JP3474621B2 - Damper device - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a damper device, and more particularly to
The present invention relates to a damper device that transmits torque between an input side rotating body and an output side rotating body.

[0002]

2. Description of the Related Art A damper device for transmitting torque and attenuating torsional vibration is arranged between an input side rotating body and an output side rotating body in an automobile. Generally, a damper device is arranged between an input side member connected to an input side rotating body, a boss portion connected to an output side rotating body, and an input side rotating body and a boss portion so that both members are relatively rotatable. And a damping portion for elastically coupling the input side member and the boss portion in the circumferential direction and damping the torsional vibration between the both members.

A flange extending outward in the circumferential direction is formed on the outer periphery of the boss portion, and the flange is supported by the bearing.

[0004]

In the above conventional damper device, the flange of the boss portion extends outward in the circumferential direction to support the bearing, so that the entire boss portion becomes large. Since the boss is a forged product, the weight increases and the cost increases. An object of the present invention is to reduce the weight of the boss portion.

Another object of the present invention is to reduce the cost.

[0006]

A damper device according to a first aspect of the present invention is a device for transmitting torque between an input side rotating body and an output side rotating body, and includes a rotating member, a boss, and a circle. It is provided with a plate member, a bearing, and a damping portion. The rotating member is connected to one of the input side rotating body and the output side rotating body. The boss portion is connected to the other of the input side rotating body and the output side rotating body. The inner peripheral portion of the disc-shaped member is fixed to the outer periphery of the boss portion. The bearing is arranged between the rotating member and the disc-shaped member and supports both members so as to be rotatable relative to each other. The damping portion elastically connects the rotating member and the disk-shaped member in the circumferential direction, and damps the torsional vibration between the rotating member and the boss portion.

In the damper device according to the second aspect of the present invention, the bearing has an outer race and an inner race, the outer race of the bearing is mounted on the disk-shaped member, and the inner race is mounted on the rotating member. In the damper device according to the third aspect of the present invention, the rotating member is a disc-shaped plate made of sheet metal and has a supporting member that supports the inner race .
In the damper device according to the fourth aspect of the present invention, the support member has a cross section L.
It is a V-shaped annular member.

In the damper device according to the fifth aspect of the invention, the disk-shaped member has an annular protrusion into which the outer race is inserted. In the damper device according to the sixth aspect, the damping section is
One sheet metal disc-shaped driven plate connected to the rotating member and having a window hole extending in the circumferential direction and a folded portion around the window hole; and a rotating member driven by the folded portion in the window hole and driven by the rotating member. An elastic member that elastically connects the plate in the circumferential direction, and a resistance portion generation that generates resistance when the rotating member and the driven plate rotate relative to each other.

In the damper device according to the seventh aspect of the present invention, the rotating member has a disk shape. Further, the disk-shaped plate is further provided, the outer peripheral portion of which is connected to the rotating member and which forms a fluid space filled with the fluid between the rotating member. Further, the inner peripheral portion of the disc-shaped plate is configured to contact the rotating member by the pressure generated in the fluid space to seal the fluid space.

In the damper device according to the eighth aspect of the present invention, the inner peripheral portion of the disc-shaped member is bent in the axial direction. Further, the rotating member has an annular protrusion with which the inner peripheral portion of the disc-shaped member can abut.

[0011]

In the damper device according to the first aspect of the present invention, the torque from the input side rotating body is transmitted to the output side rotating body via the rotating member, the damping portion, the disc-shaped member and the boss portion. When the torsional vibration is transmitted from the input side rotating body to the damper device,
The rotating member and the boss portion repeat the reciprocal twisting operation via the damping portion. At this time, the torsional vibration between the rotating member and the boss portion is damped by the damping portion.

In this damper device, the disk-shaped member fixed to the outer periphery of the boss is supported by the bearing. Therefore, it is not necessary to provide the boss portion with a portion supported by the bearing, and the boss portion can be reduced in weight. As a result, the cost is reduced. In the damper device according to the second aspect of the present invention, the outer race is attached to the disc-shaped member and the inner race is attached to the rotating member. In this case, the boss portion can be reduced in weight as in the above, and the cost is reduced.

In the damper device according to the third aspect of the present invention, the rotating member is a disc-shaped plate made of sheet metal and has a supporting member for supporting the inner race, so that the above-described action becomes more effective. In the damper device according to the fourth aspect of the present invention, the support member is an annular member having an L-shaped cross section, so that the above-described action becomes more effective.

In the damper device according to the fifth aspect of the present invention, the disk-shaped member has the annular projection into which the outer race is inserted, so that the above-described action becomes more effective. In the damper device according to the sixth aspect of the present invention, by providing the folded-back portion around the window hole of the driven plate, the surface pressure of the portion where the disk-shaped plate supports the elastic member decreases. That is, it is possible to secure the durability required by a single disc-shaped plate made of sheet metal,
As a result, the weight of the device is reduced and the cost is reduced.

In the damper device according to the seventh aspect of the present invention, the inner peripheral portion of the disk-shaped plate abuts the rotating member by the pressure generated in the fluid space to seal the fluid space, so that the conventional sealing member is omitted. You can As a result, the number of parts is reduced and the cost is reduced. In the damper device according to the eighth aspect of the present invention, the inner peripheral portion of the disc-shaped member is bent in the axial direction, and the rotating member has an annular protrusion with which the inner peripheral portion of the disc-shaped member can abut. Therefore, the above action becomes more effective.

[0016]

1 and 2 show a damper device 1 as an embodiment of the present invention. The damper device 1 is a device for transmitting torque from the crankshaft 301 on the engine side to the main drive shaft 302 of the transmission. In FIG. 1, an engine (not shown) is arranged on the left side of the drawing, and a transmission (not shown) is arranged on the right side of the drawing. Further, the line OO in FIG. 1 is the rotation axis of the damper device 1, and
The R ₁ direction (clockwise direction) is the rotation direction of the damper device 1.

The damper device 1 mainly elastically connects the flexible plate 2, the hub flange 3, the flexible plate 2 and the hub flange 3 in the circumferential direction, and damps the torsional vibration between both members. And a damping unit 4 for The flexible plate 2 is a generally disk-shaped member, is flexible in the bending direction, and has high rigidity in the rotation direction. The flexible plate 2 has a central hole 2 at the center.
a. Further, the flexible plate 2 has a plurality of bolt holes 2b on the inner peripheral portion at equal intervals in the circumferential direction. By the bolt 6 penetrating the bolt hole 2b, the inner peripheral end of the flexible plate 2 is moved to the crankshaft 301.
Fixed at the tip of. The outer peripheral edge of the flexible plate 2 is fixed to the ring member 9 by a plurality of bolts 10. The outer peripheral ends of a first input side plate 13 and a second input side plate 14, which will be described later, are sandwiched between the outer peripheral portion of the flexible plate 2 and the ring member 9. That is, the first input side plate 13 and the second input side plate 1
4 is fixed to the flexible plate 2.

The hub flange 3 includes a boss 3a and a boss 3a.
And a flange 3b integrally formed on the outer periphery of the. A spline hole 3c that engages with a spline tooth of the main drive shaft 302 extending from the transmission side is formed at the center of the boss 3a. Further, a cap member 41 is fixed to the engine side in the center hole of the boss 3c.

The hub flange 3b has a plurality of rivets 21 having an inner peripheral end of a disc-shaped inertia member 40 (disc-shaped member).
It is fixed by. The disc-shaped inertia member 40 is
An annular protrusion 40a that protrudes toward the engine is provided slightly inside the radial center. An inertia member 42 is fixed to the outer peripheral engine side of the disc-shaped inertia member 40 by a plurality of rivets 43. Further, the disc-shaped inertia member 40 has an outer peripheral cylindrical portion 40c extending toward the engine. The engine starting ring gear 11 is fixed to the outer periphery of the outer peripheral cylindrical portion 40c.

The attenuator 4 is mainly composed of the first input side plate 1
3 (rotating member) , the second input side plate 14, the driven plate 19, the coil spring 22, and the viscous resistance generating portion 25. The first input side plate 13 and the second input side plate 14 are disk-shaped disc-shaped members. First input side plate 13 and second input side plate 14
The outer peripheral portions of and are fixed to the flexible plate 2 and the ring member 9 as described above. The first input side plate 13 and the second input side plate 14 include a driven plate 19, a coil spring 22 and a viscous resistance generating section 2.
A fluid space A for housing 5 and the like is formed. The fluid space A is filled with viscous fluid.

The first input side plate 13 is a disk portion 13a.
And a central cap 13b projecting from the center of the disc portion 13a toward the engine. Central cap 1
3b is integrally formed from the disk portion 13a by drawing. The hole 13 is formed at the center of the tip of the central cap 13b.
c is formed. A cap 54 is fitted in the hole 13c. Disc portion 13a of the first input side plate 13
A plurality of inertia members 8 are fixed to the outer peripheral portion on the engine side.

A bearing 17 is arranged between the inner circumference of the first input side plate 13 and the inner circumference of the disc-shaped inertia member 40. The bearing 17 supports the inner peripheral portion of the disc-shaped inertia member 40 so as to be rotatable relative to the first input side plate 13. Disc portion 13 of first input side plate 13
An annular fixing member 52 having an L-shaped cross section is fixed to the inner peripheral portion of a. The annular fixing member 52 supports the inner race of the bearing 17. The outer race of the bearing 17 is supported inside the annular protrusion 40 a of the disc-shaped inertia member 40. The bearing 17 has a seal member that seals between the inner race and the outer race on both end faces. This seal member seals the lubricant between the inner race and the outer race, and in the fluid space A, between the inner peripheral portion of the first input side plate 13 and the inner peripheral portion of the disc-shaped inertia member 40. It is sealed.

The second input side plate 14 has a large center hole. Inner peripheral edge 14a of the second input side plate 14
Is bent to the engine side. The inner peripheral end 14a is close to the outer peripheral side of the annular protruding portion 40a of the disc-shaped inertia member 40. The inner peripheral end 14a of the second input side plate 14 is deformable and can contact the annular protrusion 40a when pressure is generated in the fluid space A.

The driven plate 19 is a single disk-shaped member made of sheet metal, and its inner peripheral end is fixed to the annular protruding portion 40a of the disk-shaped inertia member 40 by a plurality of rivets 20. In the radial middle part of the driven plate 19,
As shown in FIG. 2, a plurality of window holes 19a extending in the circumferential direction.
Are formed. Further, a folded-back portion 19b raised to the transmission side is formed on the entire circumference of the window hole 19a. A plurality of protrusions 19c extend radially outward from the outer peripheral surface of the driven plate 19. Protrusion 19
A bent portion 19d bent toward the transmission is formed at the tip of c.

The coil springs 22 are combinations of large and small coil springs, and are arranged in the window holes 19a of the driven plate 19. Sheet members 23 are arranged at both ends of the coil spring 22. The first input side plate 13 and the second input side plate 14 are provided with spring accommodating portions 13d and 14d at portions corresponding to the window holes 19a of the driven plate 19. Seat members 23 are in contact with both ends of the spring accommodating portions 13d and 14d in the circumferential direction. In this way, the input side plates 13 and 14 and the driven plate 19 are
And are elastically connected in the circumferential direction via the coil spring 22. Note that in the free state shown in FIG. 2, the sheet member 23 has the input side plate 13,
The end portions of the spring accommodating portions 13a and 14a of 14 and the end portion of the window hole 19a of the driven plate 19 are in contact with each other only at the inner peripheral portion. That is, the coil spring 22 is biased against the window hole 19a and the spring accommodating portions 13a, 1a.
It is stored in 4a.

The sheet member 23 is a driven plate 19
It is supported by the folded portion 19b formed on the. By providing the folded-back portion 19b in this way, the driven plate 19 can reduce the surface pressure generated when the coil spring 22 and the sheet member 23 are supported, and the durability is improved. As a result, it is not necessary to use a plurality of sheet metal plates or a disk-shaped plate made of a thick cast component as in the conventional case. Therefore, the driven plate is lightened and the cost is reduced.

Further, the driven plate 19 is arranged in the fluid space A. Therefore, driven plate 1
The folded portion 19b of 9 is lubricated by viscous fluid. As a result, the durability of the folded portion 19b is improved. Next, the viscous resistance generator 25 will be described. The viscous resistance generating portion 25 includes an annular housing 27 arranged on the outermost periphery in the fluid space 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 (see FIG. 2). ) And a plurality of slide stoppers 29 arranged in the annular housing 27.

The annular housing 27 is arranged inside the outer peripheral cylindrical wall of the second input side plate 14, and both axial end faces are sandwiched between the input side plates 13 and 14. The annular housing 27 is a member having a U-shaped cross-section that is open on the engine side, and as shown in FIG. 4, has a clearance 27 a that extends in the circumferential direction between the first input side plate 13 and the inner peripheral surface engine side. is doing. The outer periphery of the driven plate 19 is sandwiched in the gap 27a. In the annular housing 27, a plurality of stopper portions 27b are integrally formed at equal intervals in the circumferential direction. The stopper portion 27b divides the annular fluid chamber B into a plurality of arcuate fluid chambers B ₁ . The stopper portion 27b has a hole through which the pin 28 is inserted. Both ends of the pin 28 are non-rotatably engaged with the input side plates 13 and 14. This allows the annular housing 27 to rotate integrally with the input side plates 13 and 14.

In each stopper portion 27b, a choke portion C is formed between the stopper plate 27b and the outer peripheral surface of the driven plate 19 so as to communicate each arc-shaped fluid chamber B ₁ . When the viscous fluid passes through the choke portion C, a large viscous resistance is generated.
The protrusion 1 of the driven plate 19 is provided in each arc-shaped fluid chamber B ₁ .
A box-shaped resin slide stopper 29 that covers 9c and the bent portion 19d is arranged. Slide stopper 29
Is open on the engine side. Slide stopper 2
Reference numeral 9 has a surface that coincides with the inner peripheral surface of the annular housing 27, and is movable in the circumferential direction in the arc-shaped fluid chamber B ₁ .
As shown in FIG. 5, the slide stopper 29 has a notch 29a extending in the circumferential direction on the engine side at the inner peripheral portion. The driven plate 19 is passed through the notch 29a.
The projection 19c is inserted into the slide stopper 29. In this way, the slide stopper 29 is movable in the circumferential direction with respect to the protrusion 19c and the bent portion 19d of the driven plate 19 within a range in which the circumferential wall portion abuts the bent portion 19d.

Inside each arc-shaped fluid chamber B ₁ , a _first partition chamber 31 on the R ₂ side and a _second chamber on the R ₁ side by a slide stopper 29.
It is divided into a compartment 32. Next, the operation will be described. When torque is input to the flexible plate 2 from the crankshaft 301, the torque is transmitted to the driven plate 19 via the input side plates 13 and 14 and the coil spring 22. The torque transmitted to the driven plate 19 is applied to the disc-shaped inertia member 40.
It is transmitted to the hub flange 3 via and is output to the main drive shaft 302. Crankshaft 3
The bending vibration included in the torque transmitted from 01 is absorbed by the flexible plate 2.

Next, the operation when the torsional vibration is transmitted from the crankshaft 301 to the damper device 1 will be described. However, here, the operation when the torsional vibration is transmitted is fixed to the output side mechanism (the driven plate 19, the disc-shaped inertia member 40 and the hub flange 3) to another member (not shown) in a non-rotatable manner. On the other hand, the input side mechanism (the first input side plate 13, the second input side plate 1
4 and the annular housing 27) will be replaced with the operation when twisted.

First, a torsional vibration (hereinafter referred to as a minute vibration) having a small deviation angle in which the circumferential wall portion of the slide stopper 29 does not come into contact with the protrusion 19c and the bent portion 19d of the driven plate 19 is transmitted. The operation at this time will be described. In this case, since relative rotation does not occur between the annular housing 27 and the slide stopper 29, the viscous fluid does not pass through the choke portion C. That is, a large viscous resistance does not occur during minute vibration. Further, at the time of slight vibration, the coil spring 22 expands and contracts in a biased manner with respect to the window hole 19a of the driven plate 19 and the spring accommodating portions 13d and 14d of the input side plates 13 and 14, respectively. Therefore, a low rigidity state can be obtained. That is, in the case of minute vibration, characteristics of low rigidity and small viscous resistance are obtained, and it is possible to effectively suppress generation of abnormal noise such as gear rattle and muffled sound of the transmission.

Next, the operation when a torsional vibration having a large deflection angle (hereinafter referred to as a large vibration) is transmitted will be described. When the circumferential wall portion of the slide stopper 29 comes into contact with the bent portion 19d of the driven plate 19,
Next, the first compartment 31 or the second compartment 32 is compressed between the slide stopper 29 and the stopper portion 27d. The viscous fluid flows from the compressed compartment through the choke portion C into the other arcuate fluid chamber B ₁ . Viscous fluid is choke part C
A large viscous resistance occurs when flowing through.

As described above, a large viscous resistance can be obtained at the time of large vibration. Moreover, when the twisting angle becomes large, the seat member 23 of the coil spring 22 is moved to the window hole 1
Since the end portion of 9a and the end portions of the spring accommodating portions 13d and 14d of the input side plates 13 and 14 are entirely contacted, the rigidity is increased. That is, the characteristics of high rigidity and large viscous resistance are obtained at the time of large vibration, and the vibration at the time of tip-in / tip-out (the large vibration before and after the vehicle body which occurs when the accelerator pedal is suddenly operated) can be effectively damped.

Further, it is assumed that the micro-vibration is transmitted while the annular housing 27 is twisted with respect to the driven plate 19 by a predetermined angle. Then, the slide stopper 29
The reciprocal twisting operation is repeated with respect to the bent portion 19d within the angular range in which the circumferential wall portion abuts the protrusion 19c and the bent portion 19d. In this case, the viscous fluid is the choke part C
Does not flow, and as a result, does not generate a large viscous resistance. That is, even if the twist angle between the annular housing 27 and the driven plate 19 is large, the minute vibration can be effectively damped.

If pressure is generated in the fluid space A due to viscous resistance or centrifugal force during operation, the inner peripheral portion 14a of the second input side plate 14 moves and the disc-shaped inertia member 4 is moved.
The annular protrusion 40a of 0 abuts on the outer peripheral side. As a result, the gap between the second input side plate 14 and the disc-shaped inertia member 40 is sealed. Here, since the seal member which is conventionally required can be omitted, the structure is simplified and the cost is reduced.

[0037]

In the damper device according to the first aspect of the present invention, since the disk-shaped member fixed to the outer circumference of the boss is supported by the bearing, it is not necessary to provide the boss with a portion supported by the bearing. The weight of the boss can be reduced. In the damper device according to the second aspect of the present invention, the outer race is attached to the disc-shaped member and the inner race is attached to the rotating member. In this case, the boss portion can be reduced in weight as in the above, and the cost is reduced.

In the damper device according to the third aspect of the present invention, the rotating member is a plate-shaped disc made of sheet metal and has a supporting member for supporting the inner race, so that the above effect becomes more remarkable. In the damper device according to the fourth aspect of the present invention, since the support member is an annular member having an L-shaped cross section, the above effect becomes more remarkable.

In the damper device according to the fifth aspect of the invention, since the disc-shaped member has the annular protrusion into which the outer race is inserted, the above effect becomes more remarkable. In the damper device according to the sixth aspect of the present invention, by providing the folded-back portion around the window hole of the driven plate, the surface pressure of the portion where the disk-shaped plate supports the elastic member decreases. That is, it is possible to secure the durability required by one sheet metal disc-shaped plate, which reduces the weight of the device and reduces the cost.

In the damper device according to the seventh aspect of the present invention, the inner peripheral portion of the disk-shaped plate abuts the rotating member by the pressure generated in the fluid space to seal the fluid space, so that the conventional sealing member is omitted. You can As a result, the number of parts is reduced and the cost is reduced. In the damper device according to the eighth aspect of the present invention, the inner peripheral portion of the disc-shaped member is bent in the axial direction, and the rotating member has an annular protrusion with which the inner peripheral portion of the disc-shaped member can abut. Therefore, the above effect becomes more remarkable.

[Brief description of drawings]

FIG. 1 is a schematic partial vertical cross-sectional view of a damper device according to an embodiment of the present invention.

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

FIG. 3 is an enlarged partial view of FIG.

FIG. 4 is a view on arrow IV in FIG.

5 is a view on arrow V in FIG.

[Explanation of symbols]

1 damper device 3a boss 4 Attenuator 13 1st input side plate 17 Bearing 40 Disc-shaped inertia member

Continuation of the front page (56) Reference JP-A-4-194433 (JP, A) JP-A-5-71587 (JP, A) JP-A-5-133439 (JP, A) JP-A-6-26524 (JP , A) JP-A-4-272545 (JP, A) JP-A-4-277348 (JP, A) US Pat. No. 5367920 (US, A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16F 15/16 F16F 15/123 F16F 15/30 F16F 15/134 PCI (DIALOG)

Claims (8)

(57) [Claims] 1. A damper device for transmitting torque between an input side rotating body and an output side rotating body, comprising: a rotating member connected to one of the input side rotating body and the output side rotating body; A boss portion connected to the other of the side rotating body and the output side rotating body; a disc-shaped member having an inner peripheral portion fixed to the outer periphery of the boss portion; and between the rotating member and the disc-shaped member. A bearing arranged to support the two members so as to be rotatable relative to each other, and a rotating member and the disc-shaped member that are elastically connected in the circumferential direction, and a torsion between the rotating member and the boss portion. A damper device including a damping unit for damping vibrations. 2. The damper according to claim 1, wherein the bearing has an outer race and an inner race, the outer race is attached to the disc-shaped member, and the inner race is attached to the rotating member. apparatus. 3. The damper device according to claim 1, wherein the rotating member is a disc-shaped plate made of sheet metal, and has a supporting member that supports the inner race. 4. The damper device according to claim 3, wherein the support member is an annular member having an L-shaped cross section. 5. The damper device according to claim 1, wherein the disk-shaped member has an annular protrusion into which the outer race is inserted. 6. The damping unit is connected to the rotating member,
One sheet-metal disk-shaped driven plate having a window hole extending in the circumferential direction and a folded portion around the window hole; and the rotating member and the driven plate supported by the folded portion in the window hole. An elastic member that elastically connects and in the circumferential direction, and a resistance generating unit that generates resistance when the rotating member and the driven plate rotate relative to each other,
The damper device according to claim 1. 7. The rotating member is disc-shaped, and further comprises a disc-shaped plate having an outer peripheral portion connected to the rotating member and forming a fluid space filled with fluid between the rotating member and the rotating member. The damper device according to claim 1 or 6, wherein an inner peripheral portion of the disk-shaped plate is configured to contact the rotating member by a pressure generated in the fluid space to seal the fluid space. 8. The inner peripheral portion of the disc-shaped member is bent in the axial direction, and the rotating member has an annular projection with which the inner peripheral portion of the disc-shaped member can abut. The damper device according to claim 7.