JP3264293B2 - Torsional vibration damping device and power transmission device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torsional vibration damping device,
In particular, the present invention relates to a torsional vibration damping device for attenuating torsional vibration between an input side rotary body and an output side rotary body of a power transmission device. Still another aspect relates to a power transmission device including a viscous damping unit.

[0002]

2. Description of the Related Art As a device for attenuating torsional vibration between an input side rotating body and an output side rotating body of a power transmission device, a device utilizing viscous force of a fluid is known. 2. Description of the Related Art As a conventional device of this type, for example, there is a device that includes an annular case extending in a circumferential direction and an opening / closing member that is arranged in the annular case so as to be movable in the circumferential direction. The annular case is filled with a viscous fluid, and rotates integrally with the input-side rotating body. On the other hand, the output side member connected to the output side rotating body is exposed in the annular case, and a plurality of projections are formed on the exposed portion. The opening / closing member is formed in a cap shape, and is fitted into a projection of the output side member. And it can move a predetermined angle with respect to the projection. A choke through which the viscous fluid can pass is formed between the opening / closing member and the projection, and the choke is closed when one end of the opening / closing member contacts the projection. An annular groove is formed on both sides of the output side member, and annular projections formed at both ends on the inner peripheral side of the annular case are inserted into the grooves so that the inner peripheral side in the radial direction of the annular fluid chamber is formed. Sealed.

[0003]

In the conventional torsional vibration damping device, the two rotating members are driven by viscous resistance when the viscous fluid passes through a choke formed between the opening / closing member and the output-side member projection. Damping the torsional vibrations between them. However, this conventional device does not provide sufficient resistance to suppress longitudinal vibration of the vehicle body at the time of tip-in and tip-out and vibration at the time of starting the engine. That is,
The sealing function of the projection and the groove impairs the sealing function due to distortion of the case, and the viscous fluid in the case leaks inward in the radial direction. Therefore, the viscous fluid is insufficient in the case, and a sufficient resistance cannot be obtained.

An object of the present invention is to obtain a large resistance which cannot be obtained by the conventional structure.

[0005]

According to a first aspect of the present invention, there is provided a torsional vibration damping device which is rotatably connected to an input-side rotating body and an input-side rotating body, and receives power from the input-side rotating body. And a torsional vibration damping device for a power transmission device comprising: The torsional vibration damping device includes a viscous damping part and a dry friction part.

The viscous damping portion is formed between the input-side rotating body and the output-side rotating body, and includes a choke through which fluid passes when the input-side rotating body and the output-side rotating body rotate relative to each other. This is for attenuating the torsional vibration. The dry friction portion is configured to generate the viscosity at the viscous damping portion during the relative rotation.
The purpose of this is to attenuate torsional vibration by a dry friction force corresponding to the characteristic damping force . A torsional vibration damping device according to a second invention is a torsional vibration damping device for a power transmission device,
A first rotating member, a second rotating member, and a viscous damper mechanism are provided.

[0007] The first rotating member forms an annular fluid chamber filled with a viscous fluid. The second rotating member has a contact portion that is exposed in the fluid chamber. The viscous damper mechanism is provided in the fluid chamber and has a first relative torsion angle.
A viscous damping unit that does not operate in the range but operates in a second relative torsion angle range larger than the first relative torsion angle range to generate a viscous damping force. The viscous damper mechanism includes a first
It has first and second chokes through which fluid passes when the first rotating member and the second rotating member rotate relative to each other, and an opening / closing member that forms the first choke and moves in the fluid chamber to open and close the first choke. The opening / closing member has a contact portion for abutting a contact portion of the second rotating member to press one surface of the opening / closing member against a wall surface of the fluid chamber in a dry friction state to attenuate torsional vibration. are doing. The opening / closing member abuts against the contact portion of the second rotating member so that one surface of the opening / closing member is pressed against the wall surface of the fluid chamber in a dry friction state to attenuate torsional vibration. Contact portion.

[0008] A power transmission device according to a third aspect of the invention is an input-side rotating body to which power is input, and an output-side rotation to which power from the input-side rotating body is connected to the input-side rotating body so as to be relatively rotatable. A body, a viscous damping part, and an annular seal member. The viscous damping unit is formed between the input-side rotator and the output-side rotator, and includes a choke through which fluid passes when the input-side rotator and the output-side rotator rotate relative to each other , and is filled with the viscous fluid. Having a closed annular fluid chamber. The annular seal member is movably disposed in an annular groove formed in one of the two rotating bodies, and is pressed against the sealing surfaces of the two rotating bodies when pressure is applied to the fluid chamber to fill the fluid chamber. Seal the viscous fluid that has been applied.

[0009]

In the torsional vibration damping device according to the first aspect of the present invention, the fluid passes through the choke of the viscous damping part when the input side rotating body and the output side rotating body rotate relative to each other. As a result, a viscous resistance force is generated, and the torsional vibration is attenuated. In addition, the impression friction part acts during this relative rotation, and the viscosity generated in the viscous damping part
A dry friction force corresponding to the damping force is generated. For this reason, a large resistance that could not be obtained conventionally can be obtained.

In the torsional vibration damping device according to the second invention, when the input side rotating body and the output side rotating body rotate relatively,
In the first relative torsion angle range, the fluid passes through the first choke to generate a first viscous damping force. When the relative torsion angle increases, the contact portion of the opening / closing member contacts the contact portion of the second rotating member, and the first choke is closed. Then, in the larger second relative torsion angle range, the fluid passes through the second choke to generate a second viscous damping force.

Here, when the relative torsion angle is further increased after the opening / closing member contacts the second rotating member, one surface of the opening / closing member is pressed against the wall surface of the fluid chamber by the contact. By this pressure contact, the fluid film between the surface of the opening / closing member and the wall surface of the fluid chamber is removed, and both slide while pressing in a dry friction state. Therefore, a large frictional force can be obtained. In this structure, since a dry friction state is generated by a part of the opening and closing member that opens and closes the first choke, a large friction force can be obtained with a simple structure.

In the power transmission device according to the third aspect of the present invention, when power is input to the input-side rotating body, the power is transmitted to the output-side rotating body. When the torsional vibration is transmitted to the input side rotating body, the two rotating bodies rotate relative to each other, and the viscous fluid in the annular fluid chamber generates a viscous resistance force to attenuate the torsional vibration. Since pressure acts on the fluid chamber during this relative rotation, the seal member comes into pressure contact with the seal surfaces of both rotating bodies. For this reason, the leakage of the viscous fluid from the annular fluid chamber can be reduced, and a large resistance force that cannot be obtained with the conventional structure can be obtained.

[0013]

FIG. 1 shows an entire power transmission apparatus to which an embodiment of the present invention is applied. In the following description, the left side (engine side) in FIG. 1 is defined as the front side, and the right side (transmission side) is defined as the rear side. This power transmission device mainly includes a flywheel assembly 1, a clutch disk 101, and a clutch cover assembly 102.

As shown in FIGS. 1 to 4, the flywheel assembly 1 mainly includes a first flywheel 2, a second flywheel 3, a first flywheel 2 and a second flywheel 3. And a viscous damper mechanism 4 disposed therebetween. The first flywheel 2 is fixed to a shaft end of a crankshaft of the engine by a bolt 25. Further, the second flywheel 3 has a friction surface 3 against which a friction member of the clutch disc 101 is pressed on a rear side surface.
a. A clutch cover of the clutch cover assembly 102 is fixed to an outer peripheral portion of the second flywheel 3 on the friction surface 3a side.

The first flywheel 2 is a substantially disk-shaped member, and has a boss portion 2a projecting rearward at a central portion thereof;
Disc portion 2b extending outward from boss portion 2a and integrally formed
And a rim portion 2c extending rearward from the outer peripheral side of the disk portion 2b. An annular recess is formed between the boss 2a and the rim 2c, and the viscous damper mechanism 4 is accommodated in the recess. Two rolling bearings 22 and 23 arranged in the axial direction are mounted on the outer periphery of the boss 2a. Bearings 22, 23
Are of a lubricant-sealed type having seal members mounted on both sides, respectively, and are restricted from moving backward by a snap ring 24 fitted on the outer peripheral surface of the boss 2a.

The second flywheel 3 is a substantially disk-shaped member, and its inner peripheral portion is formed of a viscous damper mechanism 4 by a bolt 21.
Is detachably fixed to a driven member 6 (described later). The inner peripheral end of the second flywheel 3 also restricts the rearward movement of the rolling bearings 22 and 23. Also, the second
A clutch disc 10 is provided on the inner peripheral portion of the flywheel 3.
A hole 3b is formed for communicating the first side with the viscous damper mechanism 4 side.

As shown in FIGS. 2 and 3, the viscous damper mechanism 4 includes a disk-shaped drive plate 5 fixed to the first flywheel 2 and an inner peripheral portion provided with first bearings 22 and 23 via rolling bearings 22 and 23. A disk-shaped driven member 6 supported by the flywheel 2; and a coil spring 12a, which elastically couples the driven member 6 to an input-side member composed of the first flywheel 2 and the drive plate 5 in a circumferential direction. 12
b and 12c, and a viscous damper section 7 for attenuating torsional vibration by viscous force of the fluid. In the viscous damper mechanism 4, a space formed by the first flywheel 2, the drive plate 5, and the driven boss 6a of the driven member 6 is filled with a viscous fluid. The drive plate 5 has a rim portion 2 c of the first flywheel 2 whose outer peripheral end is
, And an annular seal member 20 is arranged between the inner peripheral end and the driven boss 6 a of the driven member 6. The seal member 20 and the above-described bearings 22 and 23
Seals the radially inner peripheral end of the space.

The driven member 6 is a cast member formed in a disk shape, and is disposed between the disk portion 2 b of the first flywheel 2 and the drive plate 5. The driven member 6 has the driven boss 6a extending rearward on the inner peripheral portion as described above. Rolling bearings 22 and 23 are mounted on the driven boss portion 6 a on the inner peripheral side, and the inner peripheral portion of the second flywheel 3 is fixed by bolts 21. In the driven member 6, six window holes 6b are formed at a radially intermediate portion at intervals in the rotation direction. The window hole 6b extends in the rotational direction, and the coil springs 12a, 12b and 12c are accommodated in the window hole 6b.

As shown in FIG. 3, of the six window holes 6b of the driven member 6, two window holes 6b opposed in the radial direction are provided.
(A vertical window hole in FIG. 3) is provided with a coil spring 12c.
Is housed. The coil spring 12c is in contact with both circumferential end surfaces of the window hole 6b via the spring seat 13. A large-diameter coil spring 12a and a small-diameter coil spring 12b disposed therein are accommodated in the remaining four window holes 6b. Spring seats 13 are arranged at both ends of both coil springs 12a and 12b.
A predetermined gap is secured between the base 3 and both end faces in the circumferential direction of the window hole 6b. The spring seat 13 is provided on the outer peripheral support 1.
3a and a central boss 13b, the outer periphery of the large-diameter coil spring 12a is supported by the outer periphery support 13a of the spring seat 13, and the inner periphery of the small-diameter coil spring 12b is Boss part 1
3b. In this way, the coil springs 12a and 12b are arranged concentrically by the spring seat 13 and are prevented from interfering with each other.

Each of the first flywheel 2 and the drive plate 5 has an abutting portion that abuts on an end of each spring seat 13, whereby the input side of the first flywheel 2 and the drive plate 5 is provided. And the driven member 6 are elastically connected in the rotation direction. FIG. 3 shows the contact portion 2 e of the first flywheel 2.

The viscous damper part 7 includes an annular fluid chamber 7a,
It mainly comprises a resin-made stopper member 8 arranged in the annular fluid chamber 7a and a slide stopper 10. The annular fluid chamber 7a is provided with a first flywheel rim portion 2c.
, An outer peripheral surface of the driven member 6, a space surrounded by the first flywheel disk portion 2b and the drive plate 5, and filled with a viscous fluid. The stopper members 8 are provided at six locations in the annular fluid chamber 7a at equal angular intervals in the circumferential direction, and divide the annular fluid chamber 7a into six chambers in the rotational direction. The stopper member 8 is non-rotatably connected to the first flywheel 2 and the drive plate 5 by a pin 9. In addition,
Between the outer peripheral surface of the radially inner surface and the driven member 6 of the stopper member 8, the inter-divided chambers viscous fluid choke C ₂ is formed can pass. In the driven member 6, a concave portion 6c that is recessed inward in the radial direction is formed between the window holes 6b on the outer peripheral edge. A fluid supply hole 6d extending radially outward from the center of the window hole 6b and opening to the annular fluid chamber 7a is formed in the middle of the adjacent concave portion 6c. The hole 6d is provided with the stopper member 8 in the free state.
Located in the center of.

The slide stopper 10 is a resin molded part.
The stopper is disposed between each stopper member 8 and the stopper
The chamber obtained by the member 8 is further referred to as a first Oita chamber 14.
It is divided into the second Oita room 15. Slide stopper
Reference numeral 10 denotes an arc shape whose outer peripheral surface is along the inner peripheral surface of the rim 2c.
And the inner peripheral surface is formed in an arc shape along the outer peripheral surface of the driven member 6.
Has become. Slide stopper 10 is radially inward
The projection 10a protrudes from the center. Protrusion 10a
Is disposed in the recess 6 c of the driven member 6,
The inside of c is rotated into the first sub-compartment 16 and the second sub-compartment 17
Divided. Also, the tip of the projection 10a and the bottom of the recess 6c.
Between the first sub-compartment 16 and the second sub-partition 17.
Choke C through which permeable fluid can pass₁Is formed. H
Joke C ₁Is chalk C_TwoLarger flow area
Have been. Further, a circumferential end face of the concave portion 6c and
Choke C by contacting₁Close slides
With the topper projection 10a, it spreads outward.
They are inclined at the same angle. This allows slides
The topper 10 moves in the circumferential direction and moves in the circumferential direction of the concave portion 6c.
If the abutment on the end surface continues to be pushed, the slide stopper
A component force is generated to move -10 outward in the radial direction.
Swelling.

The radially inner side of the annular fluid chamber 7a is sealed by an annular seal member 11 made of Teflon or a heat-resistant and abrasion-resistant resin. The seal member 11 is disposed between the first flywheel 2 and the driven member 6 and between the drive plate 5 and the driven member 6. As shown in detail in FIG. 5, one seal member 11 is movably disposed between an annular groove 2 d formed in the first flywheel 2 and an end face of the driven member 6. When pressure is not applied to the annular fluid chamber 7a, the seal member 11 is in the annular groove 2d as shown by the dotted line in the figure.
However, when pressure is applied to the annular fluid chamber 7a, it moves to the position indicated by the solid line in the figure, and seals the radially inner peripheral side of the annular fluid chamber 7a. A similar annular groove is also formed on the drive plate 5 side, and the other seal member 11 is arranged in this annular groove.

In such a configuration, the driven member 6
Since it does not have a protrusion protruding to the outer peripheral side, choke C
_The outer peripheral surface forming ₂ can be easily and accurately processed with a lathe. As the processing becomes easier, the manufacturing cost is reduced. Since the slide stopper 10 is a molded product, it is easy to form the projection. Next, the operation of the above embodiment will be described.

When torque is input to the first flywheel from the crankshaft on the engine side, the driven member 6 of the viscous damper mechanism 4 and the coil springs 12a, 12b, 1
Torque is transmitted to the second flywheel 3 via 2c and the like. At this time, when torsional vibration is input from the engine side, the coil springs 12a, 12b, and 12c repeat expansion and contraction, and the viscous damping unit 7 generates viscous resistance to attenuate the torsional vibration.

Next, the operation of the first flywheel 2 and the second flywheel 3 during relative rotation will be described. When torque is input to the first flywheel 2 from the crankshaft on the engine side, the first flywheel 2 and the drive plate 5 are twisted with respect to the driven member 6. Here, the rotation from Figure 4 the free state in R ₁ side. The drive plate 5 rotates in the rotation direction R1 with respect to the drive member 6.
When twisted in the side, the slide stopper 10 also similarly R ₁
Move to the side. Thereby, the capacity of the second small compartment 17 is reduced, and at the same time, the capacity of the first small compartment 16 is increased. That is, fluid flow of the second small compartment 17 with the movement of the slide stopper 10 to the first small compartment 16 through the choke C _1. Since the choke C ₁ has a large flow path cross-sectional area, the viscous resistance is small. In particular, it is preferred that this viscous drag be minimal. In this small torsion angle range, only the coil spring 12c is compressed, and the coil springs 12a and 12b
Is not compressed until it contacts the surface of the window hole 6b of the driven member 6. In this way, in the range where the twist angle is small,
Low rigidity and small viscous force work.

[0027] twist angle in the rotational direction R ₁ side is larger, the projection 10a of the slide stopper 10 abuts against the circumferential end of the recessed portion 6c of the driven member 6 (FIG. 6).
Thus, the choke C ₁ is closed, thereafter choke C ₂ to function. When the projection 10a is pressed against the circumferential end surface of the concave portion 6c, a force A perpendicular to both contact inclined surfaces is obtained.
Occurs. The force A can be divided into a circumferential component B and a radial outward component C. Due to the component force C and the centrifugal force, the slide stopper 10 is pushed outward in the radial direction, the outer peripheral surface of the slide stopper 10 is pressed against the inner peripheral surface of the rim portion 2c, and the viscous fluid in the gap is pushed out. In this manner, when the first flywheel 2 continues to rotate relative to the slide stopper 10 fixed to the driven member 6 side thereafter, a large resistance is generated between the two by dry friction. This resistance can be adjusted by changing the angles of the two contact slopes.

When the torsion angle is further increased from FIG. 6 to FIG. 7, the compression of the coil springs 12a and 12b is started. For this reason, a second-stage torsional characteristic having high rigidity can be obtained. At the same time, fluid in the first Oita chamber 14 flows into the second Oita chamber 15 through the choke C _2. Here, a large viscous resistance is obtained because the flow path cross-sectional area of the choke C ₂ is small. By adding the above-mentioned dry frictional resistance to this viscous resistance, a large resistance that could not be obtained conventionally can be obtained.

Further, at this time, when the stopper member 8 moves to the R ₁ side, the liquid supply hole 6 d of the driven member 6 opens to the second large compartment 15. Therefore, the fluid accumulated in the window hole 6b of the driven member 6 quickly flows into the second large sub-chamber 15 due to the centrifugal force and the expanding suction force from the second large sub-chamber 15. Window hole 6b
Since the inside is the location where the most viscous fluid is stored radially inside the annular fluid chamber 7a, a sufficient amount of fluid can be returned to the annular fluid chamber 7a, and the fluid is insufficient in the annular fluid chamber 7a. It becomes difficult to do.

When the torsion angle increases from FIG. 7 to FIG. 8, the stopper member 8 comes into contact with the slide stopper 10. Thereby, the relative rotation between the first flywheel 2 and the drive plate 5 and the driven member 6 is stopped. FIG. 9 is a torsion characteristic diagram of the flywheel assembly 1, in which the solid line indicates the static torsional characteristic and the dotted line indicates the dynamic torsional characteristic. In static torsional characteristics, the region of small hysteresis H ₁ seen in a range twist angle is small, the angle range in which the slide stopper 10 is choke C ₁ functions twisted relative to the driven member 6. Large hysteresis torque H ₂ is the large hysteresis torque generated by the choke C _2. Twist angle of the small hysteresis torque H ₁ at increased area seen in a state where the drive plate 5 is fixed twist angle with respect to the driven member 6, a small torsional vibration (e.g. combustion variation) of When it occurs, slide stopper 1
0 This is because the choke C ₁ functions away from the driven member recess 6c circumferential end. In this way, it is possible to generate a small hysteresis torque H ₁ regardless of the relative angle between drive plate 5 and the driven member 6, it can be effectively damped e.g. a minute vibration at the time of combustion variation.

In the dynamic torsion characteristics shown in this figure, the viscous force is much larger than in the prior art. The main reasons for this are as follows. Since a sufficient amount of fluid is returned from the window 6a of the driven member 6 to the annular fluid chamber 7a, it is difficult for the viscous fluid to run short. ◎ The seal member 11 seals the annular fluid chamber 7a,
Further, since the driven member 6 is an integral body, leakage of fluid is reduced.

The dry frictional force generated when the outer peripheral surface of the slide stopper 10 is pressed against the inner peripheral surface of the rim portion 2c is applied. Since a large viscous damping force acts on such a large torsion angle,
The longitudinal vibration of the vehicle body at the time of tip-in and tip-out and the vibration at the time of starting the engine are suppressed.

Next, a method of assembling the flywheel assembly 1 will be described. First, the rolling bearings 22 and 23 are press-fitted into the inner peripheral portion of the driven boss 6a of the driven member 6. Next, the driven member 6 to which the bearings 22 and 23 are attached is attached to the first flywheel 2. At this time,
The bearings 22 and 23 are pressed into the outer periphery of the boss 2 a of the first flywheel 2. Note that the seal member 11 is inserted into the annular groove 2d of the first flywheel 2 in advance. After attaching the driven member 6 to the first flywheel 2, the snap ring 24 is attached to the boss 2a. Further, the driven member 6 includes a spring seat 13 and a coil spring 12.
a, 12b, and 12c are attached. Then, the stopper member 8 is attached to the annular fluid chamber 7a by the pin 9, and the slide stopper 10 is further inserted. Next, the drive plate 5 in which the seal member 11 is inserted into the annular groove is fixed to the rim portion 2c of the first flywheel 2 by bolts 19. Subsequently, the seal member 20 is inserted between the inner periphery of the drive plate 5 and the outer periphery of the driven boss 6a.

After assembling the viscous damper mechanism 4 as described above, the second flywheel 3 is fixed to the driven boss 6a of the driven member 6 using the bolt 21. In such an assembling method, the second flywheel 3 can be easily attached and detached simply by removing or tightening the bolt 21. Moreover, when the second flywheel 3 is attached and detached, it is not necessary to attach and detach the bearings 22 and 23 and the seal member 20, so that the life of the bearings 22 and 23 can be prevented from being shortened, and the seal member 20 can be used for a long period of time. Another Embodiment As another embodiment of the present invention, as shown in FIG. 10, the position of the liquid supply hole can be changed to adjust the torsional characteristics. When the fluid supply hole 51 is displaced in the rotational direction R ₁ side as shown in FIG. 10, the sliding stopper 1
When 0 contacts the driven member 6 (the state of FIG. 6 in the above embodiment), the fluid supply hole 51 is open to the first large compartment 14. Then, the choke C ₂ is the stopper member 8 does not function to close the fluid supply hole 51. As described above, by changing the position, size, and number of the fluid supply holes, the torsional characteristics can be adjusted.

As still another embodiment, FIG. 11 shows an example in which the driven member and the driven boss are separated. Here, the driven member of the above embodiment is composed of three driven plates 66. The inner peripheral surface of the driven plate 66 is formed with corrugated inner teeth 66 a, and the outer corrugated teeth meshing with the corrugated internal teeth 66 a are formed on the outer periphery of the driven boss 86. Since the driven plate 66 and the driven boss 86 are separated by the serration as described above, the swing of the second flywheel 3 hardly affects the driven plate 66 side. In this example,
The attachment and detachment of the second flywheel 63 is easy, and the durability of the rolling bearings 82 and 83 is improved.

[0036]

In the torsional vibration damping device according to the first invention, a dry friction portion is provided in addition to the viscous damping portion to attenuate the torsional vibration. Is obtained, and the torsional vibration can be attenuated over a wider range. Further, in the torsional vibration damping device according to the second invention, dry friction is generated by utilizing a slide stopper provided in the damping portion due to viscosity. Therefore, a large resistance can be obtained with a simple structure.

Further, in the power transmission device according to the third aspect of the invention, the fluid chamber is sealed by a seal member movably disposed in the annular groove. For this reason, when pressure acts on the fluid chamber, the seal is assured, and the leakage of the viscous fluid can be reduced to obtain a large resistance.

[Brief description of the drawings]

FIG. 1 is a schematic cross-sectional view of a power transmission device employing an embodiment of the present invention.

FIG. 2 is a partially enlarged view of FIG. 1 and is a cross-sectional view of a flywheel assembly.

FIG. 3 is a sectional view taken along the line III-III in FIG. 2;

FIG. 4 is a partially enlarged view of FIG. 3;

FIG. 5 is a partially enlarged view of FIG. 2;

FIG. 6 is a view corresponding to FIG. 4 showing one stage of the twisting operation.

FIG. 7 is a view corresponding to FIG. 4, showing one stage of the twisting operation.

FIG. 8 is a view corresponding to FIG. 4 showing one stage of the twisting operation.

FIG. 9 is a torsion characteristic diagram of the flywheel assembly.

FIG. 10 is a view corresponding to FIG. 4 of another embodiment.

FIG. 11 is a view corresponding to FIG. 2 of still another embodiment.

[Explanation of symbols]

 Reference Signs List 1 flywheel assembly 2 first flywheel 2d annular groove 3 second flywheel 4 viscous damper mechanism 5 drive plate 6 driven member 6c concave portion 7 viscous damper portion 7a annular fluid chamber 10 slide stopper 10a protrusion 11 seal member

Continuation of the front page (56) References JP-A 1-255738 (JP, A) JP-A 2-203041 (JP, A) JP-A 2-278019 (JP, A) JP-A 5-133439 (JP , A) Microfilm (JP, U) which photographed the contents of the specification and drawings attached to the application for Japanese Utility Model Application No. 1-148314 (Japanese Utility Model Application No. 3-86231) (58) Field surveyed (Int. . ^7, DB name) F16F 15/16 F16F 15/139 F16F 15/129

Claims (3)

(57) [Claims] 1. A torsional vibration damping device for a power transmission device comprising an input-side rotating body and an output-side rotating body which are connected to each other so as to be rotatable relative to each other and to which power is transmitted, wherein the input-side rotating body and an output are provided. A viscous damping part formed between the input side rotary body and the output side rotary body, the viscous damping portion configured to attenuate torsional vibration, including a choke through which fluid passes during relative rotation between the input side rotary body and the output side rotary body. Viscous damping generated in the viscous damping section during relative rotation
A torsional vibration damping device comprising: a dry friction portion for attenuating torsional vibration by a dry friction force corresponding to a force . 2. A torsional vibration damping device for a power transmission device, comprising: a first rotating member forming an annular fluid chamber filled with a viscous fluid; and an abutment exposed in the fluid chamber. A second rotating member having a portion, provided in the fluid chamber, and formed in a first relative torsion angle range.
A viscous damper mechanism having a viscous damping portion that does not move and operates in a second relative torsional angle range larger than the first relative torsional angle range to generate a viscous damping force; A first and a second choke through which fluid passes when the first rotating member and the second rotating member rotate relative to each other; and forming the first choke and moving in the fluid chamber to form the first choke. An opening and closing member for opening and closing the choke, wherein the opening and closing member is brought into contact with a contact portion of the second rotating member to press one surface of the opening and closing member against the wall surface of the fluid chamber in a dry friction state, and A torsional vibration damping device having a contact portion for damping torsional vibration. 3. An input-side rotator to which power is input; an output-side rotator connected to the input-side rotator so as to be rotatable relative to the input-side rotator; A viscous fluid having an annular fluid chamber formed between a body and an output-side rotator, and having a choke through which fluid passes when the input-side rotator and the output-side rotator are relatively rotated, and filled with a viscous fluid. A damping portion, movably disposed in an annular groove formed in one of the two rotating bodies, and pressurizing against the sealing surfaces of the two rotating bodies when pressure is applied to the fluid chamber to form the fluid chamber. A power transmission device comprising: an annular seal member that seals a viscous fluid filled in the seal member.