JPH07224891A - Damper device - Google Patents

Abstract

PURPOSE:To simplify structure by providing a rotation member coupled to one of rotary bodies on the input side and the output side, a flange coupled to the other, and a damping part to peripherally resiliently intercouple the rotation members and a flange and damp torsional vibration generated therebetween. CONSTITUTION:Torque inputted to a flexible plat 2 through a crank shaft 301 is transmitted to a hub flange 3 through a coil ring 22 after the passage of it through a ring member 8 and plates 13 and 14 on the input side and outputted to the main drive shaft 302 side. Bending vibration contained in torque transmitted to the ring member 8 is insulated by a flexible plate 2 and hardly transmitted to a damping part 4. A damping part 4 has a viscous resistance generating part and when torsional vibration is transmitted, a rotation member and a hub flange 3 are caused to perform reciprocating torsional operation through the damping part 4 and damp twist vibration. Thus a driven plate 2 is eliminated and structure is simplified.

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 Generally, a damper device is arranged between a vehicle engine and a transmission to transmit torque. This damper device mainly includes an input member, a hub flange, and a damping portion. The input member is connected to the engine crankshaft, and the hub flange is connected to the main drive shaft extending from the transmission side. Further, the damping portion elastically connects the input side member and the hub flange in the circumferential direction, and damps the torsional vibration between them. A driven plate that connects the damping portion and the hub flange is arranged between the damping portion and the hub flange.

[0003]

In the conventional damper device, the hub flange and the driven plate are separate members, so that the number of parts is increased and the structure is complicated. Therefore, the manufacturing cost is also high. The purpose of the invention is to simplify the structure.

Another object of the present invention is to reduce costs.

[0005]

A damper device according to a first aspect of the present invention is a damper device for transmitting torque between an input side rotating body and an output side rotating body, and includes a rotating member, a hub flange, and a damping member. And a section. The rotating member is connected to one of the input side rotating body and the output side rotating body. The hub flange has a boss portion connected to the other of the input side rotating body and the output side rotating body, and a flange portion integrally formed on the outer periphery of the boss portion. The damping portion elastically connects the rotating member and the flange portion in the circumferential direction, and damps torsional vibration between the rotating member and the hub flange.

In the damper device according to the second aspect of the invention, the damping portion has a resistance generating portion that generates resistance when the rotating member and the hub flange are twisted with each other. The outer peripheral portion of the flange portion is engaged with the resistance generating portion. In the damper device according to the third aspect of the invention, the resistance generating portion generates viscous resistance, and has a fluid chamber that has an opening extending in the circumferential direction and is filled with fluid. The outer peripheral portion of the flange portion is inserted into the fluid chamber through the opening.

[0007]

In the damper device according to the first aspect of the present invention, when the torque is input from the input side rotating body, the torque is output to the output side rotating body via the rotating member, the hub flange and the damping portion. When the torsional vibration is transmitted from the input side rotating body to the damper device, the rotating member and the hub flange perform a reciprocal twisting operation via the damping portion. At this time, the damping portion dampens the torsional vibration.

In this damper device, the flange portion of the hub flange is integrally formed on the outer periphery of the boss portion. Therefore, the conventional driven plate can be omitted, and the structure is simplified. Therefore, the cost is reduced.
In the damper device according to the second aspect of the present invention, since the outer peripheral portion of the flange portion is engaged with the resistance generating portion, the above action becomes more effective.

In the damper device according to the third aspect of the present invention, since the outer peripheral portion of the flange portion is inserted into the fluid chamber, the above action becomes more effective.

[0010]

1 to 3 show a damper device 1 as one embodiment of the present invention. The damper device 1 is a device that transmits 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. Furthermore, O- in FIG.
The O line 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 101 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 the annular member in the circumferential direction, it does not hinder the bending of the flexible plate 2 in the bending direction. The outer peripheral end of the flexible plate 2 is fixed to the ring member 8 by a plurality of bolts 10 via a disc plate 9. 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 flange 3b extends to the outer periphery and engages with a damping portion 4 described later. 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 ring gear 11 is welded to the outer circumference of the inertia member 42. 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, the resonance frequency in the drive system including the damper device 1 is set to the idle speed (practical speed) of the vehicle.
It will be possible to lower it below. Here, since the ring gear 11 is used to increase the inertia moment of the inertia member 42, it is not necessary to provide a special member, and the cost is low.

The attenuator 4 is mainly composed of the first input side plate 1
3, the second input side plate 14, and the driven plate 1
9, a coil spring 22, and a viscous resistance generating portion 25. The first input side plate 13 and the second input side plate 14 are disk-shaped members made of sheet metal. 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 an outer peripheral 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 outer peripheral wall is welded to the inner periphery of the ring member 8. The first input side plate 13 and the second input side plate 14 form a fluid space A that accommodates the driven plate 19, the coil spring 22, the viscous resistance generating portion 25, and the like. The fluid space A is filled with viscous fluid.

A plurality of window holes 19a extending in the circumferential direction are formed in the radial middle portion of the flange 3b. Further, annular sealing grooves 19b are formed on both sides of the outer peripheral end of the hub flange 3b. A plurality of projections 19d extend radially outward from the outer peripheral surface 19c of the hub flange 3b. The coil springs 22 are respectively composed of large and small coil springs, and the hub flange 3
It is arranged in the window hole 19a of b. 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
Spring housing portions 13a and 14a are formed in the portion of the hub flange 3b corresponding to the window hole 19a. 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 hub flange 3b are elastically connected in the circumferential direction via the coil spring 22. In the free state shown in FIG. 2, the seat member 23 only contacts the inner ends of the spring housing portions 13a, 14a of the input side plates 13, 14 and the window hole 19a of the hub flange 3b. I don't touch. That is, the coil spring 22 is biased against the window holes 19
a and the spring accommodating portions 13a and 14a.

Next, the viscous resistance generating section 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 hub flange 3b 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. The stopper portion 27a is
The annular fluid chamber B is divided 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 non-rotatably engaged with the input side plates 13 and 14. Thereby, the annular housing 2
7 and the input side plates 13 and 14 rotate integrally. The width of the annular housing 27 that determines the viscous resistance is determined by the length of the body 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 this protrusion 27b is the hub flange. It is fitted in an annular sealing groove 19b formed in 3b to seal the inner peripheral side of the annular fluid chamber B. Protrusion 27b and sealing groove 19b
The engaging portion with the load (thrust load, radial load, load generated between the input side mechanism (input side plates 13 and 14 and the annular housing 27) and the output side mechanism (hub flange 3) via the viscous fluid. Bearing 17 whose bending load will be described later
We share with and support.

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 hub flange 3b is arranged at a position corresponding to the return hole 27c.

Each arc-shaped fluid chamber B₁Inside the hub flange 3b
Cap-shaped slide slide that covers the projection 19d of the outer peripheral side
A topper 29 is arranged. Slide stopper 2
Reference numeral 9 denotes an outer peripheral portion that matches the outer inner peripheral surface of the annular housing 27.
And has an arcuate fluid chamber B ₁Free to move in the circumferential direction
It is located in. The slide stopper 29 is a hub stopper.
The circumferential wall is a protrusion with respect to the protrusion 19d of the lunge 3b.
It is movable in the circumferential direction within the range of contact with 19d.
The slide stopper 29 is arranged in the radial direction of both wall portions in the circumferential direction.
It has a notch 29a on the inside. Also, sly
The inner sides of the axial walls of the stopper 29 are not cut.
The notch 29b is formed. Radius of stopper 29
The inner side in the direction contacts the annular protrusion 27b of the annular housing 27.
Touching.

The slide stopper 29 is used for each arc-shaped fluid chamber.
B₁Inside, R₂Side first Oita chamber 31 and R₁Second Oita on the side
It is divided into a chamber 32. Furthermore, slide stopper
The inside of 29 is driven by the protrusion 19d of the driven plate 19.
R₂Side small sub-chamber 33 and R ₁To the second sub-compartment 34 on the side
It is divided. Of the first sub-compartment 33 and the second sub-compartment 34
Between the projection 19d of the driven plate 19 and the slide slide.
The gap formed between the topper 29 and the slide stopper
Due to the notch 29b of the par 29 and the return hole 27c
Therefore, the viscous fluid can come and go freely. Furthermore, viscosity
The fluid slides between the first large compartment and the first small compartment 33.
Stopper 29 R₂Freely go through the side cutout 29a
Of the second sub-compartment 34 and the second sub-compartment 32
R of slide stopper 29 between₁Side cutout 29a
You can come and go freely. However, the slide stock
When the circumferential wall of the par 29 comes into contact with the protrusion 19d,
Viscous fluid inside and outside the circumferential direction of the ride stopper 29
Is cut off.

A choke portion C is formed between the inner peripheral surface of the stopper portion 27a and the outer peripheral surface 19c of the hub flange 3b. When the viscous fluid passes through the choke portion C, a large viscous resistance is generated. As shown in FIG. 4, the seal member 35 is sandwiched between the portions where the inertia member 42 is fixed to the flange 3b by the rivets 20. The seal member 35 is made of an annular thin sheet metal, and includes a fixing portion 35a having a plurality of holes through which the rivet 20 penetrates,
The fixed portion 35a includes an outer peripheral cylindrical portion 35b extending from the inner peripheral side toward the transmission side, and a biasing portion 35c extending from the outer peripheral cylindrical portion 35b toward the outer peripheral side. The biasing portion 35c is
The inner peripheral end of the second input side plate 14 is in contact with the engine side, and in the state shown in FIG. 4, the inner peripheral end of the second input side plate 14 is biased toward the transmission side. The hub flange 3 is biased toward the engine by the reaction force generated by this biasing force. The seal member 35 seals between the second input side plate 14 and the hub flange 3 in the fluid space A.

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 central space 15c and the radial hole 15b can be used to fill or discharge the viscous fluid in the fluid space A.

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. A disc member 41 is arranged on the transmission side of the bearing 17. The inner race of the bearing 7 is fixed in the groove of the boss 15. In this way, the boss 15 is positioned in the center hole 2a of the flexible plate 2, and the bearing 17 is further positioned. As a result, the concentricity of the flexible plate 2, 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 causes the viscous resistance generating portion 25 to have the annular protrusion 27b of the annular housing 27 and the sealing groove 19b of the hub flange 3b.
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, the coil spring 22 can be arranged on 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 seal member 35 as described above. As a result, the bearing 17 is preloaded. In this way, the seal member 35 also functions as a biasing member that seals the fluid space A and applies a preload to the bearing 17, and has a single function and a plurality of functions. As a result,
The number of parts can be reduced and the manufacturing cost can be reduced.
Further, since the seal member 35 is made of sheet metal, the cost is low.

Next, the operation will be described. When torque is input from the crankshaft 101 to the flexible plate 2, the torque is transmitted to the hub flange 3 through the ring member 8 and the input side plates 13 and 14 and the coil spring 22, and further from the main drive shaft 102. It is output to the transmission side. Bending vibration included in the torque transmitted from the crankshaft 101 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
The annular protrusion 27b of the annular housing 27 and the engagement of the sealing groove 19b of the driven plate 19 are shared and supported. Therefore, the load acting on the bearing 17 is reduced, so that the bearing 17 can be downsized in the radial direction.

Next, the operation when the torsional vibration is transmitted from the crankshaft 101 to the damper device 1 will be described. However, here, when the torsional vibration is transmitted, the output side mechanism (hub flange 3) is non-rotatably fixed to another member (not shown) and the input side mechanism (first input The operation of twisting the side plate, the second input side plate 14 and the annular housing 27) will be replaced.

The circumferential wall of the slide stopper 29 is
Small that does not contact the protrusion 19d of the driven plate 19
Torsional vibration with a deviation angle (hereinafter referred to as micro vibration) is transmitted
The operation when it is performed will be described. Enter in the free state shown in FIG.
Force side plates 13 and 14 are R ₂Suppose it is twisted to the side. You
Then, the slide stopper 29 becomes R₂Move to the side, Figure 6
As shown in, inside the slide stopper 29, the first small compartment
33 is expanded and the second sub-compartment 34 is contracted. Second subdivision
The viscous fluid slides from the chamber 34 to the first sub-chamber 33.
The notch 29 is provided between the outer periphery of the topper 29 and the protrusion 19d.
Flow freely through b and return hole 27c. Well
In addition, the viscous fluid is stored in the slide stopper 29 and the fluid space.
Come and go freely with A through return hole 27c
You can

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 is projected by the projection 19 of the flange 3b as shown in FIG.
abut on d. 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 large chamber 32
And the return hole 27c are in communication with each other, but when the twisting operation further proceeds, as shown in FIG.
The c is closed by the protrusion 19d.

From the free state shown in FIG.
When 7 is twisted to the R ₁ side, the same operation as described above is performed. Slide stopper 2 at the time of minute vibration
Since relative rotation does not occur between 9 and the annular housing 27, the second large compartment 32 is not reduced, and the choke portion C does not pass the viscous fluid. 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 with the window hole 19a of the flange 3b and the input side plate 1
The spring accommodating portions 13a and 14a of the blades 3 and 14 extend and contract 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.
Is twisted toward the R ₂ side with respect to the hub flange 3. Then, the slide stopper 29 moves 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, R _{2 of} the second large branch chamber 32 is
The side is the slide stopper 29 and the protrusion 19 of the flange 3b.
When it is sealed with d, the second large chamber 32
Starts to reduce. 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.

From the position shown in FIG. 9, the annular housing 27
When is twisted to the R ₁ side, 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, the annular housing 27 is
Predetermined angle R with respect to hub flange 3 ₂Twisted to the side
Suppose that a small vibration is transmitted by. Then, slide strike
The top 29 has a corner in which the circumferential wall does not contact the protrusion 19d.
Repeated reciprocal twisting motion with respect to the protrusion 19d within a range of degrees
You At this time, the viscous fluid does not flow through the choke portion C,
Does not generate viscous resistance. Ie annular housing
The twist angle between 27 and the hub flange 3 is large.
However, the minute vibration can be effectively absorbed.

In this embodiment, the flange 3b of the hub flange 3 extends in the outer peripheral direction and engages with the damping portion 4. Therefore, the conventional driven plate can be omitted,
The structure is simplified. As a result, the cost is reduced. Further, since the outer peripheral end of the flange 3b is engaged with the viscous resistance generating portion 25, the above effect becomes more effective. Further, since the outer circumference of the flange 3b is inserted into the annular fluid chamber B, the above effect becomes more effective.

[0034]

In the damper device according to the first aspect of the present invention, since the flange portion of the hub flange is integrally formed on the outer periphery of the boss portion, the conventional driven plate can be omitted and the structure is simplified. . Therefore, the cost is reduced. In the damper device according to the second aspect of the invention, since the outer peripheral portion of the flange portion is engaged with the resistance generating portion, the above effect becomes more effective.

In the damper device according to the third aspect of the present invention, since the outer peripheral portion of the flange portion is inserted into the fluid chamber, the above effect becomes more effective.

[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 partially cutaway front view of the damper device as viewed from the transmission side.

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

FIG. 4 is a partially enlarged view of FIG.

5 is a partially enlarged view of FIG.

FIG. 6 is a diagram corresponding to FIG. 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 a partially enlarged view of FIG. 2, showing one state of a twisting operation.

[Explanation of symbols]

 1 Damper Device 2 Flexible Plate 3 Hub Flange 3a Boss 3b Flange 4 Damping Part 25 Viscous Resistance Generating Part 301 Crank Shaft 302 Main Drive Shaft B Annular Fluid Chamber

Claims (3)

[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 hub flange having a boss portion connected to the other of the side rotating body and the output side rotating body, and a flange portion integrally formed on the outer periphery of the boss portion, and the rotating member and the flange portion in the circumferential direction. A damper unit that is elastically connected to the damping member for damping torsional vibration between the rotating member and the hub flange. 2. The damping portion has a resistance generating portion that generates resistance when the rotating member and the hub flange are twisted with each other, and an outer peripheral portion of the flange portion engages with the resistance generating portion. The damper device according to claim 1, wherein 3. The resistance generating section is for generating viscous resistance, and the resistance generating section has a fluid chamber filled with a fluid and having an opening extending in a circumferential direction. The damper device according to claim 2, wherein an outer peripheral portion of the portion is inserted into the fluid chamber through the opening.