JPH1026184A - Damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase degree of freedom in design of radially inside circumferential side of a damping section. SOLUTION: A damping device 1 comprises a flexible plate 2, a first input side plate 13, a hub flange 3, a bearing 17, and a damping section 4. The flexible plate 2 is secured as its inside circumferential edge is tightened to the end of a crankshaft 301 by means of a plurality of bolts 6 arranged on the circumference. The first input side plate 13 is secured to the outer circumferential edge of the flexible plate 2. The hub flange 3 is connected to a main drive shaft 302. The bearing 17 is disposed inside the pitch circle of the plurality of bolts 6 to supports the first input side plate 13 and the hub flange 3 for their free relative rotation. The damping section 4 interconnects the first input side plate 13 and the hub flange 3 elastically in the circumferential direction to damp torsional vibration between both components.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a damper device, and more particularly to a damper device disposed between an engine-side crankshaft and an output-side rotating body to transmit torque.

[0002]

2. Description of the Related Art In a vehicle, a damper device is provided between an engine and a transmission for transmitting torque between the two and attenuating torsional vibration. Generally, a damper device elastically connects an input member connected to a crankshaft of an engine, an output member connected to a main drive shaft extending from a transmission, and an input member and an output member in a circumferential direction. And a torsional vibration damping unit to be connected. In addition, a flexible plate is provided between the crankshaft and the input side member for absorbing bending vibration from the engine side. An inner peripheral end of the flexible plate is fixed to a tip of the crankshaft by a plurality of bolts. The plurality of bolts are arranged at equal intervals in the circumferential direction.

[0003]

In the above-mentioned conventional damper device, the bearing is arranged on the outer peripheral side of the pitch circle of the bolt. Therefore, the degree of freedom in designing the radially inner peripheral side of the damping portion is limited. An object of the present invention is to improve the degree of freedom in designing the radially inner peripheral side of the damping portion.

[0004] Another object of the present invention is to reduce costs. Still another object of the present invention is to increase the concentricity of each member.

[0005]

According to a first aspect of the present invention, there is provided a damper device for transmitting a torque between a crankshaft on the engine side and an output-side rotating body, comprising: a disk-shaped flexible plate; A member, an output-side member, a bearing, and a torsional vibration damping unit are provided. The inner peripheral end of the disk-shaped flexible plate is fixed to the distal end of the crankshaft by a plurality of fastening members arranged on the circumference. The input side member is fixed to the outer peripheral end of the flexible plate. The output side member is connected to the output side rotating body. The bearing is arranged inside a pitch circle of the plurality of fastening members, and supports the input side member and the output side member so as to be relatively rotatable. The torsional vibration damping unit elastically connects the input side member and the output side member in the circumferential direction, and attenuates torsional vibration between the input side member and the output side member.

[0006] In the damper device according to claim 2, in the device according to claim 1, the input side member includes a disk-shaped member having an outer peripheral end connected to the outer peripheral end of the flexible plate, and an inner peripheral end of the disk-shaped member. And a boss with a bearing fixed to the outer periphery. The flexible plate has a center hole, and the boss is fitted and supported in the center hole.

A third aspect of the present invention provides a damper device.
In the device of the second aspect, the output-side member further includes a disk-shaped inertia member formed to rotate integrally with the boss.

[0008]

In the damper device according to the first aspect, when torque is input from the crankshaft on the engine side, the torque passes through the disk-shaped flexible plate, the input side member, the torsional vibration damping section and the output side member. Output to the output rotator. The bending vibration transmitted from the engine is absorbed by the flexible plate and is not easily transmitted to the torsional vibration damping unit.

Here, since the bearing is arranged inside the pitch circle of the fastening member, the degree of freedom in designing the radially inner peripheral side of the torsional vibration damping portion is improved. In the damper device according to the second aspect, since the boss of the input-side member is fitted and supported in the center hole of the flexible plate, the concentricity of each member is increased.

In the damper device according to the third aspect, since the disk-shaped inertia member is provided on the output side member,
The moment of inertia of the output side mechanism increases, and the resonance frequency in the drive system including the damper device can be reduced to the idling speed of the vehicle or lower.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION

First Embodiment FIGS. 1 to 3 show a damper device 1 as one embodiment of the present invention. The damper device 1 is a device for transmitting torque from a crankshaft 301 on the engine side to a main drive shaft 302 of 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. 1 is the rotation axis of the damper device 1, and the R1 direction in FIG.

The damper device 1 mainly includes a flexible plate 2, a ring member 8 fixed to the flexible plate 2, a hub flange (output side member) 3, and a damper 4. The flexible plate 2 is a substantially disk-shaped member, is capable of bending in the bending direction, and has high rigidity in the rotation direction. The flexible plate 2 has a center hole 2a at the center. Further, the flexible plate 2 has a plurality of round holes 2b formed at equal intervals in the circumferential direction at a radially intermediate portion. A plurality of bolt holes 2c are formed at equal intervals in the circumferential direction on the inner peripheral side of the round hole 2b. The bolt 6 penetrating through the bolt hole 2 c causes the inner peripheral end of the flexible plate 2 to be
1 is fixed to the tip. Further, a plurality of arc-shaped inertia members 7 shown in FIG. Due to the inertia member 7, the moment of inertia of the damper device 1 is increased. In addition, the inertia member 7
Since the annular member has a shape obtained by dividing the annular member in the circumferential direction, the bending of the flexible plate 2 in the bending direction is guaranteed. The outer peripheral end of the flexible plate 2 is fixed to the ring member 8 via the disk plate 9 by a plurality of bolts 10. The inertia member 7 has a notch corresponding to the bolt 10.

The hub flange 3 includes a boss 3a and a boss 3a.
And a flange 3b integrally formed on the outer periphery of the main body. At the center of the boss 3a, a spline hole 3c is formed which engages with spline teeth of the main drive shaft 302 extending from the transmission side. The damper 4 mainly includes the first input side plate 13 and the second input side plate 1.
4, driven plate 19, coil spring 22
And a viscous resistance generating section 25 (torsional vibration damping section).

The first input side plate 13 and the second input side plate 14 are disk-shaped plate members. The inner peripheral end of the first input side plate 13 extends further inward in the radial direction than the inner peripheral end of the second input side plate 14. The second input side plate 14 has a cylindrical wall on the outer peripheral portion, which extends toward the engine and is fixed to the outer peripheral end of the first input side plate 13. This cylindrical wall is welded to the inner periphery of the ring member 8. Thus, the first and second input side plates 13 and 14 rotate integrally with the ring member 8. That is, the plates 13 and 14 function as a part of the input side member. The first input side plate 13 and the second input side plate 14 form an annular fluid filling chamber A that accommodates the driven plate 19, the coil spring 22, the viscous resistance generating section 25, and the like. This annular fluid filling chamber A is filled with a viscous fluid.

The driven plate 19 is a disk-shaped member, and the inner peripheral end thereof is formed by a plurality of rivets 20 at the hub flange 3.
Is connected to the flange 3b. Thus, the driven plate 19 rotates integrally with the hub flange 3. In the radially intermediate portion of the driven plate 19, FIG.
As shown in FIG. 7, a plurality of window holes 19a extending in the circumferential direction are formed. Further, on both sides of the outer peripheral end of the driven plate 19, annular sealing grooves 19b are formed. The outer peripheral surface 19c of the driven plate 19
, A plurality of projections 19d extend radially outward.

The coil spring 22 is a combination of large and small coil springs, and is disposed in the window 19 a of the driven plate 19. Sheet members 23 are disposed at both ends of the coil spring 22. The first input side plate 13 and the second input side plate 14 are formed with spring receiving portions 13a and 14a at portions corresponding to the window holes 19a of the driven plate 19. Seat members 23 are in contact with both ends in the circumferential direction of the spring housing portions 13a and 14a. Thus, the input side plates 13 and 14 and the driven plate 19
Are elastically connected in the circumferential direction via the coil spring 22. In the free state shown in FIG. 2, the sheet member 23 is connected to the input side plate 13,
The end portions of the spring housing portions 13a, 14a of 14 and the end portion of the window hole 19a of the driven plate 19 abut only at the inner peripheral portion. That is, the coil spring 22 is biased and the window hole 19a and the spring accommodating portions 13a, 1
4a.

Next, the viscous resistance generating section 25 will be described. The viscous resistance generating section 25 includes an annular housing 27 disposed at the outermost periphery in the annular fluid filling chamber A, and a plurality of pins 28 connecting the annular housing 27 to the first input side plate 13 and the second input side plate 14. , A plurality of slide stoppers 29 arranged in the housing 27.

The annular housing 27 is arranged inside the outer peripheral wall of the second input side plate 14, and both end faces in the axial direction are sandwiched between the input side plates 13 and 14. Annular housing 2
An opening extending in the circumferential direction is formed on the inner peripheral side of 7, and the outer peripheral portion of the driven plate 19 is inserted into the opening. An annular fluid chamber B filled with a viscous fluid is formed in the annular housing 27. Further, a plurality of stopper portions 27a are integrally formed in the annular housing 27 at equal intervals in the circumferential direction. Stopper part 27a
Divides the annular fluid chamber B into a plurality of arc-shaped fluid chambers B1. The stopper portion 27a has a hole through which the pin 28 is inserted. The pins 28 have input side plates 13 and 14 at both ends.
Are non-rotatably engaged. Thereby, the annular housing 27 and the input-side plates 13 and 14 rotate integrally. The length of the body of the pin 28 determines the width of the annular housing 27 that determines the viscous resistance.

At the radially inner end of the annular housing 27, there are formed annular projections 27b protruding in a direction approaching each other (the openings are formed between the projections 27b). 19 is fitted into an annular sealing groove 19b formed in the annular fluid chamber B.
Is sealed on the inner peripheral side. Projection 27b and sealing groove 1
9b is engaged with the input side mechanism (input side plates 13, 14 and annular housing 27) via a viscous fluid.
Loads (thrust load, radial load, bending load) generated between the motor and the output side mechanism (the driven plate 19, the hub flange 3) are shared and supported by a bearing 17 described later.

A return hole 27 is provided at an intermediate portion between the stopper portions 27a at radially inner sides of both end faces.
c is formed. The return hole 27c allows the viscous fluid to freely move between the annular fluid chamber B and the annular fluid filling chamber A. In the free state shown in FIG. 2, the projection 19d of the driven plate 19 is arranged at a position corresponding to the return hole 27c.

In each of the arc-shaped fluid chambers B1, a cap-shaped resin slide stopper 29 for covering the projection 19d of the driven plate 19 from the outer peripheral side is arranged. The slide stopper 29 has an outer peripheral portion coinciding with the outer inner peripheral surface of the annular housing 27, and is arranged so as to be movable in the circumferential direction in the arc-shaped fluid chamber B1. Slide stopper 29
Is movable in the circumferential direction with respect to the projection 19d of the driven plate 19 within a range where the circumferential wall portion abuts on the projection 19d. The slide stopper 29 has a notch 29a on the radially inner side of both circumferential wall portions. A notch 29b is formed radially inside both wall portions of the slide stopper 29 in the axial direction. A radially inner portion of the stopper portion 29 is in contact with an annular protrusion 27b of the annular housing 27.

The inside of each arc-shaped fluid chamber B1 is controlled by a slide stopper 29 to a first Oita chamber 31 on the R2 side and a second Oita chamber 31 on the R1 side.
It is divided into an Oita room 32. Further, inside the slide stopper 29, the first sub-compartment 33 on the R2 side and the second sub-compartment 3 on the R1 side are formed by the projections 19d of the driven plate 19.
And four. First sub-compartment 33 and second sub-compartment 3
4, a gap formed between the projection 19d of the driven plate 19 and the slide stopper 29, the notch 29b of the slide stopper 29, and the return hole 27.
By virtue of c, the viscous fluid can move freely. Further, the viscous fluid can freely move between the first large compartment 31 and the first small compartment 33 through the R2 side notch 29a of the slide stopper 29, and the second small compartment 34 and the second
The slide stopper 29 can freely move to and from the Oita chamber 32 through the cutout 29a on the R1 side of the slide stopper 29. However,
When the circumferential wall of the slide stopper 29 comes into contact with the projection 19d, the flow of the viscous fluid inside and outside the slide stopper 29 in the circumferential direction is shut off.

A portion between the inner peripheral surface of the stopper portion 27a and the outer peripheral surface 19c of the driven plate 19 forms a choke portion C. When a viscous fluid passes through the choke portion C, a large viscous resistance is generated. As shown in FIG. 4, a spring seal member 35 is sandwiched between a portion where the inner peripheral portion of the driven plate 19 and the flange 3b of the hub flange 3 are fixed by rivets 20. The spring seal member 35 is made of an annular thin sheet metal, and includes a fixing portion 35 a having a plurality of holes through which the rivets 20 pass, and a fixing portion 35
An outer cylindrical portion 35b extending from the inner peripheral side to the transmission side of FIG. 3A, and a pressure contact portion 35c extending from the outer cylindrical portion 35b to the outer peripheral side are provided. As shown in FIG. 4, the press contact portion 35 c elastically contacts the inner peripheral end portion of the second input side plate 14 on the engine side. The driven plate 19 and the hub flange 3 are urged toward the engine by the reaction force generated by the pressing force. The spring seal member 35 is
The space between the second input side plate 14 and the hub flange 3 is sealed in the annular fluid filling chamber A.

The center hole at the inner peripheral end of the first input side plate 13 is fitted to the boss 15 and fixed by welding. The engine-side outer peripheral surface 15 a of the boss 15 is fitted into the center hole 2 a of the flexible plate 2. In the boss 15, a central hole 15c penetrating in the axial direction and a radial hole 15b communicating with the central hole 15c and communicating with the annular fluid filling chamber A are formed. A rivet 16 is inserted into the center hole 15c to close the center hole 15c. During assembly,
The viscous fluid can be easily filled and discharged into the annular fluid filling chamber A using the center hole 15c and the radial hole 15b. As a result, costs are reduced.

A bearing 1 is provided between the outer peripheral surface of the boss 15 on the transmission side and the inner peripheral portion of the boss 3a of the hub flange 3.
7 are arranged. The bearing 17 supports the boss 15 and the hub flange 3 so as to be relatively rotatable. The inner ring of the bearing 17 is fixed to a groove of the boss 15. The outer ring of the bearing 17 is fixed to the inner periphery of the boss 3a. Thus, the boss 15 is positioned in the center hole 2a of the flexible plate 2, and further positions the bearing 17. As a result, the flexible plate 2, the boss 15 and the bearing 17
Concentricity is improved.

In this embodiment, the load generated between the input side mechanism and the output side mechanism is caused by the engagement between the annular projection 27b of the annular housing 27 and the sealing groove 19b of the driven plate 19 in the viscous resistance generating section 25. Also, the load acting on the bearing 17 can be reduced. Therefore, a bearing 17 having a small outer diameter can be used, and the cost is reduced. In this embodiment, the bearing 17 is disposed within the pitch circle D of the bolt 6 (FIG. 2), and as a result, the degree of freedom in designing the inner peripheral side of the damper 4 is improved. In addition, for example, the driven plate 19 can be extended to the inner peripheral side, and the coil spring 22 can be disposed more to the inner peripheral side. Further, a space for rotating the head of the crank bolt 6 can be easily secured.

The bearing 17 has a seal member for sealing between the inner ring and the outer ring at both end surfaces. This seal member seals the lubricant between the inner ring and the outer ring, and seals between the boss 15 and the inner peripheral portion of the hub flange 3 in the annular fluid filling chamber A. Hub flange 3
Is urged toward the engine by the spring seal member 35 as described above. Therefore, a preload is applied to the bearing 17 from the hub flange 3 toward the engine. As described above, the spring seal member 35 functions as a member that seals the annular fluid filling chamber A and also applies a preload to the bearing 17, and has a plurality of functions as a single member.
As a result, the number of parts can be reduced, and the manufacturing cost is reduced. Further, the cost is reduced because the spring seal member 35 is made of sheet metal.

An inertia member 42 is provided on the transmission side of the flange 3b of the hub flange 3. The inertia member 42 is a disk-shaped member that covers the transmission side of the second input side plate 14, and the inner peripheral end is fixed to the flange 3 b and the driven plate 19 by rivets 20. In addition, the inertia member 42
Is disk-shaped, the entire damper device 1 is compact in the axial direction. The provision of the inertia member 42 increases the moment of inertia of the output-side mechanism. Further, the ring gear 11 for starting the engine is welded to the outer periphery of the inertia member 42. Since the inertia member 42 is a disk-shaped member, the ring gear 11 is easily fixed. Therefore, the cost is reduced. The ring gear 11 is a member conventionally welded to the outer periphery of the ring member 8, but by moving from the input side mechanism to the output side mechanism as in the present embodiment, the moment of inertia of the output side mechanism can be easily increased. . When the moment of inertia of the output mechanism increases, the resonance frequency of the drive system including the damper device 1 can be reduced to a value equal to or lower than the idling rotational speed (practical rotational speed) of the vehicle. At this time, the conventional ring gear 1
By using 1, the cost is reduced.

Next, the operation will be described. When torque is input from the crankshaft 301 to the flexible plate 2, the torque is transmitted to the driven plate 19 via the ring member 8, the input side plates 13 and 14, and the coil spring 22. The torque of the driven plate 19 is transmitted to the hub flange 3 and further output from the main drive shaft 302 to the transmission. The bending vibration included in the torque transmitted from the crankshaft 301 to the ring member 8 is insulated by the flexible plate 2 and is not easily transmitted to the damper 4 side. Even if the bending vibration is transmitted, the bending load is shared and supported by the bearing 17 and the engagement of the annular projection 27b of the annular housing 27 with the sealing groove 19b of the driven plate 19. Therefore, since the load on the bearing 17 is reduced, the size of the bearing 17 can be reduced in the radial direction. Therefore, the bearing 17 becomes inexpensive. The bending load is also supported by the engagement between the annular protrusion 27b of the annular housing 27 and the sealing groove 19b of the driven plate 19.

Next, the operation when torsional vibration is transmitted from the crankshaft 301 to the damper device 1 will be described. However, here, when the torsional vibration is transmitted, the operation on the output side mechanism (the driven plate 19 and the hub flange 3) is fixed non-rotatably to another member (not shown). 1st input side plate 1
3. Second input side plate 14 and annular housing 27)
Will be described by substituting the operation when twisted.

A small deviation angle of torsional vibration (hereinafter referred to as "micro vibration") such that the circumferential wall of the slide stopper 29 does not contact the projection 19d of the driven plate 19
The operation when is transmitted will be described. It is assumed that the input side plates 13 and 14 are twisted to the R2 side in the free state shown in FIG. Then, the slide stopper 19 moves to the R2 side, and the first small compartment 33 is expanded and the second small compartment 34 is reduced in the slide stopper 29 as shown in FIG.
The viscous fluid flows freely from the second small compartment 34 to the first small compartment 33 through the notch 29b and the return hole 27c between the outer peripheral portion of the slide stopper 29 and the projection 19d. Further, the viscous fluid can freely flow between the inside of the slide stopper 29 and the annular fluid filling chamber A through the return hole 27c.

When the twisting operation is further continued from the state shown in FIG. 6, the circumferential wall on the R1 side of the slide stopper 29 comes into contact with the projection 19d of the driven plate 19 as shown in FIG. Thereafter, the slide stopper 29 is locked by the driven plate 19, and relative rotation occurs between the annular housing 27 and the slide stopper 29. In the state shown in FIG.
Although the Oita chamber 32 communicates with the return hole 27c, as the twisting operation proceeds further, the return hole 27c is closed by the projection 19d as shown in FIG.

From the free state shown in FIG.
When the screw 7 is twisted to the R1 side, the same operation as described above is performed. At the time of the minute vibration, since the relative rotation does not occur between the slide stopper 29 and the annular housing 27, the second large compartment 32 is not reduced, and the viscous fluid does not pass through the choke portion C. That is, large viscous resistance does not occur at the time of minute vibration. At the time of minute vibration, the coil spring 22 is connected to the window hole 19a of the driven plate 19 and the spring accommodating portions 13a, 14a of the input side plates 13, 14.
Has expanded and contracted in a biased state. Therefore, a low rigidity state is obtained. That is, 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 can be effectively suppressed.

Next, the operation when torsional vibration having a large deflection angle (hereinafter, referred to as large vibration) is transmitted will be described. From the free state shown in FIG.
Is rotated to the R2 side with respect to the driven plate 19, the slide stopper 29 moves to the R2 side. Thereafter, the operations from FIG. 5 to FIG. 8 are performed as in the case of the minute vibration. As shown in FIG. 8, the R2 side of the second large compartment 32 is the slide stopper 29 and the projection 1 of the driven plate 19.
9d, the second Oita room 3
2 begins to shrink. As a result, the viscous fluid in the second large division chamber 32 passes through the choke portion C and the arc-shaped fluid chamber B1 on the R1 side.
(Fig. 9). When the viscous fluid flows through the choke portion C, a large viscous resistance is generated. The viscous fluid flows smoothly from the annular fluid filling chamber A into each first large division chamber 31 through the return hole 27c. Therefore, the viscous fluid does not run short in the annular fluid chamber B.

When the annular housing 27 is twisted to the R1 side from the position shown in FIG. 9, the annular housing 27 passes through the neutral position and performs the reverse operation of FIG. As described above, a large viscous resistance is obtained during a large vibration. In addition, when the torsion angle increases, the sheet member 23 of the coil spring 22
The rigidity is increased because the end portions a and the spring receiving portions 13a and 14a of the input side plates 13 and 14 come into full contact with each other. In other words, during large vibrations,
The characteristic of large viscous resistance can be obtained, and the vibration at the time of tip-in and tip-out (a large front-back vibration of the vehicle body caused when the accelerator pedal is suddenly operated) can be effectively attenuated.

As shown in FIG. 9, it is assumed that the minute vibration is transmitted in a state where the annular housing 27 is twisted to the driven plate 19 at a predetermined angle R2. Then, the slide stopper 29 repeats the reciprocating twisting operation with respect to the projection 19d within an angle range in which the circumferential wall does not abut on the projection 19d. At this time, the viscous fluid does not flow through the choke portion C and does not generate a large viscous resistance. That is, even if the torsion angle between the annular housing 27 and the driven plate 19 is large, the minute vibration can be effectively absorbed. Second Embodiment FIG. 10 shows a damper device 101 as one embodiment of the present invention. Damper device 101
Is a device for transmitting torque from the crankshaft 301 on the engine side to the main drive shaft 302 of the transmission and attenuating torsional vibration. In FIG. 10, 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, O- in FIG.
The O line is the rotation axis of the damper device 101.

The damper device 101 mainly includes a flexible plate 102, a ring member 108 fixed to the flexible plate 102, a hub flange 103,
And a damper 104. The flexible plate 102 is a substantially disk-shaped member, can be bent in the bending direction, and has high rigidity in the circumferential direction. The flexible plate 102 has a center hole 102a at the center. In addition, the flexible plate 102 has a plurality of window holes 102b formed at an intermediate portion in the radial direction at equal intervals in the circumferential direction. A plurality of bolt holes 102c are formed at equal intervals in the circumferential direction on the inner peripheral side of the window hole 102b. The bolt 106 penetrating through the bolt hole 102c causes the inner peripheral end of the flexible plate 102 to
1 is fixed to the tip. Further, a plurality of arc-shaped inertia members 107 are fixed to the outer peripheral portion of the flexible plate 102 on the engine side by rivets 151. With the inertia member 107, the damper device 1
01 is increased. In addition, since the inertia member 107 has a shape obtained by dividing the annular member in the circumferential direction, the bending of the flexible plate 102 in the bending direction is guaranteed. The outer peripheral end of the flexible plate 102 is interposed between the disc-shaped plate 1 and the plurality of bolts 110.
09 is fixed to the ring member 108. The inertia member 107 has a notch corresponding to the bolt 110.

The hub flange 103 has a boss 103a,
Flange 103b integrally formed on the outer periphery of boss 103a
Consists of The boss 103a protrudes toward the engine, and has a spline hole 103c formed at the center thereof to engage with spline teeth of the main drive shaft 302 extending from the transmission side. A cap-shaped member 141 for closing the center hole is fixed to the engine side of the center hole of the boss 103a.

The damper 104 mainly includes a first input side plate 113, a second input side plate 114, a driven plate 119, a coil spring 122, and a viscous resistance generating section 125 (a torsional vibration damping section). Have.
First input side plate 113 and second input side plate 114
Is a disk-shaped sheet metal member. First input side plate 113
Is composed of a disk portion 113a and a hollow cap 113b protruding from the center of the disk portion 113a toward the engine. The hollow cap 113b is integrally formed by drawing from the center of the disk portion 113a. A center hole 113c is formed at the center of the hollow cap 113b.
The second input side plate 114 has a cylindrical wall extending to the engine side at an outer peripheral portion and fixed to the outer peripheral end of the first input side plate 113. The cylindrical wall is welded to the inner periphery of the ring member 108. Thus, the first and second input side plates 113 and 114 rotate integrally with the ring member 108. That is, the plates 113, 1
Reference numeral 14 functions as an input-side member. The first input side plate 113 and the second input side plate 114 form an annular fluid filling chamber A for accommodating the driven plate 119, the coil spring 122, the viscous resistance generator 125, and the like. The viscous fluid is filled in the annular fluid filling chamber.

The driven play 119 is a disk-shaped member, and its inner peripheral end is connected to the flange 103b of the hub flange 103 by a plurality of rivets 120. In this way, the driven plate 119 is connected to the hub flange 103.
And rotate together. That is, the driven plate 119 is
It functions as a flange of the hub flange 103, that is, as a part of the output side member. A plurality of window holes 119 extending in the circumferential direction are provided at a radially intermediate portion of the driven plate 119.
a is formed. In addition, the driven plate 119
Annular sealing grooves 119 are provided on both sides of the outer peripheral end of
b is formed. A plurality of projections 119d extend radially outward from the outer peripheral surface 119c of the driven plate 119.

The coil spring 122 is formed by combining large and small coil springs.
It is arranged in the window hole 119a of the driven plate 119. The sheet member 1 is provided at both ends of the coil spring 122.
23 are arranged. The first input side plate 11
The spring receiving portions 113d and 114d are formed in the portion corresponding to the window hole 119a of the driven plate 119 in the third input side plate 114 and the second input side plate 114, respectively. Sheet members 123 are in contact with both ends in the circumferential direction of the spring housings 113d and 114d. Thus, the input side plates 113 and 114 and the driven plate 119 are elastically connected in the circumferential direction via the coil spring 122. In the free state, the sheet member 123 is in contact with the ends of the spring housings 113d and 114d of the input side plates 113 and 114 and the end of the window hole 119a of the driven plate 119 only at the inner peripheral portion. That is, the coil spring 122 is biased and the window hole 119 a and the spring housing 113 are
d, 114d.

Next, the viscous resistance generator 125 will be described. The viscous resistance generating unit 125 includes an annular housing 127 disposed at the outermost periphery in the annular fluid filling chamber A, and a plurality of pins 128 connecting the annular housing 127 to the first input side plate 113 and the second input side plate 114. , A plurality of slide stoppers 129 disposed in the housing 127.

The annular housing 127 is disposed inside the outer peripheral wall of the second input side plate 114, and both end faces in the axial direction are sandwiched between the input side plates 113 and 114. An opening extending in the circumferential direction is formed on the inner peripheral side of the annular housing 127, and the outer peripheral portion of the driven plate 129 is inserted into the opening. An annular fluid chamber filled with a viscous fluid is formed in the annular housing 127. Further, a plurality of stopper portions 127a are integrally formed in the annular housing 127 at equal intervals in the circumferential direction. The stopper portion 127a divides the annular fluid chamber B into a plurality of arc-shaped fluid chambers. The stopper 127a is a pin 128
Has a hole through which it is inserted. Both ends of the pin 128 are non-rotatably engaged with the input side plates 113 and 114.
Thereby, the annular housing 127 and the input side plate 1
13, 114 are integrally rotated. The width of the annular housing 127 for determining the viscous resistance is determined by the length of the body of the pin 128.

At the radially inner end of the annular housing 127, annular projections 127b projecting toward each other are provided.
(The opening is formed between the protrusions 127 b). The protrusion 127 b is fitted into an annular sealing groove 119 b formed in the driven plate 119, and the inner peripheral side of the annular fluid chamber B is formed. Sealed. Annular projection 127b
The sealing portion between the groove and the sealing groove 119b is connected to the input side mechanism (input side plates 113 and 114) via a viscous fluid.
The load (thrust load, radial load, and bending load) generated between the annular housing 127 and the output side mechanism (the driven plate 119, the hub flange 103) is shared and supported by a bearing 117 described later.

A return hole 1 is provided at the center between the stopper portions 127a on the radial inner side of both end surfaces.
27c are formed. The return hole 127c allows the viscous fluid to freely move between the annular fluid chamber B and the annular fluid filling chamber A. In the free state, the protrusion 119d of the driven plate 119 is
7c.

The slide stopper 129 is a cap-shaped member that covers the projection 119d of the driven plate 119 from the outer peripheral side in each arc-shaped fluid chamber. The structures of the slide stopper 129 and the remaining viscous fluid part 125 are the same as the structures of the slide stopper 29 and the viscous resistance generating part 125 of the first embodiment, and thus the description thereof will be omitted. A spring seal member 135 is sandwiched between a portion where the inner peripheral portion of the driven plate 119 and the flange 103b of the hub flange 103 are fixed by rivets 120. The spring seal member 135 is made of an annular thin sheet metal, and has a fixed portion fixed by the rivet 120, an inner peripheral end portion of the second input side plate 114 extending from the outer peripheral side of the fixed portion, and abutting on the engine side to form an inner peripheral end portion. And a biasing portion for biasing the portion toward the transmission. The reaction force generated by this urging force causes the driven plate 119 and the hub flange 10
3 is biased toward the engine. Spring seal member 13
5 is the second input side plate 1 in the annular fluid filling chamber A.
14 and the outer periphery of the hub flange 103 are sealed.

The hollow cap 113b of the first input side plate 113 is
2a. That is, the first input side plate 113 is positioned by the flexible plate 102. Disk portion 1 of first input side plate 113
A bearing 117 is arranged between the inner circumference of 13a and the outer circumference of the boss 103a of the hub flange 103. Bearing 117
The outer ring is fixed to the first input side plate 113 by an annular fixing member 152 and a rivet 153.
The boss 103a is inserted inside the inner ring of the bearing 117,
Further, it has a portion that comes into contact with the transmission-side end surface of the inner race.

As described above, the first input side plate 11
3 is positioned in the center hole 102 a of the flexible plate 102, and the first input side plate 113 supports the bearing 117. Thereby, the flexible plate 102, the first input side plate 113, the bearing 117
And the concentricity of the hub flange 103 is improved. In this embodiment, the bearings 117 are arranged within the pitch circle of the bolts 106 for fixing the flexible plate 102 to the crankshaft 301. Therefore, the degree of freedom in designing the inner peripheral side of the damper 104 is improved. Therefore, for example, it is possible to extend the driven plate 119 to the inner peripheral side and to arrange the coil spring 122 more inside.
Further, a space for rotating the head of the bolt 106 can be easily secured.

The bearing 117 has a seal member for sealing between the inner ring and the outer ring at both end surfaces. This seal member seals the lubricant between the inner ring and the outer ring, and also allows the first input side plate 11
3 and the boss 103a of the hub flange 103 are sealed. The hub flange 103 is urged toward the engine by the spring seal member 135 as described above. Therefore, the hub 117 is provided on the bearing 117.
The engine is pre-pressed by applying force to the engine side. As described above, the spring seal member 135 is provided in the annular fluid filling chamber A.
And also functions as an urging member for applying a preload to the bearing 117, and a single member has a plurality of functions. As a result, the number of parts can be reduced, and the manufacturing cost is reduced. Further, the cost is reduced because the spring seal member 135 is made of sheet metal.

In this embodiment, the hub flange 10
The third boss 103a is inserted into the hollow cap 113b of the first input side plate 113. As a result, the axial dimension of the entire damper device 101 is reduced. Moreover,
In this structure, the bearing 117 is the first input side plate 11
3, the bearing 117 can be further downsized in the radial direction. This reduces costs.

A first inertia member 142 is provided on the transmission side of the flange 103b of the hub flange 103. The first inertia member 142 is a disk-shaped member that covers the transmission side of the second input side plate 114, and the inner peripheral end is fixed to the flange 103 b and the driven plate 119 by rivets 120. A second inertia member 144 is fixed to the transmission side of the first inertia member 142 by a rivet 143. The second inertia member 144 is a disk-shaped member, and is entirely in contact with the first inertia member 142 on the transmission side. The first inertia member 142 and the second inertia member 144 increase the moment of inertia of the output side mechanism. Further, the ring gear 111 for starting the engine is welded to the outer periphery of the first inertia member 142. The engine starting ring gear 111 is a member conventionally welded to the outer periphery of the ring member 108, but by moving from the input side mechanism to the output side mechanism as in the present embodiment, the moment of inertia of the output side mechanism can be easily changed. The ratio can be increased. When the inertia moment ratio of the output side mechanism increases, it becomes possible to lower the resonance frequency in the driving system including the damper device 101 to the idling speed (practical speed) or lower of the vehicle. As described above, the cost is reduced by using the conventionally provided engine start ring gear 111 as the inertia of the output side mechanism.

The operation is almost the same as that of the first embodiment, and the description is omitted.

[0053]

In the damper device according to the first aspect, since the bearing is disposed inside the pitch circle of the fastening member, the degree of freedom in designing the radially inner peripheral side of the torsional vibration damping portion is improved. In the damper device according to the second aspect, since the boss of the input-side member is fitted and supported in the center hole of the flexible plate, the concentricity of each member is increased.

In the damper device according to the third aspect, since the output side member has the inertia member, the ratio of the inertia moment of the output side mechanism to the inertia moment of the input side mechanism is increased, and the vibration in the practical rotation range is suppressed. be able to.

[Brief description of the drawings]

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

FIG. 2 is a cutaway plan view of the damper device as viewed from the transmission side.

FIG. 3 is a cutaway plan view of the damper device as viewed from the engine side.

FIG. 4 is an enlarged partial view of FIG. 1;

FIG. 5 is an enlarged partial 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 view corresponding to FIG. 5, showing one state of the twisting operation.

FIG. 9 is an enlarged partial view of FIG. 2 showing one state of the twisting operation.

FIG. 10 is a view corresponding to FIG. 1 in another embodiment of the present invention.

[Description of Signs] 1,101 Damper device 2,102 Flexible plate 3,103 Hub flange 4,104 Damper 6,106 Crankshaft 13,113 First input side plate 14,114 Second input side plate 15 Boss 17,117 Bearing 102a Center hole 103a Boss 113a Disk 113b Central cap 301 Crankshaft 302 Main drive shaft

Claims (3)

[Claims] 1. A damper device for transmitting torque between an engine-side crankshaft and an output-side rotator, wherein a plurality of fastening members arranged on a circumference provide an inner peripheral end to a distal end of the crankshaft. A disk-shaped flexible plate, an input-side member fixed to an outer peripheral end of the flexible plate, an output-side member connected to the output-side rotating body, and a pitch circle of the plurality of fastening members. And a bearing that supports the input-side member and the output-side member so as to be relatively rotatable, and elastically connects the input-side member and the output-side member in a circumferential direction, and the input-side member and A damper device comprising: a torsional vibration damping unit for attenuating torsional vibration between the output side member and the output side member. 2. The input-side member includes a disk-shaped member having an outer peripheral end connected to an outer peripheral end of the flexible plate, and an inner peripheral end of the disk-shaped member, and the bearing is mounted on the outer periphery. The damper device according to claim 1, comprising a boss, wherein the flexible plate has a center hole, and the boss is fitted and supported in the center hole. 3. The damper device according to claim 1, wherein the output side member further has a disk-shaped inertia member formed to rotate integrally with the boss portion.