JP3474625B2 - 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 which is arranged between an input side rotating body and an output side rotating body connected to an engine and which transmits torque.

[0002]

2. Description of the Related Art For example, a flywheel assembly is arranged as a damper device for transmitting torque between an engine and a transmission of a vehicle. The flywheel assembly has a first flywheel connected to the crankshaft on the engine side and a second flywheel assembly arranged on the transmission side.
Both flywheels are rotatably supported by bearings. A fluid space filled with a fluid is formed in the first flywheel by a disc member or the like, and both flywheels are elastically coupled in the circumferential direction in the fluid space and twisted between them. And a damping unit for damping the vibration. The ring gear for starting the engine is fixed to the outer circumference of the first flywheel.

[0003]

In an input / output system including a damper device in a vehicle, it is necessary to increase the moment of inertia of the output side mechanism in order to reduce the resonance frequency to be equal to or lower than the idle speed (practical speed) of the vehicle. is there. But first
Since the engine starting ring gear is fixed to the outer circumference of the flywheel, the inertia moment ratio of the output side mechanism cannot be sufficiently increased.

An object of the present invention is to increase the moment of inertia of the output side mechanism of the damper device. Another object of the present invention is to reduce costs.

[0005]

SUMMARY OF THE INVENTION A damper device according to the present invention includes a crankshaft on the engine side and a transmission.
Is a device that is arranged between the main drive shaft and the main drive shaft to transmit torque, and has an input side member, an output side member,
It includes a damping unit and an engine starting ring gear.
The input side member is connected to the crankshaft . The output-side member is rotatable relative to the input side member, transmitters
Center is connected to the main drive shaft
Has a hub flange . The damping portion elastically connects the input side member and the output side member in the circumferential direction, and damps the torsional vibration between the input side member and the output side member. The engine starting ring gear is fixed to the outer circumference of only the output side member . The output-side member further comprises a inertia member coupled to Ha Bufuranji, engine starting ring gear preferably fixed to the outer periphery of the inertia member.

Further, the inertia member is preferably a disc-shaped member.

[0007]

In the damper device according to the present invention, the crankshaft
The torque input from the gear shifts through the input side member, the damping unit, and the output side member to the main drive of the transmission.
It is output to the shaft . When the torsional vibration is transmitted from the crankshaft to the damper device, the input side member and the output side member repeat the reciprocal twisting operation via the damping portion.
The torsional vibration is damped by the damping unit.

In this damper device, the engine starting ring gear, which is conventionally fixed to the outer circumference of the input side member, is fixed to the outer circumference of the output side member. Therefore, the moment of inertia of the input side mechanism is reduced, and the moment of inertia of the output side mechanism is increased without providing a special member.
Increase the output-side member further comprises a inertia member coupled to Ha Bufuranji, when the engine starting ring gear is fixed to the outer periphery of the inertia member, the inertia moment of the further output-side mechanism by the inertia member To do.

If the inertia member is a disc-shaped member, the ring gear for starting the engine can be easily fixed to the outer periphery, which reduces the cost.

[0010]

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 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 in FIG. 2 is the rotation direction of the damper device 1.

The damper device 1 mainly comprises a flexible plate 2, a ring member 8 fixed to the flexible plate 2, a hub flange 3, and the ring member 8 and the hub flange 3 which are elastically connected in the circumferential direction. And a damping portion 4 for damping the torsional vibration between the two members. 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 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 in the middle portion in the radial direction. A plurality of bolt holes 2c are formed on the inner peripheral side of the round hole 2b at equal intervals in the circumferential direction. The inner peripheral end of the flexible plate 2 is fixed to the tip of the crankshaft 301 by a bolt 6 penetrating the bolt hole 2c. Further, a plurality of arc-shaped inertia members 7 shown in FIG. 3 are fixed by rivets 51 to the outer peripheral side engine side of the flexible plate 2. This inertia member 7
As a result, the moment of inertia of the damper device 1 is increased. Further, since the inertia member 7 has a shape obtained by dividing an annular member in the circumferential direction, the bending of the flexible plate 2 in the bending direction is guaranteed. Flexible plate 2
The outer peripheral edge of is fixed to the ring member 8 via a disc plate 9 by a plurality of bolts 10. The inertia member 7 has a notch corresponding to the bolt 10.

The hub flange 3 has 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. The attenuator 4 is mainly
First input side plate 13 and second input side plate 14
And driven plate 19 and coil spring 22
And a viscous resistance generator 25.

The first input side plate 13 and the second input side plate 14 are disk-shaped plate members. The inner peripheral edge of the first input side plate 13 extends further radially inward than the inner peripheral edge of the second input side plate 14. The second input side plate 14 has a cylindrical wall that extends toward the engine and is fixed to the outer peripheral end of the first input side plate 13 at the outer peripheral portion.
The cylindrical wall is welded to the inner circumference of the ring member 8. First input side plate 13 and second input side plate 1
4 is a driven plate 19, a coil spring 22
And a fluid space A for accommodating the viscous resistance generating portion 25 and the like. The fluid space A is filled with viscous fluid.

The driven plate 19 is a disk-shaped member, and the inner peripheral end of the driven plate 19 is formed by a plurality of rivets 20.
Is connected to the flange 3b. Driven plate 1
As shown in FIG. 2, a plurality of window holes 19a extending in the circumferential direction are formed in the middle portion of the radial direction 9. further,
Annular sealing grooves 19b are formed on both sides of the outer periphery of the driven plate 19. In addition, a plurality of protrusions 19d are provided from the outer peripheral surface 19c of the driven plate 19.
Extend radially outward.

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 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 of the spring accommodating portions 13a and 14a 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.

Next, the viscous resistance generator 25 will be described. The viscous resistance generating portion 25 includes an annular housing 27 arranged at the outermost periphery in the fluid space A and an annular housing 27.
The first input side plate 13 and the second input side plate 14
And 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 axial end faces 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, in the annular housing 27, a plurality of stopper portions 27a are integrally formed at equal intervals in the circumferential direction. Stopper part 27a
Divides the annular fluid chamber B into a plurality of arcuate fluid chambers B ₁ . The stopper portion 27a has a hole through which the pin 28 is inserted. Both ends of the pin 28 are the input side plates 13 and 14
Is non-rotatably engaged with. As a result, the annular housing 27 and the input side plates 13 and 14 rotate integrally. Further, the width of the annular housing 27 that determines the viscous resistance is determined by the length of the body portion of the pin 28.

An annular protrusion 27b is formed at the radially inner end of the annular housing 27 so as to project toward each other (the space between the protrusions 27b is the opening), and the protrusion 27b is a driven plate. The annular fluid chamber B is fitted into the annular sealing groove 19b formed in
The inner peripheral side of is sealed. Protrusion 27b and sealing groove 1
The engaging portion with 9b is an input side mechanism (input side plates 13 and 14 and annular housing 27) via a viscous fluid.
The load (thrust load, radial load, bending load) generated between the output side mechanism (driven plate 19 and hub flange 3) is shared and supported by the bearing 17 described later.

The return hole 27 is formed in the middle portion between the stopper portions 27a on the inner side in the radial direction 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 fluid space A. In the free state shown in FIG. 2, the protrusion 19d of the driven plate 19 is arranged at a position corresponding to the return hole 27c.

In each arc-shaped fluid chamber B ₁ , 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 that coincides with the outer inner peripheral surface of the annular housing 27 and is movably arranged in the arc-shaped fluid chamber B ₁ in the circumferential direction. Slide stopper 29
Is movable in the circumferential direction with respect to the projection 19d of the driven plate 19 within a range in which the circumferential wall portion abuts the projection 19d. The slide stopper 29 has notches 29a on the inner sides in the radial direction of both wall portions in the circumferential direction. Further, notches 29b are formed on the inner sides in the radial direction of both axial wall portions of the slide stopper 29. The radially inner portion of the stopper portion 29 is in contact with the annular protrusion 27b of the annular housing 27.

Inside each arc-shaped fluid chamber B ₁ , a first large chamber 31 on the R ₂ side and a second large chamber on the R ₁ side by a slide stopper 29.
It is divided into a large branch room 32. Furthermore, the slide stopper 29, the second small compartment 3 of the first small compartment 33 and R ₁ side of the R ₂ side by the protrusion 19d of the driven plate 19
It is divided into 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, a notch 29b of the slide stopper 29, and a return hole 27.
The viscous fluid can freely move back and forth by c. Further, the viscous fluid can freely move between the first large compartment 31 and the first small compartment 33 through the R ₂ side notch 29a of the slide stopper 29, and the second small compartment 34 and the second small compartment 34.
It is possible to freely move between the Oita chamber 32 and the slide stopper 29 through the notch 29a on the R ₁ side. However,
When the circumferential wall of the slide stopper 29 comes into contact with the protrusion 19d, the flow of the viscous fluid inside and outside the slide stopper 29 in the circumferential direction is blocked.

A choke portion C is formed between the inner peripheral surface of the stopper portion 27a and the outer peripheral surface 19c of the driven plate 19. When the 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 the inner peripheral portion of the driven plate 19 and the flange 3b of the hub flange 3 fixed by the rivet 20. The spring seal member 35 is made of an annular thin sheet metal, and has a fixing portion 35 a having a plurality of holes through which the rivet 20 passes, and a fixing portion 35.
The outer peripheral cylindrical portion 35b extends from the inner peripheral side of a to the transmission side, and the pressure contact portion 35c extends from the outer peripheral cylindrical portion 35b to the outer peripheral side. As shown in FIG. 4, the press contact portion 35c elastically contacts the inner peripheral end portion of the second input side plate 14 on the engine side. Due to the reaction force generated by this pressure contact force, the driven plate 19 and the hub flange 3 are urged toward the engine. The spring seal member 35 is
In the fluid space A, the second input side plate 14 and the hub flange 3 are sealed.

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

The 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 rotatable relative to each other. The inner race of the bearing 17 is fixed in the groove of the boss 15. The outer race of the bearing 17 is fixed to the inner circumference of the boss 3a. In this way, the boss 15 has the flexible plate 2
The bearing 17 is positioned in the center hole 2a of the above. As a result, the flexible plate 2,
The concentricity of the boss 15 and the bearing 17 is improved. In this embodiment, the load generated between the input side mechanism and the output side mechanism is
In the viscous resistance generating portion 25, the annular protrusion 27b of the annular housing 27 and the sealing groove 19b of the driven plate 19 are provided.
The bearing 17 is also supported by being shared by fitting with
The load acting on can be reduced. Therefore, the bearing 17 can be made smaller in the radial direction, and the cost is reduced. The bearing 17 is arranged in the pitch circle D (FIG. 2) of the crank bolt 6. As a result, the degree of freedom in designing the inner peripheral side of the damping section 4 is improved. Therefore, for example, it becomes possible to extend the driven plate 19 to the inner peripheral side and arrange the coil spring 22 to the inner peripheral side. Further, a space for rotating the head of the crank bolt 16 can be easily secured.

The bearing 17 has seal members for sealing 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 also seals between the boss 15 and the inner peripheral portion of the hub flange 3 in the fluid space A. The hub flange 3 is biased toward the engine by the spring seal member 35 as described above. Therefore, the bearing 17 is preloaded from the hub flange 3 to the engine side. In this way, the spring seal member 35 seals the fluid space A and the bearing 1
It also functions as a member for applying a preload to 7, and a single member has a plurality of functions. As a result, the number of parts can be reduced and the manufacturing cost can be reduced. Further, since the spring seal member 35 is made of sheet metal, the cost is low.

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 thereof is fixed to the flange 3b and the driven plate 19 by the rivet 20. By providing the inertia member 42, the moment of inertia of the output side mechanism is increased. Further, the engine starting ring gear 11 is welded to the outer periphery of the inertia member 42. Since the inertia member 42 is a disc-shaped member, it is easy to fix the ring gear 11. Therefore, the cost is reduced.
The ring gear 11 is a member that is conventionally welded to the outer periphery of the ring member 8. However, by moving from the input side mechanism to the output side mechanism as in this embodiment, the moment of inertia of the output side mechanism can be easily increased. . When the moment of inertia of the output side mechanism increases, it becomes possible to reduce the resonance frequency in the drive system including the damper device 1 to the idling speed (practical speed) of the vehicle or less. The cost is reduced by using the conventional ring gear 11.

Next, the operation will be described. When torque is input from the crankshaft 301 to the flexible plate 2, the torque passes through the ring member 8 and the input side plates 13 and 14, and is transmitted to the driven plate 19 via the coil spring 22. Driven plate 1
The torque of 9 is transmitted to the hub flange 3 and further output from the main drive shaft 302 to the transmission side. Bending vibration contained in the torque transmitted from the crankshaft 301 to the ring member 8 is insulated by the flexible plate 2 and is difficult to be transmitted to the damping portion 4 side. Even if the bending vibration is transmitted, the bending load is applied to the bearing 17 and the annular protrusion 27 of the annular housing 27.
b and the groove 19b for sealing of the driven plate 19 are engaged and supported in a shared manner. Therefore, the bearing 1
Since the load on the bearing 7 is reduced, the bearing 17 can be downsized in the radial direction. Therefore, the bearing 17 becomes inexpensive.

Next, the operation when the 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 output side mechanism (the driven plate 19 and the hub flange 3) is non-rotatably fixed to another member (not shown) and the input side mechanism ( First input side plate 1
3, second input side plate 14 and annular housing 27)
Will be replaced with the operation when twisted.

Torsional vibration with a small deviation angle such that the circumferential wall portion of the slide stopper 29 does not come into contact with the projection 19d of the driven plate 19 (hereinafter referred to as minute vibration).
The operation when is transmitted will be described. It is assumed that the input side plates 13 and 14 are twisted toward the R ₂ side in the free state shown in FIG. Then, the slide stopper 19 moves to the R ₂ side, and as shown in FIG. 6, the first small compartment 33 is expanded and the second small compartment 34 is contracted in the slide stopper 29.
The viscous fluid freely flows from the second small chamber 34 to the first small chamber 33 through the notch 29b and the return hole 27c between the outer peripheral portion of the slide stopper 29 and the protrusion 19d. Further, the viscous fluid can freely move between the inside of the slide stopper 29 and the fluid space A through the return hole 27c.

When the twisting operation is further continued from the state shown in FIG. 6, the circumferential wall portion of the slide stopper 29 on the R ₁ side comes into contact with the projection 19d of the driven plate 19 as shown in FIG. After that, the slide stopper 29 is locked to the driven plate 19, and relative rotation occurs between the annular housing 27 and the slide stopper 29. In the state shown in FIG. 7, the second
The large branch chamber 32 and the return hole 27c are in communication with each other, but when the twisting operation further progresses, the return hole 27c is blocked by the projection 19d as shown in FIG.

From the free state shown in FIG.
Even when 7 is twisted to the R ₁ side, the same operation as described above is performed. At the time of slight vibration, relative rotation does not occur between the slide stopper 29 and the annular housing 27, so that the second large chamber 32 is not reduced and the viscous fluid does not pass through the choke portion C. That is, a large viscous resistance does not occur at the time of minute vibration. Further, at the time of slight vibration, the coil spring 22 is provided in the window hole 19a of the driven plate 19 and the spring accommodating portions 13a and 14a of the input side plates 13 and 14, respectively.
It is expanding and contracting in a biased state. 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 generation of abnormal noise such as gear rattle and muffled noise of the transmission can be effectively suppressed.

Next, the operation when a 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.
When is rotated to the R ₂ side with respect to the driven plate 19, the slide stopper 29 is moved to the R ₂ side. After that, the operations from FIG. 5 to FIG. 8 are performed as in the case of the minute vibration. As shown in FIG. 8, the slide stopper 29 and the projection 1 of the driven plate 19 are provided on the R ₂ side of the second large compartment 32.
When it is sealed with 9d, the second large chamber 3
2 begins to shrink. As a result, the viscous fluid in the second large chamber 32 passes through the choke portion C and the arc-shaped fluid chamber B ₁ on the R ₁ side.
(Fig. 9). When the viscous fluid flows through the choke portion C, a large viscous resistance is generated. In addition, in each of the first large compartments 31, the fluid space A is passed through the return hole 27c.
The viscous fluid flows in smoothly. Therefore, the viscous fluid does not run short in the annular fluid chamber B.

When the annular housing 27 is twisted to the R ₁ side from the position shown in FIG. 9, it passes through the neutral position and the operation opposite to that in FIG. 9 is performed. As described above, a large viscous resistance is 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 13a and 14a of the input side plates 13 and 14 come into contact with the entire surface, rigidity is increased. That is, the characteristics of high rigidity and large viscous resistance can be obtained at the time of large vibration, and the vibration at the time of tip-in / tip-out (the large vibration in the front and rear of the vehicle body caused when the accelerator pedal is suddenly operated) can be effectively damped .

As shown in FIG. 9, it is assumed that the minute vibration is transmitted in a state where the annular housing 27 is twisted with respect to the driven plate 19 toward the predetermined angle R ₂ side. Then, the slide stopper 29 repeats the reciprocal twisting operation with respect to the protrusion 19d within an angular range in which the circumferential wall portion does not contact the protrusion 19d. At this time, the viscous fluid does not flow through the choke portion C, and a large viscous resistance is not generated. That is, even if the twist angle between the annular housing 27 and the driven plate 19 is large, minute vibrations can be effectively absorbed.

[0035]

In the damper device according to the present invention, the engine starting ring gear, which was fixed to the outer circumference of the input side member, is fixed to the outer circumference of the output side member. The moment of inertia of the side mechanism can be increased. When the engine starting ring gear is fixed to the outer circumference of the inertia member, the inertia member further increases the completion moment of the output side mechanism.

If the inertia member is a disk-shaped member, the ring gear for starting the engine can be easily fixed to the outer periphery, which reduces the cost.

[Brief description of drawings]

FIG. 1 is a schematic vertical 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.

5 is an enlarged partial view of FIG.

FIG. 6 is a diagram corresponding to FIG. 5, showing one state of a twisting operation.

FIG. 7 is a diagram corresponding to FIG. 5, showing one state of a twisting operation.

FIG. 8 is a diagram corresponding to FIG. 5, showing one state of a twisting operation.

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

[Explanation of symbols]

1 damper device 2 Input side member 4 Attenuator 11 ring gear 42 Inertia member

─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-5-87190 (JP, A) JP-A-4-272545 (JP, A) Actual development Sho-55-161946 (JP, U) Actual expansion 1- 141943 (JP, U) Actual development Sho 58-137147 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16F 15/134 F16F 15/123 F16F 15/30 F16F 15/16 PCI (DIALOG)

Claims (3)

(57) [Claims] 1. A crankshaft and a transformer on the engine side
A damper device for transmitting disposed torque between the mission of the main drive shaft, an input-side member connected to the crankshaft, a rotatable relative to the input side member, said transmitters
Center is connected to the main drive shaft
An output side member having a hub flange, and the input side member and the output side member are elastically connected in the circumferential direction to damp torsional vibration between the input side member and the output side member. A damper device, comprising: a damping part; and an engine starting ring gear fixed to the outer periphery of only the output side member. Wherein said output-side member, the front Symbol further comprising inertia member connected to the hub flange, the engine starting ring gear is fixed to the outer periphery of the inertia member, according to claim 1 Damper device. 3. The inertia member is a disc-shaped member.
The damper device according to claim 2.