JP2021032357A - Torsional damper - Google Patents

Abstract

To provide a torsional damper of high durability, reliability and economic efficiency, capable of absorbing and damping vibration generated in transmitting torque for a long period by suppressing change of a compression ratio of elastic members while securing rigidity of inertia mass members even when a plate thickness of the inertia mass member is reduced.SOLUTION: A torsional damper 1 includes: a hub plate 2; a pair of annular inertia mass members 3A and 3B; a pair of annular elastic members 4A and 4B; an outer bent portion 3a and an inner bent portion 3b obtained by axially bending outer peripheral portions of both of the pair of annular inertia mass members 3A and 3B; a fitting portion 5 for compressing and holding the pair of elastic members 4A and 4B between both surfaces of the hub plate 2 and the inertia mass members 3A and 3B opposed thereto by axially fitting the outer bent portion 3a and the inner bent portion 3b to each other and restraining the same; and a boss portion 6 obtained by bending at least one of inner peripheral portions 7a and 7b of the pair of inertia mass members 3A and 3B toward an axial direction.SELECTED DRAWING: Figure 2

Description

The present invention relates to a torsional damper, and more particularly to a torsional damper used for an internal combustion engine of an automobile, a truck, a bus, a construction machine, an industrial machine, or the like.

Patent Document 1 discloses a torsional rubber damper in which first and second elastic members are compressed and sandwiched between a hub and first and second inertial mass members, respectively. In this torsional rubber damper, the first and second inertial mass members are fixed to each other by fitting or the like.

Japanese Unexamined Patent Publication No. 2016-33411

The compressibility of the pair of elastic members consisting of the first and second members is determined by their thickness and the distance from the hub to the pair of inertial mass members consisting of the first and second members. When the compression reaction force of the pair of elastic members is greater than or equal to the bonding force between the pair of inertial mass members, the pair of inertial mass members are separated from each other in the direction in which the compression of the pair of elastic members is released, that is, the pair of inertial mass members. The mass members move so as to open each other in the axial direction, and the compression ratio of the pair of elastic members decreases.

Recently, there is a demand for cost reduction by reducing the weight of torsional dampers and reducing the materials used. Even if the compression reaction force of the pair of elastic members does not exceed the joining force of the pair of inertial mass members, if the thickness of the pair of inertial mass members is made thinner than before, the rigidity of the inertial mass members will increase. descend. Therefore, the inner peripheral portion of the inertial mass member may be deformed in the direction of bending outward in the axial direction due to the compressive reaction force of the elastic member. Such deformation of the inertial mass member also reduces the compressibility of the elastic member.

Therefore, even when the thickness of the inertial mass member is reduced, the deformation of the inner peripheral portion of the inertial mass member is suppressed, the rigidity of the inertial mass member is ensured, and the change in the compression ratio of the elastic member is suppressed. Durable, reliable, and economical inertia that can absorb and dampen various vibrations (twisting vibrations and vertical vibrations) generated when torque is transmitted from the rotating shaft to the member to be transmitted for a long period of time. Dampers are required.

The present invention has been made in view of such a problem, and an object of the present invention is to provide an elastic member while ensuring the rigidity of the inertial mass member even when the thickness of the inertial mass member is reduced. It is an object of the present invention to provide a highly durable, reliable and economical torsional damper capable of suppressing a change in compression ratio and absorbing and attenuating vibration generated during torque transmission for a long period of time.

In order to achieve the above object, the torsional damper of the present invention has a hub plate to which the rotation shafts can be concentrically attached and a pair of rings arranged on the outer peripheral portions of both sides extending in the radial direction of the hub plate. An inertial mass member to be formed, a pair of annular elastic members arranged between both sides of the hub plate and a pair of inertial mass members, and an outer peripheral portion of both of the pair of inertial mass members in the axial direction of the rotation axis. Inertia of a pair of elastic members facing both sides of the hub plate by fitting and restraining the bent outer and inner bent portions and the outer bent portion and the inner bent portion in the axial direction. It includes a joint portion that is compressed and sandwiched between the mass members, and a boss portion in which at least one of the inner peripheral portions of the pair of inertial mass members is bent in the axial direction.

According to the torsional damper of the present invention, even when the thickness of the inertial mass member is reduced, the change in the compression ratio of the elastic member is suppressed while ensuring the rigidity of the inertial mass member, and the torque is transmitted. It is possible to provide a highly durable, reliable and economical torsional damper capable of absorbing and attenuating generated vibration for a long period of time.

It is a top view of the torsional damper which concerns on 1st Embodiment of this invention. It is a vertical sectional view of the torsional damper of FIG. It is the enlarged sectional view of the fitting part of the conventional torsional damper. It is an enlarged cross-sectional view of the fitting part of the torsional damper of FIG. It is an enlarged cross-sectional view of the fitting part of the torsional damper which concerns on the modification of FIG. It is an enlarged cross-sectional view of the fitting part of the torsional damper which concerns on 2nd Embodiment of this invention.

Hereinafter, the torsional damper according to each embodiment of the present invention will be described with reference to the drawings.
<First Embodiment>
FIG. 1 shows a plan view of a torsional damper according to a first embodiment of the present invention. FIG. 2 shows a vertical cross-sectional view of the torsional damper of FIG. The torsional damper (hereinafter, may be abbreviated as a damper) 1 includes a hub plate 2, an inertial mass member 3, and an elastic member 4.

The hub plate 2 is made of metal and is formed in a disk shape by casting, forging, sheet metal, or the like. At the center of the hub plate 2 in the radial direction, a shaft hole 2a is formed in which the center of rotation coincides with a rotation shaft (not shown) such as the crankshaft of an engine, that is, the rotation shafts can be attached concentrically. A plurality of bolt holes 2b are formed around the shaft holes 2a, and bolts (not shown) can be inserted through these bolt holes 2b to bolt and attach a boss (not shown) to the hub plate 2. As a result, the rotating shaft is rotatably attached to the hub plate 2 and the damper 1 via the boss so as to coincide with the center of rotation.

In some cases, the rotating shaft is attached to the center of rotation of the hub plate 2 with a single bolt. Further, when the end portion of the rotating shaft is formed in a flange shape, the rotating shaft can be directly bolted to the hub plate 2 without a boss. Further, thereafter, the axial direction of the rotating shaft, that is, the penetrating direction of the rotating shaft in the shaft hole 2a of the hub plate 2 is defined as the "axial direction", and the radial direction perpendicular to the rotating shaft, that is, the direction in which both sides of the hub plate 2 extend. Is the "radial direction", and the positive and negative rotation directions of the rotation axis, that is, the circumferential direction of the hub plate 2 or the inertial mass member 3 is the "circumferential direction".

The inertial mass member 3 is made of metal and is formed in an annular shape by casting, casting, sheet metal, etc., and is composed of a pair of inertial mass members 3A and 3B (hereinafter, may be collectively referred to as inertial mass members 3). .. The pair of inertial mass members 3A and 3B are arranged on the outer peripheral portions of both sides extending in the radial direction of the hub plate 2, and are swingable at least in the circumferential direction with respect to the rotation axis, preferably further on the rotation axis. On the other hand, it can swing in the radial direction (including the vertical direction as seen in FIGS. 1 and 2).

The elastic member 4 is a rubber ring having a function of so-called damper rubber, and is formed of a rubber material such as ethylene propylene rubber (EPDM) or a resin elastomer, and forms a pair of annular elastic members 4A and 4B (hereinafter referred to as hereafter). It is composed of an elastic member 4). The pair of elastic members 4A and 4B are arranged between both sides of the hub plate 2 and the pair of inertial mass members 3A and 3B, respectively.

A first outer bent portion 3a and a first inner bent portion 3b are formed by bending both outer peripheral portions of the pair of inertial mass members 3A and 3B in the axial direction, respectively. A fitting portion (joint portion) 5 is formed by fitting and restraining the first outer bent portion 3a and the first inner bent portion 3b in the axial direction, and by forming the fitting portion 5. A pair of elastic members 4A and 4B are compressed and sandwiched between both surfaces of the hub plate 2 and the inertial mass members 3A and 3B facing each other.

The fitting portion 5 is a portion forming an annular shape in the circumferential direction of the damper 1. By forming the fitting portion 5, the pair of elastic members 4A and 4B are compressed, and the hub plate 2 and the pair of inertial mass members 3A and 3B are elastically connected. If the first outer bent portion 3a and the first inner bent portion 3b are constrained to each other in the axial direction, a joint portion using means other than fitting is formed instead of the fitting portion 5. Is also good.

The damper 1 configured in this way elastically connects the hub plate 2 mounted on the rotating shaft and the inertial mass member 3 with the elastic member 4. Therefore, due to the viscoelasticity of the elastic member 4, the pair of inertial mass members 3A and 3B swing in the circumferential direction with respect to the rotation axis, and further swing in the radial direction with respect to the rotation axis. As a result, various fluctuations (twisting vibration and vertical vibration) that occur when torque is transmitted to the member to be transmitted (not shown) are absorbed and damped by the damper 1.

A fixing liquid is interposed between the pair of elastic members 4A and 4B and the hub plate 2 and the pair of inertial mass members 3A and 3B, respectively. The fixing liquid causes the pair of molded elastic members 4A and 4B to be post-bonded to the hub plate 2 and the pair of inertial mass members 3A and 3B. More specifically, a post-bonding method is used in which a pair of elastic members 4A and 4B can be compressed and fixed to a hub plate 2 and a pair of inertial mass members 3A and 3B in a state of being in contact with each other. A known adhesive or vulcanized adhesive can be used as the fixing liquid. A silane coupling agent is preferable as the fixing liquid that can be applied to the post-bond method and is used for anti-vibration rubber such as natural rubber, NBR, and EPDM.

The damper 1 configured in this way elastically connects the hub plate 2 mounted on the rotating shaft and the inertial mass member 3 with the elastic member 4. Therefore, the viscoelasticity of the elastic member 4 absorbs and attenuates various vibrations (twisting vibration and vertical vibration) generated when torque is transmitted from the rotating shaft to a member to be transmitted (not shown).

Here, the damper 1 of the present embodiment includes a boss portion 6 in which the inner peripheral portions of both of the pair of inertial mass members 3A and 3B are bent in the axial direction.
FIG. 3 shows an enlarged cross-sectional view of the fitting portion 5 of the conventional damper 1. In the conventional damper 1, the boss portion 6 is not formed. Therefore, even when the compression reaction force of the pair of elastic members 4A and 4B does not exceed the fitting force of the pair of inertial mass members 3A and 3B, the plate thickness of the pair of inertial mass members 3A and 3B is thinner than before. If this is the case, the rigidity of the inertial mass member 3 will decrease.

Therefore, as shown by the broken line in FIG. 3, the inner peripheral portions 7a and 7b of the pair of inertial mass members 3A and 3B are deformed in the axial direction indicated by the arrow due to the compressive reaction force of the elastic member 4. I have something to do. Such deformation of the inertial mass member 3 lowers the compressibility of the elastic member 4, lowers the functions of vibration absorption and vibration damping by the elastic member 4, and deteriorates the performance of the damper 1.

FIG. 4 shows an enlarged cross-sectional view of the fitting portion 5 of the damper 1 of FIG. The boss portion 6 of the present embodiment has a second inner bent portion (inner bent portion) 8a in which both inner peripheral portions 7a and 7b of the pair of inertial mass members 3A and 3B are bent toward the hub plate 2. It is formed from 8b. The individual second inner bent portions 8a and 8b are formed by bending the inner peripheral portions 7a and 7b at substantially 90 degrees so as to be along the axial direction toward the hub plate 2, respectively, and further, the inner peripheral portions 7a. , 7b is formed over the entire circumference.

Further, the second inner bent portions 8a and 8b are formed so as to have a first gap G1 between the pair of elastic members 4A and 4B in the radial direction, respectively. Therefore, during the operation of the damper 1, the second inner bent portions 8a and 8b do not come into contact with the elastic members 4A and 4B, respectively, and the boss portion 6 functions as vibration absorption and vibration damping by the elastic members 4A and 4B. Is not hindered.

Further, the second inner bent portions 8a and 8b are formed so as to have a second gap G2 between them and the hub plate 2 in the axial direction, respectively. Therefore, during the operation of the damper 1, the second inner bent portions 8a and 8b do not come into contact with the hub plate 2, and the boss portion 6 rotates the hub plate 2, and the elastic member 4 absorbs and damps the vibration. Function is not impaired.

As described above, according to the damper 1 of the present embodiment, the thickness of the pair of inertial mass members 3A and 3B is increased by forming the boss portions 6 on the inner peripheral portions 7a and 7b of the inertial mass members 3A and 3B. Even when the thickness is made thinner than before, the rigidity of the inertial mass member 3 can be ensured. As a result, it is possible to prevent the inner peripheral portions 7a and 7b of the inertial mass member 3 from being warped and deformed due to the compressive reaction force of the elastic member 4.

Therefore, the compressibility of the pair of elastic members 4A and 4B can be maintained in the state at the time of manufacturing the damper 1, and the transmitted member is transmitted from the rotating shaft while reducing the weight of the damper 1 and the cost by reducing the materials used. The vibration generated when torque is transmitted to the damper can be absorbed and damped for a long period of time, and the durability, reliability, and economy of the damper 1 can be improved.

FIG. 5 is an enlarged cross-sectional view of the fitting portion 5 of the damper 1 according to the modified example of FIG. If the second inner bent portions 8a and 8b are formed by bending the inner peripheral portions 7a and 7b toward the hub plate 2, respectively, the rigidity of at least the inertial mass member 3 can be ensured. Therefore, the bending angle of the inner peripheral portions 7a and 7b is not limited to 90 degrees, and may be less than 90 degrees as shown in FIG.

Further, in both the forms of FIGS. 4 and 5, since the boss portion 6 is formed by the second inner bent portions 8a and 8b, the width of the damper 1 in the axial direction does not increase, so that the damper 1 It also has the advantage of contributing to the promotion of compactness. Further, when the second inner bent portions 8a and 8b are formed on the pair of inertial mass members 3A and 3B, the processing directions related to the bending are the same as those of the first outer bent portion 3a and the first inner bent portion 3b, respectively. It becomes the direction.

Therefore, the forming process of the boss portion 6 is easy. Further, since the end faces of the inner peripheral portions 7a and 7b, that is, the end faces of the second inner bent portions 8a and 8b are directed to the side of the hub plate 2, that is, inward in the axial direction, the presence or absence of burrs on the end faces is strictly controlled. No need. Therefore, in the case of the present embodiment, it is possible to improve the productivity of the damper 1 when forming the boss portion 6.

<Second Embodiment>
FIG. 6 shows an enlarged cross-sectional view of the fitting portion 5 of the damper 1 according to the second embodiment of the present invention. In the following description, the same configuration as that of the first embodiment will be omitted by adding the same reference numerals to the drawings, and the configuration different from that of the first embodiment will be mainly described.

The damper 1 of the present embodiment has a boss portion 6 as in the case of the first embodiment. The boss portion 6 of the present embodiment is formed as a second outer bent portion (outer bent portion) 9a, 9b in which the inner peripheral portions 7a and 7b are bent toward the opposite sides of the hub plate 2, respectively. The individual second outer bent portions 9a and 9b are bent at substantially 90 degrees so that the inner peripheral portions 7a and 7b are opposite to the hub plate 2, that is, along the axial direction toward the outer side in the axial direction. It is formed, and is further formed over the entire circumference of the inner peripheral portions 7a and 7b.

Even with such a boss portion 6, it is possible to secure the rigidity of the inertial mass member 3 when the plate thickness of the pair of inertial mass members 3A and 3B is made thinner than before. Further, in the case of this embodiment, the production control for securing the first and second gaps G1 and G2 described above is not necessary, and for that reason, the productivity of the damper 1 when forming the boss portion 6 is improved. Can be planned.

Although the description of the embodiment of the present invention is completed above, the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, the boss portion 6 is not limited to the first and second embodiments, and may be formed by bending only one of the inner peripheral portions 7a and 7b in the axial direction. In this case, depending on the specifications of the damper 1, for example, it is suitable when the plate thickness of only one of the pair of inertial mass members 3A and 3B is thinner than the conventional one.

Further, the boss portion 6 may be composed of one of the second inner bent portions 8a and 8b and one of the second outer bent portions 9a and 9b. Further, the boss portion 6 may be formed over only a part of the inner peripheral portions 7a and 7b in the circumferential direction. Even in these cases, when the plate thickness of the inertial mass member 3 is made thinner than before, the rigidity of the inertial mass member 3 can be improved rather than the boss portion 6 not being formed at all.

1 Tortional damper
2 Hub plate
2a shaft hole
2b Bolt holes 3, 3A, 3B Inertial mass members
3a 1st outer bend
3b 1st inner bent part 4, 4A, 4B Elastic member
5 Fitting part
6 Boss 7a, 7b Inner peripheral part of inertial mass member 8a, 8b Second inner bent part 9a, 9b Second outer bent part
G1 first gap
G2 second gap

Claims (6)

A hub plate to which the rotating shaft can be attached concentrically,
A pair of annular inertial mass members arranged on the outer peripheral portions of both sides extending in the radial direction of the hub plate, and
A pair of annular elastic members arranged between both sides of the hub plate and the pair of inertial mass members, respectively.
By constraining the outer peripheral portions of both of the pair of inertial mass members to each other in the axial direction of the rotation axis, the pair of elastic members are compressed between both sides of the hub plate and the inertial mass members facing each other. A torsional damper including a joint portion to be sandwiched and a boss portion in which at least one of the inner peripheral portions of the pair of inertial mass members is bent in the axial direction. The torsional damper according to claim 1, wherein the boss portion includes an inner bent portion in which the inner peripheral portion is bent toward the hub plate. The torsional damper according to claim 2, wherein the inner bent portion has a first gap between the inner bent portion and the elastic member in the radial direction. The torsional damper according to claim 3, wherein the inner bent portion has a second gap between the inner bent portion and the hub plate in the axial direction. The torsional damper according to any one of claims 2 to 4, wherein the boss portion includes an outer bent portion in which the inner peripheral portion is bent toward the side opposite to the hub plate. The torsional damper according to any one of claims 1 to 5, wherein the boss portion is formed over the entire circumference of the inner peripheral portion.

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