JPH0727172A - Fly wheel assembly - Google Patents

Abstract

PURPOSE:To ensure desired viscous resistance through sufficient supply of fluid to a fluid chamber by a method wherein a passage for supply of fluid communicated with a fluid chamber on an outer periphery through a window hole to contain a resilient member is formed in the intermediate part in a radial direction of a driven member. CONSTITUTION:When torque is inputted to a first fly wheel 2 from a member on the engine side, torque is transmitted to a second member 6 to a first member through resilient members 12a and 12b to rotate a second fly wheel. When twist vibration is transmitted and relative rotation is generated between a first fly wheel 2 and a second fly wheels, the resilient members 12a and 12b repeat expansion and contraction and a viscous damping part causes the generation of viscous resistance to damp contraction or twist vibration. In this case, viscous fluid leaks from a fluid chamber 7a and viscous fluid is supplied in the fluid chamber 7 through the window hole 6b of the second member 6 by means of a passage 6d for supplying fluid. In which case, the window hole 6b of the second member 6 is a place where a most amount of viscous fluid is contained and a sufficient amount of viscous fluid is supplied in the fluid chamber 7a and a desired viscous resistance force is generated.

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 pair of flywheels which are rotatably connected to each other and provided with a viscous damping portion for damping torsional vibrations between the flywheels. Flywheel assembly.

[0002]

2. Description of the Related Art In a flywheel used for an automobile engine, for example, a split type flywheel (flywheel assembly) has been proposed. The split-type flywheel is arranged between the first flywheel and the second flywheel, and both flywheels are elastically connected to each other in the circumferential direction. And a viscous damper mechanism for damping the torsional vibration of the.

The viscous damper mechanism includes a drive plate connected to the first flywheel, a driven plate connected to the second flywheel, a torsion spring provided between the plates, and a viscous damping portion. There is. The viscous damping part is formed on the outer peripheral part of the space formed by the first flywheel and the drive plate, and has an annular fluid chamber filled with the viscous fluid and a choke through which the fluid passes. Then, when the two flywheels rotate relative to each other, viscous fluid passes through the choke to generate viscous resistance, and the torsional vibration is attenuated.

[0004]

In the viscous damper mechanism having the above structure, the viscous fluid leaks from the fluid chamber, so that the fluid is replenished from the space on the inner peripheral side thereof. This replenishment is performed through a replenishing passage such as a cutout portion of the case forming the fluid chamber. However, the conventional structure has a problem in that the viscous fluid is not replenished in the fluid chamber through the replenishment passage, and a desired viscous resistance cannot be obtained.

An object of the present invention is to replenish a fluid chamber with a sufficient amount of viscous fluid so that a desired viscous resistance can be obtained.

[0006]

A flywheel assembly according to the present invention includes a first flywheel, a second flywheel rotatably supported by the first flywheel, first and second members, and an elastic member. It has a member and a viscous damping part. The first member is connected to the first flywheel, and secures a space for accommodating the viscous fluid between the first member and the first flywheel. The second member is connected to the second flywheel, is disposed in the space, and forms a fluid chamber filled with a viscous fluid inside the outer periphery with the first flywheel and the first member. The elastic member includes first and second elastic members.
The members are elastically connected. The viscous damping unit moves the viscous fluid in the fluid chamber when the first and second members rotate relative to each other to generate viscous resistance. Then, the second member has a window hole for accommodating the elastic member in the middle portion in the radial direction,
It has a passage for fluid replenishment that leads from the window hole to the fluid chamber.

[0007]

In the flywheel assembly according to the present invention, when torque is input from the engine side member to the first flywheel, the torque is transmitted from the first member to the second member via the elastic member, and further, 2 Rotate the flywheel. The torsional vibration is transmitted to the first flywheel and the second flywheel.
When relative rotation occurs with the flywheel, the elastic member repeatedly expands and contracts, and the viscous damping unit generates viscous resistance to damp torsional vibration. At this time, the viscous fluid leaks from the fluid chamber, but the viscous fluid is replenished into the fluid chamber through the fluid replenishment passage from the window hole of the second member. Where the second
Since the window hole of the member is a place where the viscous fluid is most accumulated, the fluid chamber is replenished with a sufficient amount of the viscous fluid and a desired viscous resistance force is obtained.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows the entire power transmission device in which an embodiment of the present invention is adopted. In the following description, the left side (engine side) of FIG. 1 is the front and the right side (transmission side) is the rear. The power transmission device mainly includes a flywheel assembly 1, a clutch disc 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 arranged between them. The first flywheel 2 is fixed to the shaft end of the crankshaft of the engine with bolts 25. The second flywheel 3 has a friction surface 3 against which the friction member of the clutch disc 101 is pressed to the rear side surface.
a. The clutch cover of the clutch cover assembly 102 is fixed to the outer peripheral portion of the second flywheel 3 on the friction surface 3a side.

The first flywheel 2 is a generally disk-shaped member, and has a boss portion 2a projecting rearward at the center,
A disc portion 2b extending outward from the boss portion 2a and integrally formed
And a rim portion 2c extending rearward from the outer peripheral side of the disc portion 2b. An annular recess is formed between the boss portion 2a and the rim portion 2c, and the viscous damper mechanism 4 is housed in this recess. Two rolling bearings 22 and 23 arranged in the axial direction are mounted on the outer periphery of the boss portion 2a. Bearings 22, 23
Is a lubricant-sealed type in which seal members are mounted on both sides, and the backward movement is restricted by a snap ring 24 fitted on the outer peripheral surface of the boss portion 2a.

The second flywheel 3 is a generally disk-shaped member, and the viscous damper mechanism 4 has an inner peripheral portion by means of bolts 21.
It is detachably fixed to the driven member 6 (described later). Further, the inner peripheral end of the second flywheel 3 also regulates the rearward movement of the rolling bearings 22 and 23. Also, the second
The clutch disc 10 is provided on the inner peripheral portion of the flywheel 3.
A hole 3b that connects the first side and the viscous damper mechanism 4 side is formed.

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 of the viscous damper mechanism 4 via rolling bearings 22 and 23. A disk-shaped driven member 6 supported by the flywheel 2, a coil spring 12a that elastically connects the driven member 6 and the input side member including the first flywheel 2 and the drive plate 5 in the circumferential direction, 12
b and 12c, and a viscous damper portion 7 for damping the torsional vibration by viscous force of the fluid. In the viscous damper mechanism 4, a viscous fluid is filled in the space formed by the first flywheel 2, the drive plate 5, and the driven boss portion 6a of the driven member 6. The drive plate 5 has a rim portion 2c of the first flywheel 2 with a plurality of bolts 19 at the outer peripheral end.
An annular seal member 20 is disposed between the inner peripheral end and the driven boss portion 6a of the driven member 6. The seal member 20 and the bearings 22, 23 described above
Sealing member seals the radially inner peripheral end of the space.

The driven member 6 is a disk-shaped casting member, and is arranged between the disk portion 2b of the first flywheel 2 and the drive plate 5. As described above, the driven member 6 has the driven boss portion 6a extending rearward on the inner peripheral portion. Rolling bearings 22 and 23 are mounted on the inner peripheral side of the driven boss portion 6a, and the inner peripheral portion of the second flywheel 3 is fixed by bolts 21. The driven member 6 is formed with six window holes 6b at an intermediate portion in the radial direction at intervals in the rotation direction. The window hole 6b extends in the rotation direction, and the coil springs 12a, 12b and 12c are housed in the window hole 6b.

As shown in FIG. 3, of the six window holes 6b of the driven member 6, the two window holes 6b facing each other in the radial direction.
A coil spring 12c is provided in the (vertical window in FIG. 3).
Is housed. The coil spring 12c is in contact with both end surfaces in the circumferential direction of the window hole 6b via the spring seat 13. A coil spring 12a having a large diameter and a coil spring 12b having a small diameter 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 outer peripheral surface 3 and the circumferential end surfaces of the window hole 6b. The spring seat 13 is the outer peripheral support 1
3a and a central boss portion 13b, the large diameter coil spring 12a has an outer peripheral portion supported by the outer peripheral support portion 13a of the spring seat 13, and the small diameter coil spring 12b has an inner peripheral portion having a spring seat 13a. Boss part 1
It is supported by 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.

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

The viscous damper portion 7 includes an annular fluid chamber 7a,
It is mainly composed of a resin molding stopper member 8 arranged in the annular fluid chamber 7a and a slide stopper 10. The annular fluid chamber 7a includes the first flywheel rim portion 2c.
Of the driven member 6, the first flywheel disc portion 2b and the drive plate 5 and is filled with a viscous fluid. The stopper members 8 are provided at six positions 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 connected to the first flywheel 2 and the drive plate 5 by a pin 9 so as not to rotate relative to each other. In addition,
A choke C ₂ is formed between the radially inner surface of the stopper member 8 and the outer peripheral surface of the driven member 6 so that the viscous fluid can pass between the divided chambers. In the driven member 6, between the window holes 6b at the outer peripheral edge, a recessed portion 6c that is recessed inward in the radial direction is formed. A fluid replenishment hole 6d that extends radially outward from the center of the window hole 6b and opens into the annular fluid chamber 7a is formed in the middle of the adjacent recesses 6c. This 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.
And is arranged between each stopper member 8 and
-The chamber obtained by the member 8 is further referred to as a first Oita chamber 14.
It is divided into a second large branch chamber 15. Slide stopper
10 has an arcuate outer peripheral surface along the inner peripheral surface of the rim 2c.
The inner peripheral surface has an arc shape along the outer peripheral surface of the driven member 6.
Has become. Slide stopper 10 is radially inward
It has a protrusion 10a protruding in the center. Protrusion 10a
Is disposed in the recess 6c of the driven member 6, and the recess 6
The inside of c is divided into the first sub-compartment 16 and the second sub-compartment 17 in the rotating direction.
It is divided. In addition, the tip of the protrusion 10a and the bottom surface of the recess 6c
Between the first subcompartment 16 and the second subdivision 17
Chalk C that allows permeable fluid to pass₁Are formed. Chi
York C ₁Is choke C₂Larger flow passage cross-sectional area
Has been done. Further, the circumferential end surface of the recess 6c and the
Abut on the choke C₁Close slides
The topper protrusion 10a expands as it goes outward.
It is tilted at the same angle. This allows slides
The topper 10 moves in the circumferential direction to move the recess 6c in the circumferential direction.
If it touches the end face and continues to be pressed, slide stopper
A component force is generated to move the -10 radially outward.
Growling.

The inner side in the radial direction of the annular fluid chamber 7a is sealed by an annular sealing member 11 made of Teflon or a heat-resistant and abrasion-resistant resin. The seal member 11 is arranged 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, the one seal member 11 is movably arranged between the annular groove 2d formed in the first flywheel 2 and the end surface of the driven member 6. When no pressure is applied to the annular fluid chamber 7a, the seal member 11 is provided with an annular groove 2d as shown by a dotted line in the figure.
Although disposed inside, when pressure is applied to the annular fluid chamber 7a, the annular fluid chamber 7a 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 this structure, the driven member 6 is
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 machined by a lathe. By facilitating the processing as described above, the manufacturing cost is reduced. Since the slide stopper 10 is a molded product, the protrusion can be easily formed. 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 are provided.
Torque is transmitted to the second flywheel 3 via 2c and the like. At this time, when the torsional vibration is input from the engine side, the coil springs 12a, 12b, 12c repeatedly expand and contract, and the viscous damping portion 7 generates a viscous resistance force to damp the torsional vibration.

Next, the operation of the first flywheel 2 and the second flywheel 3 at the time of 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, it is assumed that the rotation is to the R ₁ side from FIG. 4 in the free state. The drive plate 5 rotates in the 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. As a result, the volume of the second sub-compartment chamber 17 becomes smaller and the volume of the first sub-compartment chamber 16 becomes larger at the same time. That is, with the movement of the slide stopper 10, the fluid in the second small compartment 17 flows to the first small compartment 16 through the choke C ₁ . Since the choke C ₁ has a large flow passage cross-sectional area, the viscous resistance is small. Further, in this small torsion angle range, only the coil spring 12c is compressed, and the coil springs 12a and 12b move to the spring seat 13
Is not compressed until it comes into contact with the window 6b surface of the driven member 6. In this way, in the range where the twist angle is small,
Low rigidity and small viscous force works.

When the twist angle toward the direction of rotation R ₁ becomes large, the projection 10a of the slide stopper 10 comes into contact with the circumferential end surface of the recess 6c of the driven member 6 (FIG. 6).
As a result, the choke C ₁ is closed, and thereafter the choke C ₂ functions. Since the projection 10a is pressed against the circumferential end surface of the recess 6c, a force A perpendicular to both contact inclined surfaces is generated.
Occurs. The force A can be decomposed into a component B in the circumferential direction and a component C in the outer radial direction. The component C and the centrifugal force push the slide stopper 10 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 way, 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 force is generated between them due to dry friction. This resistance force can be adjusted by changing the angles of both contact inclined surfaces.

When the twist angle further increases from FIG. 6 to FIG. 7, the compression of the coil springs 12a and 12b starts. Therefore, the torsional characteristic of the second stage having high rigidity can be obtained. At the same time, the fluid in the first large compartment 14 flows through the choke C ₂ to the second large compartment 15. Here, a large viscous resistance is obtained because the channel 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 force that has not been obtained in the past can be obtained.

Further, at this time, the stopper member 8 moves to the R ₁ side, so that the liquid supply hole 6d 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 compartment 15 due to the centrifugal force and the expanding suction force from the second large compartment 15. Window 6b
Since the inside is the portion where the most viscous fluid is accumulated inside the annular fluid chamber 7a in the radial direction, a sufficient amount of fluid can be returned to the annular fluid chamber 7a, and the annular fluid chamber 7a is deficient in fluid. Hard to do.

When the twist angle increases from FIG. 7 to FIG. 8, the stopper member 8 contacts the slide stopper 10. As a result, 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 torsion characteristic and the dotted line indicates the dynamic torsion characteristic. In the static torsional characteristics, the small hysteresis H ₁ region seen in the small torsional angle range is the angular range in which the slide stopper 10 is twisted with respect to the driven member 6 and the choke C ₁ functions. The large hysteresis torque H ₂ is a large hysteresis torque generated by the choke C ₂ . A small hysteresis torque H ₁ is observed in a region where the twisting angle is large because a small torsional vibration (for example, combustion fluctuation) occurs when the drive plate 5 is twisted by a certain angle with respect to the driven member 6. When it occurs, slide stopper 1
This is because 0 is separated from the driven member concave portion 6c in the circumferential direction and the choke C ₁ functions. In this way, a small hysteresis torque H ₁ can be generated irrespective of the relative angle between the drive plate 5 and the driven member 6, so that, for example, minute vibration during combustion fluctuation can be effectively damped.

In the dynamic torsional characteristic of this figure, the viscous force is much larger than that of the conventional one. The reasons for this are mainly as follows. A sufficient amount of fluid is returned to the annular fluid chamber 7a from the window 6a of the driven member 6, so that the viscous fluid is less likely to run short. ◎ The seal member 11 seals the annular fluid chamber 7a,
Furthermore, since the driven member 6 is an integral body, the amount of fluid leakage is reduced.

A dry frictional force generated by pressing the outer peripheral surface of the slide stopper 10 against the inner peripheral surface of the rim portion 2c is applied. In this way, a large viscous damping force works for a large torsion angle, so
The front-back vibration of the vehicle body during tip-in / tip-out and the vibration at engine start 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 portion 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 circumference of the boss portion 2a of the first flywheel 2. The seal member 11 is previously inserted into the annular groove 2d of the first flywheel 2. After mounting the driven member 6 on the first flywheel 2, the snap ring 24 is mounted on the boss portion 2a. Further, the driven member 6 includes a spring seat 13 and a coil spring 12.
Attach a, 12b and 12c. Then, the stopper member 8 is attached to the annular fluid chamber 7a by the pin 9, and the slide stopper 10 is inserted. Next, the drive plate 5 in which the seal member 11 is inserted in the annular groove is fixed to the rim portion 2c of the first flywheel 2 with the bolt 19. Then, the seal member 20 is inserted between the inner periphery of the drive plate 5 and the outer periphery of the driven boss portion 6a.

After assembling the viscous damper mechanism 4 as described above, the second flywheel 3 is fixed to the driven boss portion 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 only by removing or tightening the bolt 21. Moreover, since it is not necessary to attach and detach the bearings 22 and 23 and the seal member 20 when attaching and detaching the second flywheel 3, it is possible to prevent the life of the bearings 22 and 23 from being shortened and to use the seal member 20 for a long period of time. Other Embodiments 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 twisting characteristic. As shown in FIG. 10, when the fluid supply hole 51 is displaced toward the rotation direction R ₁ side, the slide stopper 1
When 0 comes into contact with the driven member 6 (the state of FIG. 6 of the above-described embodiment), the fluid supply hole 51 is opened to the first large compartment 14. Then, the choke C ₂ does not function until the stopper member 8 closes the fluid supply hole 51. In this way, the twisting characteristic can be adjusted by changing the position, size and number of the fluid supply holes.

As yet another embodiment, FIG. 11 shows an example in which the driven member and the driven boss portion are separate bodies. Here, the driven member of the above embodiment is composed of three driven plates 66. Wavy inner teeth 66 a are formed on the inner circumference of the driven plate 66, and wavy outer teeth that mesh with the wavy inner teeth 66 a are formed on the outer circumference of the driven boss 86. Since the driven plate 66 and the driven boss 86 are separated by serrations in this way, the swing of the second flywheel 3 is unlikely to affect the driven plate 66 side. Also in this example,
The second flywheel 63 can be easily attached and detached, and the durability of the rolling bearings 82 and 83 is improved.

[0031]

In the flywheel assembly according to the present invention, the second member is formed with the fluid replenishing passage that communicates with the fluid chamber through the window hole of the second member. The window hole of the second member is a place where a large amount of viscous fluid is accumulated during operation, so that a sufficient amount of viscous fluid is returned to the fluid chamber and a desired viscous resistance force is obtained.

[Brief description of drawings]

FIG. 1 is a schematic cross-sectional view of a power transmission device adopting 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 line III-III of FIG.

FIG. 4 is a partially enlarged view of FIG.

5 is a partially enlarged view of FIG.

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

FIG. 7 is a diagram corresponding to FIG. 4 showing one stage of a twisting operation.

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

FIG. 9 is a twist characteristic diagram of a 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]

 1 Flywheel Assembly 2 1st Flywheel 3 2nd Flywheel 4 Viscous Damper Mechanism 5 Drive Plate 6 Driven Member 7 Viscous Damper Part 12a, 12b, 12c Coil Spring 6b Window Hole 6d Fluid Supply Hole

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification code Internal reference number FI technical display location 9030-3J F16F 15/16 E

Claims (1)

[Claims] 1. A viscous fluid is contained between a first flywheel and a second flywheel rotatably supported by the first flywheel, and a first flywheel connected to the first flywheel. A first member that secures a possible space, and a fluid chamber that is connected to the second flywheel and that is disposed in the space and is filled with a viscous fluid inside the first flywheel and the first member on the outer peripheral portion. Second to make up
A member, an elastic member that elastically connects the two members, and a viscous damping unit that moves a viscous fluid in the fluid chamber to generate viscous resistance when the both members relatively rotate, and the second member is A flywheel assembly having a window hole for accommodating the elastic member in a radial middle portion and a fluid supply passage communicating with the fluid chamber from the window hole.