JPH062052Y2 - Torque fluctuation absorber - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial application] The present invention relates to an engine torque fluctuation absorbing apparatus, and more particularly to a torque fluctuation absorbing apparatus whose reliability is improved.

[Conventional technology]

In a power transmission device for an engine of a car, a ship, etc., if a torsional vibration or torque fluctuation generated on the input side from the engine is transmitted as it is or is amplified and transmitted to the output side, the output side device may be damaged. Is installed.

Conventionally, as a torque fluctuation absorbing device, for example, the actual Kaisho 61-2
There is one disclosed in Japanese Patent No. 3547.

That is, as shown in FIGS. 4 and 5, the drive plate 2 is connected to the engine crankshaft 1 as a drive shaft by bolts so as to rotate integrally with the shaft 1. In this drive plate 2, ring-shaped drive plate main bodies 2a and 2b are sandwiched by steel plate side plates 2c and 2d from both sides, and these are integrally connected by rivets 3 and screws 4.

Of the side plates 2c and 2d forming part of the drive plate 2, the side plate 2d on the flywheel 6 side is bent so that its outer peripheral portion is bent to have a substantially L-shaped cross section so as to cover the outer periphery of the flywheel 6. A portion 2d 'is formed, and the bent portion 2d' covers the outer peripheral opening of the gap 11 formed so as to extend in the radial direction between the drive plate 2 and the flywheel 6. A ring gear 5 for a starter is attached to the outer periphery of the drive plate body 2a by press fitting, shrink fitting, or the like.

The flywheel 6 faces the drive plate 2 and at a position coaxial with the drive plate 2, the flywheel 6 is rotatable relative to the drive plate 2.
It is supported by the drive plate 2 via.

Reference numeral 8 is a pin for aligning a clutch (not shown), and 9 is a screw hole for attaching a clutch cover (not shown).

The flywheel 6 includes a flywheel body 6a and a dribble plate 6b so as to form an annular recess 6c (see FIG. 6) for accommodating a damping / torque limit mechanism 15 described later.
It is divided into two parts and the flywheel body 6a
The driven plate 6b and the driven plate 6b are integrally connected to each other by a bolt 10.

A spring mechanism 12 is provided between the drive plate 2 and the flywheel 6. This spring mechanism 1
2 is a coil spring 13 and the same coil spring 1
Spring seats 14 and 14 provided at both ends of the spring 3, spring seats 14 and 14, and elastic bodies 14a and 14a fixed to the inner ends of the spring seats 14 and 14 and having a spring constant larger than that of the spring 13. Composed of. These spring seats 14 and 14 have the same shape as each other,
The elastic bodies 14a, 14 are provided at both ends of the coil spring 13.
The a can come into surface contact with each other.

Of these, one spring seat 14 abuts on one side of the radial protrusion of the ring-shaped main body 2a of the drive plate 2, and the other spring seat 14 is a damping and
The torque limit mechanism 15 has a structure capable of abutting the radially outwardly extending portions 16b of the driven disks 16 of the torque limit mechanism 15. A gap exists between these spring seats 14 and the members with which the spring seats 14 can abut when torque is not applied to the crankshaft 1.

As shown in FIG. 6, the damping / torque limit mechanism 15 includes an inner wall surface 6d of the flywheel body 6a and an inner wall surface of the driven plate 6b that form an annular recess 6c of the flywheel 6.
It is held between 6e and a pair of driven discs 1
6 and the driven discs 16 interposed between both driven discs 16 and 16 and the inner wall surface 6d of the flywheel body 6a.
Alternatively, it is composed of a cone spring 17 as an elastic member for urging the inner wall surface 6e of the driven plate 6b, and a lining 16a made of a friction material provided on the surface of each driven disk 16 on the side in contact with the inner wall surface 6d or 6e. ing.

The lining 16a is adapted to dampen vibrations of torque fluctuations due to sliding friction loss with the flywheel body 6a or the driven plate 6b. Although the cone spring 17 determines the pressing force of the driven disc 16 against the flywheel body 6a and the driven plate 6b, the cone spring 17 has a spring constant such that the pressing force has an appropriate magnitude.

The hysteresis mechanism 18 is interposed between the drive plate 2 and the flywheel 6, and as shown in FIG. 7, a plate 19 that can rotate integrally with the drive plate 2.
And a friction material 19a attached to the plate 19 and engaged with the flywheel 6, and a friction material 19a interposed between the drive plate 2 and the plate 19
And a disc spring 20 that urges the disc spring.

The space in which the hysteresis mechanism 18 is housed is rigidly formed by the side plate 2C of the drive plate 2 and the flywheel 6.

A bent portion is formed in a part of the plate 19, and the plate 19 is circumferentially attached to the drive plate 2 by engaging the bent portion with a hole 22 formed in the side plate 2c of the drive plate 2. Fixed. The friction material 19a is made of a material whose main component is polyimide resin.

With the above-described configuration, the rotational torque of the crankshaft 1 of the engine is transmitted to the drive plate 2 that rotates integrally with the crankshaft 1, and is transmitted to the flywheel 6 via the spring mechanism 12, the damping / torque limit mechanism 15 and the hysteresis mechanism 18. Transmitted.

At this time, minute fluctuations in the rotational torque of the crankshaft 1 and engine vibrations are absorbed by the spring system of the spring mechanism 12, the damping / torque limit mechanism 15, and the damping system of the hysteresis mechanism 18.

FIG. 8 is a characteristic diagram of torque transmission through these spring and damping systems. Characteristic A ′ shows play due to a gap existing between the spring seat 14 and a member with which the spring seat 14 can abut. Is shown.

The characteristic B'is generated when the spring seat 14 comes into contact with a member (for example, the radially outwardly extending portion 16b of the driven disc 16) which the spring seat 14 can come into contact with and the spring 13 bends (compressive deformation). Is compressed by the spring 13 so that the spring seats 14, 1
The four elastic bodies 14a, 14a are brought into contact with each other and the spring seats 14, 14 are elastically deformed.

Further, the characteristic D'is that when the torsional torque from the crankshaft 1 reaches the limit torque, the flywheel 6 and the driven disc 16 of the damping / torque limit mechanism 15 are controlled.
It is caused by the slip that occurs between and.

The characteristics A ′, B ′, C ′ form a hysteresis loop by the action of the hysteresis mechanism 18.

Therefore, when the torque from the crankshaft 1 is low, first, the play between the spring seat 14 and the driven disc 16 and the low friction force of the hysteresis mechanism 18 effectively act to obtain the characteristic A ′. When a torque larger than that is applied, the spring seat 14 and the extended portion 16b of the driven disc 16 come into contact with each other, and the spring 13
Bends to obtain the characteristic B ', and further, the torque increases and the deflection of the spring 13 increases, so that the spring seat 14,
When the elastic bodies 14a, 14a of the spring seat 14 come into contact with each other and more torque is applied, the elastic body 14 of the spring seat 14
a itself bends to obtain the characteristic C '. Then, when the torque further increases and becomes more than necessary, the damping / trick limit mechanism 15 is in a dynamic friction state in which the lining 16a on the driven disk 16 side and the flywheel 6 continue to generate a slippage, resulting in a dynamic friction state. The characteristic D'that the torque of is cut is obtained.

At this time, the friction material 19a of the hysteresis mechanism 18 also continues to slide with the flywheel 6 and contributes to the formation of the characteristic D '.

In this way, the rotational torque is effectively absorbed by the torque fluctuation and transmitted to the transmission side.

[Problems to be solved by the invention]

By the way, in the above-described conventional torque fluctuation absorbing apparatus, when the friction material 19a and the flywheel 6 slip and the torque fluctuation is absorbed for a long period of time, the friction material 19a wears and the disc spring 20 rubs. The force of pressing the material 19a changes, and the function of the hysteresis mechanism 18 deteriorates.
The space in which the hysteresis mechanism 18 is housed is fixed to a certain size, and the force pressing the friction material 19a cannot be adjusted, so that the functional deterioration of the hysteresis mechanism 18 cannot be compensated. Furthermore, there is a problem that it is impossible to adjust the friction characteristic value of the hysteresis mechanism 18 to a desired value.

The present invention is intended to solve the above-mentioned problems, and an object of the present invention is to provide a torque fluctuation absorbing device that compensates for the deterioration of the function of the hysteresis mechanism and can adjust the friction characteristic value to a desired value. To do.

[Means for solving problems]

Therefore, in the torque fluctuation absorbing device of the present invention, the inertial body is composed of the drive plate connected to the drive shaft and the flywheel coaxially with the drive plate and rotatable relative to the drive plate. In the torque fluctuation absorbing device in which the hysteresis mechanism is interposed between the drive plate and the flywheel, the torque fluctuation absorbing device is fixed to the flywheel side and supports the drive plate and the flywheel so as to be rotatable relative to each other. A bearing for supporting the relative position of the bearing, a stopper plate for positioning and fixing the bearing, and a bolt provided on the drive plate for fixing and supporting the stopper plate, and a tapered portion is formed on the drive plate side of the bearing. Together with the taper part on the drive plate side Aligned taper portion A taper portion that is aligned is formed on the drive plate side, and the bearing is slightly moved between the two taper portions due to the pressing force of the stopper plate, and the friction characteristic of the hysteresis mechanism is set to a desired value. It is characterized by being configured to be adjustable.

[Action]

In the above-described torque fluctuation absorbing device of the present invention, the stopper plate supporting the bearing is adjusted by adjusting the bolt tightening force or by adjusting the stopper plate bending force and tightening the bolt by tightening the bolt. A slight deviation is caused between the drive plate and the taper portion, and the gap between the drive plate and the flywheel is adjusted to adjust the friction characteristic of the hysteresis mechanism to a desired value.

〔Example〕

A torque fluctuation absorbing apparatus as an embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view of an essential part thereof, FIG. 2 (a) is its sectional view, and FIG. 2 (b) is its sectional view. A partially broken plan view and FIG. 3 are graphs showing the torque transmission characteristics.

As shown in FIGS. 1 and 2 (a) and (b), the engine crankshaft 1 serving as a drive shaft has bolts 2a and 2a so that the drive plate 2 rotates integrally with the same.
Are connected by.

The drive plate 2 is provided with a flywheel 6 coaxially and relatively rotatable with respect to the drive plate 2, and an inertial body (hereinafter referred to as “two-division flywheel”) is formed by the flywheel 6 and the drive plate 2. .) Is configured. A ring gear 5 for a starter is attached to the outer periphery of the drive plate 2 by press fitting, shrink fitting, or the like.

The relative rotation between the drive plate 2 and the flywheel 6 is realized by a bearing 7, which is fixed to the inner peripheral edge of the flywheel 6,
It is fitted to the drive plate 2. A taper portion 7b is formed at an end portion 7a of the bearing 7 on the flywheel 6 side. The drive plate 2 is formed with a taper portion 2b aligned with the taper portion 7b at a position corresponding to the taper portion 7b of the bearing 7 when the bearing 7 is fitted. Further, the outside of the bearing 7 is pressed by a stopper plate 50 attached to the bolt 2a in a washer shape. The plate 50 also presses the pilot bearing 51 in the same manner as the bearing 7. The pilot bearing 51
Is to rotatably support a clutch shaft (not shown) extending from the Trins mission side (not shown).

A spring mechanism 12 similar to the conventional example is provided between the drive plate 2 and the flywheel 6. The spring mechanism 12 includes a coil spring 13 and spring seats 14, 14 provided at both ends of the coil spring 13.
And elastic bodies 14a and 14a fixed to the inner ends of the spring seats 14 and 14 and capable of deforming with a spring constant larger than that of the spring 13. The spring seats 14, 14 have the same shape as each other and are provided at both ends of the coil spring 13 so that the elastic bodies 14a, 14a can come into surface contact with each other.

Of these, one of the spring seats 14, 14 abuts on the sub-plates 41, 42 on the drive plate 2 side, and the other spring seat 14 extends outward in the radial direction of each driven disk 16 of the damping / torque limit mechanism 15 described later. The structure is such that it can come into contact with the portion 16b. A gap exists between these spring seats 14 and 14 when the crankshaft 1 is not torqued, and between the spring seats 14 and the members with which the spring seats 14 can abut.

The damping / torque limit mechanism 15 is provided in the annular recess 6C formed between the drive plate 2 and the flywheel 6.
Is provided. This damping / trick limit mechanism 15
Is a pair of driven discs 16 and 16 and a cone spring 17 as an elastic member which is interposed between the driven discs 16 and 16 and biases the driven discs 16 and 16 to the wall surface of the flywheel 6 and the wall surface of the drive plate 2. And the linings 16a, 16a made of friction material provided on the side surface of the flywheel 6 and the side surface of the drive plate 2 of each driven disk 16,16.

Further, a hysteresis mechanism 18 similar to the conventional example is interposed between the drive plate 2 and the flywheel 6.

The hysteresis mechanism 18 includes a plate 19 that can rotate integrally with the drive plate 2, a friction member 19a that is attached to the plate 19 and that engages with the flywheel 6, and a seat 19b and a plate 19 that are provided on the drive plate 2 side. And a disc spring 20 which urges the friction material 19a toward the flywheel 6 between the two.

Although not shown, a bent portion is formed in a part of the plate 19, and the plate 19 is fixed to the drive plate 2 in the circumferential direction by engaging the bent portion with a hole formed in the drive plate 2. To be done. Also, the friction material 1
9a is made of a material whose main component is polyimide resin.

Since the torque fluctuation absorbing apparatus as one embodiment of the present invention is configured as described above, the engine crankshaft 1
Is transmitted to the drive plate 2 that rotates integrally with the crankshaft 1, and is transmitted to the flywheel 6 via the damping / torque limit mechanism 15 and the hysteresis mechanism 18.

When the friction material 19a and the flywheel 6 slip and the torque fluctuation is absorbed and the friction material 19a wears, the hysteresis mechanism 18 deteriorates in function. The position of the bearing 7 is adjusted by changing the pressing force of.

Specifically, the tightening force of the bolt 2a is adjusted to increase the pressing force on the bearing 7, and the taper portions 7b and 2b of the bearing 7 and the drive plate 2 are slightly displaced so that the drive plate 2 Close the gap with the flywheel 6. Then, the gap between the sheet 19b and the plate 19 is reduced, and the repulsive force of the disc spring 20 is increased. Thereby, the function of the hysteresis mechanism 18 can be restored.

As described above, the performance deterioration of the hysteresis mechanism 18 can be compensated. Further, the friction characteristic value H (see FIG. 3) of the hysteresis mechanism 18 can be adjusted to a desired value.

Further, since the stopper plate 50 presses the bearing 7 as well as the pilot bearing 51, it also has a function of preventing the pilot bearing 51 from coming off.

The adjustment of the pressing force on the bearing 7 is hard (thickness).
The stopper plate 50 is used to adjust with the tightening force of the bolt 2a, or the bending force of the stopper plate 50 (thickness of the stopper plate 50) is adjusted, and the bolt 2a is tightly tightened.

[Effect of device]

As described in detail above, according to the torque fluctuation absorbing apparatus of the present invention, the bearing fixed to the flywheel side and supporting the drive plate and the flywheel so as to be rotatable relative to each other, and the relative positions thereof are provided. , A stopper plate for positioning and fixing the bearing, and a bolt provided on the drive plate for fixing and supporting the stopper plate, wherein a taper portion is formed on the drive plate side of the bearing and the taper portion is formed on the drive plate side. Is formed so that the bearing is slightly moved between the two tapered portions by the pressing force of the stopper plate to adjust the friction characteristic of the hysteresis mechanism to a desired value. With a simple structure that reduces the function of the hysteresis mechanism. Ukoto can. Further, there is an advantage that the friction characteristic value of the hysteresis mechanism can be adjusted to a desired value.

[Brief description of drawings]

1 to 3 show a torque fluctuation absorbing device as an embodiment of the present invention. FIG. 1 is a sectional view of a main part thereof, FIG. 2 (a) is its sectional view, and FIG. 2 (b). Is a partially cutaway plan view, and FIG. 3 is a graph showing the torque transmission characteristics,
4 to 8 show a conventional torque fluctuation absorbing device,
FIG. 4 is a vertical sectional view (sectional view taken along the line IV-IV in FIG. 5),
FIG. 5 is a view taken along the line V-V in FIG. 4, FIG. 6 is an enlarged view of a VI portion in FIG. 4, FIG. 7 is an enlarged view of a VII portion in FIG. 4, and FIG. It is a graph shown. DESCRIPTION OF SYMBOLS 1 ... Engine crankshaft as drive shaft, 2 ... Drive plate, 2a ... Bolt, 2b ... Tapered part of drive plate 2, 5 ... Starter ring gear, 6 ... Flywheel, 6c ... Annular recess of flywheel 6, 7 ... bearing, 7a ... end of flywheel 6 side of bearing 7, 7b ... tapered portion of bearing 7, 12 ... spring mechanism,
13 ... Coil spring, 14 ... Spring seat, 1
4a: Elastic body, 15: Damping / torque limit mechanism, 16
Driven disc, 16a Line, 17 Cone spring, 18 Hysteresis mechanism, 19 Plate, 19a Friction material, 20 Disc spring, 40 Retaining plate, 41, 42 Sub plate, 50 Stopper plate 51 Pilot bearing.

Claims (1)

[Scope of utility model registration request] 1. A drive plate connected to a drive shaft,
An inertial body is composed of the drive plate and a flywheel that is coaxially rotatable relative to the drive plate, and a hysteresis mechanism is interposed between the drive plate and the flywheel. In the absorbing device, a bearing that is fixed to the flywheel side and that supports the drive plate and the flywheel such that they can rotate relative to each other and a relative position between these, a stopper plate that positions and fixes the bearing, and the drive plate And a taper portion for fixing and supporting the stopper plate, and a taper portion is formed on the drive plate side of the bearing and a taper portion that is aligned with the taper portion is formed on the drive plate side. Depending on the pressing force, the above bearing There characterized in that it is configured to be adjusted to a desired value the frictional characteristics of the hysteresis mechanism is slightly moved between the two tapered portions, the torque fluctuation absorbing apparatus.