JPH08270732A - Damper device and fly wheel mechanism - Google Patents

Abstract

PURPOSE: To improve design free degree of a damping part on the radial inner periphery side by elastically connecting an input side member and an output side member in the circumferential direction and also mounting a torsional vibration damping part for damping torsional vibration between the input side member and the output side member. CONSTITUTION: When torque is entered from a crank shaft 301 to a flexible plate 2, the torque is transmitted to a driven plate 19 through a coil spring 22 via a ring member 8 and input side plates 13 and 14. The torque of the driven plate 19 is transmitted to a hub flange 3 and outputted from a main drive shaft 302 to a transmission side. Bent vibration included in the torque transmitted front the crank shaft 301 to the ring member 8 is isolated by the flexible plate 2 thereby it is hard to be transmitted to a damper 4 side. Thus, load provided on a bearing 17 is less, so that the bearing 17 is minimized radially and free degree of design at inner periphery side of the damping part 4 may be improved.

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 a flywheel mechanism, and more particularly to a damper device and a flywheel mechanism arranged between an engine side crankshaft and a transmission side input shaft for transmitting 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 them and attenuating torsional vibration. Generally, a damper device includes an input side member connected to a crankshaft of an engine, an output side member connected to a main drive shaft extending from a transmission, and an input side member and an output side member elastically in a circumferential direction. And a torsional vibration damping portion to be connected. A flexible plate for absorbing bending vibration from the engine side is provided between the crankshaft and the input side member. The flexible plate has an inner peripheral end fixed to the 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 conventional damper device described above, the bearing is arranged on the outer peripheral side of the pitch circle of the bolt. Therefore, the degree of freedom in design on the radially inner side of the damping portion is limited. An object of the present invention is to improve the degree of freedom in design on the radially inner side of the damping portion.

Still another object of the present invention is to shorten the radial direction of the bearing. Still another object of the present invention is to shorten the axial direction of the damper device.

[0005]

A damper device according to a first aspect of the present invention is a device for transmitting torque between a crankshaft on the engine side and an input shaft on the transmission side, and an input side member, an output side member and a bearing. And a torsional vibration damping unit. The input side member has a disc plate. The output side member has a boss that extends to the inner peripheral side of the disc plate and is connected to the transmission side input shaft,
It is arranged on the input side member so as to be relatively rotatable. The bearing is arranged between the inner circumference of the disc plate and the outer circumference of the boss, and supports the input side member and the output side member so as to be rotatable relative to each other. The torsional vibration 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.

In the damper device according to the first aspect, the torque is transmitted from the input side member to the output side member via the torsional vibration damping portion. When the torsional vibration is input, the input side member and the output side member rotate relative to each other, and the torsional vibration damping unit dampens the vibration. Since the boss is arranged on the inner peripheral side of the disc plate of the input side member, the axial dimension of the entire damper device is shortened. Further, since the bearing is arranged between the inner circumference of the disc plate and the outer circumference of the boss, the bearing is miniaturized in the radial direction. As a result, the degree of freedom in design on the radially inner side of the torsional vibration damping portion is improved. Here, since the output side member is connected to the transmission side input shaft, the output side member is difficult to displace, and an extremely large force does not act on the bearing.

In the damper device according to the second aspect, the boss is arranged within most of the axial range of the input side member. In the damper device according to the second aspect, since the boss is arranged in most of the axial range of the input side member, the axial size of the entire damper device is shortened. The damper device according to a third aspect further includes a support member that is fixed to the inner peripheral portion of the disc plate and that supports the outer ring of the bearing together with the inner peripheral portion of the disc plate.

In the damper device according to the third aspect, the outer ring of the bearing is securely supported by the inner peripheral portion of the disc plate and the supporting member. In the damper device according to the fourth aspect, the input side member further includes another disc plate that forms together with the disc plate the fluid-filled annular chamber in which the torsional vibration damping portion is arranged. The output side member has a flange extending from the boss to the outer peripheral side and engaging with the torsional vibration damping portion.

In the damper device according to the fourth aspect, since the torsional vibration damping portion is arranged in the annular chamber filled with the fluid, each component is lubricated and the service life is long. Further, since the annular chamber is formed by the two disc plates, the axial dimension of the damper device is short. In the damper device according to the fifth aspect, the output side member further has a mass body.

In the damper device according to the fifth aspect, the mass moment increases the moment of inertia of the output side mechanism. In the damper device according to claim 6, the mass body is
The disk-shaped member has an inner peripheral portion fixed to the flange. In the damper device according to the sixth aspect, since the mass body has a disk shape, the axial dimension of the entire damper device is short.

According to a seventh aspect of the flywheel mechanism,
It is a mechanism that transmits torque between the crankshaft on the engine side and the input shaft on the transmission side, and includes an input side member, an output side member, a bearing, and a torsional vibration damping portion. The input side member forms an annular chamber filled with fluid. The output side member has a boss that extends to the inner peripheral side of the input side member and is connected to the transmission side input shaft, and a flywheel that rotates integrally with the boss, and is arranged so as to be rotatable relative to the input side member. The bearing is arranged between the inner periphery of the input side member and the outer periphery of the boss, and supports the input side member and the output side member so as to be rotatable relative to each other. The torsional vibration damping part is
It is disposed in the annular chamber, and elastically connects the input side member and the output side member in the circumferential direction and damps torsional vibration between the input side member and the output side member.

In the flywheel mechanism according to the seventh aspect, since the output side member has the flywheel, when the moment of inertia of the output side mechanism increases, the resonance frequency of the vehicle in the drive system including the flywheel mechanism increases. It is possible to reduce the idle speed (practical speed) or lower. Since the boss is arranged on the inner peripheral side of the disc plate of the input side member, the axial dimension of the entire flywheel mechanism is shortened. Further, since the bearing is arranged between the inner circumference of the disc plate and the outer circumference of the boss, the bearing is miniaturized in the radial direction. As a result, the degree of freedom in design on the radially inner side of the torsional vibration damping portion is improved. Here, since the output side member is connected to the transmission side input shaft, the output side member is difficult to displace, and an extremely large force does not act on the bearing.

In the flywheel mechanism according to the eighth aspect, the output side member further has a flange extending from the boss to the outer peripheral side to engage with the torsional vibration damping portion in the annular chamber and to which the flywheel is fixed. ing. In the flywheel mechanism according to the eighth aspect, the flywheel is fixed to the flange, so that the moment of inertia of the output side member is increased.

In the flywheel mechanism according to the ninth aspect, the input side member includes a pair of disc plates forming an annular chamber and a ring-shaped mounting member fixed to the outer periphery of the pair of disc plates. Have In the flywheel mechanism according to claim 9, since the input side member is composed of the pair of disc plates and the ring-shaped mounting portion, it has a sufficient moment of inertia without increasing the axial dimension. There is.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION First Embodiment FIGS. 1 to 3 show a flywheel mechanism 1 as an embodiment of the present invention. The flywheel mechanism 1 is a device for transmitting torque from a crankshaft 301 on the engine side to a main drive shaft 302 of a 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 is the rotation direction of the damper device 1.

The flexible plate 2 is fixed to the crankshaft 301 in advance, and the flywheel mechanism 1 is attached to the flexible plate 2. 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. In addition, the flexible plate 2 has a plurality of round holes 2 formed in the middle portion in the radial direction at equal intervals in the circumferential direction.
b. 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. The inertia member 7 increases the moment of inertia of the damper device 1. 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. The outer peripheral end of the flexible plate 2 is fixed to a ring member 8 (described later) via a disc plate 9 by a plurality of bolts 10. The inertia member 7 has a notch corresponding to the bolt 10.

The flywheel mechanism 1 mainly comprises a ring member 8 fixed to the flexible plate 2, a hub flange 3, and a damper 4. Hub flange 3
The (output side member) includes a boss 3a and a flange 3b integrally formed on the outer periphery of the boss 3a. At the center of the boss 3a, the spline hole 3 that engages with the spline teeth of the main drive shaft 302 extending from the transmission side.
c is formed.

The damper 4 mainly comprises a first input side plate 13, a second input side plate 14, a driven plate 19, a coil spring 22 and a viscous resistance generating portion 25.
(Torsion vibration damping unit). The first input side plate 13 and the second input side plate 14 are disc-shaped plate members. The inner peripheral end of the damper first input side plate 13 extends further radially inward than the inner peripheral end 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. In this way, the first and second input side plates 13 and 14 rotate integrally with the ring member 8. That is, the plate 13,
Reference numeral 14 functions 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 houses the driven plate 19, the coil spring 22, the viscous resistance generating portion 25, and the like. The viscous fluid is filled in the annular fluid filling chamber A. Since the ring member 8 is fixed to the outer peripheral portions of the plates 13 and 14, the inertia moment of the input side member is sufficiently secured without increasing the axial dimension of the damper 4.

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. In this way, the driven plate 19 rotates integrally with the hub flange 3. That is, the driven plate 19 functions as a flange of the hub flange 3, that is, as a part of the output side member. 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, annular sealing grooves 19b are formed on both side surfaces of the outer periphery of the driven plate 19, respectively. In addition, the outer peripheral surface 1 of the driven plate 19
A plurality of protrusions 19d extend radially outward from 9c.

The coil springs 22 are a combination of large and small coil springs, and are arranged in the window hole 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 housing portions 13a, 1
It is stored in 4a.

Next, the viscous resistance generating section 25 will be described. The viscous resistance generating unit 25 includes an annular housing 27 arranged on the outermost periphery in the annular fluid filled 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 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.

At the radially inner end of the annular housing 27, annular protrusions 27b are formed 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.

Inside each arc-shaped fluid chamber B ₁ , there is arranged a cap-shaped resin slide stopper 29 which covers the projection 19d of the driven plate 19 from the outer peripheral side. 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 branch 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 part 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 ring of the bearing 17 is fixed in the groove of the boss 15. The outer ring of the bearing 17 is fixed to the inner circumference of the boss 3a. 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 flexible plate 2, the boss 15 and the bearing 17
Improves concentricity.

The hub flange 3 is connected to the main drive shaft 302 of the transmission. Therefore, the hub flange 3 is less likely to be displaced, and an extremely large force does not act on the bearing 17. The bearing 17 is arranged inside the pitch circle D (FIG. 2) of the crank bolt 6. The load generated between the input side mechanism and the output side mechanism is the viscous resistance generating section 25.
In the above, since the annular projection 27b of the annular housing 27 and the sealing groove 19b of the driven plate 19 are shared and supported, the load acting on the bearing 17 can be further reduced. By reducing the diameter of the bearing 17,
The cost is reduced, and the degree of freedom in design on the inner peripheral side of the attenuator 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 portion 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 on both end faces. The 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, the bearing 17 is preloaded from the hub flange 3 to the engine side. In this way, 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 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 spring seal member 35 is made of sheet metal, the cost is low.

An inertia member 42 (inertial body) 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. Further, since the inertia member 42 has a disc shape, the flywheel mechanism 1
The whole is compact in the axial direction. By providing the inertia member 42, the moment of inertia of the output side mechanism is increased. Further, the inertia member 42
A ring gear 11 for starting the engine is welded to the outer periphery of the. 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 flywheel mechanism 1 to be equal to or lower than the idle speed (practical speed) of the vehicle. 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 included 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 damper 4 side. Even if the bending vibration is transmitted, since the hub flange 3 is supported by the main drive shaft 302, it is difficult to displace, and the load acting on the bearing 17 is small. Therefore, since the load on the bearing 17 is reduced, the bearing 1
7 can be miniaturized in the radial direction. Therefore, the bearing 17 becomes inexpensive. The bending load is applied to the annular protrusion 27 of the annular housing 27.
It is also shared and supported by the engagement of b with the sealing groove 19b of the driven plate 19.

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 microvibration).
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 R ₁ side circumferential wall portion of the slide stopper 29 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, 14a of the input side plates 13, 14.
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 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. Second Embodiment FIG. 10 shows a flywheel mechanism 101 as an embodiment of the present invention. The flywheel mechanism 101 is
It is a device for transmitting torque from the crankshaft 301 on the engine side to the main drive shaft 302 of the transmission and for damping 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. The line O-O in FIG. 10 is the rotation axis of the flywheel mechanism 101.

The flexible plate 102 is previously fixed to the crankshaft 301, and the flywheel mechanism 101 is attached to the flexible plate 102.
Is attached. The flexible plate 102 is a substantially disk-shaped member, is bendable in the bending direction, and has high rigidity in the circumferential direction. The flexible plate 102 is
It has a central hole 102a at the center. Further, the flexible plate 102 has a plurality of window holes 102b that are formed at equal intervals in the circumferential direction in the radial middle portion. A plurality of bolt holes 102c are formed on the inner peripheral side of the window hole 102b at equal intervals in the circumferential direction. The inner peripheral end of the flexible plate 102 is fixed to the front end of the crankshaft 301 by the crank bolt 106 penetrating the bolt hole 102c. Furthermore, the flexible plate 1
A plurality of arc-shaped inertia members 107 are fixed by rivets 151 on the engine side of the outer peripheral portion of 02. The inertia member 107 increases the moment of inertia of the damper device 101. In addition, the inertia member 1
Since 07 is a shape obtained by dividing an annular member in the circumferential direction, the flexible plate 102 is guaranteed to bend in the bending direction. The outer peripheral edge of the flexible plate 102 is
It is fixed to the ring member 108 by a plurality of bolts 110 with a disc-shaped plate 109 interposed therebetween. The inertia member 107 has a notch corresponding to the bolt 110.

The flywheel mechanism 101 is mainly composed of a ring member 108 fixed to the flexible plate 102.
A hub flange 103 and a damper 104. The hub flange 103 includes the boss 103a and the boss 1
03a and a flange 103b integrally formed on the outer periphery thereof. The boss 103a projects toward the engine side, and has a spline hole 103 that engages with spline teeth of the main drive shaft 302 that extends from the transmission side at the center.
c is formed. A cap-shaped member 141 that closes 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 portion 125 (torsion vibration damping portion). I have it.
First input side plate 113 and second input side plate 114
Is a disc-shaped sheet metal member. First input side plate 11
3 is composed of a disc portion 113a and a hollow cap 113b protruding from the center of the disc portion 113a toward the engine side. The hollow cap 113 is integrally formed by drawing from the center of the disc portion 113a. A central hole 113c is formed at the center of the hollow cap 113b. The second input side plate 114 has a cylindrical wall that extends toward the engine at the outer peripheral portion and is fixed to the outer peripheral end of the first input side plate 113. The cylindrical wall is welded to the inner circumference of the ring member 108. In this way, the first and second input side plates 113 and 114 rotate integrally with the ring member 108. That is, the plate 11
3,114 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 that houses the driven plate 119, the coil spring 122, the viscous resistance generating portion 125, and the like. The viscous fluid is filled in the annular fluid filling chamber A. This viscous fluid lubricates each component and prolongs its life. Since the first and second input side plates 113 and 114 are disc plates, the axial dimension of the damper 104 is short. Since the ring member 108 is fixed to the outer peripheral portions of the plates 113 and 114, the moment of inertia of the input side member is sufficiently secured without increasing the axial dimension of the damper 104.

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 attached to the hub flange 103.
Rotates together with. In other words, the driven plate 119
It functions as a flange of the hub flange 103, that is, as a part of the output side member. The driven plate 119 has a plurality of window holes 119 extending in the circumferential direction at the middle portion in the radial direction.
a is formed. In addition, driven plate 119
An annular sealing groove 119 is provided on each side surface of the outer peripheral edge of the
b is formed. A plurality of projections 119d extend radially outward from the outer peripheral surface 119c of the driven plate 119.

The coil springs 122 are made 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
3 and the second input side plate 114 are provided with spring accommodating portions 113d and 114d at portions corresponding to the window holes 119a of the driven plate 119. Seat members 123 are in contact with both ends of the spring accommodating portions 113d and 114d in the circumferential direction. In this way, the input side plates 113, 114 and the driven plate 119 are elastically connected in the circumferential direction via the coil spring 122. In the free state, the seat member 123 is only in contact with the end portions of the spring housing portions 113d and 114d of the input side plates 113 and 114 and the end portions of the window holes 119a of the driven plate 119 only at the inner peripheral portion. That is, the coil spring 122 is biased against the window hole 119a and the spring accommodating portion 113.
a, 114a.

Next, the viscous resistance generating section 125 will be described. The viscous resistance generating unit 125 includes an annular housing 127 arranged on the outermost periphery in the fluid space A, a plurality of pins 128 connecting the annular housing 127 to the first input side plate 113 and the second input side plate 114, and a housing. A plurality of slide stoppers 12 arranged in 127
It is composed of 9 and 9.

The annular housing 127 is arranged inside the outer peripheral wall of the second input side plate 114, and both axial end faces 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, in the annular housing 127, a plurality of stopper portions 127a are integrally formed 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 portion 127a has a pin 128.
Has a hole through which is inserted. Both ends of the pin 128 are non-rotatably engaged with the input side plates 113 and 114.
As a result, the annular housing 127 and the input side plate 1 are
13 and 114 rotate together. In addition, the width of the annular housing 127 that determines 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 protrusions 127b protruding toward each other are provided.
Is formed (the opening between the protrusions 127b is the opening), and the protrusion 127b is fitted into the annular sealing groove 119b formed in the driven plate 119 to close the inner peripheral side of the annular fluid chamber B. It is sealed. Annular protrusion 127b
The engaging seal portion between the seal groove 119b and the seal groove 119b is connected to the input side mechanism (the input side plates 113 and 114) via the viscous fluid.
Also, the load (thrust load, radial load, and bending load) generated between the annular housing 127) and the output side mechanism (driven plate 119, hub flange 103) is shared with and supported by the bearing 117 described later.

It should be noted that the return hole 1 is formed in the center portion between the stopper portions 127a on the inner side in the radial direction of both end faces.
27c is formed. The return hole 127c allows the viscous fluid to freely move between the annular fluid chamber B and the fluid space A. In the free state, the protrusion 119d of the driven plate 119 is arranged at a position corresponding to the return hole 127c.

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 rest of the viscous fluid portion 125 are the same as the structures of the slide stopper 29 and the viscous resistance generating portion 125 of the first embodiment, and thus the description thereof is omitted. A spring seal member 135 is sandwiched in a portion where the inner peripheral portion of the driven plate 119 and the flange 103b of the hub flange 103 are fixed by the rivet 120. The spring seal member 135 is made of an annular thin metal plate, and is fixed to the fixed portion by the rivet 120 and the inner peripheral end portion of the second input side plate 114 that extends from the outer peripheral side of the fixed portion and contacts the engine side. And a biasing unit that biases the unit toward the transmission. Due to the reaction force generated by this urging force, the driven plate 119 and the hub flange 10 are
3 is urged to the engine side. Spring seal member 13
5 seals between the second input side plate 114 and the outer periphery of the hub flange 103 in the fluid space A.

The hollow cap 113b of the first input side plate 113 is provided in the center hole 10 of the flexible plate 102.
It is inserted in 2a. That is, the first input side plate 113 is positioned and centered by the flexible plate 102 (crankshaft side centering portion) fixed to the crankshaft 301. The boss 103a of the hub flange 103 is the first input side plate 1
It is arranged in 13 hollow caps 113b. The boss 103a is housed within most of the axial dimension of the damper 104 (first and second input side plates 113, 114). As a result, the flywheel mechanism 101 is axially compact. First input side plate 113
Inner periphery of the circular disk portion 113a and the boss 1 of the hub flange 103
A bearing 117 is arranged between the outer periphery of 03a.
The bearing 117 has an outer ring fixed to the first input side plate 113 by a support member 152 having an annular outer ring and a rivet 153. This ensures that the bearing 117 is in the first position.
It is supported by the input side plate 113. Boss 103a
Has a portion that is inserted inside the inner ring of the bearing 117 and that abuts on the transmission-side end surface of the inner ring.

In this way, the first input side plate 11
3 is positioned (centered) in the central hole 102a of the flexible plate 102, and the first input side plate 113 thereof supports the bearing 117. Thereby, the flexible plate 102, the first input side plate 113,
The concentricity of the bearing 117 and the hub flange 103 is improved.

The bearing 117 is composed of the first input side plate 113.
Since it is arranged between the inner circumference of the crank bolt 106 and the outer circumference of the boss 103a, the diameter is small enough to be arranged inside the pitch circle D of the crank bolt 106. Therefore, the degree of freedom in designing the inner peripheral side of the damper 104 is improved. Therefore, for example, the driven plate 119 can be extended to the inner peripheral side and the coil spring 122 can be arranged further inside. Further, it is possible to easily secure a space for rotating the head portion of the crank bolt 106. The hub flange 103 is connected to the main drive shaft 302 of the transmission. Therefore, the hub flange 103 is hard to displace, and an extremely large force does not act on the bearing 117.

The bearing 117 has a seal member for sealing between the inner ring and the outer ring on both end faces. The seal member seals the lubricant between the inner ring and the outer ring, and also seals between the inner periphery of the first input side plate 113 and the boss 103a of the hub flange 103 in the fluid space A. The hub flange 103 is biased toward the engine by the spring seal member 135 as described above. Therefore, the bearing 117 is preloaded by applying a force from the hub flange 103 to the engine side. In this way, the spring seal member 135 also functions as a biasing member that seals the annular fluid filling chamber A and applies a preload to the bearing 117, 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 spring seal member 135 is made of sheet metal, the cost is low.

Further, in this embodiment, the hub flange 10
The third boss 103 a is inserted into the hollow cap 113 b of the first input side plate 113. As a result, the overall axial dimension of the damper device 101 is reduced. Moreover,
In this structure, the bearing 117 has the first input side plate 11
Since the inner peripheral portion of 3 is arranged between the inner peripheral portion and the outer periphery of the boss 103a, 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 its inner peripheral end is fixed to the flange 103b and the driven plate 119 by the rivet 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 disc-shaped member, and is in full contact with the transmission side of the first inertia 142. The inertia moment of the output side mechanism is increased by the first inertia member 142 and the second inertia member 144. Since the first and second inertia members 142 and 144 are disc-shaped, the damper device 101 as a whole is axially compact. Further, the engine starting ring gear 111 is welded to the outer periphery of the first inertia member 142. The engine starting ring gear 111 is a member that is 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 this embodiment, the moment of inertia of the output side mechanism can be easily achieved. The ratio can be increased. When the inertia moment ratio of the output side mechanism increases, it becomes possible to reduce the resonance frequency in the drive system including the damper device 101 to be equal to or lower than the idle speed (practical speed) of the vehicle. The cost is reduced by using the conventional engine starting ring gear 111.

Since the operation is almost the same as that of the first embodiment, its explanation is omitted.

[0058]

In the damper device and the flywheel mechanism according to the present invention, since the boss is arranged on the inner peripheral side of the disc plate of the input side member, the overall axial dimension of the damper device is shortened. . Further, since the bearing is arranged between the inner circumference of the disc plate and the outer circumference of the boss, the bearing is miniaturized in the radial direction. As a result, the degree of freedom in design on the radially inner side of the torsional vibration damping portion is improved. Here, since the output side member of the damper device is connected to the transmission side input shaft, the output side member is less likely to be displaced, and an extremely large force does not act on the bearing.

[Brief description of drawings]

FIG. 1 is a schematic vertical sectional view of a flywheel mechanism according to an embodiment of the present invention.

FIG. 2 is a cutaway plan view of the flywheel mechanism as viewed from the transmission side.

FIG. 3 is a cutaway plan view of the flywheel mechanism 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.

FIG. 10 is a diagram corresponding to FIG. 1 according to another embodiment of the present invention.

[Explanation of symbols]

 1,101 Flywheel mechanism 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 part 113a Disc part 113b Central cap 301 Crankshaft 302 Main drive shaft

Claims (9)

[Claims] 1. A damper device for transmitting torque between an engine-side crankshaft and a transmission-side input shaft, comprising: an input-side member having a disc plate; and an extension member extending to an inner peripheral side of the disc plate. An output side member having a boss connected to the transmission side input shaft, the output side member being rotatably arranged on the input side member, and arranged between an inner circumference of the disc plate and an outer circumference of the boss, A bearing for supporting the input side member and the output side member so as to be rotatable relative to each other, and elastically coupling the input side member and the output side member in the circumferential direction, and the input side member and the output side member. And a torsional vibration damping unit for damping torsional vibration between the dampers. 2. The damper device according to claim 1, wherein the boss is disposed within most of the axial range of the input side member. 3. The damper according to claim 1, further comprising a support member fixed to an inner peripheral portion of the disc plate and supporting an outer ring of the bearing together with the inner peripheral portion of the disc plate. apparatus. 4. The input side member further includes another disc plate that forms together with the disc plate a fluid-filled annular chamber in which the torsional vibration damping portion is arranged, and the output side member. The damper device according to any one of claims 1 to 3, wherein the damper device has a flange that extends outward from the boss and that engages with the torsional vibration damping portion. 5. The damper device according to claim 1, wherein the output side member further has a mass body. 6. The damper device according to claim 5, wherein the mass body is a disk-shaped member having an inner peripheral portion fixed to the flange. 7. A flywheel mechanism for transmitting torque between a crankshaft on the engine side and an input shaft on the transmission side, the input side member forming an annular chamber filled with a fluid, and the input side member. An output side member having a boss extending to an inner peripheral side and connected to the transmission side input shaft; and a flywheel that rotates integrally with the boss, the output side member being rotatably arranged relative to the input side member; A bearing, which is arranged between the inner circumference of the member and the outer circumference of the boss, supports the input side member and the output side member in a relatively rotatable manner, and is arranged in the annular chamber, and the input side member and the output side A flywheel provided with a torsional vibration damping portion for elastically coupling the member in the circumferential direction and damping the torsional vibration between the input side member and the output side member. Eel mechanism. 8. The output side member further has a flange extending from the boss toward the outer peripheral side to engage with the torsional vibration damping portion in the annular chamber and to which the flywheel is fixed. The flywheel mechanism according to Item 7. 9. The input-side member includes a pair of disc plates forming the annular chamber, and a ring-shaped mounting member fixed to the outer periphery of the pair of disc plates. The flywheel mechanism according to Item 7 or 8.