JP2606715Y2 - Viscous damping mechanism - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flywheel assembly, and more particularly, to a flywheel assembly for transmitting torque from an input rotary body to an output rotary body.

[0002]

2. Description of the Related Art Flywheel assemblies are commonly located, for example, between the engine and the transmission of a motor vehicle. The flywheel assembly includes a first flywheel connected to a crankshaft on the engine side, a second flywheel rotatably supported by the first flywheel, and a first flywheel and a second flywheel. It comprises an elastic coupling mechanism for coupling, and a viscous damping section including a fluid chamber disposed between the first flywheel and the second flywheel. The viscous damping portion has a throttle portion through which the fluid passes when the first flywheel and the second flywheel are twisted relative to each other. Decay energy.

[0003]

In a conventional flywheel assembly, a fluid chamber is formed by a fluid chamber housing fixed to a first flywheel. An annular engagement projection is formed at the inner peripheral end of the fluid chamber housing, and the engagement projection engages with an engagement recess of a driven plate that rotates integrally with the second flywheel. The periphery is sealed.

As described above, in the conventional configuration, the fluid chamber is formed by separately providing the fluid chamber housing.
The number of parts increases and the structure is complicated. An object of the present invention is to simplify the structure of a viscous damping portion of a flywheel assembly.

[0005]

According to the present invention, there is provided a method for reducing viscosity according to claim 1.
Damping mechanism dampens torsional vibration by generating viscous resistance
And a first rotating member and a second rotating member.
And multiple cap-shaped slide stoppers and multiple
And a plurality of stoppers. 1st
An annular fluid chamber with an annular opening is formed in the transfer member
Have been. The second rotating member is on the opening side of the first rotating member.
And a plurality of protrusions extending from the opening into the fluid chamber.
Have. Multiple cap-shaped slide stoppers
It is located indoors and can be moved within a predetermined angle range with respect to the projection
Engage with Noh. The plurality of sealing members have openings in the fluid chamber.
Is arranged so that it can be in close contact with the
Arc-shaped plate-shaped members, and slides formed at both ends of the plate-shaped members.
And an engaging portion extending into the id stopper. Engagement
When the part is in contact with the slide stopper,
No fluid flows. The pressure generated in the fluid chamber by the sealing member
Can seal the opening. Multiple switches
The topper rotates integrally with the first rotating member, and a plurality of
Between the slide stopper and the plate-like member
Form a chalk. The viscous damping mechanism according to claim 2.
In claim 1, the seal member is in contact with the second rotating member.
Seal the opening while ensuring a gap between them.

[0006]

[0007]

[0008]

[0009]

In the viscous damping mechanism according to the first aspect, the first rotating portion is provided.
When the material and the second rotating member rotate relative to each other, the slide stop
The par and the protrusion are engaged, and the engaging part of the seal member is
The fluid in the space between the tightly contacted part and the choke part
Flows through the chalk. At this time, viscous drag occurs
Live. The seal member is opened by the pressure generated at this time.
Seal the fluid chamber in close contact with the part. Therefore, simple
The structure improves sealing performance. A viscous damper according to claim 2.
The seal member and the second rotating member according to claim 1,
And no sliding occurs between them.

[0010]

[0011]

[0012]

EXAMPLES First Embodiment FIG. 1 and 2 show a flywheel assembly 1 according to a first embodiment of the present invention. Flywheel assembly 1
Is a device disposed between the engine of the vehicle and the transmission for transmitting torque from the engine side to the transmission side. In FIG. 1, an engine (not shown) is arranged on the left side of the figure, and a transmission (not shown) is arranged on the right side of the figure. Further, the OO line in FIG. 1 is the rotation axis of the flywheel assembly 1, and the R ₁ direction in FIG. 2 is the rotation direction of the hulawheel assembly 1.

The flywheel assembly 1 mainly includes a first flywheel 2, a second flywheel 3 rotatably supported on the first flywheel 2 via a bearing 4, and a second flywheel 3. Driven plate 1 that rotates together
5, an elastic connecting mechanism 8 for elastically connecting the first flywheel 2 and the driven plate 15 in the circumferential direction,
A viscous damper 9 disposed between the flywheel 2 and the driven plate 15 for damping torsional vibration between the two.
And

The first flywheel 2 is a substantially disk-shaped member, and has a central boss 2a protruding toward the second flywheel 3 and an outer peripheral annular wall 2b. Boss part 2a
An annular concave portion is formed between the outer peripheral wall 2b and the outer peripheral wall 2b. A large diameter center hole is formed at the center of the boss 2a, and a bearing 4 is mounted on the outer periphery of the boss 2a. The bearing 4 has a boss 2a formed by a head of a bolt 11 penetrating the boss 2a.
It is fixed to the end face. The bolt 11 penetrates a hole 2c formed in the boss 2a to fix the first flywheel 2 to a crankshaft (not shown). On the transmission side of the outer peripheral annular wall 2b of the first flywheel 2, an annular portion 2g that protrudes radially outward is formed.
A ring gear 12 is fixed to the outer periphery of the outer peripheral annular wall 2b of the first flywheel 2.

The second flywheel 3 is a substantially disk-shaped member and has a boss 3a at the center. Boss part 3
“a” protrudes toward the first flywheel 2, and a bearing 4 is mounted on an inner peripheral portion thereof. That is, the boss 3a
An annular receiving portion 3b provided on the inner peripheral side of the front end of the bearing 4 is in contact with the engine side of the bearing 4, and a snap ring 13 attached to the inner peripheral side of the boss portion 3a is in contact with the transmission side of the bearing 4. I have. The bearing 4 is of a lubricant sealing type, and seals an inner peripheral portion of an annular space A described later between the boss portions 2a and 3a. As shown in FIG. 2, the driven plate 15
Are formed. further,
The transmission-side end surface of the second flywheel 3 is a friction surface 3d against which a friction member of a clutch disk (not shown) is pressed.

A disk-shaped seal plate 5 is fixed to the transmission side of the first flywheel 2. The outer peripheral end of the seal plate 5 is a caulked portion 5a that is caulked so as to surround the annular portion 2g of the outer peripheral annular wall 2b of the first flywheel 2. A seal member 14 is arranged between the caulked portion 5a and the end face of the outer peripheral annular wall 2b. As described above, since the outer peripheral portion of the seal plate 5 is caulked to the outer peripheral portion of the first flywheel 2, the flange portion conventionally formed on the first flywheel can be omitted. Therefore, the outer diameter of the first flywheel 2 and thus the flywheel assembly 1 can be reduced. Also,
The seal plate 5 is fixed to the first flywheel 2 by a plurality of rivets 7 arranged at equal intervals in the circumferential direction. The seal plate 5 forms an annular space A filled with a viscous fluid such as grease between the annular space of the first flywheel 2 and the annular recess. An annular seal member 30 for sealing the annular space A is disposed between the inner peripheral end of the seal plate 5 and the outer peripheral surface of the boss 3a of the second flywheel 3.

The driven plate 15 is a disk-shaped member formed by a pair of driven plates 15A and 15B disposed in the annular space A. Driven plate 15
As shown in FIG. 2, the inner peripheral end has a corrugated inner tooth 15 a at its inner peripheral end. The corrugated inner teeth 15a mesh with the corrugated outer teeth 3c formed on the second flywheel 3, so that the driven plate 15 can rotate integrally with the second flywheel 3. The driven plate 15 is formed with five window holes 15b extending in the circumferential direction at intervals in the circumferential direction. Further, a plurality of projections 15c are formed on the outer peripheral surface 15d of the driven plate 15 so as to protrude radially outward from between the window holes 15b. The projection 15c is inserted into a fluid chamber B of the viscous damping section 9 described later.

Next, the elastic connection mechanism 8 will be described.
The elastic connection mechanism 8 includes a coil spring 17 extending in a circumferential direction and sheet members 18 disposed at both ends of the coil spring 17. Coil spring 17
And the sheet member 18, the window 1 of the driven plate 15
5b. In addition, the first flywheel 2
A spring receiving groove 2f is formed in a portion corresponding to the window hole 15b of the driven plate 15 on the surface on the transmission side in the radially intermediate portion. One end of the sheet member 18 is in contact with both ends in the circumferential direction of the spring receiving groove 2f. Thus, the first flywheel 2 and the driven plate 15 are elastically connected in the circumferential direction via the elastic connecting mechanism 8. Note that, in the free state shown in FIG.
Only the inner peripheral portion is in contact with the end of the spring receiving groove 2f and the end of the window hole 15b of the driven plate 15. That is, the coil spring 17 is biased to the window hole 1
5b.

Next, the viscous damping section 9 will be described. The viscous damping section 9 includes an annular fluid chamber B formed by the first flywheel 2 and the seal plate 5.
As shown in detail in FIG. 3, the fluid chamber B is constituted by the transmission-side end surface of the first flywheel 2, the inner peripheral surface of the outer peripheral annular wall 2b, and the engine-side end surface of the seal plate 5. Further, a plurality of arc-shaped protrusions 2d formed by lathing are formed on the outer peripheral side of the spring receiving groove 2f of the first flywheel 2. A gap of a predetermined length is secured between each protrusion 2d. This gap portion is in the free state shown in FIG.
Is offset slightly R ₂ side with respect to the projection 15c. Further, the seal plate 5 has a protrusion 5b protruding toward the engine by press working at a portion corresponding to the protrusion 2d of the first flywheel 2. Projection 2
An opening D that opens radially inward in the fluid chamber B and extends in the circumferential direction is formed between d and 5b. The outer peripheral surfaces of the protrusion 2d of the first flywheel 2 and the protrusion 5b of the seal plate 5 are aligned.

The outer peripheral surface 15d of the driven plate 15
It is sandwiched between the protrusion 2d and the protrusion 5b. A slight gap is formed between the outer peripheral side surfaces of the driven plate 15 and the protruding portions 2d and 5b. The protrusion 2
The return holes H where the viscous fluid can freely pass between the fluid chamber B and the annular space A are provided in the portion where the d and 5b are not formed.
(FIG. 4). The outer peripheral surface 15d is shorter in diameter than the outer peripheral surfaces of the protrusion 2d and the protrusion 5b. In such a state, the projection 15c of the driven plate 15 is inserted into the fluid chamber B.

In the fluid chamber B, five stoppers 21 are arranged at equal intervals in the circumferential direction. The stopper 21 is a block made of rubber or resin, and has a hole through which the rivet 7 penetrates. The stopper 21 is sandwiched between the first flywheel 2 and the seal plate 5 while being compressed in the axial direction, and as a result, the degree of adhesion between the stud pin 7 and the hole of the stopper 21 is improved.

An annular fluid chamber B is formed by the stopper 21.
Is divided into five arc-shaped fluid chambers B ₁ (FIG. 2). The circumferential center of each arcuate fluid chamber B _1, projection 15c of the driven plate 15 is disposed. Each arc-shaped fluid chamber B
_{In 1} , a cap-shaped slide stopper 22 that covers the projection 15 c of the driven plate 15 from the outer peripheral side is disposed. The slide stopper 22 has an outer peripheral portion 22a having an arcuate surface coinciding with the inner peripheral surface of the outer peripheral annular wall 2b of the first flywheel, and a stopper portion 22b extending radially inward from both ends of the outer peripheral portion 22a. I have. Since the slide stopper 22 does not have a conventional side portion, it can be removed in the axial direction from the projection 15c.
The outer peripheral portion 22a and the stopper portion 22b are
The end surface of the flywheel 2 is in contact with the end surface of the seal plate 5. In this state, the slide stopper 22 is movable in the circumferential direction in each arc-shaped fluid chamber B within _1. However, the slide stopper 22 is provided with the stopper portion 22 for the projection 15 c of the driven plate 15.
The twisting operation is possible only within a range until b contacts the projection 15c. Further, a notch 22c is formed at a radially inner end of the stopper portion 22b.

The slide stopper 22 divides the inside of each arc-shaped fluid chamber B ₁ into a large chamber 24 A on the R ₂ side and a large chamber 24 on the R ₁ side.
B. Further, the slide stopper 22
Inner is divided into the small compartment 25B of the small compartment 25A and R ₁ side of the R ₂ side by the projection 15c of the driven plate 15. However, between the sub-chamber 25A and the sub-chamber 25B,
A viscous fluid can freely flow back and forth by a gap formed between the projection 15c of the driven plate 15 and the first flywheel 2 and the seal plate 5.

An Oita chamber 24B of _one arc-shaped fluid chamber B1,
Sealing member 23 is disposed than over the inside of the Oita chamber 24A arcuate fluid chamber B ₁ of R ₁ side. The seal member 23 is a thin plate-shaped member extending in the circumferential direction,
The outer peripheral surface of the projection 2 d of the first flywheel 2 and the outer peripheral surface of the projection 5 b of the seal plate 5 are in contact with each other. As shown in FIG. 3, a predetermined gap S is secured between the sealing member 23 and the outer peripheral surface 15d of the driven plate 15, as shown in FIG. At both ends of the sealing member 23, bent portions 23a bent outward in the radial direction are provided.
Are formed. Each bent portion 23a is disposed between the protrusion 15c and the stopper portion 22b of the slide stopper 22. In the free state shown in FIG. 2, although the bent portion 23a of the R ₁ side is in contact with the stopper portion 22b,
Bent portion 23a of the R ₂ side is closer to the protrusion 15c side away from the stopper portion 22b. As described above, the circumferential length of the seal member 23 is set longer than the distance between the respective slide stoppers 22 in the circumferential direction.

The inner peripheral surface of the stopper 21 and the sealing member 23
A choke portion C is formed between the outer peripheral surface and the outer peripheral surface. When a viscous fluid passes through the choke portion C, a large viscous resistance is generated. Next, the operation will be described. From the engine side crankshaft (not shown)
When torque is input to the flywheel 2, the torque is transmitted via the coil spring 17 to the driven plate 15.
And further transmitted to the second flywheel 3. The torque of the second flywheel 3 is transmitted to the transmission via a clutch (not shown).

Next, an operation when torsional vibration is transmitted from the engine to the first flywheel 2 will be described. However, here, when the torsional vibration is transmitted, the operation of the driven plate 15 (the second flywheel 3) is fixed to another member (not shown) so that the first flywheel 2 is not rotatable. The operation will be described as a twisting operation.

Stopper part 2 of slide stopper 22
2b is a small deviation angle torsional vibration that does not come into contact with the projection 15c of the driven plate 15 (hereinafter referred to as micro vibration).
The operation when is transmitted will be described. From the free state shown in FIG. 5, the first flywheel 2 and the seal plate 5
Twist to _one side. Then, the slide stopper 22 also moves together with the sealing member 23 on the R ₁ side, as shown in FIG. 6, in the slide stopper 22, the small compartment 25A is small compartment 25B is reduced is expanded. The viscous fluid flows freely from the small compartment 25A to the small compartment 25B. The viscous fluid can freely move between the small compartments 25A and 25B and the annular space A through the return hole H.

[0028] Returning from the state shown in FIG. 6 to the neutral state shown in FIG. 5, then the first flywheel 2 is twisted R ₂ side. Then, folding the beginning R ₁ side stopper portion 22b of the slide stopper 22 is sealing member 23 bend 23a
Contact, thereafter the slide stopper 22 is brought sealing member 23 moves to the R ₂ side. After that, small branch room 25B
Is reduced, and the sub-chamber 25A is expanded.
Also at this time, the viscous fluid is supplied to the small compartment 25A and the small compartment 25B.
It is possible to move freely between the rooms, and the small branch room 25A,
It is possible to freely move back and forth between 25B and the annular space A through the return hole H. That is, large viscous resistance does not occur at the time of minute vibration.

In the case of the minute vibration described above, the coil spring 17 expands and contracts with respect to the window hole 15b of the driven plate 15 in an uneven contact state. Therefore, a low rigidity state is obtained. In other words, in the case of minute vibration, characteristics of low rigidity and small viscous resistance are obtained, and generation of abnormal noise such as rattling noise and muffled noise of the transmission is effectively suppressed. In the above operation, the seal member 23 rotates together with the first flywheel 2 and rotates relative to the driven plate 15, but a gap S is formed between the seal member 23 and the outer peripheral surface 15d of the driven plate 15. Since (FIG. 3) is secured, no frictional resistance occurs between the two. Thereby, the resistance at the time of the minute vibration can be reduced.

Next, the operation when torsional vibration having a large deviation angle (hereinafter referred to as large vibration) is transmitted will be described. First flywheel 2 and the seal plate 5 from the free state shown in FIG. 8 is a began twisted in R ₂ side with respect to the driven plate 15. Then, the slide stopper 22 moves together with the first flywheel 2 to the R ₂ side. When the stopper portion 22b comes into contact with the bent portion 23a of the seal member 23, the slide stopper 2
2 continues to move to the R ₂ side together with the sealing member 23.
Then, as shown in FIG. 7, the small sub-chamber 25B is reduced,
The small compartment 25A is expanded. Projection 15c while sandwiching the bent portion 23a R ₁ side of the stopper portion 22b is between
9, the slide stopper 22 and the seal member 23 are locked by the protrusion 15 c of the driven plate 15 as shown in FIG. 9. From this state further R
_When the twisting operation to the _second side is continued, the Oita chamber 24B is reduced and the Oita chamber 24A is expanded. At this time, the viscous fluid Oita chamber 24B slide stopper 22 can not flow to the R ₂ side by the contact of the bent portion 23a and the protrusion 15c, through the choke C R ₁ side Oita chamber 2
It flows to 4A (arc-shaped fluid chamber B ₁ of R ₁ side). When the viscous fluid flows through the choke portion C, a large viscous resistance occurs. At this time, the seal member 23 is urged radially inward by the pressure generated in the Oita chamber 24B. As a result, the seal member 23 is connected to the protrusion 2 of the first flywheel.
d and the protruding portion 5b of the seal plate 5. As a result, the sealing performance of the fluid chamber B is improved and a large viscous resistance can be ensured, and a frictional resistance is generated between the fluid chamber B and the protrusions 2d and 5d of the seal member 23. Incidentally, the sealing member 23 is longer than the circumferential length of the two slide stopper 22, R ₂ of R ₁ side bent portion 23a and the slide stopper 22 of the sealing member 23 in the state of FIG. 10
A gap is secured between the stopper and the side stopper. Therefore, the viscous fluid flows smoothly from the slide stopper 22 into the large chamber 24A.

[0031] from the position shown in FIG. 10, when the first flywheel 2 and the seal plate 5 is screwed to the R ₁ side, it passes through the neutral position, performs the inverse operation as Figures 8-10. As described above, a large viscous resistance and a frictional resistance are obtained during a large vibration. In addition, when the torsion angle is increased, the sheet member 18 of the coil spring 17 comes into full contact with the end of the window 15b, so that the rigidity is increased. In other words, in the case of large vibration, high rigidity and large resistance characteristics are obtained, and vibration during tip-in and tip-out (large vibration before and after the vehicle body caused when the accelerator pedal is suddenly operated) is effectively attenuated. it can.

As shown in FIG. 10, the micro-vibration is transmitted with the first flywheel 2 is twisted a predetermined angle R ₂ side with respect to the driven plate 15. Then, the slide stopper 22 has the stopper portion 22b formed with the protrusion 15.
The reciprocating twisting operation is repeated with respect to the protrusion 15c within the angle range where the protrusion 15c abuts on the protrusion 15c. In this case, only a small viscous resistance is generated, and the torsional vibration having a small deviation angle can be effectively absorbed. That is, even if the torsion angle between the first flywheel 2 and the driven plate 15 is large, a small viscous resistance can be generated with respect to torsional vibration having a small deviation angle.

The first flywheel 2 and the seal plate 5 are omitted from the conventional fluid chamber housing and drive plate.
The following two advantages can be obtained by the structure in which the fluid chamber B is formed by the above. The first advantage is that the flywheel assembly 1
Is that the number of components of the viscous damping part 9 is reduced and the structure is simplified. A second advantage is that the cross-sectional area of the annular fluid chamber B is increased by about 1.5 times. Thereby, the viscous resistance when the fluid passes through the choke portion C increases.

Further, the sealing member 23 is provided in the Oita chamber 24A,
Since the inner peripheral side of 24B is sealed, it is not necessary to form a sealing groove in the driven plate 15, and as a result, there is no need to improve the accuracy of the gap between the mating surfaces of the two driven plates 15A and 15B. I have. Conventionally, unless the precision of the gap between the mating surfaces is improved, a viscous fluid leaks from the gap and a large viscous resistance cannot be obtained. Further, since the seal member 23 is sandwiched between the protrusions 2d and 5b and the stopper 21 and the slide stopper 22, it is difficult for the seal member 23 to be deformed or to fly outward in the radial direction even when a centrifugal force is applied. Further, the bent portion 23a of the seal member 23 is provided with the protrusion 15c and the slide stopper 22.
Of the slide stopper 22 and the projection 15c at the time of torsional vibration having a large deviation angle is improved. Further, since both ends of the seal member 23 are free from other members in the circumferential direction, even if the seal member 23 is deformed due to thermal expansion, it functions without being damaged.

Further, since the caulked portion 5a of the seal plate 5 is caulked on the outer periphery of the first flywheel 2,
Even if pressure is generated in the fluid chamber B, the seal plate 5 does not separate from the end face of the outer peripheral annular wall 2b. As a result, the sealing performance of the fluid chamber B is improved. In addition, since the side surface of the slide stopper 22 is omitted, the slide stopper 22 can be easily attached to and detached from the protrusion 15c of the driven plate 15 during assembly or removal. In addition, since the side surface of the projection 15c does not slide with the slide stopper 22, the conventionally required machining of the projection 15c becomes unnecessary, and the driven plate 15 can be manufactured only by pressing.

The seal plate 5 is connected to the first flywheel 2
In a state before assembling, the outer peripheral portion of the seal plate 5 is formed with a cylindrical portion extending toward the engine. Roll caulking is performed by a caulking device in a state where the cylindrical portion covers the annular portion 2g of the first flywheel 2. as a result,
The cylindrical portion is bent so as to enclose the annular portion 2g, and becomes the caulked portion 5a. Second Embodiment In the second embodiment shown in FIGS. 11 to 13, the same reference numerals are used for the same structure as the first embodiment, and different reference numerals are used for different parts. Hereinafter, only different structures will be described. (1) Structure of Slide Stopper The slide stopper 22 has a side wall 22b that comes into contact with both side surfaces of the protrusion 15c. (2) Sealing structure of fluid chamber An annular projection 101 is formed on the protruding portion 2d by turning. In addition, 1 constituting the driven plate 15
On the pair of plates 115A and 115B, concave and convex portions formed by pressing at positions corresponding to the protrusions 101 are formed. That is, the first driven plate 115A is formed with the annular convex portion 102a and the annular concave portion 102b. The second driven plate 115B has an annular convex portion 103a and an annular concave portion 103b.
The annular convex portion 102a of the first driven plate 115A is fitted in the annular concave portion 103b of the second driven plate 115B. Thereby, the first driven plate 115
The sealing performance of the mating surface between A and the second driven plate 115B is improved.

The projection 101 is provided on the first driven plate 11
5A is fitted in the annular recess 102b. Also, the second
The annular projection 103a of the driven plate 115B is in contact with the inner peripheral side of the projection 5b of the seal plate 5. As described above, the first flywheel 2 and the driven plate 1
The opening D of the annular fluid chamber B is sealed by the engagement between the projections and the recesses formed on the seal plate 5 and the seal plate 5.

In the viscous damping mechanism according to the present invention, the seal portion
By using a material, the structure can be simplified.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view of a flywheel assembly according to a first embodiment.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a partially enlarged view of FIG. 1;

FIG. 4 is a partially enlarged view of FIG. 1;

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

FIG. 6 is a view corresponding to FIG. 5 showing one state of a twisting operation.

FIG. 7 is a view corresponding to FIG. 5, showing one state of a twisting operation.

FIG. 8 is a partially enlarged view of FIG. 2;

FIG. 9 is a view corresponding to FIG. 8 showing one state of a twisting operation.

FIG. 10 is a view corresponding to FIG. 8 showing one state of the twisting operation;

FIG. 11 is a schematic longitudinal sectional view of a flywheel assembly according to a second embodiment, corresponding to FIG. 1;

FIG. 12 is a view corresponding to FIG. 2 in a second embodiment.

FIG. 13 is a view corresponding to FIG. 3 in the second embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Flywheel assembly 2 1st flywheel 3 2nd flywheel 5 Seal plate 8 Elastic connection mechanism 9 Viscous damping part B Fluid chamber C Choke part D Opening

Claims (2)

(57) [Scope of request for utility model registration] 1. A torsional vibration is reduced by generating viscous resistance.
An annular fluid chamber (B) having an annular opening (D), which is a viscous damping mechanism (9) for damping.
A first rotating member (2, 5), which is arranged on the opening side of the first rotating member,
A plurality of projections (15c) extending from the portion into the fluid chamber.
A second rotating member (15), which is disposed in the fluid chamber and has a predetermined angular range with respect to the projection.
Cap-shaped slides movably engaged within the enclosure
A topper (22) disposed in the fluid chamber so as to be in close contact with the opening;
An arcuate plate-like member extending between a number of slide stoppers,
The slide stopper formed at both ends of the plate member
And an engaging portion (23a) extending inward.
In the state of contact with the slide stopper,
The body does not flow and the opening created by the pressure in the fluid chamber
Seal members (23) capable of sealing parts
And the plurality of slides rotate integrally with the first rotation member.
A chalk portion disposed between the topper and the plate-like member;
And a plurality of stoppers (21) forming (C) . 2. The sealing member is between the second rotating member and the second rotating member.
The opening is sealed while securing a gap in the opening.
2. The viscous damping mechanism according to 1.