KR920000691B1 - Clutch actuator - Google Patents

Abstract

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Description

Clutch actuator

1 and 2 show a first embodiment of an adjustable clutch actuator to which the present invention is applied, and FIG. 1 is a cross-sectional view of the non-adjustable clutch actuator.

2 is a cross-sectional view of the actuator at the time of the power piston moving.

3 is an enlarged cross-sectional view of main parts of the adjustable clutch actuator according to the second embodiment of the present invention;

4 is a system diagram of an automatic clutch system of a vehicle using a conventional adjustable clutch actuator.

* Explanation of symbols for the main parts of the drawings

1: non-adjustable clutch actuator 2: piston rod

2a: tip of small diameter 2b: inclined end

3: power piston 4: cylinder

4a: operation chamber 4b: back pressure chamber

5: compression spring 6: relay piston

7: Push rod 9, 14, 15 as clutch operating mechanism: Solenoid valve

18: engaging portion 19: rod

20: cap-shaped member 20b: inner peripheral surface

23 steel ball as engagement member 24 support member

26: one-way engagement mechanism 28: hemispherical recess.

The present invention relates to an adjustable clutch actuator used in a mechanical automatic clutch system of a motor vehicle. 4 shows a conventional automatic clutch system of an automobile, and in the figure, 1 is an unregulated clutch actuator conventionally used to control a clutch.

The clutch actuator 1 causes the power piston 3 having the piston rod 2 to reciprocate in the cylinder 4 freely, and moves the power piston 3 in the operating chamber 4a in the direction of movement. The compression spring (5) which is always lightly applied is arranged so as to be arranged in the direction of cutting the clutch (to move the clutch in the direction of disconnection), and the tip of the piston rod (2) It is connected to one end surface of the relay piston 6.

In addition, one end of the push rod (output rod) 7 is connected to the other end surface of the relay piston 6, and the other end of the push rod 7 is connected to the clutch lever (not shown) through the outer lever 8. Connected.

Therefore, when the clutch disconnection signal is issued by the controller 13 to shift, the first solenoid valve 9 opens the valve and the compressed air into the operating chamber 4a of the clutch actuator 1 from the air storage tank 10. Is supplied, thereby causing the power piston 3 and the piston rod 2 to move in the direction of the arrow A. FIG. In conjunction with this, since the relay piston 6 and the push rod 7 move in the direction of arrow A, the outer lever 8 rotates around the support shaft 11 in the direction of arrow B and at the same time A clutch lever (not shown) is rotated so that the clutch is disconnected.

In addition, after the clutch is completely disconnected and the predetermined gear shifting operation is performed, a control signal is supplied to the controller 13 from the stroke sensor 12 arranged and provided in relation to the outer lever 8, and in response thereto, the second Of the solenoid valve 14 or the third solenoid valve 15 is operated.

That is, in the generation of automobiles, the second solenoid valve 14 intermittently opens and closes in the half clutch region, and the compressed air in the operation chamber 4a is gradually exhausted via the back pressure chamber 4b to power the piston. (3) is gradually moved, and the clutch is connected.

In the case of the gear shift after the one-side oscillation, the third solenoid valve 15 is continuously controlled to be in an open state so that the power piston 3 is rapidly doubled (the power piston 3 returns to its original position). In this case, the clutch is connected and the same terminology is used in the A 'direction, hereinafter in the drawing), whereby the clutch is rapidly connected.

Here, as the clutch plate is gradually worn out by the continuous intermittent operation of the clutch, the positions of the push rod 7, the relay piston 6 and the power piston 3 are relatively opposed to the spring force of the compression spring 5. The difference is in the double direction direction (arrow A 'direction).

The operating chamber 4a has a retraction margin of length L so as to sufficiently absorb the fluctuation of the power piston 3 with the wear of the clutch plate.

However, as described above, in the so-called non-adjustable clutch actuator 1, manual adjustment is unnecessary, so that the retraction margin of the length L of the operation chamber 4a becomes a volume loss so that a large amount of air is required to operate the power piston 3. In addition, as the reciprocating operation of the power piston 3 becomes longer, the clutch single operation becomes smooth, resulting in a defect in which the responsiveness deteriorates.

The present invention has been invented in view of the above facts, and an object thereof is to provide a non-regulating clutch actuator having no loss and good responsiveness despite a very simple configuration.

SUMMARY OF THE INVENTION The gist of the present invention is to arrange a piston having a piston rod so that reciprocating motion is free in a cylinder, to install an operability and a back pressure chamber in the cylinder, and to interlock with a piston rod arranged to the side of the back pressure chamber to clamp the clutch. A clutch actuator comprising: (a) a cap-shaped member arranged so as to slide freely in a back pressure chamber of the cylinder and disposed in relation to a tip of the piston rod, an inner circumferential surface of the cap-shaped member and a tip of the piston rod; (B) a compression spring disposed between the opening member of the cap-shaped member and the piston; and (b) a one-way engagement mechanism constituted by an engagement member provided between the outer circumference and an end of the piston rod. c) each of the clutch actuating mechanisms installed in connection with the closed end of the cap-shaped member; When the pressure fluid is supplied into the operating chamber of the piston and the piston rod is moved to the side of the back pressure chamber by a predetermined stroke, the piston rod and the cap-like member are integrally coupled by the engaging member, When the clutch actuation mechanism is double acting, the coupling between the piston rod and the cap-like member is released to allow movement of the cap-like member toward the piston side against the spring force of the compression spring.

EXAMPLE

EMBODIMENT OF THE INVENTION Hereinafter, the Example of the adjustable clutch actuator which applied this invention is demonstrated with reference to FIG. 1 and FIG.

In FIG. 1 and FIG. 2, parts common to those in FIG. 3 are denoted by the same reference numerals, and description thereof is omitted.

First, Figure 1 shows a first embodiment of the present invention. As shown in Fig. 1, the cylinder 4 of the clutch actuator 1 includes a large diameter portion 4c and a small diameter portion 4d, respectively, so that one end of the large diameter portion 4c is closed and the small diameter portion 4d is closed. One end of) opens. Here, in the large diameter part 4c of this cylinder 4, the power piston 3 is arrange | positioned so that reciprocation may be made free, and by this, the operating chamber 4a and the back pressure chamber ( 4b) is formed.

Moreover, the compressed air inlet port 17 which communicates with the operation chamber 4a is provided in the closing wall 4e of the cylinder 4.

The relatively long piston rod 2 is integrally formed in the center part of the above-mentioned power piston 3 to the side of the back pressure chamber 4b. Here, a through hole is formed in the shaft center of the power piston 3 and the piston rod 2, and the rod 19 is arrange | positioned in this through hole so that it may move relatively freely and is arrange | positioned.

In addition, a wide engagement portion 18 is integrally formed at the left end of the rod 19, and the engagement portion 18 and the hole portion 3a of the power piston 3 are formed. The compression spring 21 is mounted in the formed room. Moreover, the tip part 2a of the piston rod 2 is comprised by the small diameter, The edge part 2b is set as the inclined surface of the shape which spreads an end toward the side of the power piston 3. As shown in FIG.

Further, in the small diameter portion 4d of the cylinder 4, the cap shape (the user cylindrical member 20) reciprocates in a state in which the bottom portion 20a is directed toward the open end side of the small diameter portion 4d. It is arrange | positioned so that it may become free.

One open end side of the cap-shaped member 20 is disposed to protrude into the back pressure chamber 4b of the cylinder 4, and is disposed between the spring support surface 20c formed at the front end and the power piston 3. The compression spring 5 set to the load suitable for the non-adjustable clutch is arrange | positioned so that it may be arrange | positioned. In addition, the compression spring 21 is set to a weaker load on the compression spring (5).

In addition, the tip portion 2a of the piston rod 2 is inserted into the recessed portion of the cap-shaped member 20 described above, and a push rod (output rod) 7 is connected to the bottom portion 20a. In Fig. 1, reference numeral 22 denotes freely stretched dust boots mounted on the open end of the small-diameter portion 4d of the cylinder 4.

In addition, a supporting member 24, which is prevented from being separated by the stopper ring 25, is attached to the distal end of the rod 19 protruding from the piston rod 2, and the supporting member 24 and the piston rod ( The some steel ball 23 is arrange | positioned between the edge part 2b of 2).

That is, between the inner peripheral surface 20b of the cap-shaped member 20 and the outer peripheral surface of the distal end portion 2a of the piston rod 2, a plurality of steel balls 23 are arranged so as to be rolled freely, and at the same time, the steel balls The compression spring 30 which applies the force 23 to the direction disengaged from the said edge part 2b is arrange | positioned.

In addition, the compression spring 30 is set to a weaker load than the compression spring 21.

Therefore, the one-way engagement mechanism 24 is comprised by the cap-shaped member 20, the steel ball 23, the support member 24, and the piston rod 2. As shown in FIG.

Next, the operation of the unregulated clutch actuator 1 of the present example will be described.

First, the compressed air is supplied to the operating chamber 4a through the compressed air inlet 17 of the cylinder 4, and the power piston 3 receives the force in the moving direction (arrow A direction) by the pressure. . Accompanying this, the power piston 3 is slightly moved in the A direction with respect to the engagement portion 18 and the rod 19 against the spring force of the compression spring 5 and the compression spring 30.

Therefore, after the piston rod 12 has moved in the reciprocating direction by a predetermined stroke, the steel ball 23 is inclined in the piston rod 2 to be blocked by the support member 24 as shown in FIG. It mounts on the edge part 2b, and is fully crimped | bonded between the edge part 2b and the inner peripheral surface 20b of the cap-shaped member 20. As shown in FIG.

As a result, the cap-shaped member 20, the steel ball 23, and the piston rod 2 are combined in three pieces, and are moved in the direction of arrow A as the pressure of the compressed air in the operating chamber 4a while being in three pieces. . Accompanying this, the push rod 7 also swings in the direction of the arrow, and the clutch is disconnected.

On the other hand, the clutch is connected as follows.

That is, as the compressed air is discharged from the operating chamber 4a, the power piston 3 doubles and returns to a position at which the reaction force from the clutch side becomes almost equal to the spring force of the compression spring 5. At this time, between the engaging portion 18 and the closing wall 4e of the cylinder 4, the cap-shaped member 20, the steel ball 23, and the piston rod 2 are integrally formed at the time of a long run (in the A direction). It leaves the interval of stroke required, and by the compression spring 5, the power piston 3 is further doubled (in the A 'direction) and moves until it comes in contact with the closing wall 4e, whereby The engaged state of the engagement mechanism 26 is released.

At this time, the cap-like member 20 is pressed in the moving direction (A direction) by receiving the spring force of the compression spring 5.

In addition, when the clutch lever and the push rod 7 are moved in the moving direction along with the wear of the clutch plate, the clutch plate is automatically absorbed.

That is, the push rod 7 moves in the double direction more than before the clutch operation due to the wear of the clutch plate, or the amount thereof is a small value for one clutch operation, and the power piston 3 is driven by the spring 5. It does not affect the stroke required for releasing the engagement of the cap-like member 20 with. Therefore, even if the clutch plate is worn or the compressed air is completely exhausted, the engagement between the power piston 3 and the steel ball 23 and the cap-shaped member 20 is released, and the cap-shaped member 20 is compressed by the compression spring 5. The inner side of the small diameter portion 4d of the cylinder 4 is moved by the amount of abrasion of the clutch plate against the spring force of c) so that the position difference of the push rod 7 is effectively absorbed.

As described above, according to the non-adjustable clutch actuator 1, it is possible to reduce the volume of the operation chamber 4a by arranging and installing the adjustment compression spring 5 to the side of the back pressure chamber 4d, so that there is no volume loss. I can do it. As a result, responsiveness and air consumption can be reduced.

3 shows a second embodiment of the present invention.

In the present embodiment, a plurality of hemispherical recesses 27 are formed on the inner circumferential surface 20 of the cap-shaped member 20, and the steel ball 23 moves to the piston (when the piston rod 2 moves) (when the clutch is disconnected). 2) is attached to the end 2b of the grain formed so that it is configured to engage with the recess (27). In addition, everything else is comprised like the case of 1st Example mentioned above.

In this case, the engagement at the time of reciprocation of the cap-shaped member 20, the steel ball 23, and the piston rod 2 can be performed more reliably.

The embodiments of the present invention have been described above, and the present invention is not limited to the described embodiments, and various modifications and changes are possible based on the technical idea of the present invention.

For example, the one-way engagement mechanism 26 is not limited to using the steel ball 23, but is brought into an engaged state at the time of the movement of the power piston 3 in the reciprocating direction, and in the double acting direction (a state in which the clutch is connected). At the time of movement, if the engagement state has a function of a so-called one-way clutch so as to release, it belongs to the present invention.

As described above, according to the present invention, since the one-way engagement mechanism is provided at the tip of the piston rod, and the adjustment compression spring is placed in the back pressure chamber of the cylinder, the operation chamber of the cylinder can be divided by the amount of retraction caused by wear of the clutch plate. Compared with the conventional non-adjustable clutch actuator provided by lengthening, the volume of the operating chamber can be reduced, so that the volume loss can be eliminated, and not only can the response be extremely excellent in operation. In addition, the consumption of compressed air can be suppressed in a very small amount.

In addition, the conventional unregulated clutch actuator using such a compression spring has the advantages of simple structure compared to the so-called oil sealing method, but the configuration related to the present invention is also very simple.

In addition, since the compression spring for adjustment is arranged to be arranged in the back pressure chamber of the cylinder, there is an advantage that the spring force of the compression spring can be used for power cylinder double acting.

Claims (1)

A piston (3) having a piston rod (2) is installed in the cylinder (4) so as to reciprocate freely, and an operating chamber (4a) and a back pressure chamber (4b) are installed in the cylinder (4). A clutch actuator interlocked with a piston rod (2) arranged on the side of (4b) to interlock a clutch, wherein (a) is arranged so as to slide freely in the back pressure chamber (4b) of the cylinder and the piston rod ( Engaging portion provided between the cap-shaped member 20 disposed in relation to the tip of 2), the inner circumferential surface 20b of the cap-shaped member 20, and the outer circumferential portion of the distal end portion 2a of the piston rod 2 ( 23, 24, 30 and the one-way engagement mechanism 26 consisting of the front end of the piston rod (2), (b) the compression spring disposed between the open end of the cap-like member 20 and the piston (3) (5) and (c) a clutch actuated in connection with the closed end 20a of the cap-shaped member 20 Each mechanism is provided so that pressure fluid is supplied into the operating chamber 4a of the cylinder 4 so that the piston 3 and the piston rod 2 can be moved to the side of the back pressure chamber 4b by a predetermined stroke. When the piston rod 2 and the cap-shaped member 20 are integrally coupled to each other by the engaging members 23, 24, and 30, and one of the clutch actuating mechanisms is doubled, the piston rod ( 2) and the coupling between the cap-like member 20, the clutch actuator, characterized in that configured to allow movement of the cap-like member 20 to the piston side against the spring force of the compression spring (5).

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