JP3408660B2 - Damper 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 bent leaf spring and a damper mechanism using the bent leaf spring.

[0002]

2. Description of the Related Art In a vehicle, for example, a damper mechanism for absorbing torque fluctuations of an engine is provided between a member on the engine side and a member on the transmission side. The damper mechanism is incorporated in a clutch disc assembly, a flywheel assembly, or the like. The damper mechanism includes an input side member and an output side member that can rotate relative to each other, a coil spring arranged to limit the rotation when both members rotate relative to each other, and a friction resistance when both members rotate relative to each other. Alternatively, it includes a resistance generating mechanism that generates viscous resistance.

Such a damper mechanism requires a large space in the circumferential direction and the axial direction because of the structure of the coil spring which constitutes the damper mechanism. Therefore, it becomes difficult to incorporate the damper mechanism as described above into a front-wheel drive vehicle whose space in the axial direction is particularly limited.
The damper mechanism disclosed in Japanese Patent Laid-Open No. 6-174011 uses a bent leaf spring instead of the coil spring, thus achieving space saving. Bending leaf springs
It is a member formed by bending a plate member having a constant width into a wavy shape. The bending leaf spring is arranged in an arcuate chamber formed by the input side member and the output side member, transmits torque from the input side member to the output side member, and expands and contracts when both members rotate relative to each other. As a result, when the torsional vibration is transmitted to the input side member, the bending leaf spring repeatedly expands and contracts and, for example, the oil filled in the arcuate chamber flows between the bending leaf spring and the wall surface of the arcuate chamber. , Generate a predetermined viscous resistance. As a result, the torsional vibration is damped.

[0004]

Generally, a damper mechanism is divided into an input side mechanism and an output mechanism side with an elastic member as a boundary. Then, the inertia moment of the output side mechanism is increased to shift the resonance frequency to a region equal to or lower than the idle speed of the engine. In this case, it is more effective in damping the vibration that the frictional resistance (or the viscous resistance) is reduced with respect to the minute torsional vibration that occurs in the engine speed practical range.

In the conventional damper mechanism using the bent leaf spring, as the bent leaf spring is compressed, the bent portion on the outer peripheral side of the bent leaf spring projects outward in the radial direction and slides on the outer peripheral wall of the arcuate chamber. Move. The frictional resistance generated at this time increases as the twist angle increases. Especially, since the entire bent leaf spring is moved to the outer peripheral side by the centrifugal force, the frictional resistance becomes larger. Due to such frictional resistance, it is not possible to sufficiently damp the vibration generated in the practical engine speed range.

An object of the present invention is to reduce the frictional resistance caused by the sliding motion of the curved leaf spring and the outer peripheral wall.

[0007]

A damper mechanism according to a first aspect of the present invention includes a first rotating member, a second rotating member, a bent leaf spring, and a connecting member. The second rotating member forms a pair of arcuate chambers with the first rotating member. The pair of bent leaf springs are respectively arranged in the arcuate chambers, and each of the bent leaf springs is formed of a plate member extending in a wavy shape.
The rotating member and the second rotating member are in contact with each other. The connecting member is a member for balancing the radially outward forces acting on the pair of bent leaf springs.

In the damper mechanism according to the second aspect, the connecting member is composed of a pair of annular plates and a pair of pins. A pair of annular plates extends across both of the pair of arcuate chambers and is rotatably disposed on opposite axial sides of the bent leaf spring. The pair of pins extend axially in the inner peripheral side bent portion of the pair of bent leaf springs, and both ends thereof are fixed to the pair of annular plates.

In the damper mechanism according to the third aspect, the pin is arranged near the center of the pair of bent leaf springs in the longitudinal direction. In the damper mechanism according to the fourth aspect, the connecting member includes the annular plate and the pair of abutting portions. The annular plate extends over both of the pair of arcuate chambers and is rotatably disposed on one axial side of the bent leaf spring. The pair of abutting portions extends in the axial direction from the annular plate and engages with the outer peripheral side of the outer peripheral side bent portions of the pair of curved leaf springs, respectively.

In the damper mechanism according to the fifth aspect, the contact portion is formed near the center of the pair of curved leaf springs in the longitudinal direction. A damper mechanism according to a sixth aspect includes a first rotating member, a second rotating member, a plurality of bent leaf springs, and a connecting member. The second rotating member forms a plurality of arcuate chambers with the first rotating member. The plurality of bent leaf springs are respectively arranged in the respective arcuate chambers, and each of the bent leaf springs is formed of a plate member that extends in a state of being alternately bent. The connecting member is a member for balancing the radially outward forces acting on the plurality of bent leaf springs.

[0011]

In the damper mechanism according to the first aspect, when the first rotating member rotates, the torque is transmitted to the second rotating member via the bent leaf spring. When the torsional vibration is input to the first rotating member, the first rotating member rotates relative to the second rotating member. At this time, the bent leaf spring repeatedly expands and contracts in the circumferential direction between both rotary members. The bending leaf spring tries to push outward in the radial direction at the time of compression, and further tries to move outward in the radial direction by centrifugal force, but the connecting member exerts an outward force in the radial direction on each of the pair of bending leaf springs. Since they are balanced with each other, frictional resistance generated between the bent leaf spring and the outer peripheral wall of the arcuate chamber is reduced.

In the damper mechanism according to the second aspect of the present invention, the pair of bent leaf springs each try to move radially outward during compression, but the pins extending into the inner circumferential side bent portion move radially outward. Is reduced, resulting in less frictional resistance between the bent leaf spring and the outer peripheral wall of the arcuate chamber.
In the damper mechanism according to the third aspect of the present invention, the pin extends into the inner peripheral side bent portion near the longitudinal center of the pair of bent leaf springs, so that the torsion angle of the bent leaf springs can be maximized.

In the damper mechanism according to the fourth aspect of the present invention, the pair of curved leaf springs try to move outward in the radial direction during compression, but the pair of abutting portions has the outer circumference of the bent portion on the outer peripheral side of the curved leaf spring. Since it is engaged with the side, the outward movement in the radial direction is hindered. As a result, the frictional resistance generated between the bent leaf spring and the outer peripheral wall of the arcuate chamber is reduced. In the damper mechanism according to claim 5, since the abutting portion is engaged with the outer peripheral side bent portion near the center in the longitudinal direction of the pair of bent leaf springs, the twist angle of the bent leaf springs is secured to the maximum. it can.

In the damper mechanism according to the sixth aspect, for example, when the first rotating member rotates, the torque is transmitted to the second rotating member via the plurality of bent leaf springs. When the torsional vibration is transmitted to the first rotating member, the first rotating member rotates relative to the second rotating member. At this time, the bent leaf spring repeatedly expands and contracts. The curved leaf spring tends to push outward in the radial direction during compression, and further, the curved leaf spring tends to move outward in the radial direction by the action of centrifugal force. However, since the connecting members balance the radial outward forces acting on the plurality of curved leaf springs, the plurality of curved leaf springs are restricted from moving radially outward, and as a result, The frictional resistance generated between the arcuate chamber and the outer peripheral wall is reduced.

[0015]

First Embodiment FIGS. 1 and 2 show a flywheel assembly in which a damper mechanism according to an embodiment of the present invention is adopted. Figure 1
At, O-O is the axis of rotation of the flywheel assembly.

This flywheel assembly is mainly designed to be fixed to a crankshaft (not shown) on the engine side.
A flywheel 1 and a second flywheel 3 rotatably supported by the first flywheel 1 via a bearing 2.
A pair of bent leaf springs 18 for transmitting torque between the two flywheels are provided. The first flywheel 1
A hub 5 arranged in the central portion, a disc-shaped input plate 6 arranged on the side surface of the hub 5 on the engine side, and a counter plate 7 arranged to face the input plate 6 in the axial direction,
It has an annular first flywheel body 8 fixed to the outer peripheral portion of the input plate 6. The hub 5 and the input plate 6 are fixed to a crankshaft (not shown) by bolts 9 and washer plates 10. Further, the hub 5, the input plate 6 and the washer plate 10 are fixed to each other by rivets 19. Input plate 6
An outer peripheral cylindrical portion 6a extending toward the transmission side is formed on the outer peripheral portion of the outer peripheral cylindrical portion 6a, and the outer peripheral cylindrical portion 6a is welded to the inner peripheral side of the first flywheel body 8. An outer peripheral tubular portion 7a extending toward the engine is provided on the outer peripheral portion of the facing plate 7.
The outer peripheral tubular portion 7a is formed by
It is welded to the inner peripheral side of a. A ring gear 11 is fixed to the outer periphery of the first flywheel body 8.

The second flywheel 3 includes the output plate 1
2, an annular second flywheel main body 13, and a disc-shaped intermediate plate 14 arranged between the output plate 12 and the second hula wheel 13, which are formed by a plurality of rivets 15. Connected to each other. The output plate 12 includes a support portion 12a on the inner peripheral side supported by the bearing 2 and a mounting flange portion 12b extending from the support portion 12a to the outer peripheral side and having the rivet 15 fixed thereto. The support portion 12a is in contact with the engine side surface and the outer peripheral surface of the bearing 2. And the mounting flange portion 12b
A seal member (not shown) for sealing the both is disposed between the outer peripheral portion of and the inner peripheral portion of the counter plate 7. The inner peripheral portion of the intermediate plate 14 is in contact with the surface of the bearing 2 on the transmission side. The second flywheel body 13 has a friction surface 13a for frictionally engaging a clutch disc (not shown).

The input plate 6, the counter plate 7, and the output plate 12 described above constitute a fluid chamber 17. The fluid chamber 17 is filled with a viscous fluid such as grease. Further, as shown in FIG. 2, the outer peripheral portion of the counter plate 7 is formed with locking portions 7b projecting toward the inner peripheral side at two locations facing each other in the radial direction. Further, on the outer peripheral portion of the support portion 12a of the output plate 12, there are formed locking portions 12c projecting to the outer peripheral side at two positions facing the locking portion 7b in a free state. With such a configuration, the annular fluid chamber 17 is divided into a pair of arc-shaped chambers. A pair of bent leaf springs 18 are respectively arranged in these arcuate chambers.

The bent leaf spring 18 will be described in detail with reference to FIG. As shown in the figure, the bent leaf spring 18 extends in a state in which a plate member having a constant width is bent in a wave shape. More specifically, a plurality of spring elements including a ring portion 20 and a lever portion 21 are connected in series. It is connected.
The plurality of ring portions 20 are annular bodies having substantially the same diameter, and a predetermined gap S ₁ is provided between adjacent ring portions 20 in a free state. The inside of the ring portion 20 is an open ring portion 23. A gap S ₂ is formed between the ring-opening portions 23 in the free state and the set state. Lever portions 21 extend outward from both sides of the ring opening portion 23, respectively. The lever portions 21 extend so as to widen their distances toward the outside, and are continuous with the lever portions 21 of the opposing ring portions 20 on one side.

The width of the bent leaf spring 18 is equal to that of the fluid chamber 17
Of the fluid chamber 17 and its radial length is slightly shorter than the length of the fluid chamber 17. Further, the ring portions 20 on both outer peripheral sides of the bent leaf spring 18 are in contact with the locking portions 7b, and the ring portions 20 on both inner peripheral sides are in contact with the locking portions 12c. The connecting member 31 is composed of a pair of annular plates 32 and 33 and a pair of rivet pins 34 for connecting the annular plates 32 and 33 to each other. Annular plates 32, 33
As is apparent from the drawing, extends over both of the pair of arcuate chambers 17 and is rotatably arranged on both axial sides of the inner peripheral portion of the bent leaf spring 18. The inner diameters of the annular plates 32 and 33 are the same as those of the support portion 12 of the output plate 12.
slightly larger than the diameter of a. A pair of rivet pins 34
Are axially pierced in the inner peripheral side ring portion 20 in the vicinity of the center of the bending leaf spring 18 in the longitudinal direction, and both ends thereof are the annular plates 3.
It is fixed to 2, 33.

On the outer peripheral side of the fluid chamber 17, a large gap 35 is secured between the bending leaf spring 18 and the input plate 6 in the axial direction, and further between the bending leaf spring 18 and the counter plate 7 in the axial direction. Next, the operation will be described.
The torque transmitted from the crankshaft on the engine side to the first flywheel 1 is transmitted to the bending leaf spring 18 via the engagement portion 7b of the input plate 6 and the counter plate 7, and further from the bending leaf spring 18 to the output plate 12. It is transmitted to the second flywheel 3 via the locking portion 12c.

When a torsional vibration is input to this flywheel assembly, the first flywheel 1 and the second flywheel 3 rotate relative to each other, and the bending leaf spring 18 extends in the circumferential direction between the two flywheels. Repeat expansion and contraction. In the first embodiment, since the gap 35 is formed between the bent leaf spring 18 and the side wall of the fluid chamber 17, a large viscous resistance does not occur. When the bending leaf spring 18 is compressed, each lever portion 2
The opening angle of 1 becomes small, and a bending moment acts on the ring portion 20. At this time, the lever portion 21 bends around the ring opening portion 23 as a fulcrum. The bending moment is uniformly distributed in the lever portion 21 in the longitudinal direction, and elastic energy is dispersed and stored in the plurality of ring portions 20.

The torsional characteristics in this case are as follows:
It is determined by the torsional rigidity of 8. That is, in a small twist angle range having the gap S ₂ in the ring opening portion 23, the ring portion 20 and the lever portion 21 bend in the same direction with the outer peripheral portion of the ring portion 20 of the bending leaf spring 18 as a fulcrum. The torsional rigidity at this time is small. When the twisting angle increases, the gap S ₂ becomes 0, and the ring portion ₂ with the open ring portion 23 as a fulcrum.
Elastic energy is stored at 0. The torsional rigidity at this time is large.

When the bent leaf spring 18 is compressed, each element tries to push out toward the outer peripheral side. Also, the bent leaf spring 1
The centrifugal force acts on the whole 8. However, in this case, since the connecting member 31 balances the radially outward forces acting on the pair of curved leaf springs, the pair of curved leaf springs 18 are unlikely to move radially outward. Has become. As a result, the frictional resistance generated between the bent leaf spring 18 and the cylindrical outer peripheral portion 7a is reduced. As a result, in particular, minute vibrations that occur in the engine engine speed range are sufficiently damped with the characteristics of low rigidity and low resistance.

Since the rivet pin 34 is inserted into the inner peripheral side ring portion 20 near the longitudinal center of each bending leaf spring 18, the bending angle of the bending leaf spring 18 is maximized. Second Embodiment In the flywheel assembly shown in FIG. 4, the bent leaf spring 1
The width of 8 and the width in the fluid chamber 17 are formed to be substantially equal. Specifically, the thickness of each of the input plate 6 and the counter plate 7 on the outer peripheral side is increased, and the bending leaf spring 18 is bent.
The gap between and is small. As a result, the bent leaf spring 1
When 8 expands and contracts, the viscous fluid bends and the leaf spring 18 and the fluid chamber 1
7 and the viscous resistance is generated. Third Embodiment In the flywheel assembly shown in FIGS. 5 and 6, the connecting member 41 is arranged in the fluid chamber 17. Connecting member 41
Is an annular plate 43 that extends over the entire fluid chamber 17, an extension portion 44 that extends radially outward from two radially opposed portions of the annular plate 43, and an abutment portion 45 that extends from the extension portion 44 to the transmission side. It is configured. As is apparent from FIG. 5, the annular plate 43 is arranged on the engine side of the bent leaf spring 18 in the fluid chamber 17. The inner peripheral side surface of the contact portion 45 has a curved leaf spring 1
8 is engaged with the outer peripheral side of the outer peripheral ring portion 20 near the center in the longitudinal direction so as to rotate integrally. Further, the outer peripheral side surface of the contact portion 45 is slidable along the outer peripheral tubular portion 7a.

In this embodiment, when the bending leaf spring 18 is compressed, the bending leaf spring 18 tends to push outward in the radial direction, and a centrifugal force acts on the bending leaf spring 18. However, since the abutting portions 45 balance the radial outward forces acting on the curved leaf springs 18, the curved leaf springs 18 are unlikely to move radially outward. As a result, the bending leaf spring 18 and the outer peripheral tubular portion 7
The frictional resistance that occurs with a is reduced. Further, since the contact portion 45 is engaged with the outer peripheral ring portion 20 near the longitudinal center of the bending leaf spring 18, the twisting angle of the bending leaf spring 18 can be maximized.

[Modification] In the above-described embodiment, the present invention is applied to the damper mechanism using a pair of bent leaf springs. However, three or more bent leaf springs are arranged in three or more arc-shaped chambers, respectively. The present invention can also be used for the mechanism.

[0028]

In the damper mechanism according to the first aspect of the present invention, the curved leaf spring tends to push outward in the radial direction during compression, and further tends to move outward in the radial direction by centrifugal force.
Since the connecting member balances the radially outward forces acting on each of the pair of bent leaf springs, the frictional resistance generated between the bent leaf springs and the outer peripheral wall of the arcuate chamber is reduced.

In the damper mechanism according to the second aspect of the present invention, the pair of bent leaf springs each try to move outward in the radial direction at the time of compression, but the extension extending in the radial direction is caused by the pin extending into the inner peripheral side bent portion. Is reduced, resulting in less frictional resistance between the bent leaf spring and the outer peripheral wall of the arcuate chamber.
In the damper mechanism according to the third aspect of the present invention, the pin extends into the inner peripheral side bent portion near the longitudinal center of the pair of bent leaf springs, so that the torsion angle of the bent leaf springs can be maximized.

In the damper mechanism according to the fourth aspect of the present invention, the pair of curved leaf springs try to move outward in the radial direction during compression, but the pair of abutting portions has the outer periphery of the bent portion on the outer peripheral side of the curved leaf spring. Since it is engaged with the side, the outward movement in the radial direction is hindered. As a result, the frictional resistance generated between the bent leaf spring and the outer peripheral wall of the arcuate chamber is reduced. In the damper mechanism according to claim 5, since the abutting portion is engaged with the outer peripheral side bent portion near the center in the longitudinal direction of the pair of bent leaf springs, the twist angle of the bent leaf springs is secured to the maximum. it can.

In the damper mechanism according to the sixth aspect of the present invention, the curved leaf spring tends to push outward in the radial direction during compression, and the curved leaf spring tends to move outward in the radial direction by the action of centrifugal force. However, since the connecting members balance the radial outward forces acting on the plurality of curved leaf springs, the plurality of curved leaf springs are restricted from moving radially outward, and as a result, The frictional resistance generated between the arcuate chamber and the outer peripheral wall is reduced.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a flywheel assembly according to a first embodiment of the present invention.

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

FIG. 3 is a partial front view of a bent leaf spring.

FIG. 4 is a diagram corresponding to FIG. 1 in the second embodiment.

FIG. 5 is a diagram corresponding to FIG. 1 in the third embodiment.

6 is a sectional view taken along line VI-VI of FIG.

[Explanation of symbols]

1 first flywheel 3 second flywheel 17 Fluid chamber 18 Bent leaf spring 31, 41 Connecting member

Front page continuation (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16F 15/133 F16F 15/134 F16F 15/30 F16D 13/64 F16D 3/64 F16D 3/56

Claims (6)

(57) [Claims] 1. A second rotating member which forms a pair of arcuate chambers between the first rotating member and the first rotating member.
The rotary member and a plate member that is disposed in each of the arcuate chambers and extends in a wavy bent state.
A pair of bent leaf springs in which the rotary member and the second rotary member are in contact with each other, and a connecting member for balancing the radially outward forces acting on the pair of bent leaf springs, respectively. Damper mechanism with. 2. A pair of annular plates extending in both of the pair of arcuate chambers and rotatably arranged on both axial sides of the bent leaf spring, and the pair of bent leaf springs. 2. The damper mechanism according to claim 1, wherein the damper mechanism is configured by a pair of pins that extend in the inner peripheral side bent portion in the axial direction and both ends thereof are fixed to the pair of annular plates. 3. The damper mechanism according to claim 2, wherein the pin is arranged in the vicinity of the longitudinal center of the pair of bent leaf springs. 4. The connecting member extends along both of the pair of arcuate chambers and is rotatably disposed on one axial side of the bent leaf spring. The connecting member extends axially from the annular plate. The damper mechanism according to claim 1, comprising a pair of abutting portions that engage with the outer peripheral side of the outer peripheral side bent portions of the pair of bent leaf springs, respectively. 5. The damper mechanism according to claim 4, wherein the contact portion is formed near the center of the pair of curved leaf springs in the longitudinal direction. 6. A second rotating member which forms a plurality of arcuate chambers between the first rotating member and the first rotating member.
The rotary member and a plate member that is disposed in each of the arcuate chambers and extends in a wavy bent state.
A damper including a plurality of bent leaf springs in which the rotating member and the second rotating member are in contact with each other, and a connecting member for balancing the radially outward forces acting on the plurality of bent leaf springs. mechanism.