JPH0222501Y2 - - Google Patents

Description

[Detailed Description of the Invention] Industrial Application Field This invention relates to a clutch disk used in clutch devices for automobiles and the like.

Conventional technology Recently, a clutch disk using working fluid as a damper device has been proposed as a means to effectively prevent muffled noise caused by torsional resonance occurring in the drive system on the output shaft side of the engine and vibrations during acceleration and deceleration of the vehicle. (For example, Japanese Patent Publication No. 59-34895). This clutch disk includes a damper device disposed between an input member and an output member that are connected to each other so as to be rotatable relative to each other. a partition plate fixed to the output member so as to separate the two hollow chambers, and a working fluid is sealed in the two hollow chambers, and the partition plate has a partition plate fixed to the output member to separate the two hollow chambers. The structure includes an orifice that provides flow resistance to the displacement flow of the working fluid to be performed.

According to the conventional clutch disk having such a configuration, twisting occurs in the circumferential direction between the input member and the output member, and as a result of this twisting, the hollow chamber on one damper seat side is rapidly compressed. and the sudden pressure rise in one hollow chamber due to the compression,
The orifice provided in the partition plate allows the fluid to be gradually released into the other hollow chamber, thereby effectively attenuating torque fluctuations in the drive system.

Problems to be solved by the invention By the way, the damping force obtained by the orifice provided in the partition plate is obtained by the flow resistance of a working fluid with a certain viscosity, but the viscosity of this working fluid is Varies depending on fluid temperature. Therefore, for example, when the fluid temperature of the working fluid decreases, the viscosity of the working fluid increases, and the damping force increases accordingly, resulting in an excessive amount of damping.

Means for Solving the Problems In order to solve these conventional problems, this invention provides a method for attaching adjacent arms to either the output side arm formed on the output member or the input side arm formed on the input member. It forms a communication path that communicates between the fluid chambers, and acts on excessive pressure in any of the fluid chambers facing this communication path to open this communication path and prevent excessive damping force. The structure is equipped with a damping force adjustment valve to prevent this from occurring.

Function: In this device having such a configuration, relative rotation occurs between the input member and the output member when the fluid temperature of the working fluid sealed in the plurality of fluid chambers is decreased, and the adjacent fluid chambers are rotated relative to each other. When excessive pressure occurs in one of the fluid chambers, in response to this excessive pressure, the damping force adjustment valve formed on either the output side arm formed on the output member or the input side arm formed on the input member is activated. By opening the communication passage and bypassing a portion of the working fluid to be exchanged and flowing between the fluid chambers through the orifice, generation of excessive damping force due to passage only through the orifice is avoided. Acts to prevent.

Embodiments Hereinafter, embodiments of this invention will be described based on the drawings.

FIG. 1a is a partially exploded front view showing one embodiment of the clutch disk according to this invention, and FIG. 1b is a first embodiment of the clutch disk.
It is a - line cross section in figure a.

As shown in FIGS. 1a and 1b, the clutch disk according to this embodiment has a spline coupling portion 1 serving as an output shaft coupling portion on the inner periphery, and a flange portion 2 protruding radially outward on the outer periphery. and an input member 5 which is rotatable relative to the output member 3 and has a cover part 4 that surrounds the outer peripheral side of the flange part 2 and forms a liquid-tight space S therein. Input side arms 6 projecting radially inward at positions equidistant in the circumferential direction of the input member 5, and output side arms 7 protruding radially outward at positions equidistant circumferentially on the flange portion 2. . . . are connected so as to be relatively rotatable by compression springs 9 which are elastic bodies. The inside of the liquid-tight space S is partitioned by these input-side arms 6 and output-side arms 7, and is a fluid chamber 8 whose volume increases or decreases depending on the relative rotation of the input member 5 and the output member 3. . . . is formed, and a working fluid such as silicone oil is sealed inside the fluid chamber 8 . Also, during relative rotation, the volumes of the fluid chambers 8 increase and decrease to form a pair, and in this embodiment, all adjacent fluid chambers 8..., that is, between the inner periphery of the input member 5 and the output side arm. 7..., and between the inner periphery of the input side arm 6... and the outer periphery of the output side arm 7... formed on the output member 3, there is a line between each fluid chamber 8... Orifices 10a, 10b for providing flow resistance to the displacement flow of the working fluid to be
... are formed respectively.

The input member 5 includes a pair of drive plates 5a, 5b disposed opposite to each other on both sides of the flange portion 2, and a pair of drive plates 5a, 5b disposed oppositely on both sides of the flange portion 2.
A back plate 5c is fitted into the inside of the back plate 5c via a rotation stopper 6b.
The pair of drive plates 5a, 5b are integrally connected at their outer peripheries with cushioning plates 11... by cushioning rivets 12.... Said back plate 5
c is formed from an annular portion 5d along the inner circumferential surface of each drive plate 5a, 5b, and three input side arms 6 projecting inward at equidistant positions in the circumferential direction of this annular portion 5d. The input arm 6 has a substantially wedge shape that tapers radially inward from the annular portion 5d side. On the other hand, the output side arms 7 formed on the output member 3 are located between the respective input side arms 6 and have a fan-like shape that expands outward in the radial direction. These input side arm 6... and output side arm 7...
Each of the compression springs 9 disposed in between is formed of two large and small compression springs 9a and 9b arranged concentrically, and both ends of each compression spring 9 are connected to the input side arm 6. . . . and the output side arm 7 . In addition, the output side arm 7...
Two communication passages 13, 13, a first and a second, are formed to communicate between the adjacent fluid chambers 8, 8, and the first and second communication passages 13, 13 are formed.
At a position facing the communication path 13, the first communication path 13 is opened by excessive pressure generated in one of the adjacent fluid chambers 8, 8, and an excessive damping force is generated. The first damping force adjustment valve 14 prevents
is provided at a position facing the second communication passage 13 to prevent the second communication passage 13 from opening due to excessive pressure generated in the other fluid chamber 8 and from generating an excessive damping force. A second damping force adjustment valve 14 is provided. This damping force adjustment valve 14... is used to open and close the communication passage 13,
Check ball 1 slidably inserted into 13
4a, and a spring 14b which urges the check ball 14a with a predetermined spring force in the direction of closing the communicating path 13.
One end of this spring 14b is held by a spring stopper member 14c. Further, between the pair of drive plates 5a, 5b, and between the pair of drive plates 5a, 5b and the hub portion 3a formed on the output member 3, each fluid chamber 8...
In order to prevent the working fluid sealed inside from leaking to the outside, a seal ring 15a and a seal member 15b are interposed, respectively. In FIG. 1b, 16 is a blind plug that closes the working fluid inlet/outlet 17, 18 is an annular friction facing attached to the cushioning plate 11 by facing rivets 19, 2
0 is a hub portion 3a formed on the output member 3 in order to smoothly rotate the output member 3 and the input member 5 relative to each other.
This is a bearing disposed between the drive plates 5a and 5b and the center hole side portion of each drive plate 5a, 5b.

Next, the operation of the clutch disc according to this embodiment having such a configuration will be explained.

First, when the input member 5 rotates in the circumferential direction with respect to the output member 3 due to the drive torque from the engine, the input arm 6 formed on the back plate 5c constituting the input member 5 moves in the same direction. It will rotate to. Therefore, among the two compression springs 9, 9 disposed on both sides of the input side arms 6, one compression spring 9 is compressed by each input side arm 6. Therefore,
The driving torque is transmitted to the output member 3 via one compression spring 9. At this time, the fluctuation torque of the drive torque is absorbed by the spring reaction force of each compression spring 9 on one side. At the same time, the flow resistance of the working fluid passing through each orifice 10a, 10b, . . . causes attenuation. That is, when the input member 5 rapidly rotates in the circumferential direction with respect to the output member 3, the two fluid chambers 8 separated by the output arms 7 formed on the output member 3 , the pressure in one of the fluid chambers 8 in which the one compression spring 9 is disposed increases rapidly, while the pressure in the other fluid chamber 8 in which the other compression spring 9 is disposed rapidly decreases. Therefore, due to these pressure differences, the working fluid in one fluid chamber 8 flows between the outer periphery of the output side arm 7 and the inner periphery of the input member 5, and between the input side arm 6... Each narrow orifice 10a, 10 is formed between the inner circumference of the output member 3 and the outer circumference of the flange portion 2 formed on the output member 3.
b... and flows into the other fluid chamber 8 with a desired flow resistance. Therefore, due to the energy loss of the working fluid that occurs at that time, vibrations in the rotational direction of the input member 5 relative to the output member 3 are attenuated.

In this case, when the fluid temperature of the working fluid sealed in each fluid chamber 8 decreases and the viscosity of the working fluid increases accordingly, this occurs when the working fluid passes through each orifice 10a, 10b. Energy loss increases, and damping force increases accordingly. That is, when the viscosity of the working fluid increases to a predetermined value or more, excessive pressure may be generated within each fluid chamber 8, and an excessive amount of damping may occur.

However, in this embodiment, since the output side arm 7 is provided with the damping force adjustment valve 14, when excessive pressure occurs in one fluid chamber 8, the excessive pressure in this one fluid chamber 8 and this fluid chamber The check ball 14a moves against the spring force of the spring 14b due to the pressure difference between the check ball 14a and the pressure in the other fluid chamber 8, which is lower than the pressure in the other fluid chamber 8, and opens the communication passage 13 in accordance with the pressure difference.
Therefore, the working fluid flowing from one fluid chamber 8 on the side where excessive pressure is generated to the other fluid chamber 8 on the low pressure side passes not only through the orifices 10a and 10b but also through the communication passage 14b. So,
Generation of an excessive damping force due to passing only through the orifices 10a and 10b is prevented, and therefore, generation of an excessive amount of damping can be prevented. In addition, each adjacent fluid chamber 8...
...The check ball 14a is moved a required amount according to the pressure difference between the
3 can be opened, it is possible to maintain substantially constant damping characteristics regardless of changes in viscosity due to changes in temperature of the working fluid. Therefore, it is possible to prevent so-called jerky vibrations of the vehicle during acceleration and deceleration.

Next, FIGS. 2a and 2b are a fragmented front view of main parts and a cross-sectional view taken along the line -- in FIG. 2a, showing another embodiment of this invention.

In this embodiment, a communication passage 23 that communicates between adjacent fluid chambers 8 is formed in the output side arm 7 formed on the output member 3, and each fluid chamber 8 is provided at a position facing the communication passage 23. A damping force adjustment valve 24 is provided which opens this communication passage 23 due to excessive pressure generated in the damping force and prevents generation of an excessive damping force. This damping force adjustment valve 24 includes a check valve 24b that is fitted into a radial groove 24a formed on the outer periphery of the output side arm 7 so as to be able to protrude and retract in the radial direction, and a check valve 24b that is connected to the communication path 24 by the check valve 24b. a spring 24 that biases with a predetermined spring force in the direction of closing the
It is composed of c.

Even in the case of this configuration, as in the case of each of the embodiments described above, the viscosity of the working fluid sealed in each fluid chamber 8 becomes higher than a predetermined value, and excessive pressure is generated in one of the fluid chambers 8. When this occurs, this excessive pressure presses the head side of the check valve 24b constituting the damping force adjustment valve 24, causing the check valve 24b to move radially inward against the spring force of the spring 24c. Since it moves, communication path 2
3 is opened by an amount corresponding to the excessive pressure. Therefore, even if excessive pressure occurs in one fluid chamber 8,
In addition to the orifice 10b formed between the inner periphery of the input arm 6 formed on the input member 5 and the outer periphery of the flange portion 2 formed on the output member 3, it also passes through the communication path 23. The working fluid is transferred from one fluid chamber 8 with excessive pressure to the other fluid chamber 8 with low pressure.
..., the energy loss of the working fluid can be kept to a low level, and therefore, generation of excessive damping force can be prevented.

Note that the output side arm 7 is provided with a check valve 2.
An air vent passage 27 for communicating the radial groove 24a in which the seal member 4b is accommodated and the seal chamber 26 in which the axially slidable seal member 25 is accommodated.
is formed, so when the check valve 24b sinks radially inward in the radial groove 24a,
The air in the radial groove 24a can be discharged to the seal chamber 26 side by the amount of the inflow volume of the check valve 24b. Therefore, the check valve 24b can be easily retracted radially inward within the radial groove 24a.

Next, FIGS. 3a and 3b are a fragmented front view of essential parts and a cross-sectional view taken along the line -- in FIG. 3a, showing another embodiment of this invention.

In this embodiment, a communication passage 33 that communicates between adjacent fluid chambers 8 is formed in the input side arm 6 formed on the input member 5, and each fluid chamber 8 is provided at a position facing the communication passage 33. A damping force adjustment valve 34 is provided that opens this communication passage 33 due to excessive pressure generated in the damping force and prevents generation of an excessive damping force. This damping force adjustment valve 34 includes a check valve 34b that is fitted into a radial groove 34a formed on the outer periphery of the input side arm 6 so as to be able to protrude and retract in the radial direction, and a check valve 34b that connects the communication path 33 with the check valve 34b. a spring 34 that biases with a predetermined spring force in the direction of closing the
It is composed of c.

Even with this configuration, as in the case of each of the embodiments described above, the viscosity of the working fluid sealed in each fluid chamber 8 increases, and excessive pressure occurs in one of the fluid chambers 8. Then, due to this excessive pressure, the check valve 34b that constitutes the damping force adjustment valve 34 moves radially inward against the spring force of the spring 34c, so that the communication passage 33
is opened by an amount corresponding to the excessive pressure. Therefore, even if excessive pressure occurs in one fluid chamber 8, the orifice 1 formed between the outer periphery of the output side arm 7 formed on the output member 3 and the outer periphery of the input member 5
In addition to 0a, the working fluid can also flow through the communication path 33 from one fluid chamber 8 with excessive pressure to the other fluid chamber 8 with low pressure.
Generation of excessive damping force can be prevented.

Note that the input side arm 6 and the output side arm 7 are provided with a volume change compensating section 35 that compensates for a volume change due to a temperature change of the working fluid sealed in each fluid chamber 8. When the working fluid itself thermally expands as the temperature rises, the hollow elastic body 3 constituting the volume change compensating section 35
The hollow elastic body 35a is accommodated in the through hole 35b and the radial groove 34.
Since the air vent hole 36 is formed between the check valve 34b and the radial groove 34a, when the check valve 34b sinks radially inward in the radial groove 34a, the radius is Directional groove 3
The air in the check valve 4a can be discharged into the through hole 35b, so that the check valve 34b can be smoothly retracted radially inward.

Next, FIGS. 4a and 4b are a fragmented front view of main parts and a fourth embodiment showing still another embodiment of this invention.
It is a - line sectional view in figure a.

In this embodiment, a communication path 43 that communicates between adjacent fluid chambers 8 is formed in the output side arm 7 formed on the output member 3, and each fluid chamber 8 is provided at a position facing the communication path 43. A damping force adjustment valve 44 is provided that opens this communication passage 43 due to excessive pressure generated in . . . and prevents generation of excessive damping force. This damping force adjustment valve 44 includes a check valve 44b that is fitted into a radial groove 44a formed on the outer periphery of the output side arm 7 so as to be retractable in the radial direction, and a check valve 44b that is connected to the communication path 43 by the check valve 44b. a spring 44 that biases with a predetermined spring force in the direction of closing the
c, and this check valve 44b
A communication hole 44d, which can communicate with the communication path 43, is formed to penetrate in the width direction approximately at the center.

Even in the case of this configuration, as in the case of each of the embodiments described above, the viscosity of the working fluid sealed in each fluid chamber 8 becomes higher than a predetermined value, and excessive pressure is generated in one of the fluid chambers 8. When this occurs, this excessive pressure presses the head side of the check valve 44b that constitutes the damping force adjustment valve 44, causing the check valve 44b to move radially inward against the spring force of the spring 44c. Because of the movement, the communication hole 44d formed in the check valve 44b and the communication path 43 formed in the output side arm 7 match each other with a predetermined opening area. Therefore, the orifice 10 formed between the output member 3 and the input member 5
In addition to the fluid chambers 8a and 10b, one of the fluid chambers 8 under excessive pressure passes through the communication path 43 and communication hole 44d.
Since the working fluid can be caused to flow into the other low-pressure fluid chamber 8, it is possible to prevent excessive damping force from being generated.

In addition, as shown in FIG. 4b, the flange portion 2 formed on the output member 3 and the seal member 1 which also serves as a bearing
5c and 15c, an air chamber 26 is formed between the air chamber 26 and the radial groove 44.
Since an air vent hole 45 is formed between the check valve 44a and the check valve 44a, when the check valve 44b is recessed radially inward in the radial groove 44a, the radius of the check valve 44b is Directional groove 4
The air in the check valve 44a can be discharged into the air chamber 26, so that the check valve 44b can be smoothly retracted radially inward.

Next, FIG. 5a is a fragmentary front view of a main part showing still another embodiment of this invention.

In this embodiment, communication passages 53, 53 are formed in the input side arm 6 formed on the input member 5, and these communication passages 53, 53 communicate between adjacent fluid chambers 8.
A damping force adjustment valve 54 is provided at a position facing the damping force regulating valve 53, which opens the communicating passages 53, 53 due to excessive pressure generated in each fluid chamber 8, thereby preventing generation of an excessive damping force. This damping force adjustment valve 54 is provided through a circumferential hole 54 formed approximately at the center of the input side arm 6.
A cylindrical member 54b movably inserted into a.
and a spring 54c that biases the cylindrical member 54b from both sides in the axial direction. The cylindrical member 54b controls the opening and closing of each of the communicating passages 53, 53, and the cylindrical member 54b is provided with a flow resistance for the replacement flow of the working fluid to be performed between the fluid chambers 8... An orifice 54d is formed to provide this. Further, stopper members 54e, 54e that hold one end of each spring 54c, 54c are fixed to the openings at both ends of the circumferential hole 54a.

Even with this configuration, the same actions and effects as in each of the embodiments described above can be obtained. That is, when the viscosity of the working fluid sealed in each fluid chamber 8 becomes higher than a predetermined value and excessive pressure occurs in one fluid chamber 8, the pressure in one fluid chamber 8 and the other fluid chamber 8 increase. 8, the cylindrical member 54b moves within the circumferential hole 54a against the spring force of one spring 54c, as shown in FIG. The communication paths 53, 53, which have been closed until now, are opened with a predetermined opening area. Therefore, in addition to the orifice 54d formed in the cylindrical member 54b, the working fluid flows from one fluid chamber 8 into the other fluid chamber 8 through the communication passages 53, 53 and the circumferential hole 54a. Therefore, generation of excessive damping force can be prevented. Further, in the case of this embodiment, since the amount of movement of the cylindrical member 54b can be changed depending on the viscosity of the working fluid, each communication passage 5 whose opening and closing is controlled by the cylindrical member 54b is
The opening area of No. 3, 53 can be continuously increased or decreased. Therefore, a substantially constant damping resistance can be obtained regardless of the viscosity of the working fluid.

Effects of the invention As is clear from the above explanation, according to this invention, either the output side arm formed on the output member or the input side arm formed on the input member, which separates the fluid chamber, has an adjacent It forms a communication path that communicates between the matching fluid chambers, and acts on the excessive pressure in any of the fluid chambers facing this communication path to open this communication path and prevent excessive damping force. Since a damping force adjustment valve is provided to prevent the occurrence of the damping force, even if the viscosity of the working fluid increases above a predetermined level due to a decrease in the temperature of the working fluid sealed in each of the fluid chambers, the damping force will be reduced. The function of the regulating valve makes it possible to prevent excessive damping force from occurring. Therefore, it is possible to prevent an excessive amount of damping from occurring.

[Brief explanation of the drawing]

FIG. 1a is a partially exploded front view showing one embodiment of the clutch disk according to this invention, and FIG. 1b is a first embodiment of the clutch disk.
- line sectional view in figure a, figure 2a and 2
Figure b is a fragmented front view of main parts showing another embodiment of this invention, a sectional view taken along the line - in Figure 2a, and Figure 3a.
Figures 3 and 3b are a fragmented front view of the main part showing another embodiment of this invention and a sectional view taken along the line -- in Fig. 3a, and Figs. 4a and 4b are main parts showing still another embodiment of this invention. Fragmented front view and 4th
Fig. 5a is a fragmented front view of main parts showing still another embodiment of this invention, and Fig. 5b is a state in which the cylindrical member is moved due to excessive pressure in one fluid chamber. FIG. 1...Spline joint part, 2...Flange part,
3...Output member, 4...Cover part, 5...Input member, 6...Input side arm, 7...Output side arm,
8...Fluid chamber, 9...Elastic body (compression spring), 10
a, 10b, 54d... Orifice, 13, 2
3, 33, 43, 53... communication path, 14, 24,
34, 44, 54...damping force adjustment valve.

Claims (1)

[Scope of utility model registration request] A liquid-tight space formed between an input member and an output member that are relatively rotatably connected via an elastic body,
The output member is divided into an output side arm projecting radially outward from the flange portion of the output member and an input side arm extending radially inward from the inner periphery of the input member, so that relative rotation of the input member and the output member is controlled. Accordingly, in a clutch disk, a fluid chamber whose volume increases and decreases is formed, and a working fluid is sealed in this fluid chamber, while a pair of fluid chambers whose volumes mutually increase and decrease are communicated via an orifice seat. , a communication path that communicates between the adjacent fluid chambers is formed in either the output side arm or the input side arm, and facing the communication path, there is a communication path in which of the fluid chambers. A clutch disk characterized by being provided with a damping force adjustment valve that acts on excessive pressure to open this communication path and prevent generation of excessive damping force.