JPH10132028A - Motive power transmitting mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve durability of a motive power transmitting mechanism and others, and provide a compact torsion mechanism by arranging a driving side member and a driven side member concentrically and relatively rotatably, and arranging a sliding mechanism having a periphery serving as a sliding surface between them. SOLUTION: A driving side inertial body is composed of a drive plate 3 fixed to an engine at its side of a crankshaft 1, a ring gear 4, an inertial ring 5 and an inner ring 6. A driven side inertial body is composed of a flywheel 7 and a driven plate 8. A sliding bearing mechanism is arranged between the inertial bodies in a radial direction, which is composed of a sliding bearing 18 spline-fitted to an outer peripheral part of the inner ring 6 for relatively rotatably keeping them, and disc springs 19 arranged on both sides. A torsion mechamism prepared by serially arranging plural torsion springs and a hysterisis mechanism inclusing a frictional member 13 and a disc spring 14 are arranged between the inertial bodies in a rotational direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission mechanism, and more particularly to a power transmission mechanism for transmitting power from an engine mechanism to a transmission mechanism so as to be able to connect and disconnect and absorb torque fluctuations.

[0002]

2. Description of the Related Art As an example of a conventional power transmission mechanism, FIGS. 4 and 5 show a torque fluctuation absorbing device disclosed in GB2269440. Referring to FIGS. 4 and 5, a torque fluctuation absorbing device provided for absorbing torque fluctuation between the engine and the transmission includes drive side members 53, 54, 60 and driven side member 55, 56, 59,
A coil spring 50 as a torsion mechanism and a hysteresis mechanism 62 arranged between the side surfaces of the drive-side member (drive plate) 53 and the driven-side member (driven plate) 56 to exhibit hysteresis by frictional sliding;
The driving force from the engine is transmitted to the driven side members 55 to 56 and 59 via the driving side members 60 to 53 and 54 fixed to the drive shaft and the coil spring 50. In order to hold the driven-side member (flywheel) 59 concentrically and relatively rotatable with respect to the driving-side member (inner hub) 60, the outer peripheral surface of the driving-side member 60 and the inner peripheral surface of the driven-side member 59 A rolling bearing 61 is provided.

A bearing provided between the outer peripheral surface of the driving member and the inner peripheral surface of the driven member for holding the driven member concentrically and relatively rotating with respect to the driving member is disclosed in Japanese Patent Application Publication No.
No. -43176 proposes a torque fluctuation absorbing device in which a flange-shaped sliding bearing is inserted between a driving side member and a driven side member in a radial direction. In this sliding bearing, both outer peripheral surfaces of the drive side member and the inner peripheral surface of the driven side member are used as sliding surfaces.

According to the torque fluctuation device disclosed in GB2269440, grease is sealed in a space for accommodating a torsion spring 50 provided on an outer peripheral portion of the device as a torsion member, and the space inside the device on the inner peripheral side of the space is accommodated. Of the driven side plate 56 and the drive side plate 54
A seal 58 and a thin plate spring 57 in a compressed state are arranged between the inner peripheral portion in the axial direction, thereby allowing the relative rotation between the driving plate 54 and the driven plate 56 and exerting a sealing function.

In the apparatus of the above-mentioned GB 2269440, the driving side member (drive plate) 53 is made of an iron plate for cost reduction.

Further, referring to FIG.
In the device of No. 440, the outer peripheral side of the torsion spring 50 and the inner peripheral side of the drive side plates 53, 54 prevent the torsion spring 50 from moving to the outer peripheral side due to centrifugal force and sliding with the drive side plates 53, 54. To do
The outer peripheral side of the spring seats 51, 52 extends between the outer peripheral side of the torsion spring 50 and the inner peripheral side of the drive side plates 53, 54.

[0007]

However, the first problem is to be solved.
In addition, the use of rolling bearings, such as the torque fluctuation absorbing device of GB2269440, increases the cost. Further, the sliding bearing disclosed in Japanese Patent Publication No. 56-43176, the outer peripheral surface of the driving member and the inner peripheral surface of the driven member are both sliding surfaces. There is a problem that the concentricity of the driven-side member with respect to the driving-side member cannot be maintained, and vibration due to the imbalance of the concentricity occurs.

Second, referring to FIG. 4 and FIG. 5, according to the above GB Patent No. GB2269440, according to the mechanism for sealing the space for accommodating the torsion spring 50 disposed on the outer peripheral portion of the torque fluctuation device, The seal 58 is arranged on the inner peripheral side of the apparatus so as not to apply a strong pressure due to the rotation of the apparatus, and the grease moves to the outer peripheral side of the apparatus by centrifugal force during the rotation of the apparatus.
6 becomes dry, the abrasion proceeds, the sealing function is lost, and grease leaks from the seal 58.

In addition, a hysteresis mechanism is arranged on the innermost side of the sealed space, and grease adheres to a thrust plate of the hysteresis mechanism or a friction member is provided depending on the rotation speed of the device. Hysteresis becomes unstable due to a dry state. further,
Since the above space is closed, heat radiation is poor, and in a dry state, the thrust plate having a small heat capacity becomes hot, lining wear is accelerated, and the hysteresis function is gradually lost.

Third, referring to FIG. 4 and FIG. 5, in the device of the above-mentioned GB2269440, the driving side plate 53 is made of an iron plate for cost reduction. When the driving side plate 53 is subjected to the stress, the driving side plate 53 may be cracked or broken due to concentrated stress generated near a portion where the driving side plate 53 is fixed to the driving shaft.

Fourth, referring to FIG. 4 and FIG. 5, in the apparatus of the above-mentioned GB 2269440, the outer peripheral sides of the spring seats 51 and 52 are arranged on the outer peripheral side of the torsion spring 50 and the inner peripheral sides of the drive side plates 53 and 54. Since this space is consumed by the extension, the housing position of the torsion spring 50 is on the inner peripheral side by the amount of the spring seats 51 and 52 on the outer peripheral side. For this reason, there is a problem that a sufficient torque fluctuation absorbing characteristic cannot be obtained unless a higher rigidity and a large torsion spring 50 are used.

In view of the above problems, an object of the present invention is to improve the durability of a power transmission mechanism and each of the mechanisms constituting the power transmission mechanism. Another object is to reduce the size of the torsion mechanism, which is a component when the power transmission mechanism is configured as a torque fluctuation absorbing device.

[0013]

In order to achieve the above-mentioned object, means according to a first aspect of the present invention comprises a driving member for rotating and transmitting power, and a driven member for transmitting and rotating the power. A power transmission mechanism in which members are disposed substantially concentrically and relatively rotatably with each other, wherein the drive side member is disposed on one of an inner diameter side and an outer diameter side, and the driven side member is disposed on the other side, and Disposed between the member and the driven member in the radial direction,
A sliding bearing is provided, which is substantially concentrically engaged with one of the driving-side member and the driven-side member, and the other of which has a sliding surface.

Preferably, the sliding bearing is disposed in a space surrounded by the driving-side member and the driven-side member, and a radially inward side of the sliding surface and / or a side surface of the sliding bearing. The lubricant reservoir is provided on a side surface of the driving-side member and / or the driven-side member facing a side surface of the slide bearing, and the lubricant stored in the lubricant reservoir is radially outside the lubricant reservoir by centrifugal force. A clearance is provided between a side surface of the sliding bearing and a side surface of the driving-side member and / or a side surface of the driven-side member facing the side surface of the sliding bearing so as to be supplied to the sliding surface located on the side. It is characterized by having. More preferably, the sliding bearing is provided between a side surface of the sliding bearing and the driving member or the driven member facing the sliding bearing, and abuts the sliding bearing to move the sliding bearing in the axial direction. A disc spring is provided which urges the side member or the driving side member and prevents lubricant from leaking from the side surface of the slide bearing in the axial direction. In particular, preferably, a seal member is provided on the outer peripheral side of the disc spring so as to prevent lubricant from leaking radially outward from the outer peripheral portion of the disc spring.

According to a second aspect of the present invention, a driving member for rotating and transmitting power and a driven member for transmitting and rotating the power are arranged substantially concentrically and relatively rotatable with each other. A power transmission mechanism, between the driving side member and the driven side member, a torsion mechanism for absorbing a rotational torque fluctuation of the driving side member and the driven side member is housed, and the torsion mechanism is housed therein. Placed in a space that
A first hysteresis mechanism that includes at least one friction member and that generates hysteresis by sliding the friction member against the drive-side member or the driven-side member; and a first hysteresis mechanism that is disposed outside a space that houses the torsion mechanism. And a second hysteresis mechanism that generates a hysteresis different from the first hysteresis mechanism by sliding.

According to a third aspect of the present invention, a driving member that rotates and transmits power and a driven member that transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other. A power transmission mechanism, between the driving side member and the driven side member, a torsion mechanism for absorbing a rotational torque fluctuation of the driving side member and the driven side member is housed, and the torsion mechanism is housed therein. A first hysteresis mechanism which is arranged on the inner peripheral side of the space to be provided and has at least one friction member, and which generates hysteresis by sliding of the friction member with respect to the driving side member or the driven side member,
A second hysteresis mechanism that is disposed outside the space that houses the torsion mechanism and that generates a hysteresis different from the first hysteresis mechanism by sliding of a friction member;
Wherein the inner periphery of the space is sealed by the first hysteresis mechanism.

According to a fourth aspect of the present invention, a driving member for rotating and transmitting power and a driven member for transmitting and rotating the power are disposed substantially concentrically and relatively rotatable with each other. A power transmission mechanism, wherein a torsion mechanism that absorbs fluctuations in rotational torque between the drive side member and the driven side member is accommodated in a space surrounded by the drive side member and / or the driven side member, Outside the space, a second hysteresis mechanism including a friction member and generating hysteresis by sliding of the friction member is disposed, and a second hysteresis mechanism is arranged between the friction member and one of the drive side member or the driven side member in the axial direction. A disc spring is provided, and the friction member receives the urging force of the disc spring and is locked to the other of the driving side member or the driven side member by frictional force, and the driving member or the receiving member is It has a predetermined angle clearance in the rotation direction of the device with respect to the other of the side members, and can be engaged when relative rotation between the driving side member and the driven side member reaches the predetermined angle or more. And

According to a fifth aspect of the present invention, a driving member for rotating and transmitting power and a driven member for transmitting and rotating the power are arranged substantially concentrically and relatively rotatable with each other. A power transmission mechanism, wherein an inner peripheral side of the driving side member is fixed to a driving shaft, a hole is formed in an intermediate portion,
An outer peripheral portion and an inner peripheral portion are connected in a substantially arm shape.

According to a sixth aspect of the present invention, a driving member for rotating and transmitting power and a driven member for transmitting and rotating the power are disposed substantially concentrically and relatively rotatable with each other. A power transmission mechanism, wherein a torsion member that absorbs rotational torque fluctuation is arranged in series between the drive side member and the driven side member in the device rotation direction, and is inserted from the end of the torsion member to the inner peripheral side. And a spring seat for locking the torsion member in the radial direction.

In order to achieve the above object, the seventh aspect of the present invention is described.
Means in the viewpoint of, the driving side member that rotates and transmits power, and the driven side member that is transmitted and rotated by the power,
A power transmission mechanism arranged substantially concentrically and relatively rotatable with respect to each other via a bearing, wherein an inner race or an outer race of the bearing is fixed to a driven member.

In order to achieve the above object, an eighth aspect of the present invention is provided.
Is a power transmission in which a driving-side member that rotates and transmits power and a driven-side member that is connected to a flywheel and rotated by the transmission of the power are substantially concentrically and relatively rotatably arranged with each other. A mechanism is characterized in that an inertial body is formed on at least one outer periphery of the driving side member and the driven side member.

In a second aspect, preferably, the driving-side member and the driven-side member are disposed substantially concentrically and relatively rotatable via a bearing, and the first or second hysteresis mechanism is connected to the torsion. It is arranged on the inner peripheral side of the mechanism and on the outer peripheral side of the bearing. According to this means, since the working radius of the friction member can be increased, a large friction torque can be obtained even when the surface pressure applied to the friction member is reduced. In addition, the driving side member (for example, 2
Since the drive plates have a function of holding the friction member, it is not necessary to separately provide a member for holding the friction member. In addition, since the friction member penetrates the driven member, both sides of the friction member can be sandwiched by the driving member, and a predetermined clearance can be provided between the friction member and the driven member in the circumferential direction. . As a result, the amplitude corresponding to the circumferential gap (torque fluctuation)
In some cases, substantially no frictional force is generated, and the frictional force is generated after an amplitude exceeding the amplitude range corresponding to the gap is generated. That is, the hysteresis can be changed according to the magnitude of the amplitude. Further, by dividing the friction member into a plurality of parts, the hysteresis can be changed stepwise. Here, by making the area of the friction member having no clearance between the driven side member and the driving side member larger than that of the friction member having the clearance, the side receiving a large shock generated in the initial stage of torque fluctuation is provided. An excessive force is prevented from being applied to the friction member.

Further, a hysteresis mechanism is constituted so that a pressing force for urging the friction member sliding with the flywheel acts on the bearing, and the direction of the pressing force and the release bearing (lever) mechanism turn off the power. Therefore, even if the friction member of the hysteresis mechanism is worn out, the axial direction play of the bearing (the bearing disposed between the driving member and the driven member) is previously killed by adjusting the moving direction. Low release stroke loss. There is no need to separately provide a member for retaining the bearing. Also, flywheels generally have a large heat capacity,
By using the flywheel as the friction member, the temperature of the hysteresis mechanism at the time of occurrence of sliding is stabilized, so that hysteresis of a stable size is always exhibited. It is preferable that the arrangement of the friction member with respect to the engine-side surface or the transmission-side surface of the flywheel is adjusted in accordance with the operation direction of the release bearing mechanism.

In a third aspect, preferably, by reducing the spring constants of the springs at both ends of the springs arranged in series between the driving-side member and the driven-side member, most of the vehicle noise is reduced by the engine. Is caused by the small amplitude generated at the time of low torque output. By arranging a spring with a low spring constant in a portion where the influence of the spring seat sliding friction is small, the torsion (damper) mechanism has low rigidity,
With a small hysteresis characteristic, the vibration absorbing ability at low torque is improved. In addition, by making the maximum compression length of a plurality of springs arranged in series common, the shape of the intermediate spring seat (such as the length of the boss in the circumferential direction) can be unified. Can be reduced. Preferably, by setting the natural length of the torsion spring having a relatively small spring constant to be relatively large and making the natural length of the larger torsion spring small, even if the inner diameter of the torsion spring is the same, a plurality of torsion springs can be obtained. It is possible for the springs to have the same length at maximum compression. Further, by setting the outer diameter position of the spring seat to the outer diameter side from the outer diameter position of the torsion member in the interposed state, the torsion member does not interfere with the sliding surface between the spring seat and the driving side member or the driven side member. The wear is prevented.

It is preferable that a spring seat made of glass fiber reinforced nylon has a low aggressiveness to the sliding surface and a high strength. Also, by making the spring seat made of glass fiber reinforced nylon and the slider made of polyimide,
The thermal expansion coefficients of the two become closer and the thermal stress becomes smaller. Further, a polyimide spring seat has excellent heat resistance and has little wear even at high temperatures. In addition, the aggressiveness on the sliding surface is small and the wear is small. Further, since the coefficient of friction of the spring seat is reduced, the hysteresis at the time of small amplitude can be reduced.

Also, by varying the radial width of the space in which the spring seat is disposed, the seat slides when the torque fluctuates, so that the driven plate presses the spring seat in the circumferential direction and moves when the spring seat moves on the guide surface. (The inner wall of the drive plate) so that no wear occurs when load torque is generated. The outer peripheral surface of the spring seat, that is, the sliding surface, can be reduced in surface roughness by turning, and wear of the spring seat can be reduced. Grease may be applied to the sliding surface to reduce frictional resistance.

From a seventh viewpoint, preferably, a plate-like material having elasticity (preferably, an iron plate press-formed product) is used as the bearing fixing member, whereby an elastic force is generated at the bearing press-fitting portion, and a dimensional error is generated. This prevents excessive pressure from being applied to the bearing and reduces the cost.

In an eighth aspect, preferably, the outer periphery of the driving side member or the driven side member is made an inertia body,
Butt welding with the inertial body alone can be eliminated. Or,
The centrifugal force of the ring-shaped inertial body is supported by the throttle on the outer peripheral portion of the drive-side member (drive plate), so that the ring-shaped inertial body can be easily fixed.

In general, the above-mentioned means are configured such that a driving member which rotates and transmits power and a driven member which transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other. In particular, the present invention is suitably applied to a torque fluctuation absorbing device, a clutch device and the like.
The preferred means in the above viewpoint can be applied to other viewpoints.

Note that, within the scope of the principle of the present invention disclosed in the specification and the drawings, the means having the above-mentioned features include:
The present invention can be applied to other than a torque fluctuation absorber having a general configuration including a torsion mechanism and / or a hysteresis mechanism.

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a side sectional view of a power transmission mechanism according to an embodiment of the present invention, and FIG. 2 is a partially cutaway sectional view taken along line II-II of FIG. FIG. 3 is an enlarged view around the slide bearing shown in FIG.

Referring to FIGS. 1 to 3, a first drive plate 2 bolted to the crankshaft 1 of the engine, a second drive plate 3 welded and fixed to the outer periphery of the first drive plate 2, The ring gear 4, the inertia ring 5, and the inner ring 6 constitute an engine-side inertial body (drive-side member) J1, and have a flywheel 7 and a driven plate 8 slidable with a friction clutch disk assembly 26 for connecting and disconnecting the output of the engine. Constitutes a transmission-side inertial body (driven-side member) J2. The torque of the engine is input to the transmission mechanism input shaft 23 via both the inertia bodies J1 and J2 and further via a clutch mechanism so as to be connectable and disconnectable.
A sliding bearing mechanism for holding the transmission-side inertia body J2 substantially concentrically and relatively rotatable with respect to the engine-side inertia body J1 is disposed between the two inertia bodies J1 and J2 in the radial direction. A torsion mechanism and first and second hysteresis mechanisms for absorbing fluctuations in the rotation torque of the engine are provided between the rotation directions of the inertia bodies J1 and J2, and the first hysteresis mechanism is one of the torsion mechanisms. Also serves as a peripheral seal. More specifically, the torsion mechanism is surrounded by first and second drive plates that are axially opposed to each other from the outside in the axial direction and the radial direction, and is surrounded by the driven plate 8 and the first hysteresis mechanism from the inside in the radial direction. It is located in a closed space. Inner ring 6 and first
The inner peripheral portion of the drive plate 2 is positioned in the axial direction by a spacer 20 whose outer peripheral portion has a polygonal shape, and the inner ring 6 is engaged with the inner peripheral portion of the first drive plate 2 by rivets 21. By changing the plate thickness of the spacer 20, the axial height of each member can be adjusted. Therefore, a power transmission mechanism can be designed according to each model only by changing the spacer. The power transmission mechanism main body can be used in common between them. On the transmission side of the flywheel 7, a clutch disk assembly 26, a diaphragm spring 25, and a release bearing mechanism 24 are arranged. When the release bearing mechanism 24 is urged toward the engine by the release fork and the inner peripheral portion of the diaphragm spring 25 is urged toward the engine, the diaphragm spring 25 is connected to the clutch disk assembly via the pressure plate 27. The force for urging the flywheel 26 toward the flywheel 7 is weakened, the clutch disc assembly 26 is separated from the flywheel 7, and the transmission of engine power is temporarily interrupted. Next, the configuration of each mechanism will be described in detail.

The sliding bearing mechanism is firstly driven by rivets 21.
An inner ring 6 fixed to the drive plate 2, bent in the axial direction from the device radial direction, and having a tip extending in the axial direction; a driven plate 8 side surface and a device axial concave portion of the flywheel 7 (flange portion); ), And a slide bearing 18 that is spline-fitted to the outer peripheral portion of the inner ring 6, a disc spring 19 disposed on the engine-side side surface of the slide bearing 18, and a sealing material 2 disposed around the outer periphery of the disc spring 19.
2 The disc spring 19 performs a sealing function on the side surface and the inner peripheral side of the slide bearing 18, and the seal member 22 performs a sealing function on the outer peripheral side of the slide bearing 18. A lubricant reservoir (groove) 18 a is formed on both side surfaces of the slide bearing 18. This lubricant reservoir 18a
Is provided with an axial gap between the flywheel 7 and the driven plate 8 at the outer peripheral portion, and the lubricant is supplied to the sliding surface by centrifugal force. Note that a groove extending in the radial direction may be provided instead of the axial gap to secure the lubricant passage. Further, a groove 18b is provided on the sliding surface (outer peripheral surface) of the slide bearing 18 along the axial direction.
The circumferential gap between them is arranged at an angle smaller than the allowable relative rotation angle of the engine-side inertial body J1 and the transmission-side inertial body J2, and the lubricant supplied from the lubricant reservoir 18a spreads over the entire sliding surface. Surely supplied. Instead of providing a clearance between the side surface of the sliding bearing and the side surface of the drive-side member or the driven-side member, a groove may be provided as a lubricating oil passage and communicated with the axial groove 18b. Further, the inner ring 6 can be manufactured at low cost by processing and forming an iron plate.

The torsion mechanism includes a torsion spring 9 in a space surrounded by the first and second drive plates 2 and 3 in the outer peripheral portion of the apparatus and between the rotation directions of the first and second drive plates 2 and 3 and the driven plate 8. Four of them are arranged in series, the driven plate 8 holds one end of the torsion spring 9 via the spring seat 10,
The other end of the torsion spring 9 is held by the drawn portions of the first and second drive plates 2 and 3 or the block shown in FIG. 6, and torque is transmitted through the torsion spring 9. Therefore, the periodic torque fluctuation peculiar to the internal combustion engine is absorbed by the bending of the torsion spring,
The output shaft 23 transmits a smooth rotational motion force. further,
A stopper 10b is disposed in the torsion spring 9, and when the deflection of the torsion spring approaches the limit,
Stopper 10b and boss 10a of spring seat 10
Abuts on the torsion spring 9 to prevent over-compression. Further, the boss 10a can be shortened, the moment applied to the boss 10a is reduced, and the boss 10a is hardly broken. When the spring length is set short, as in the case of the torsion springs 9b at both ends in the circumferential direction shown in FIG. 7, the boss portions 10a directly contact each other to prevent the overcompression. A lubricant (for example, grease) is sealed in the space. Further, a relief (clearance) 49 for preventing interference between the step formed by turning and the spring seat 10 is provided on the spring seat 10 on the receiving surface of the drawn shape portion of the first drive plate 2.

The first hysteresis mechanism and the inner peripheral side sealing mechanism of the torsion mechanism are provided on the inner peripheral side of the first and second drive plates 2 and 3 (in the vicinity of the inner peripheral side of the torsion mechanism and relatively in the device). (An outer peripheral side), and an annular friction member (thrust lining) 13, a driven plate 8, a disc spring 14, and an annular friction are sequentially arranged from the first drive plate 2 to the second drive plate 3 along the device axial direction. It is composed of a member (thrust lining) 12. The positioning of the friction member 13 is performed at the stepped portion of the first drive plate 2 that has been pressed. The friction member 12 is bent from the outside in the device radial direction toward the engine side in the axial direction, and the protrusion that extends is engaged with the notch of the driven plate 8 in the device rotation direction and rotates together with the driven plate 8.
The disc spring 14 connects the friction member 13 to the first drive plate 2.
To the side of the first drive plate 2,
The friction member 12 is urged toward the second drive plate 3 to contact the side surface of the flywheel 7. Friction members 13, 12
And the disc spring 14 are connected to the first and second drive plates 2 and 3.
In addition to filling the gap on the inner peripheral side of the driven plate 8 and preventing the lubricant from leaking, it slides on the first and second drive plates 2 and 3 to exhibit a relatively small hysteresis function.

The second hysteresis mechanism which exhibits a relatively large hysteresis function is located on the transmission side (output side) of the flywheel 7, and is arranged outside the space in which the torsion mechanism is housed and in which the lubricant is sealed. .
The second hysteresis mechanism includes a flywheel 7 on the transmission side and an inner peripheral side of the flywheel 7 in order from the flywheel 7 toward the transmission along the device axial direction.
An annular friction member (thrust lining) 15 that abuts against the side surface and slides frictionally, an annular thrust plate 16, and a disc spring 17 are provided. Protrusions are provided in the inner periphery of the friction member 15 in a spline shape. Corresponding to these protrusions, recesses are provided in the outer periphery of the extension of the inner ring 6 in the form of splines. A predetermined angular clearance W (see FIG. 2) is provided along the direction, and when the relative rotation between the engine-side inertial body J1 and the transmission-side inertial body J2 becomes equal to or larger than the predetermined angle W (for example, during a resonance action), both rotate. In the direction (circumferential direction) to generate a large hysteresis to increase the damping ability between J1 and J2. The outer periphery of the thrust plate 16 is engaged with a pin 11 for fixing the driven plate 8 to the flywheel 7 in the apparatus rotation direction. The disc spring 17 is locked to the head of the pin 11 and urges the friction member 15 through the thrust plate 16 toward the side surface of the flywheel 7 to make contact therewith. Note that the friction member 15 is frictionally locked between the flywheel 7 and the thrust plate 16 while being urged by the disc spring 17 (sandwich holding).
Have been.

A plurality of substantially trapezoidal shapes (a long side is on the radially outer side, a short side is on the inner side, in other words, an "outwardly-opened diaper shape" is formed at a radially intermediate portion of the first drive plate 2 along the circumferential direction. The hole 29 of ")" is provided, and the outer peripheral portion of the first drive plate 2 and the inner peripheral portion fixed to the crankshaft 1 by bolts are in a so-called "arm-like connection" (spring-like connection). The center of the substantially trapezoidal hole 29 in the radial direction faces the vertex of the polygonal spacer 20 (axial positioning member), and the side of the spacer 20 faces the arm between the holes 20. Then, the bolt hole and the hole 29 where the first drive plate 2 is fixed to the crankshaft 1 are located at substantially the same position in the circumferential direction (at substantially the same angle, and substantially on a straight line in the radial direction).
As a result, the contact length and contact area between the polygonal spacer 20 and the first drive plate 2 are increased, concentrated stress due to bending stress in the axial direction is dispersed, and destruction of the first drive plate 2 is prevented. , Durability is improved.

Next, the function of the power transmission mechanism having the torque fluctuation absorbing function will be described. First, the function of the sliding bearing mechanism will be described. The engine torque is transmitted from the first and second drive plates 2 and 3 to the spring seat 10,
The power is transmitted to the flywheel 7 via the torsion spring 9, the driven plate 8, and the pin 11. The inner peripheral side of the slide bearing 18 is engaged with the inner ring 6 which is the engine-side inertia body J1 in the device rotation direction, and the slide surface of the slide bearing 18 is limited to the outer peripheral surface 18a. It slides only on the inner peripheral surface of a certain flywheel 7. Since the sliding surface is limited to one surface side (particularly, the outer peripheral surface side), lubricating oil is forcibly supplied to the sliding surface by centrifugal force, and an oil film is formed to prevent wear of the sliding surface. Therefore, the durability is improved, the concentric deviation of the transmission-side inertial body J2 with respect to the engine-side inertial body J1 is prevented, and the increase of vibration due to the concentric deviation is also prevented. Note that it is also possible to engage the slide bearing with the driven member in the rotational direction, and to configure the peripheral surface with respect to the drive member as a sliding surface. At this time, the driving side member is provided on the outer peripheral side, and the driven side member is provided on the inner peripheral side.
For example, an axially extending portion of the inner ring is arranged along the outer peripheral surface of the slide bearing, the inner peripheral surface of the extended portion is formed as a sliding surface, and the flywheel is extended in the engine-side axial direction on the inner peripheral surface side of the sliding bearing. , Engage the slide bearing and the extension of the flywheel in the direction of rotation. Note that the engagement surface and the sliding surface may be reversed.

Further, the lubricant stored in the lubricant reservoir 18a is supplied to the outer peripheral surface of the sliding bearing 18 having the sliding surface by the centrifugal force accompanying the rotation of the device, and forms an oil film. The seal member 22 prevents the lubricant from leaking radially outward from between the driven plate 8 and the side surface of the flywheel 7 due to the centrifugal force. Further, even when the engine is stopped (when the centrifugal force is zero), one side of the inner diameter side of the slide bearing 18 is in contact with the inner side surface of the flywheel 7 by the disc spring 19 and the other is in contact with the inner diameter of the disc spring. Prevents leakage of lubricant from the peripheral side. For example, when the inner peripheral surface of the sliding bearing slides on the driven member disposed on the inner peripheral side of the sliding bearing, a clearance is provided on the sliding inner diameter side so that the lubricant is supplied to the sliding surface to form a lubricant reservoir. , So that a lubricant can be supplied to the sliding surface.

Next, the function of the torsion mechanism will be described. When the device rotates, the torsion spring 9 is urged radially outward (outer peripheral sides of the first and second drive plates) by centrifugal force. However, the projection 10a of the spring seat 10 is inserted into the inner periphery of the torsion spring 9, and locks the torsion spring 9 substantially inward and outward (prevents movement in the radial direction). . As described above, the spring seat 10 can prevent the torsion spring 9 from moving outward in the radial direction on the inner peripheral side of the torsion spring 9, and it is necessary to arrange a holding member for preventing the movement on the outer peripheral side of the torsion spring 9. Torsion spring 9
Can be arranged radially outward by the amount occupied by the holding member. For this reason, the torsion spring 9
A low rigidity or a small torsion spring can be used depending on the spring force of the spring disposed on the outside in the radial direction. In addition, since a low-rigidity torsion spring can be used, the durability of the torsion spring 9 and its surroundings is improved, and the cost is reduced. By arranging the stopper 10b at the middle part of the inner periphery of the torsion spring 9, the deflection of the torsion spring is restricted to prevent an excessive load and also prevent a bending due to a centrifugal force.

Next, the function of the inner peripheral side sealing mechanism and the small hysteresis mechanism (first hysteresis mechanism) of the torsion mechanism will be described. A lubricant (grease) for lubricating the spring seat 10 is sealed in a closed space accommodating the torsion spring 9. The outer peripheral side of this space is sealed by the entire circumference welded portion of the first and second drive plates 2 and 3, and the inner peripheral side is the friction disposed between the first and second drive plates 2 and 3 in the axial direction. Sealed by the member 13, the driven plate 8, the disc spring 14, and the friction member 12. In addition, when the first and second drive plates 2 and 3 and the driven plate 8 rotate relative to each other, the friction members 13 and 12 move to the first and second drive plates 2 and 3.
Hysteresis is generated by sliding with respect to. As described above, since the inner peripheral side seal of the space accommodating the torsion spring 9 is brought into surface contact between the friction members 13 and 12 and the first and second drive plates 2 and 3, the lubricant is less likely to leak, and the torsion mechanism is provided. The durability is improved. Further, even if the friction members 13 and 12 are worn,
4, the friction members 13 and 12 are urged toward the first and second drive plates 2 and 3, respectively, so that the surface contact state is maintained. As described above, by providing a mechanism that serves both as a sealing mechanism and a hysteresis mechanism, the apparatus can be made more compact.

Further, the flywheel 7, the clutch disc assembly 26 and the like as a whole move leftward in FIG.
4 urges the friction member 13 toward the first drive plate 2 via the driven plate 8, so that the lift amount of the lever portion 24 that urges the diaphragm spring 25 due to long-term use is corrected, and the clutch operation is performed. No extra play is created.

Next, the function of the second hysteresis mechanism will be described. Due to the relative rotation of the engine-side inertia body J1 and the transmission-side inertia body J2, the friction member 15 in the second hysteresis mechanism slides against the side surface of the flywheel 7 and the thrust plate 16 to generate hysteresis and frictional heat ( In particular, the temperature of the thrust plate 16 having a small heat capacity is easily increased.)
Is arranged in an open space, the frictional heat is quickly radiated to the external space, and the friction member 15 is less likely to wear due to overheating, and the durability is improved. Further, since the friction member 15 and the inner ring 6 have a clearance of W in the circumferential direction, friction occurs only when the relative twist angle between J1 and J2 is W or more. That is, since the frictional heat is generated intermittently, the heat radiation effect is enhanced. As described above, since the cooling performance of the friction member 15 is improved, the grade of the friction member 15 can be reduced, and the cost can be reduced. In addition, such a friction member is disposed between the driving side member in the axial direction, and the driven side member has a clearance at a predetermined angle and is opposed to the rotation direction (circumferential direction).
When the relative rotation of J2 occurs, the friction member and the driven member can be engaged with each other, and the friction member can be frictionally slid with respect to the driving member holding and holding the friction member. It is said.

As described above, the durability of each mechanism constituting the power transmission mechanism is improved, so that the durability of the power transmission mechanism is naturally improved. Further, the cost of the device is reduced by using a sliding bearing, and the device is downsized by using both a hysteresis mechanism and a sealing mechanism of a torsion portion. further,
The first hysteresis mechanism, which also serves as the seal mechanism of the torsion mechanism, and the second hysteresis mechanism realize a multi-stage hysteresis with a compact configuration. In the present embodiment, an example in which the power transmission mechanism of the present invention is applied to a torque fluctuation absorbing mechanism has been described. However, the present invention is not limited to this torque fluctuation absorbing mechanism, and may be applied to other mechanisms such as a clutch mechanism. It is also possible to apply to the power transmission mechanism. Further, the sliding surface of the sliding bearing can be changed from the outer peripheral side to the inner peripheral side, and the engagement of the sliding bearing in the rotational direction can be changed from the driving side member to the driven side member. Also,
It is also possible to change the sliding surface of the friction member from the driving side member to the driven side member (the same applies to a member in which the friction member engages in the rotation direction).

A power transmission mechanism according to another embodiment of the present invention will be described with reference to FIGS. Regarding this power transmission mechanism, a description will be given of differences between the power transmission mechanism according to the above-described embodiment of the present invention and the configuration and functions thereof.

In another embodiment of the present invention, the second hysteresis mechanism is disposed on the inner peripheral side of the torsion mechanism used in a dry state and on the outer peripheral side of the bearing (see FIG. 7). The second hysteresis mechanism is arranged at predetermined intervals in the circumferential direction, and includes a plurality of friction members 13 and friction members 1 slidably contacting the first drive plate 2.
3, the thrust plate 12 in contact with the surface on the drive plate 3 side, the thrust plate 12 and the drive plate 3
And a disc spring 14 interposed between them. The friction member 13 arranged in a ring shape as a whole receives the urging force of the disc spring 14 via the ring-shaped thrust plate 12, thereby causing the first and second drive plates 2 and 2 to rotate.
It is sandwiched between three. Further, the friction members 13 penetrate through a plurality of holes (windows, which may be notches) formed at predetermined intervals along the circumferential direction of the driven plate 8, and the holes of the friction member 13 and the driven plate 8 are formed. A predetermined clearance W1 is provided in the circumferential direction between the inner walls. The outer peripheral end of the thrust plate 12 is bent and extends toward the second drive plate 3 along the axial direction. A hole is formed in the inner peripheral portion of the second drive plate 3, and the extending portion of the thrust plate 12 passes through the hole. The thrust plate 12 is held by the second drive plate 3 by the extension and the hole,
Positioning or detenting is performed in the circumferential direction.

The function of the second hysteresis mechanism will be described (particularly, see FIGS. 7 and 8). In the second hysteresis mechanism, the friction member 13 and the driven plate 8
(See FIG. 7), the clearance between J1 (drive-side member, first and second drive plates, etc.) and J2 (driven-side member, driven plate, etc.). When the torsion angle (amplitude) is equal to or greater than W1, the driven plate 8 contacts and urges the friction member 13 so that the friction member 13 slides against the first drive plate 2 and the friction force is reduced. Occur. That is, the hysteresis can be changed depending on the magnitude of the amplitude. Further, since the friction members can be divided and arranged as described above, a low-cost friction material having high productivity can be used. Further, the number of members of the second hysteresis mechanism of the present embodiment is smaller than that of the above-described embodiment. Note that the friction member is divided into smaller friction members and the yield of the friction members is improved (in the case where the friction member is a sheet type), rather than using the friction member alone. In addition, the production amount per shot increases (when the friction member is a resin type).

Hereinafter, a preferred modification of the second hysteresis mechanism will be described. The clearances W1 can be set to different sizes. For example, the size of the clearance W1 is changed stepwise. As a result, it is possible to set hysteresis that changes in multiple stages according to the relative twist angle (amplitude). Further, a part of the clearance W1 is set to zero (it is assumed that there is substantially no gap between the friction member and the driven plate).
Thereby, for each of the small twist angle and the wide twist angle,
Different hysteresis is set, and the first hysteresis mechanism and the second hysteresis mechanism (small hysteresis mechanism and large hysteresis mechanism, actuated according to the magnitude of the relative torsion angle)
A non-operating mechanism and a hysteresis mechanism, which always operates when relative torsion occurs, can be shared.

Referring to FIGS. 6 and 9, the first hysteresis mechanism is located inside the clutch mechanism (clutch disc assembly), and includes the clutch mechanism and flywheel 7.
Between the sliding surfaces of the clutch disk. The first hysteresis mechanism includes a flywheel 7 and a flange 6a (a tip protruding outward in the radial direction) of an inner ring (receiving an inner race of a bearing) 6 formed of an iron plate. And a friction member 15 which is divided into a plurality and divided at a center interval of 120 °, and which are arranged sequentially in the axial direction between the friction member 15 and the friction member 1 (which exerts the axial load holding function of the hysteresis mechanism).
A ring-shaped thrust plate 16 abutting on the plate 5 and a disc spring 17 for urging the friction member 15 (and the ball bearing 18) in the direction of the arrow (see FIG. 6) via the thrust plate 16. The engine-side surface of the friction member 15 is in contact with the transmission-side surface of the flywheel 7. A plurality of protrusions are formed on the other side of the friction member 15 so as to protrude from the radial center of the friction member 15 along the axial direction. Thrust plate 16 is friction member 15
A plurality of holes are formed in the surface in contact with the protrusions, and the projections of the friction member 15 penetrate and engage with these holes, respectively. Thereby, the positioning of the friction member 15 is performed. Like the thrust plate 12 shown in FIG. 8, the inner peripheral end of the thrust plate 16 is bent and extends toward the transmission in the axial direction (not shown in FIG. 9). The extending portion of the thrust plate 16 penetrates a hole or notch provided on the flange surface of the inner ring 16 and engages with the hole or notch. Thus, the positioning of the thrust plate 16 is performed. The outer race of the ball bearing 18 is received on a bearing receiving flange of the flywheel 7.

Further, corresponding to the gap between the friction members 15 adjacent to each other (at the same angle in the circumferential direction), the cylindrical surface of the inner ring 6 radially inside the gap is radially communicated. Holes 6b are formed. The holes 6b improve the cooling performance of the friction member 15, the thrust plate 16, and the like, and discharge the friction material powder that has dropped through the holes 6b, thereby reducing the abrasion of the friction member 15 and the like. This stabilizes the friction torque over time.
In order to improve the wear resistance and stabilize the friction torque, the friction member 15 is preferably made of polyimide.

The function of the first hysteresis mechanism will be described. Due to the relative rotation of the engine-side inertial body J1 and the transmission-side inertial body J2, the friction member 15 in the first hysteresis mechanism slides against the side surface of the flywheel 7 and the thrust plate 16 to generate hysteresis. At that time, frictional heat is generated (particularly, the thrust plate 16 having a small heat capacity tends to rise in temperature), but the thrust plate 16 is arranged in an open space, and a hole 6 b is provided at the predetermined position of the inner ring 6. Therefore, the frictional heat is quickly dissipated to the external space, and the members near the frictional member 15 do not easily wear due to overheating, and the durability is improved.

Note that a clearance may be provided between the friction member 15 and the inner ring 6 in the circumferential direction. A guide groove along the circumferential direction may be formed by pressing in a portion of the first drive plate 2 where the friction member 13 slides. The rattling when the friction member 13 slides is reduced, and a stable friction force is always generated.

Next, a bearing mechanism between the engine-side inertial body J1 and the transmission-side inertial body J2 will be described.
As a bearing between J1 and J2, a ball bearing 18 is provided in a space surrounded by the first drive plate 2, the flywheel 7, and the inner ring 6 on the inner peripheral side of the power transmission mechanism.
Are arranged. The inner peripheral side of the ball bearing 18 is engaged with an inner ring 6 (via an inner race) fixed to the crankshaft 1 in the rotational direction. A rolling surface of the ball is formed by the inner race and the outer race of the ball bearing 18. The axial load applied to the ball bearing 18 is received by the flange portion 6 a of the inner ring 6, and the disc spring 17 moves the ball bearing 18 through the flywheel 7 abutting on the outer peripheral surface of the ball bearing on the transmission side. 1 to the drive plate 2 side. On the other hand, the inner peripheral portion of the first drive plate 2 facing the ball bearing 18 is drawn to form a concave portion, and the inner peripheral portion (inner race) of the engine-side end surface of the ball bearing 18 is the first peripheral portion. The outer peripheral portion (outer race) does not contact the first drive plate 2.

The driven plate 8 and the flywheel 7 are fixed to each other by screwing using bolts 11, so that when the bolts are tightened, a large load in the radial direction is applied when fixing with rivets. Is not applied, so that an excessive pressure is locally prevented from being applied to the ball bearing 18 and the bearing life is extended. That is, the deformation that occurs when the driven plate and the flywheel are riveted (rivet fixed) does not occur. In addition, an excessively large load is locally prevented from being applied to the ball bearing 18, and the bearing life is extended.

Next, an inertia member provided on the outer peripheral portion of the power transmission mechanism for reducing the rotation fluctuation will be described.
Referring to FIG. 6, an inertia body 5 is attached to the outer peripheral portion of second drive plate 3 by welding before the entire power transmission mechanism is assembled. As a result, the inertia of the engine-side inertial body J1 increases, so that the amplitude of the input vibration is reduced. As the inertial body 5, the use of a steel strip or a drawn material obtained by roll forming improves the material yield, and is therefore preferable in terms of cost. Further, it is preferable to attach an inertial body to the outer peripheral side of the flywheel 7 because the inertial effect is improved. The flywheel 7 is a pot type (a type in which the clutch cover mounting surface is closer to the transmission than the friction surface), so that the flywheel 7 has an increased outer peripheral weight, and the inertia of the transmission-side inertial body J2 increases. In addition, a rotation fluctuation with respect to a torque fluctuation transmitted via a torsion spring (described later) is reduced.

Referring again to FIG. 6, a ring gear 4 is disposed on a flange surface formed on the outer peripheral portion of first drive plate 2. The mounting position of the ring gear 4 is on the engine side of the inertial body 5 welded to the drive plate 3. The tooth surface of the ring gear 4 is chamfered to the height of the tooth. As described above, since the portion on the cutting exit side during the hobbing is chamfered, burrs are less likely to appear and the deburring step can be omitted. Also, especially when a resin sheet is used for the torsion mechanism,
At a position as far as possible from this resin sheet, the first
And the second drive plate 3 are preferably welded. In the power transmission mechanism shown in FIG. 10, the first drive plate 2 and the second drive plate 3 are welded (fillet welding,
(All circumference welding, spot welding). Referring to FIG. 10, more preferably, the outer peripheral contact surfaces of first drive plate 2 and second drive plate 3 are provided with a space on the inner peripheral side of the corresponding contact surface (a torsion mechanism is arranged in the space). Is provided, and a partial gap 3a communicating the outside is provided. Through this partial gap, mud that has entered the space where the torsion mechanism is arranged is eliminated, and the cooling effect is enhanced because air flows from inside to outside due to centrifugal force. In the illustration of FIG. 10, a concave portion is provided on the second drive plate 3 side, but such a concave portion may be formed on the first drive plate 2 side or both drive plates 2 and 3.

In particular, with reference to FIG. 7, the torsion mechanism of the present embodiment includes a space surrounded by the first and second drive plates 2 and 3 at the outer peripheral portion of the apparatus and the first and second drive plates 2 and 3. A plurality of torsion springs 9 are arranged in series between the driven plates 8 in the rotation direction. Both ends of the plurality of torsion springs 9 (positions at which the first and second drive plates 2 and 3 hold the torsion spring 9b in the circumferential direction and the driven plate 8).
The spring wire diameters of the torsion springs 9b and the like are relatively thinner than the inner torsion springs 9a, and the spring constants of the torsion springs 9b at both ends are equal to the inner torsion springs 9b.
The spring constant is relatively small as compared with the spring constants a (the so-called torsion springs 9a at both ends are downsized). In the first and second drive plates 2 and 3,
Spring seat 1 on one side of torsion spring 9b
A block member for abutting and pressing through the zero is attached. This block member is on the drive side (engine side)
Increase inertia of inertia. A concave portion is provided in the spring seat 10 fitted to one end of the other torsion spring, and a convex portion is provided on an outer peripheral portion of the driven plate 8 facing the concave portion, and the convex portion is fitted with the concave portion. It is possible. Furthermore, the torsion spring 9
Spring seats 10 are fitted to both ends of a and 9b. The spring seats 10 each have a substantially triangular base protruding inward in the radial direction and bosses 10a protruding from both side surfaces of the base, and the boss 10a is an inner peripheral portion of the torsion springs 9a and 9b. (Internal cavity) to support the torsion springs 9a and 9b in the radial direction of the power transmission mechanism. However, the boss 10a that fits into the inner cavity (torsion spring 9a side) of the torsion spring 9b at both ends in the rotation direction has a larger diameter (thicker) than the boss that fits the inner torsion spring 9a. I have. The spring seat 10 having boss portions at both ends thereof and fitted to the inner torsion spring 9a has a substantially plane-symmetric shape. On the outer peripheral surface of the spring seat 10, a slider 10c having a low coefficient of friction integrally formed with the spring seat 10 is provided. Such a slider may be fitted into a spring seat, and a return for preventing the slider from coming off may be provided. Slider 10c
Is in sliding contact with a rolled steel plate 30 attached to the inner peripheral surface of the first drive plate 2. Further, as shown in the figure, the radial dimension (width) of the spring seat is larger than the radial dimension of the torsion springs 9a, 9b, so that the torsion springs 9a, 9b are connected to the inner periphery of the first drive plate 2. Sliding with the surface is prevented. The inner wall surface of the first drive plate 2 to be drawn is likely to have a press flaw in a direction perpendicular to the sliding direction of the spring seat 10, and the press flaw may accelerate abrasion of the spring seat. Then, by applying the rolled steel plate 30 to the spring seat sliding surface, the sliding surface is mirror-finished, and the spring seat wear is reduced.

A stopper 10b, which comes into contact with the spring seat 10 when the torsion spring 9a is compressed, is provided on the inner peripheral portion of the inner torsion spring 9a. No stopper is provided on the torsion spring 9b at both ends, and when the torsion spring 9b is compressed, the end faces of the boss portions 10a of the spring seat 10 directly contact each other. Referring to FIG. 11, the torsion springs 9a and 9b are arranged to open outward at the initial position (the outer peripheral side of the spring is longer than the inner peripheral side, the interval between the spring seating surfaces (end faces) is wider on the outer peripheral side, In the initial position, the seat surface is at a predetermined angle with respect to a radial line passing through the center of the closing power transmission mechanism so that the angle between the spring seat surfaces is parallel at the time of maximum compression.) At the maximum compression, the spring end faces are parallel to each other. In the coil spring, the amount of deflection at the center is proportional to the load, and the allowable stress (elastic force) is proportional to the amount of deflection at the maximum bending portion. Therefore, the allowable load becomes maximum when the maximum bending portion is the central portion.

Next, the function of the torsion mechanism will be described. When the device rotates, the torsion spring 9a,
9b is urged radially outward by centrifugal force. However, the boss 10a of the spring seat 10 is inserted into the inner periphery of the torsion springs 9a and 9b, and the torsion springs 9a and 9b are substantially radially inward and outward.
Is locked. In addition, the radial dimension of the spring seat 10 is larger than the diameter dimension of the torsion springs 9a and 9b, and the slider 10c is provided at the outermost periphery of the spring seat. Is in contact with the inner peripheral surface of the first drive plate 2 and is highly prevented from sliding.

As the torsion angle between the first and second drive plates 2 and 3 and the driven plate 8 increases, the amount of compression of the torsion springs 9a and 9b increases, but the boss 10a of the spring seat 10 Boss part 10
a and the boss portions 10a abut each other via the stopper 10b, so that the torsion springs 9a, 9
The amount of compression of b is limited.

Next, a power transmission mechanism according to still another embodiment of the present invention will be described with reference to FIGS. In this power transmission mechanism, the outer peripheral end of the first drive plate 2 is a tongue-shaped portion 2a (by drawing), and the inertial body 5 is caulked between the tongue-shaped portion 2a and the second drive plate 3. ing. The torsion spring 9 is a hollow cylindrical high elastic rubber member. According to this embodiment, the allowable deflection is large and the torsional angle can be widened (the torsional angle width capable of absorbing the torque fluctuation is large). Further, since the weight of the torsion member can be reduced, centrifugal force applied to the spring seat is reduced, and wear of the spring seat can be reduced.

[0063]

As described above, according to each power transmission mechanism of the present invention, the sliding bearing mechanism, the torsion mechanism, the inner peripheral side seal mechanism of the torsion mechanism, the first and second power transmission mechanisms, which constitute the power transmission mechanism, are provided. The durability of the hysteresis mechanism and the drive-side member are improved without increasing costs.
By configuring a power transmission mechanism such as a torque fluctuation absorbing device from each of the mechanisms with improved durability, it is possible to achieve a longer life.

In particular, according to the power transmission mechanism having the sliding bearing of the present invention, the play between the driving side member and the driven side member is suppressed, and the rotational vibration is reduced. Further, according to the power transmission mechanism having the torsion mechanism of the present invention, the sealing ability of the space accommodating the torsion mechanism by the friction member is high. The leakage prevention capability is enhanced, and the friction member also exhibits a hysteresis function. Further, by providing the hysteresis mechanism outside the space accommodating the torsion mechanism, the heat radiation of the hysteresis mechanism is improved, and the durability is improved. Also, a lubricant may be sealed in the space,
By providing a hysteresis mechanism outside this space,
Since the hysteresis mechanism is not affected by the lubricant, the hysteresis is stabilized. Further, by forming a hole at a predetermined position of the drive-side member, the rigidity of the drive-side member in the axial direction is reduced (it becomes substantially springy), and particularly, vibration in the device axial direction is absorbed, and damage to the drive-side member is prevented. Is prevented. Further, by locking the torsion spring on the inner peripheral side thereof, the torsion spring can be disposed on the outer peripheral side of the device as compared with the related art, and the rigidity and compactness of the torsion spring can be achieved.

[Brief description of the drawings]

FIG. 1 is a side sectional view of a power transmission mechanism according to an embodiment of the present invention.

FIG. 2 is a partially broken cross-sectional view taken along the line II-II in FIG.

FIG. 3 is an enlarged view around the sliding bearing shown in FIG. 1;

FIG. 4 is a partially cutaway front view of a torque fluctuation absorber according to a conventional example.

5 is a side sectional view of the torque fluctuation absorber shown in FIG.

FIG. 6 is a side sectional view of a power transmission mechanism according to another embodiment of the present invention.

FIG. 7 is a partially cutaway sectional view taken along the line VII-VII in FIG. 6;

8 is a partially enlarged view of a second (located on the outer diameter side) hysteresis mechanism shown in FIG. 6;

FIG. 9 is a partially enlarged view of the first (located on the inner diameter side) hysteresis mechanism shown in FIG. 6;

FIG. 10 is a partially enlarged view of a contact portion of the first and second drive plates shown in FIG.

FIG. 11 is a view for explaining a preferred form of a torsion spring.

FIG. 12 is a side sectional view of a power transmission mechanism according to still another embodiment of the present invention.

FIG. 13 is a partially cutaway sectional view taken along the line XIII-XIII in FIG.

[Explanation of symbols]

 Reference Signs List 1 crankshaft 2 first drive plate 3 second drive plate 4 ring gear 5 inertia ring 6 inner ring 6a flange 6b hole 7 flywheel 8 driven plate 9 torsion spring 9a torsion spring with large spring constant 9b torsion spring with small spring constant 10 Spring seat 10a Projection (boss) 10b Stopper 10c Slider 11 Pin 12 Friction member 13 Friction member 14 Disc spring 15 Friction member 16 Thrust plate 17 Disc spring (thrust spring) 18 Slide bearing, ball bearing 18a Lubricant pool 18b Groove ( Groove extending in the axial direction) 19 disc spring 20 spacer 21 rivet 22 sealing member 23 transmission mechanism input shaft 24 release bearing mechanism 25 diaphragm spur Ring 26 Clutch disc assembly W Clearance W1 Clearance 30 Rolled steel plate 31 Bolt 49 Release (clearance)

Continuing from the front page (72) Inventor Seirin Kobayashi 2-1-1 Asahi-cho, Kariya-shi, Aichi Prefecture Aisin Seiki Co., Ltd. (72) Inventor Hideharu Sadakari 2-1-1, Asahi-cho, Kariya-shi, Aichi Aisin Seiki shares In company

Claims (78)

[Claims] 1. A power transmission mechanism in which a drive-side member that rotates and transmits power and a driven-side member that transmits and rotates the power are substantially concentrically and relatively rotatably arranged. The drive side member is disposed on one of the side and the outer diameter side, and the driven side member is disposed on the other side. The drive side member or the driven side member is disposed between the drive side member and the driven side member in the radial direction. A power transmission mechanism characterized by comprising a sliding bearing which is engaged substantially concentrically with one of the two and has a sliding surface on the other. 2. The power transmission mechanism according to claim 1, wherein a lubricant is provided on at least one of the peripheral surfaces of the slide bearing, the driving member, and the driven member. 3. The sliding bearing is disposed in a space defined by the driving-side member and the driven-side member, and a radially inward side of the sliding surface and / or a side surface of the sliding bearing. The power transmission mechanism according to claim 2, wherein the lubricant reservoir is provided on a side surface of the driving side member and / or the driven side member facing a side surface of the slide bearing. 4. The sliding bearing is provided between a side surface of the sliding bearing and the driving side member or the driven side member facing the sliding bearing and abuts the sliding bearing to move the sliding bearing in the axial direction. Biasing toward the side member or the driving side member,
The power transmission mechanism according to any one of claims 1 to 3, further comprising a disc spring for preventing lubricant from leaking from a side surface of the slide bearing in an axial direction. 5. A seal member disposed on an outer peripheral side of the disc spring to prevent lubricant from leaking radially outward from an outer peripheral portion of the disc spring. The power transmission mechanism described in the above. 6. A power transmission mechanism in which a drive-side member that rotates and transmits power and a driven-side member that transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other, Between the driving side member and the driven side member, a torsion mechanism for absorbing a fluctuation in rotational torque of the driving side member and the driven side member is housed, and is disposed in a space for housing the torsion mechanism, and at least one A first hysteresis mechanism that includes a friction member and generates hysteresis by sliding of the friction member with respect to the drive side member or the driven side member, and is disposed outside a space that houses the torsion mechanism, and the friction member slides. A power transmission mechanism comprising: a second hysteresis mechanism that generates a hysteresis different from the first hysteresis mechanism. 7. A power transmission mechanism in which a driving-side member that rotates and transmits power and a driven-side member that transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other, A torsion mechanism that absorbs fluctuations in rotational torque between the driving side member and the driven side member is accommodated between the driving side member and the driven side member, and is disposed on an inner peripheral side of a space accommodating the torsion mechanism. A first hysteresis mechanism that includes at least one friction member and generates hysteresis by sliding the friction member against the drive-side member or the driven-side member; and a friction member that is disposed outside a space that houses the torsion mechanism. A second hysteresis mechanism that generates a hysteresis different from the first hysteresis mechanism due to sliding of the first hysteresis mechanism. A power transmission mechanism inner peripheral side, characterized in that it is sealed. 8. A power transmission mechanism in which a driving-side member that rotates and transmits power and a driven-side member that transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other, A torsion mechanism that absorbs fluctuations in rotational torque between the driving side member and the driven side member is accommodated in a space surrounded by the driving side member and / or the driven side member, and a friction member is provided outside the space. A second hysteresis mechanism that generates hysteresis by sliding of the friction member is disposed; a disc spring is disposed between the friction member and one of the driving side member and the driven side member in the axial direction; Receives the urging force of the disc spring, is locked by frictional force to the other of the driving side member or the driven side member, and rotates the apparatus with respect to the other of the driving side member or the driven side member. A power transmission mechanism having a predetermined angle clearance in a direction, and capable of engaging when relative rotation between the drive side member and the driven side member reaches the predetermined angle or more. 9. A power transmission mechanism in which a driving-side member that rotates and transmits power and a driven-side member that transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other, A power transmission mechanism characterized in that an inner peripheral side of a driving side member is fixed to a driving shaft, a hole is formed in an intermediate portion, and an outer peripheral portion and an inner peripheral portion are connected in a substantially arm shape. 10. The power transmission according to claim 10, wherein a hole at an intermediate portion of the drive side member is arranged at the same position in a circumferential direction as a bolt hole fixed to the drive shaft. mechanism. 11. A driving device according to claim 1, further comprising a substantially annular spacer fixed to said driving shaft and having a polygonal outer periphery, wherein said polygonal side portion of said outer periphery of said driving side member is positioned on said driving side. The power transmission mechanism according to claim 10, wherein the power transmission mechanism is configured to face a portion of the member connected in an arm shape in a device radial direction. 12. A power transmission mechanism in which a drive-side member that rotates and transmits power and a driven-side member that transmits and rotates the power are arranged substantially concentrically and relatively rotatable with each other, A torsion member that absorbs fluctuations in rotational torque is arranged in series between the drive side member and the driven side member in the device rotation direction, and is inserted from the end of the torsion member to the inner peripheral side to radially move the torsion member. A power transmission mechanism comprising a spring seat for locking. 13. A power transmission mechanism in which a driving member that rotates and transmits power and a driven member that transmits and rotates the power are substantially concentrically and relatively rotatable via bearings. A power transmission mechanism, wherein an inner race or an outer race of the bearing is fixed to a driven side member. 14. A power transmission mechanism in which a drive-side member that rotates and transmits power and a driven-side member that is connected to a flywheel and rotated by the transmission of the power are arranged substantially concentrically and relatively rotatable with each other. A power transmission mechanism, wherein an inertia body is formed on at least one outer periphery of the driving-side member and the driven-side member. 15. The drive-side member and the driven-side member are disposed substantially concentrically and relatively rotatable via a bearing, and the first hysteresis mechanism is provided on an inner peripheral side of the torsion mechanism and the bearing. The power transmission mechanism according to claim 6, wherein the power transmission mechanism is disposed on an outer peripheral side of the power transmission unit. 16. The friction member of the first hysteresis mechanism is sandwiched between the driving members via a disc spring or a thrust plate, and the other side of the friction member penetrates the driven member. The power transmission mechanism according to claim 15, wherein: 17. The friction member penetrates a hole or notch formed in the driven member, and a clearance exists between a penetrating portion of the friction member and the hole or the notch in a circumferential direction. The power transmission mechanism according to claim 16, wherein: 18. The power transmission mechanism according to claim 16, wherein the friction member of the first hysteresis mechanism is divided into a plurality of members. 19. A groove extending in a circumferential direction for guiding sliding of a friction member of the first hysteresis mechanism is formed in the drive-side member.
The power transmission mechanism described in the above. 20. A power transmission mechanism according to claim 18, further comprising means for holding said friction member against a centrifugal force acting on said friction member. 21. The divided friction member penetrates a hole or notch formed in the driven member, and a portion where the divided friction member penetrates the driven member and the hole or the notch. 19. The power transmission according to claim 18, wherein clearances are respectively provided between the notches in a circumferential direction, and at least one of the plurality of clearances has a size different from other clearances. mechanism. 22. The power transmission mechanism according to claim 21, wherein at least one of the clearances is substantially zero. 23. The friction area of the friction member, wherein the clearance between the hole and the notch of the driven member is substantially zero, the clearance between the hole and the notch of the driven member is reduced. The power transmission mechanism according to claim 22, wherein the power transmission mechanism is larger than a friction area of the other friction member. 24. The power transmission mechanism according to claim 6, wherein the second hysteresis mechanism is disposed inside the power transmission mechanism with respect to a friction surface of a clutch mechanism capable of connecting and disconnecting the power transmission. Power transmission mechanism. 25. A flywheel connected to the driven member, a clutch mechanism for contacting or substantially separating from the flywheel to disconnect and connect the transmission of power, and displacing the clutch mechanism in an axial direction. And a release bearing mechanism for causing the clutch mechanism to make and break the power. The friction member of the second hysteresis mechanism slides on the flywheel and the direction of the pressing force acting on the friction member. 7. The power transmission mechanism according to claim 6, wherein a direction in which the release bearing mechanism moves when the transmission of the power is cut off via the clutch mechanism is set to be the same. 26. When the clutch release bearing mechanism is of a push type that moves toward the engine when the transmission of the power is cut off, the fly that slides on the second hysteresis mechanism with the clutch mechanism. The power transmission mechanism according to claim 25, wherein the power transmission mechanism is disposed on a friction surface side of the wheel. 27. When the clutch release bearing mechanism is of a pull type that moves to the transmission side when the transmission of the power is cut off, the second hysteresis mechanism is provided on a surface of the flywheel facing the engine. 26. The power transmission mechanism according to claim 25, wherein the power transmission mechanism is disposed on a side. 28. The power transmission mechanism according to claim 6, wherein the friction member of the second hysteresis mechanism is divided into a plurality of friction members. 29. A thrust plate is disposed between a friction member of the second hysteresis mechanism and the driving member or the driven member, and is formed on the friction member of the second hysteresis mechanism on the thrust plate. 7. A projection is provided which engages with the formed hole and circumferentially engages the friction member.
The power transmission mechanism described in the above. 30. An inner ring is provided on a peripheral surface side of the plurality of friction members, and a peripheral surface of the inner ring is engaged or engageable with the plurality of friction members in a circumferential direction. 29. A friction member having a gap in a circumferential direction with respect to each other, and a hole communicating with a gap between the plurality of friction members is provided in a peripheral surface of the inner ring.
The power transmission mechanism described in the above. 31. A thrust spring is arranged to urge the friction member of the second hysteresis mechanism toward the sliding surface of the friction member, and the urging force of the thrust spring is applied to the driving member and the driven member. 7. The power transmission mechanism according to claim 6, wherein the bearing disposed therebetween acts in the same direction as the direction in which the bearing is prevented from coming off. 32. The power transmission mechanism according to claim 6, wherein the friction member of the second hysteresis mechanism is made of polyimide. 33. The torsion member includes torsion springs having different spring constants from each other. In the plurality of torsion springs arranged in series, the torsion springs having a relatively small spring constant are arranged at both ends, and the torsion springs are arranged inside. The power transmission mechanism according to claim 12, wherein the torsion spring having a relatively large spring constant is arranged. 34. The power transmission mechanism according to claim 33, wherein in the plurality of torsion springs arranged in series, the wire diameter of the torsion springs at both ends is small. 35. The torsion member is a coil spring, and a spring seat is disposed at an end of the coil spring. A radially central portion of the spring seat projects in the circumferential direction and fits in the coil spring bore. 13. The power transmission mechanism according to claim 12, wherein a boss portion that fits is formed. 36. The maximum compression amount of the coil spring is:
The power transmission mechanism according to claim 35, wherein the power transmission mechanism is defined by a circumferential length of the boss. 37. A plurality of torsion springs arranged in series with each other, wherein the torsion springs have the same length at maximum compression.
Or a power transmission mechanism according to claim 36. 38. The power transmission mechanism according to claim 35, wherein a stopper pin is provided between the bosses disposed at both ends of the torsion spring at an inner peripheral portion of the torsion spring. 39. The difference between the circumferential length of the stopper pin and the maximum compression length of the torsion spring, and the length of the bosses projecting from both ends of the torsion spring in the circumferential direction of the boss. The power transmission mechanism according to claim 38, wherein: 40. The torsion spring is a coil spring, and a receiving surface of the spring seat abutting on the end surface of the coil spring is rotated at an initial position so that the end surfaces of the coil spring are parallel to each other in a maximum flexing state. 36. The power transmission mechanism according to claim 35, wherein the power transmission mechanism is set to open outward with respect to the center. 41. The power transmission mechanism according to claim 12, wherein said torsion member is made of high elasticity rubber. 42. A power transmission mechanism according to claim 12, wherein an outer diameter of said spring seat is larger than an outer diameter of said torsion member. 43. A power transmission mechanism according to claim 42, wherein said spring seat is made of glass fiber reinforced nylon. 44. A slider having a high abrasion resistance and a low coefficient of friction is provided between the spring seat and an inner wall surface of the drive side member surrounding an outer peripheral side of the spring seat. Item 13. The power transmission mechanism according to Item 12. 45. A power transmission mechanism according to claim 44, wherein said spring seat is made of glass fiber reinforced nylon, and said slider is made of polyimide. 46. A power transmission mechanism according to claim 44, wherein said spring seat is made of polyimide. 47. The driven-side member includes, as a holding portion for holding the spring seat in a circumferential direction, a projection projecting in a circumferential direction to support a centrifugal force acting on the spring seat; The radius of the surface facing the outer peripheral surface of the spring seat and guiding the sliding of the spring seat is determined by the direction in which the driven member biases the spring seat disposed opposite the driven member and the circumferential end surface. The power transmission mechanism according to claim 12, wherein the power transmission mechanism gradually increases toward. 48. A surface facing the outer peripheral surface of the spring seat and guiding sliding of the spring seat,
13. The power transmission mechanism according to claim 12, wherein flaws in a direction perpendicular to the sliding direction of the spring seat are removed by turning. 49. An outer wall of a drive plate throttle-shaped portion, which is the drive side member, is relieved to form the spring seat circumferential receiving surface.
8. The power transmission mechanism according to 8. 50. A relief for preventing interference between a step formed by turning and the spring seat is provided on the receiving surface of the drawn portion of the drive plate. Item 49. The power transmission mechanism according to Item 48. 51. A power transmission mechanism according to claim 50, wherein an inner diameter of an inner wall surface of said drive side member surrounding an outer peripheral side of said spring seat is larger than an outer diameter of said torsion member. 52. A rolled steel plate is disposed radially between said spring seat and an inner wall surface of said driving member surrounding an outer peripheral side of said spring seat.
2. The power transmission mechanism according to 2. 53. A power transmission mechanism according to claim 52, wherein the rolling direction of said rolled steel sheet and the sliding direction of said spring seat are the same. 54. The power transmission mechanism according to claim 12, wherein a block member for pressing the torsion member in a circumferential direction is attached to the drive side member. 55. Grease is applied to the outer peripheral surface of the spring seat or the inner wall surface of the drive side member on which the spring seat slides facing the outer peripheral surface of the spring seat. The power transmission mechanism described in the above. 56. The driving member according to claim 1, wherein said first member contacts said first member.
A drive plate and a second drive plate,
The torsion member is disposed in a space surrounded by the first and second drive plates, and a contact surface between the first and second drive plates is provided with a gap communicating the space in which the torsion member is disposed with the outside. The power transmission mechanism according to claim 12, wherein the power transmission mechanism is provided. 57. A power transmission mechanism according to claim 56, wherein said gap comprises a recess formed in said first drive plate or said second drive plate. 58. The power transmission mechanism according to claim 13, wherein said inner ring to which said bearing is fixed is a plate-like material having elasticity. 59. The power transmission mechanism according to claim 13, wherein said inner ring has a flange portion for supporting said second hysteresis mechanism and said bearing in the axial direction. 60. A thrust plate abutting on the friction member and having one end extending toward the flange portion is disposed between the friction member of the second hysteresis mechanism and the flange portion in the axial direction. The power transmission mechanism according to claim 59, wherein a notch or a hole for preventing the thrust plate from rotating is formed in the portion, the notch or the hole being engageable with the flange portion of the thrust plate. 61. A surface of the drive-side member facing an end surface of the bearing on the engine side is in contact with one of an end surface of an inner race and an end surface of an outer race of the bearing, and is contacted with the other end surface. The power transmission mechanism according to claim 13, wherein the power transmission mechanism does not abut. 62. The power transmission mechanism according to claim 13, wherein the crankshaft of the engine and the divided drive side member are screwed to each other with bolts. 63. A power transmission mechanism according to claim 14, wherein an inertia body is formed on an outer peripheral portion of said drive side member. 64. A power transmission mechanism according to claim 63, wherein said inertial body is formed by roll forming a steel strip or a drawn material. 65. A power transmission mechanism according to claim 64, wherein said inertial body is fixed to said drive side member by welding. 66. A power transmission mechanism according to claim 63, wherein an outer peripheral portion of said drive side member is drawn in an axial direction to form an inertia body. 67. A power transmission mechanism according to claim 66, wherein a ring-shaped inertia member formed by roll-forming a strip or a drawn material is disposed inside a throttle formed on an outer peripheral portion of said drive side member. . 68. A power transmission mechanism according to claim 67, wherein said ring-shaped inertia body is caulked at a throttle portion formed on an outer peripheral portion of said drive side member. 69. The drive-side member, comprising a first drive plate and a second drive plate, wherein the second drive plate is swaged at a tongue of the first drive plate. Item 64. The power transmission mechanism according to Item 14 or 63. 70. A power transmission mechanism according to claim 14, wherein an inertia body is provided on an outer peripheral portion of said flywheel. 71. A power transmission mechanism according to claim 14, wherein a tooth surface of a ring gear for activation provided on an outer peripheral side of said drive side member is chamfered by a tooth length. 72. A power transmission mechanism according to claim 14, wherein a spacer is disposed between an axial end surface of a crankshaft for transmitting said power from an engine and said driving member. 73. The drive-side member includes a first drive plate and a second drive plate, and absorbs a rotational torque variation in series between the drive-side member and the driven-side member in the device rotation direction. The power transmission mechanism according to claim 14, wherein a resin torsion member is disposed, and the first drive plate and the second drive plate are welded at a position apart from the resin torsion member. 74. The driving-side member and the driven-side member,
A clearance is provided between the inner ring fixed to the crankshaft of the engine and the friction member of the second hysteresis mechanism so as to be substantially concentric and relatively rotatable via a bearing. A power transmission mechanism according to claim 28. 75. The drive as opposed to a side surface of the sliding bearing and a side surface of the sliding bearing as a lubricating oil passage so that the lubricant is supplied to the sliding surface located radially outward by centrifugal force. The power transmission mechanism according to claim 2, wherein a clearance is provided between a side surface of the side member and / or a side surface of the driven side member, or a groove is provided in the driving side member and / or the driven side member. 76. The power transmission mechanism according to claim 1, wherein a groove extending in an axial direction is provided on the sliding surface. 77. A plurality of grooves extending in the axial direction provided on the sliding surface are provided at an interval equal to or less than a relative twist angle between the driving side member and the driven side member.
6. The power transmission mechanism according to 6. 78. The surface of the rolled steel sheet on the spring seat side is mirror-finished.
The power transmission mechanism described in the above.