JP2606701Y2 - 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 between the engine and the transmission of a motor vehicle. The flywheel assembly includes a first flywheel connected to an engine-side crankshaft, a second flywheel mounted with a clutch and rotatably supported by the first flywheel, and a second flywheel. A rotating driven plate, an elastic connection mechanism for elastically connecting the first flywheel and the driven plate in a circumferential direction, and a viscous damping unit including a fluid chamber disposed between the first flywheel and the driven plate. It is composed of The fluid chamber is constituted by a fluid chamber housing fixed to the 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 formed on the driven plate to seal the inside of the fluid chamber. are doing.

[0003] The outer peripheral end of the driven plate is inserted into the fluid chamber housing from the inner peripheral side, and a plurality of projections are formed on the outer periphery of the driven plate at equal intervals in the circumferential direction. Further, a cap-shaped slide stopper that covers the protrusion of the driven plate from the outer peripheral side is disposed in the fluid chamber. The slide stopper is movable in the circumferential direction within a predetermined angle range with respect to the projection of the driven plate. Further, a choke portion through which the fluid passes when the slide stopper relatively moves within the first flywheel is formed in the viscous fluid chamber.

In such a structure, torsional vibrations having different deflection angles (torsional angles) are transmitted to the flywheel assembly from the vehicle engine. Different resistances are generated and attenuated for different torsional vibrations. When the torsional vibration having a small deflection angle is transmitted, the slide stopper repeats the reciprocating operation with the first flywheel with respect to the protrusion of the driven plate. At this time, since there is no relative movement between the slide stopper and the first flywheel, no fluid flows through the choke. Therefore, torsional vibration having a small deviation angle can be effectively absorbed.

Further, when torsional vibration having a large deflection angle is transmitted, the slide stopper engages with the projection of the driven plate, and rotates relative to the first flywheel. As a result, the fluid flows through the choke, and a large viscous resistance is generated. Therefore, torsional vibration having a large deviation angle is effectively attenuated.

[0006]

SUMMARY OF THE INVENTION In the above conventional configuration,
Since the driven plate and the housing are in sealing engagement, there are the following disadvantages. That is, when the torsional vibration having a small deflection angle is transmitted, the driven plate and the housing slide and frictionally slide. Therefore, the resistance increases. Further, when torsional vibration having a large deflection angle is transmitted, the sealing performance of the seal engagement portion is not ensured, and the viscous resistance cannot be sufficiently increased.

An object of the present invention is to effectively dampen different types of torsional vibrations.

[0008]

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
Also than the first rotary member, a second rotary member of to
And multiple slide stoppers and multiple stoppers
It has. The first rotating member has an annular opening.
An annular fluid chamber filled with fluid is formed. Second
The rotating member is disposed on the opening side of the first rotating member, and has an opening.
A plurality of protrusions extending from the portion into the fluid chamber. Multiple switches
The rider is located in the fluid chamber and at a predetermined angle to the protrusion
A plurality of cap portions movably engaged within the range;
Extending in the circumferential direction from both ends of the
And an arc-shaped seal portion which is arranged so as to be able to be in close contact. Multiple
Stops integrally with the first rotating member to form a plurality of switches.
Located between ride stoppers and between the seals
Form a chalk.

[0009]

[0010]

In the torsional vibration damping mechanism according to the present invention, the displacement angle
When a small degree of torsional vibration occurs, the slide stopper
-Rotates integrally with the first rotating member. At this time cho
No large viscous drag occurs because the fluid does not pass through the
No. Also, unlike the conventional case, the seal portion is provided on the second rotating member.
Since it is not provided, the first rotating member and the second rotating member
No frictional resistance occurs between the two. Large displacement angle torsion
When vibration occurs, the slide stopper is moved to the second rotating member.
Of the first rotating member
I do. As a result, the fluid passes through the choke and
Resistance occurs. At this time, the pressure generated in the fluid chamber
The sealing portion is brought into close contact with the opening of the fluid chamber. others
Therefore, the sealing property is improved and a large viscous resistance is obtained.

When torsional vibration with a small deviation angle is transmitted,
The stopper member rotates integrally with the first flywheel.
At this time, since the fluid does not pass through the choke portion, no large viscous resistance is generated. Further, since a seal portion is not provided on the driven plate as in the related art, no frictional resistance is generated between the driven plate and the driving member. For this reason, when torsional vibration with a small deviation angle is transmitted, the vibration is attenuated with a very small viscous resistance.

When torsional vibration having a large deflection angle is transmitted,
The stopper member is engaged with the driven plate and twisted relative to the first flywheel. As a result, the fluid passes through the choke, and a large viscous resistance is generated.
At this time, the stopper member is brought into close contact with the opening of the fluid chamber due to the pressure generated in the fluid chamber. For this reason, the sealing property is improved, and a large viscous resistance is generated.

[0013]

1 and 2 show a flywheel assembly 1 according to an embodiment of the present invention. The flywheel assembly 1 is a device that is arranged between an engine of a vehicle and a transmission and transmits torque from the engine to the transmission. 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.
Of the rotation axis, the R ₁ direction in FIG. 2 is a rotational direction of the flywheel 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. A driven plate 15 engaged so as to rotate integrally, an elastic connecting mechanism 8 for elastically connecting the driven plate 15 and the first flywheel 2 in a circumferential direction, a first flywheel 2 and the driven plate 1
5 and a viscous damping portion 9 for damping torsional vibration therebetween.

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 bearing 4 is mounted on the outer periphery of the boss 2a. Bearing 4
Is held on the transmission-side end face of the boss 2a by a retaining plate 31 held by the head of a bolt 11 penetrating the boss 2a. The retaining plate 31 is attached to the first flywheel 2 by rivets 32.
It is fixed to. The bolt 11 penetrates a bolt hole 2c formed in the boss 2a, and fixes the first flywheel 2 to a crankshaft (not shown).

The second flywheel 3 is a substantially disk-shaped member and has a boss 3a at the center. Boss part 3a
Protrudes toward the first flywheel 2 and covers the boss 2 a of the first flywheel 2. A bearing 4 is mounted on the inner periphery of the boss 3a. That is, the annular receiving portion 3b provided on the inner peripheral side of the tip of the boss portion 3a is in contact with the engine side of the bearing 4, and the snap ring 13 attached on the inner peripheral side of the boss portion 3a is connected to the transmission of the bearing 4. Abuts on the side. The bearing 4 is of a lubricant sealing type and seals an inner peripheral portion of an annular space A described later. The boss 3 a is caulked to the inner peripheral end of the driven plate 15 by a plurality of rivets 34. Further, a transmission-side end surface of the second flywheel 3 is a friction surface 3d on 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 periphery of the seal plate 5 is formed by a plurality of bolts 7 arranged at equal intervals in the circumferential direction.
It is fixed to. 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. Between the outer peripheral surface of the seal plate 5 and the inner peripheral surface of the outer peripheral annular wall 2b,
An annular seal member 14 is provided. Further, between the inner peripheral end of the seal plate 5 and the outer peripheral surface of the boss 3a of the second flywheel 3, an annular seal member 30 for sealing the annular space A is arranged.

The driven plate 15 is a disk-shaped member disposed in the annular space A. Driven plate 15
The inner peripheral end is caulked to the boss 3a of the second flywheel 3 by a rivet 34. The driven plate 15 is movable in the axial direction with respect to the second flywheel 3. The driven plate 15 has a plurality of window holes 15b extending in the circumferential direction at intervals in the circumferential direction. Further, a plurality of projections 15c protruding radially outward from a portion between the window holes 15b are formed on the outer peripheral surface 15d of the driven plate 15. Protrusion 15
c is inserted into a fluid chamber B of a viscous damping unit 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 1
The sheet 7 and the sheet member 18 are disposed in the window hole 15b of the driven plate 15. Each coil spring 17
Is composed of a large coil spring 17a and a small coil spring 17b arranged inside the large coil spring 17a. A spring receiving groove 2h (FIG. 1) is formed in a portion corresponding to the window hole 15b of the driven plate 15 on a side surface of the first flywheel 2 on the radially intermediate transmission side. One end of the sheet member 18 is in contact with both circumferential ends of the spring receiving groove 2h. Thus, the first flywheel 2 and the driven plate 15 are elastically connected in the circumferential direction via the elastic connecting mechanism 8. In the free state shown in FIG. 2, the seat member 18 is connected to the end of the spring receiving groove 2h of the first flywheel 2 and the driven plate 1
5, only the inner peripheral portion is in contact with the end of the window hole 15b. That is, the coil spring 17 is housed in the spring receiving groove 2h and the window hole 15b in an uneven contact state.

Next, the viscous damping unit 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.
The annular fluid chamber B is formed on the outer periphery of the space A by the transmission-side end surface of the first flywheel 2, the inner peripheral surface of the outer annular wall 2b, and the engine-side end surface of the seal plate 5. An annular recess 2g formed by cutting is formed on the outer peripheral side of the spring receiving groove 2h of the first flywheel 2. In the seal plate 5, the annular recess 2g of the first flywheel 2 is formed.
The annular concave portion 5a is formed by cutting at a portion corresponding to. An opening D that opens radially inward in the fluid chamber B and extends in the circumferential direction is formed between the annular concave portions 2g and 5a.

The outer periphery of the driven plate 15 is disposed between the annular recesses 2g and 5a. 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 bolt 7 passes. A gap is provided between the bolt 7 and the through hole of the stopper 21.

The stopper 21 divides the annular fluid chamber B into five solid fluid chambers B ₁ (FIG. 2). At the center of the solid fluid chamber B _1, projections 15 of the driven plates 15
c is arranged. Each solid fluid chamber B within _1, the slide stopper 22 is arranged to cover the outer peripheral side projections 15c of the driven plate 15. The slide stopper 22 includes a cap portion 2 that covers the protrusion 15c from the outer peripheral side.
2a and a seal portion 22b extending outward from the cap portion 22a in the circumferential direction. Cap part 22
a is an outer peripheral portion 22c having an arcuate surface coinciding with the inner peripheral surface of the outer peripheral annular wall 2b of the first flywheel;
Stopper portion 22d extending radially inward from both ends of c
And a side surface 22e abutting on both end surfaces of the projection 15c. Both stopper portions 22d are separated from the protrusion 15c by a predetermined angle. That is, the slide stopper 21 is movably engaged with the driven plate 15 within a predetermined angle range. As shown in FIG.
A large gap S in the axial direction is secured between e and the projection 15c of the driven plate 15. The seal portion 22b is
It has an arc-shaped surface that matches the outer peripheral surface 15d of the driven plate 15. Arc-shaped projections 22f extending in the circumferential direction are formed on both axial sides of the seal portion 22b. The arc-shaped projection 22f is also formed on the inner peripheral side of the side surface part 22d. The arc-shaped projections 22 f are inserted into the annular recess 22 g of the first flywheel 2 and the annular recess 5 a of the seal plate 5. In this state, a predetermined gap is secured between the seal portion 2b and the outer peripheral surface 15d of the driven plate 15.

The cap portion 22 of the slide stopper 22
a is the respective solid fluid chamber B ₁ is divided into a Oita chamber 24B Oita chamber 24A and the R ₁ side of the R ₂ side. Furthermore, in the cap portion 22a of the slide stopper 22 is small compartments of R ₂ side by the projection 15c of the driven plate 15 25
It is divided into a small compartment 25B of A and R ₁ side. A predetermined gap is secured between the seal portions 22b of the adjacent slide stoppers 22. This gap is a return hole H through which the viscous fluid can flow between the fluid chamber B and the inner annular space A. Note that a portion between the outer peripheral surface of the seal portion 22b and the stopper 21 is a choke portion C. When a viscous fluid passes through the choke portion C, a large viscous resistance is generated.

Next, the operation will be described. When torque is input to the first flywheel 2 from a crankshaft (not shown) on the engine side, the torque is transmitted to the driven plate 15 via the coil spring 17 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, the operation when the torsional vibration is transmitted is described by the driven plate 15 (the second flywheel 3).
Will be described as an operation in which the first flywheel 2 is twisted with respect to the other member (not shown) so that it cannot rotate.

First, the operation when torsional vibration (hereinafter referred to as "micro vibration") having a small deviation angle, in which the stopper portion 22d of the slide stopper 22 does not abut on the projection 15c of the driven plate 15, will be described. First flywheel 2 and the seal plate 5 and twisted R ₁ side from the free state shown in FIG. Then, the slide stopper 22 is moved to the R ₁ side together with the first flywheel 2. As a result, as shown in FIG. 4, the small compartment 25A is reduced and the small compartment 25B is expanded in the slide stopper 22. At this time, the viscous fluid in the small compartments 25A and 25B can flow into the annular space A through the gap between the slide stopper 22 and the driven plate 15, and on the contrary, the viscous fluid in the annular space A Can flow into.

[0027] Returning from the state shown in FIG. 4 to the neutral state shown in FIG. 3, additionally the first flywheel 2 is twisted R ₂ side. Then, the slide stopper 22 moves together with the R ₂ side of the first flywheel 2. Thereafter, FIG.
As shown in FIG. 5, the small compartment 25B is reduced and the small compartment 25A is expanded. In the case of the minute vibration described above, since the slide stopper 22 rotates integrally with the flywheel 1, no viscous fluid flows through the choke portion C, and no large viscous resistance is generated. Further, since there is no need to provide a sealing groove in the driven plate 15, frictional resistance is less likely to be generated between the input side member (the first flywheel 2, the seal plate 5) and the driven plate 15 during a minute vibration. . Specifically, the driven plate 15
Outer peripheral surface 15d and seal portion 2 of slide stopper 22
2b and a driven plate 1
5 and the side 2 of the slide stopper 22
Since the large axial gap S is provided between the slide stopper 22 and the driven plate 15 in the case of torsional vibration having a small deviation angle, the slide stopper 22 and the driven plate 15 repeat the relative torsional operation. No frictional resistance occurs between them.

Further, in this case, the coil spring 17 expands and contracts in a biased state with respect to the window hole 15b of the driven plate 15, and a low rigidity state is obtained. That is, in the case of minute vibration, characteristics of low rigidity and small resistance are obtained, and generation of abnormal noise such as gear rattle and muffled sound can be effectively suppressed. Next, an operation when torsional vibration having a large deviation angle (hereinafter, referred to as large vibration) is transmitted will be described.

The first flywheel 2 and the seal plate 5 from the free state shown in FIG. 6 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. Then, as shown in FIG. 5, the small compartment 25B is reduced and the small compartment 25A is expanded. When R ₁ side of the stopper portion 22d abuts against the projection 15c, as shown in FIG. 7, the slide stopper 22 is driven plates 1
5 is locked to the projection 15c. When twisting operation from this state to further R ₂ side is continued, the relative rotation between the first flywheel 2 and the slide stopper 22 occurs. When Oita chamber 24A Oita chamber 24B is reduced is gradually being expanded, viscous fluid Oita chamber 24B flows Oita chamber 24A of R ₁ side through the choke portion C.
When the viscous fluid flows through the choke portion C, a large viscous resistance is generated. At this time, the seal portion 22b of the slide stopper 22 is strongly pressed against the annular concave portion 2b of the first flywheel 2 and the annular concave portion 5a of the seal plate 5 due to the pressure generated in the Oita chamber 24B, and the two slide frictionally. At the same time, the sealing performance of the fluid chamber B is improved.

During the operation, the viscous fluid is quickly filled into the Oita chamber 24A from the annular space A through the return hole H. From the position shown in FIG. 8, when the first flywheel 1 and the seal plate 5 is screwed to the R ₁ side, it passes through the neutral position, performs the inverse operation and 6-8.
As described above, a large viscous resistance is obtained during a large vibration. In addition, when the torsion angle increases, the sheet member 18 of the coil spring 17 comes into full contact with the end of the window hole 15b, so that the obtained rigidity is increased. That is, in the case of torsional vibration having a large deflection angle, characteristics of high rigidity and high resistance are obtained, and vibration at the time of tip-in and tip-out can be effectively attenuated.

The first flywheel 2 as shown in FIG. 8 is in a state of twisted constant angle R ₂ side with respect to the driven plate 15, the micro-vibration is transmitted. Then, the slide stopper 22 has the stopper portion 22d with the protrusion 15c.
The reciprocating torsion operation is repeated with respect to the projection 15c within the angle range where the projection 15c abuts. At this time, only a small viscous resistance is generated, and the minute vibration can be effectively absorbed. That is, the first
Even if the twist angle between the flywheel 2 and the driven plate 15 is large, a small viscous resistance can be generated with respect to minute vibration.

The following two advantages can be obtained by the conventional structure in which the fluid chamber B is formed by the first flywheel 2 and the seal plate 5 without the fluid chamber housing and the drive plate. A first advantage is that the number of components constituting the viscous damping part 9 in the flywheel assembly 1 is reduced,
That is, 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 is increasing.

Further, since the slide stopper 22 seals the inner peripheral sides of the large chambers 24A and 25B, the sealing mechanism for the fluid chamber B is greatly simplified. In this embodiment, the driven plate 15 and the second flywheel 3 are engaged by rivets 34. Therefore, there is no need to form serrations or the like on the two members for the engagement between the driven plate 15 and the second flywheel 3, thereby reducing the manufacturing cost.

Conventionally, the driven plate 15 and the second flywheel 3 can be moved in the axial direction by serration or the like because the driven plate 15 is formed with a sealing groove and has a dimension corresponding to the axial dimension of the driven plate 15. This is because the required accuracy was high. In this embodiment, there is no need to provide a sealing groove in the driven plate 15,
The required accuracy of the axial dimension may be low, and the driven plate 15 and the second flywheel 3 are connected with rivets 34.
There is no problem even if fixed at.

[0035]

In the flywheel assembly according to the present invention, different types of torsional vibrations can be effectively attenuated because the slide stopper has a seal portion for sealing the fluid chamber.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view of a flywheel assembly according to an embodiment of the present invention.

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

FIG. 3 is a partially enlarged view of FIG. 2;

FIG. 4 is a view corresponding to FIG. 3, showing one state of a twisting operation.

FIG. 5 is a view corresponding to FIG. 3, showing one state of a twisting operation.

FIG. 6 is a partially enlarged view of FIG. 2;

FIG. 7 is a view corresponding to FIG. 6 showing one state of a twisting operation.

FIG. 8 is a view corresponding to FIG. 6, showing one state of a twisting operation.

[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 15 Driven plate B Annular fluid chamber 22 Slide stopper 22a Cap part 22b Seal part C Choke part D Opening

Claims (1)

(57) [Scope of request for utility model registration] 1. A torsional vibration is reduced by generating viscous resistance.
A viscous damping mechanism (9) for decay, which has an annular opening (D) and is filled with a fluid;
A first rotating member (2, 5) in which a chamber (B) is formed; and a first rotating member disposed 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.
A plurality of cap portions (22a) movably engaged within the enclosure
And extending in the circumferential direction from both ends of the
An arc-shaped sheet arranged in the body chamber so as to be able to adhere to the opening.
Slide stoppers having a slide portion (22b)
(22), the plurality of slides rotate integrally with the first rotating member, and
A chalk portion between the topper and the seal portion
(C) a plurality of stoppers (21) to be formed.
Viscous damping mechanism (9).