should be absorbed by the low-rigidity body is reduced, the low-rigidity body itself can be made smaller than in claim 1.

Further, in the structure of claim 4, since the low-rigidity body is divided in the radial direction and the resin layer is sandwiched between the low-rigidity body in the first or second aspect, the friction block and the low-rigidity body are formed. At the time of collision with, the resin layer is deformed along the end faces of the two low-rigidity bodies facing each other. Therefore, the same function and effect as those of the above-mentioned claim 1 can be obtained, and the resin layer is sandwiched between the low-rigidity bodies. Thereby, the assembling property and durability of the resin layer are improved as compared with the first embodiment.

Further, in the structure of claim 5, a predetermined gradient is applied to each of the surfaces of the low-rigidity body sandwiching the resin layer, so that the damping force when the resin layer 20 is deformed. However, the structure of the third embodiment or the fourth embodiment is larger than that when it is used alone, and the low-rigidity body itself can be further downsized.

The low-rigidity member in each of the above claims is
As described in claim 6, it is preferable that the shock absorbing material is made of a para-aromatic polyamide fiber felt weave structure.

[Brief description of drawings]

FIG. 1 is a diagram showing a configuration of a vibration damping device for a torsional damper according to a first embodiment of the present invention.

2 (a) and 2 (b) are diagrams showing a configuration of a main part of a vibration damping device for a torsional damper according to a second embodiment of the present invention.

3 (a) and 3 (b) are diagrams showing a configuration of a main part of a vibration damping device for a torsional damper according to a third embodiment of the present invention.

4 (a) and 4 (b) are diagrams showing a configuration of a main part of a vibration damping device for a torsional damper according to a fourth embodiment of the present invention.

5 (a) and 5 (b) are views showing a configuration of a main part of a vibration damping device for a torsional damper according to a fifth embodiment of the present invention.

6 (a) and 6 (b) are diagrams showing a configuration of a main part of a vibration damping device for a torsional damper according to a sixth embodiment of the present invention.

FIG. 7 is a diagram showing a vibration damping device for a conventional torsional damper.

FIG. 8 is a diagram showing a vibration damping device for a conventional torsional damper.

FIG. 9 is a diagram showing a hysteresis torque characteristic according to the conventional example.

[Explanation of symbols]

 2 Hub plate 2b Circumferential slot 4 Side plate 5 Side plate 6 Torsion spring 7 Retaining plate 8 Retaining plate 9 Friction block 10 Disc spring 11 Low rigidity body 20 Resin layer

 ─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Atsuhiro Mori 2 Takaracho, Kanagawa-ku, Yokohama-shi, Kanagawa Nissan Motor Co., Ltd.

Claims (6)

[Claims] 1. A hub plate connected to one of two rotating bodies to be drivingly connected to each other, a side plate coaxially adjacent to the hub plate and connected to the other rotating body, and these hub plates and A torsion spring arranged in the circumferential direction to transmit power between the side plates and one of the hub plate and the side plate are pressed so as to make frictional contact with each other, and collide against the other after the relative movement within the circumferential limit range. A torsional damper having a friction block engaging in contact with it, and an abutting portion of the friction block and a hub plate or side plate engaging in engagement with the friction block after relative movement within a circumferential limit range. A vibration damping device for a torsional damper comprising a low-rigidity body interposed between the friction block and the abutting portion. , Characterized in that a resin layer in the low rigid member and circumferentially series, the vibration damping device of the torsional damper. 2. The vibration damping device for a torsion damper according to claim 1, wherein a predetermined curvature in a convex direction is given to an end portion of the friction block on the abutting side. 3. The vibration damping device for a torsion damper according to claim 1, wherein the end face of the abutting portion of the hub plate is provided with a predetermined inclination. 4. The low-rigidity body is divided in the radial direction, and the resin layer is sandwiched between them.
The vibration damping device for a torsional damper according to claim 1. 5. The vibration damping device for a torsion damper according to claim 4, wherein the surfaces of the low-rigidity body sandwiching the resin layer are each provided with a predetermined gradient. 6. The low-rigidity body is made of a shock absorbing material made of a felt woven structure of para-aromatic polyamide fiber, according to claim 1. Vibration damper for torsional damper.