JPH0542265Y2 - - Google Patents

Description

[Detailed Description of the Invention] Technical Field The present invention relates to a friction clutch, and in particular a type that interrupts the transmission of rotational torque by moving a release member in a backward direction away from a clutch disk against the biasing force of a diaphragm spring. This invention relates to improvements to friction clutches.

BACKGROUND OF THE INVENTION Friction clutches, which transmit rotational torque by means of frictional force, have been widely used in power transmission devices for automobiles and the like as clutch devices for transmitting and interrupting rotational torque. One type of such a friction clutch includes: (a) a pressure plate disposed between the flywheel and the clutch cover so as to be non-rotatable but movable in the axial direction; and (b) the clutch cover and the release member. a diaphragm spring provided between the clutch housing and having an intermediate portion abutted against the pressure plate to bias the pressure plate in a forward direction approaching the flywheel; , the clutch disk is normally compressed between the pressure plate and the flywheel to transmit rotational torque, but as the release member is moved backward against the biasing force of the diaphragm spring, the clutch disk is compressed between the pressure plate and the flywheel. Retract the shear plate to cut off rotational torque transmission. There is a so-called pull type.

Problems that the invention aims to solve By the way, in such pull-type friction clutches, the release member as well as the pressure plate are always urged in the forward direction by the diaphragm spring, so the clutch lining may wear more than the allowable amount. If the clutch wears out or is damaged for some reason, the release member is also moved forward as the pressure plate moves forward, which could interfere with the clutch disk and damage the release bearing, torsion member, etc.

In contrast, a friction clutch in which a pressure plate is provided with a stopper that contacts the clutch cover to restrict excessive movement of the pressure plate is described, for example, in Japanese Utility Model Publication No. 51-27396. . However, such a stopper is intended to prevent the strap interposed between the pressure plate and the clutch cover from being plastically deformed by the diaphragm spring when the clutch is disassembled. The permissible movement amount of the pressure plate whose movement is regulated by is relatively large. That is,
Even if such a stopper is provided, it is normal that it does not have the effect of regulating the forward end position of the pressure plate in the event of damage to the clutch lining, etc. Otherwise, the release member and clutch disk will interfere with each other. In this way, the pressure plate may move forward to a position where it comes into contact with the flywheel across the disk plate, or the release member and clutch disk may interfere with each other. Even if the pressure plate moves forward to a position where it moves forward, there is no risk that the strap will be plastically deformed due to the forward movement to that extent.

On the other hand, even if the clutch lining is damaged, the pressure plate remains at the position where it contacts the flywheel across the disc plate, or at the position defined by the strap provided to prevent plastic deformation of the strap. Since further advancement is prevented, the release member must be placed in a position sufficiently far away from the clutch disk in advance so that it will not interfere with the clutch disk even if the release member is advanced as the pressure plate advances. Although interference between the release member and the clutch disk can be prevented by arranging the friction clutch in the axial direction, the axial dimension of the friction clutch becomes significantly large. In particular, the forward end position of the pressure plate when the release member and clutch disk interfere, that is, the distance between the clutch cover and the pressure plate, is determined by the types of clutch components, dimensional tolerances, assembly errors, etc. Therefore, in order to reliably prevent interference between the release member and the clutch disk, it is necessary to arrange the release member at a distance from the clutch disk more than necessary.

Means for Solving the Problems The present invention has been made to solve the above problems, and its gist is to provide a clutch housing with a pressure plate (a) and a diaphragm spring (b). Normally, the clutch disk is compressed between the pressure plate and the flywheel to transmit rotational torque, but when the release member is retreated against the biasing force of the diaphragm spring, In a friction clutch of the type that cuts off the transmission of rotational torque by retracting a pressure plate, the pressure plate (c) is erected and inserted through an insertion hole formed in the clutch cover. The stopper pin is provided with a flange having a larger diameter than the insertion hole, and the cross section forms a substantially U-shape and the plate thickness varies depending on the distance between the release member and the clutch disk when the d-clutch is assembled. One type is selected from a plurality of types, and is integrally fitted into the portion of the clutch cover in which the insertion hole is formed, and brought into contact with the flange of the stopper pin, whereby the release member and the clutch disk are connected. and a spacer for adjusting the forward end position of the pressure plate so as not to interfere with the clutch cover, and e the clutch housing is provided with a hole at approximately the same axial position as the clutch cover. be.

Function and Effects of the Invention According to such a friction clutch, even if the release member is moved forward as the pressure plate is moved forward due to wear or breakage of the clutch lining, the clutch cover is not fitted into the clutch cover. Due to the contact between the spacer and the flange of the stopper pin, the pressure plate is prevented from moving forward before the release member interferes with the clutch disk, so the release member is also prevented from moving further and may interfere with the clutch disk. This eliminates the risk of damaging the release bearing, torsion member, etc.

Moreover, the spacer that defines the forward end position of the pressure plate is selected from among multiple types with different thicknesses depending on the distance between the clutch disk and the release member when the clutch is assembled. Therefore, even if the clutch component parts such as the clutch disk and pressure plate are changed, the forward end position can be easily adjusted according to those parts. Even if the forward end position fluctuates due to dimensional tolerances of the clutch components, it can be adjusted to the correct position when the clutch is assembled.

In addition, with this invention, the forward end position of the pressure plate can be adjusted simply by selecting one from among multiple types of spacers with different plate thicknesses and fitting it into the clutch cover. Compared to the case where the forward end position is adjusted by the amount of insertion, there is an advantage that the adjustment work can be performed easily and quickly. That is, the spacer is fitted to the clutch cover by inserting a tool through a hole provided in the clutch housing, but when adjusting using a screw member, the tool must be rotated within a limited range. As a result, adjustment work was troublesome and there was a risk of interference and damage to other members.

In addition, by defining the forward end position of the pressure plate by the contact between the stopper pin and the spacer, interference between the release member and the clutch disk is prevented, so that the pressure plate can move toward the disk. Even if the strap is moved forward until it comes into contact with the flywheel across the plate, or until it is stopped by a stopper for preventing plastic deformation of the strap, the release member and clutch disk are prevented from interfering with each other. Furthermore, the axial dimensions of the friction clutch can be kept smaller than if the release member were previously arranged at a sufficient distance from the clutch disk.

Embodiment Hereinafter, an embodiment of the present invention will be described in detail based on the drawings.

Figure 1 is a diagram showing a friction clutch used in an automobile power transmission device, and shows a clutch housing 1.
0, a crankshaft 12 and an output shaft 14 of the engine are arranged so as to be relatively rotatable on the same straight line. A disk-shaped flywheel 16 is integrally fixed to the end of the crankshaft 12, and a clutch cover 18 is fixed to the flywheel 16 to prevent the pressure plate 20 from relative rotation. It is held movable in the axial direction. The pressure plate 20 is elastically attached to the clutch cover 18 via a plurality of straps (not shown) provided at equal angular intervals in the circumferential direction.

A clutch disk 22 is disposed on the output shaft 14 so as to be non-rotatable but movable in the axial direction. The clutch disk 22 includes a hub 24 spline-fitted to the output shaft 14, and a disk plate 26 inserted between the flywheel 16 and the pressure plate 20.
Clutch linings 28, 28 are fixed to portions of the disk plate 26 facing the flywheel 16 and pressure plate 20, respectively. This disk plate 26 is attached to the hub 24 via a plurality of torsion rubbers 30 arranged at equal angular intervals in the circumferential direction, and the friction between the clutch lining 28, the flywheel 16, and the pressure plate 20 is reduced. The rotational torque transmitted from the crankshaft 12 to the disk plate 26 by force is transmitted to the hub 24 and further to the output shaft 14 via the torsion rubber 30.

In addition, the clutch disk 22 of the output shaft 14
A cylindrical release hub 32 is provided on the rear side, that is, on the opposite side from the flywheel 16. The release hub 32 is fitted into a cylindrical member 34 arranged in a fixed position so as to be movable in the axial direction, and a release bearing 36 is attached to the front end thereof. Between the release bearing 36 and the clutch cover 18, an outer peripheral edge is engaged with the clutch cover 18 via a pivot ring 38, and an inner peripheral edge is engaged with the outer peripheral part of the release bearing 36. A diaphragm spring 40 is provided.

The diaphragm spring 40 is composed of a disc spring whose inner circumferential side protrudes leftward in FIG. The pressure plate 2
0 in the forward direction approaching the flywheel 16. Thereby, such friction clutches are held in a connected state in which the clutch disk 22 is compressed between the flywheel 16 and the pressure plate 20 to transmit rotational torque. FIG. 1 shows this state.

On the other hand, a flange 44 is provided at the rear end of the release hub 32, and is engaged with a release fork 46. The release fork 46 is rotatably provided around a pin 48 and has an output rod 52 of a release cylinder 50 at the other end.
The tips of the two can be brought into contact with each other. Then, when the clutch pedal (not shown) is depressed and the output rod 52 of the release cylinder 50 is pushed out, the release fork 46 is moved from the pin 48.
The release hub 32 is moved back against the biasing force of the diaphragm spring 40. Along with this, the pressure plate 20 is retracted by the elastic restoring force of the strap, and the clamping state of the clutch disk 22 is released, so that the friction clutch is activated to cut off the transmission of rotational torque. can be switched to the state. That is, this friction clutch is of a pull type that cuts off the transmission of rotational torque by retracting (pulling) the release hub 32.
In this embodiment, the release hub 32 and release bearing 36 constitute a release member.

Here, the outer peripheral surface of the pressure plate 20 is provided with a plurality of protrusions 54 protruding toward the outer circumferential side at equal angular intervals in the circumferential direction, and each of the protrusions 54 has a stopper pin 68 toward the rear. has been erected. As is clear from FIGS. 2 and 3, these stopper pins 68 are inserted through the insertion holes 58 formed in the clutch cover 18, and have larger ends than the insertion holes 58. A radial flange 66 is provided. Also,
A spacer 72 having a U-shaped cross section and having a notch 70 through which the stopper pin 68 can be inserted is removably fitted integrally into the portion of the clutch cover 18 where the insertion hole 58 is formed.
The forward end position of the pressure plate 20 is defined by the flange 66 of the stopper pin 68 coming into contact with the spacer 72. A plurality of types of spacers 72 having different thicknesses are prepared, and by appropriately replacing them, the forward end position of the pressure plate 20 can be changed.

The spacer 72 that defines the forward end position of the pressure plate 20 prevents the release member, which is moved forward as the pressure plate 20 advances, from being clutched even if the pressure plate 20 advances to the forward end position. In order not to interfere with the disc 22, the parts closest to each other among the components of the release member and the clutch disc 22, in this embodiment, the release bearing 36 and the torsion rubber 30, are
According to the dimension X (see FIG. 4) between the two, one is selected and used from a plurality of types having different plate thicknesses. Specifically, for example, as shown in FIG. Flange 66 and spacer 72 in a state where clutch disk 22 is pressed between plate 20 and flywheel 16
In other words, the dimension between the position of the pressure plate 20 in that state and the forward end position where the flange 66 abuts the spacer 72 is δ, and the distance between the pivot ring 38 of the diaphragm spring 40 and the When the dimension from the point P where the engagement protrusion 42 of the pressure plate 20 comes into contact with the point Q where it abuts is a, and the dimension from the point P to the point R where it engages with the release bearing 36 is b, the above dimension δ
One of the plurality of types of spacers 72 is selected and fitted to the clutch cover 18 so that the following equation δ<X·a/b (1) is satisfied. Note that the above-mentioned dimension X is determined from the axial position of the release hub 32, for example.

The clutch housing 10 has a tool insertion hole 100 at approximately the same axial position as the clutch cover 18.
A tool is inserted into the spacer 72 through the tool insertion hole 100, and the spacer 72 is fitted into the clutch cover 18. The tool insertion hole 100 is
After the spacer 72 is attached, it is closed with a lid 102 made of resin.

In the friction clutch of this embodiment, when the pressure plate 20 is moved forward by a distance δ from the state at the time of assembly due to wear or damage of the clutch lining 28, the pressure plate 20 is moved forward by a distance δ. The forward movement of the flange 66
The release bearing 36 is prevented from coming into contact with the spacer 72, and during this time the release bearing 36 is advanced by δ·b/a. However, since the dimension X between the release bearing 36 and the torsion rubber 30 at the time of assembly is larger than δ・b/a from the above equation (1), the release bearing 36
6 becomes δ・as the pressure plate 20 moves forward.
Even if it is moved forward by b/a, the release bearing 36 and torsion rubber 30 will not interfere and be damaged.

Note that if the above-mentioned dimension δ is too small, the pressure plate 20 will be prevented from advancing before the clutch lining 28 reaches its allowable wear life, and the clutch lining 28 will not be able to be used effectively. When y is the wear dimension until 28 reaches the allowable wear life, the dimension δ is set to a value larger than 2y.

Further, the spacer 72 that defines the forward end position of the pressure plate 20 is selected from among a plurality of types having different thicknesses depending on the dimension X when the clutch is assembled, and is fitted into the clutch cover 18. Therefore, even if the clutch component parts such as the clutch disk 22 are changed, the forward end position can be easily adjusted according to those parts, and the forward end position can be easily adjusted according to the dimensional tolerances of the clutch structural parts. Therefore, even if the forward end position fluctuates, it can be adjusted to the correct position when the clutch is assembled.

In addition, the forward end position of the pressure plate 20 can be adjusted by simply selecting one from a plurality of types of spacers 72 with different plate thicknesses and fitting it onto the clutch cover 18. Compared to the case where the forward end position is adjusted by the amount, there is an advantage that the adjustment work can be performed easily and quickly. That is, the spacer 72 is fitted to the clutch cover 18 by inserting a tool through the tool insertion hole 100 provided in the clutch housing 10, but when adjusting using a screw member, the tool is limited. Since the rotation operation had to be performed within a range, the adjustment work was troublesome and there was a risk of interference with other components and damage.

Furthermore, due to the contact between the flange 66 of the stopper pin 68 and the spacer 72, the pressure plate 2
Since the forward end position of 0 is defined and interference between the release bearing 36 and the torsion rubber 30 is prevented, the pressure plate 20 holds the flywheel 1 with the disc plate 26 in between.
The release bearing 36 and torsion rubber 30 are prevented from interfering even when the strap is moved forward until it comes into contact with the strap 6 or until it is stopped by a stopper provided to prevent plastic deformation of the strap. Furthermore, the axial dimensions of the friction clutch can be kept smaller than if the release member were previously disposed at a sufficient distance from the clutch disk 22.

Further, by defining the forward end position of the pressure plate 20 as described above, the pressure plate 20 is elastically moved toward the clutch cover 18.
Since plastic deformation of the strap attached to the clutch is also prevented, the movement of the pressure plate 20 when the friction clutch is disengaged is not hindered. Note that even before the spacer 72 is attached, the amount of separation of the pressure plate 20 from the clutch cover 18 is regulated by the contact between the flange 66 of the stopper pin 68 and the clutch cover 18. This prevents plastic deformation of the strap even before it is assembled to the clutch cover 18.
Improves assembly workability.

On the other hand, as shown in FIG. If the clutch lining 28 on the plate 20 side is damaged for some reason and the pressure plate 20 is advanced by the thickness c of the clutch lining 28, the release bearing 36 will be damaged accordingly.
It is moved forward by b/a. If the amount of forward movement c·b/a is larger than the dimension X, there is a risk that the release bearing 36 and the torsion rubber 30 will interfere with each other, causing damage to them. FIG. 5 shows this state.

Also, if both clutch linings 28, 28 are damaged and the pressure plate 20 is advanced by the sum 2c of the plate thickness of both clutch linings 28, 28, the release bearing 36 will be damaged accordingly. At the same time, the clutch disk 22 is also advanced by a distance c until it abuts the flywheel 16. Therefore, the amount of forward movement of the release bearing 36 is 2c.
b/a is the dimension (X
+c), release bearing 36 and torsion rubber 30 as described above.
There was a risk of interference and damage to them. However, the stopper 64 is designed to allow the pressure plate 20 to move forward by 2c.

Note that if the dimension X between the release bearing 36 and the torsion rubber 30 is set to a sufficiently large value, even if the release bearing 36 is moved forward as described above, it will not interfere with the torsion rubber 30. If an attempt is made to make the clutch cover 18 larger than necessary, the axial height of the clutch cover 18 and the length of the clutch housing 10 will become larger, and there will be problems such as poor assembly workability. For this reason, in conventional friction clutches, the above-mentioned dimension /a)-
This is set to a value slightly larger than y, and if the clutch lining 28 is excessively worn or damaged and the pressure plate 20 is advanced as described above, the lever ratio b/a and plate thickness Release bearing 36 depending on the size of dimension y with respect to c
There was a problem that the torsion rubber 30 and the torsion rubber interfered with each other.

Although one embodiment of the present invention has been described above in detail based on the drawings, the present invention can also be implemented in other embodiments.

For example, in the above embodiment, the pressure plate 2
Although the clutch cover 18 is attached to the clutch cover 18 via a strap, a lug drive system in which the pressure plate 20 is directly driven by the clutch cover 18 may also be adopted.

In addition, the formula (1) above is based on the release bearing 36 when the clutch disk 22 does not move at all.
Although the dimension δ is determined so as not to interfere with the torsion rubber 30, the clutch disk 22 is also moved forward as the pressure plate 20 moves forward due to wear of the clutch lining 28 on the flywheel 16 side. It is also possible to set the dimension δ in consideration of such advancement of the clutch disk 22.

Further, in the above embodiment, the release bearing 36
The case where the torsion rubber 30 and the torsion rubber 30 interfere has been explained, but if other parts such as the release hub 32 interfere, it goes without saying that the dimension δ should be set by setting the dimension between the parts that interfere with each other as X. be.

Although no other examples are given, the present invention can be implemented with various modifications and improvements based on the knowledge of those skilled in the art without departing from the spirit thereof.

[Brief explanation of the drawing]

FIG. 1 is a sectional view showing an embodiment of the present invention applied to a friction clutch used in an automobile power transmission device. FIG. 2 is an enlarged sectional view of the stopper pin portion of the friction clutch shown in FIG. 1. FIG. 3 is a view from the right in FIG. 2. FIG. 4 is a cross-sectional view showing a main part of the friction clutch shown in FIG. 1, and is a diagram for explaining how to determine the dimension δ for defining the forward end position of the pressure plate. FIG. 5 is a sectional view of a main part of an example of a conventional friction clutch, showing a state in which a release bearing and a torsion rubber interfere with each other. 10... Clutch housing, 16... Flywheel, 18... Clutch cover, 20... Pressure plate, 22... Clutch disc,
26... Disc plate, 28... Clutch lining, 30... Torsion rubber, 32... Release hub, } (release member), 36... Release bearing, 40... Diaphragm spring, 58... Insertion hole, 66... Flange , 68...
...stop pin, 72...spacer, 100...
Tool insertion hole (hole), X...Separation dimension.

Claims (1)

[Claims for Utility Model Registration] A pressure plate disposed between the flywheel and the clutch cover so as to be non-rotatable but movable in the axial direction, and a pressure plate disposed between the clutch cover and the release member. , a diaphragm spring whose intermediate portion is brought into contact with the pressure plate and urges the pressure plate in a forward direction approaching the flywheel, and is housed in the clutch housing, and is housed in the clutch housing, and is housed in the clutch housing, and is housed in the clutch housing. A clutch disk is compressed between the pusher plate and the flywheel to transmit rotational torque, and the release member is moved back against the biasing force of the diaphragm spring, causing the pressure plate to move backward. In a friction clutch of the type that interrupts the transmission of rotational torque by rotating the clutch cover, the pressure plate is provided upright and is inserted into an insertion hole formed in the clutch cover, and the tip has a diameter larger than that of the insertion hole. A stopper pin is provided with a flange, and one is selected from a plurality of types having a substantially U-shaped cross section and different plate thicknesses depending on the distance between the release member and the clutch disk when the clutch is assembled. is integrally fitted into the portion of the clutch cover in which the insertion hole is formed, and is brought into contact with the flange of the stopper pin, thereby preventing the release member and the clutch disk from interfering with each other. 1. A friction clutch, comprising: a spacer for adjusting a forward end position of a clutch plate; and a hole is provided in the clutch housing at approximately the same axial position as the clutch cover.