KR101816451B1 - Apparatus for compensating the wear of friction clutch - Google Patents

Abstract

The present invention relates to an apparatus to compensate wear of a frictional clutch, capable of reducing manufacturing costs. According to the present invention, the apparatus comprises: a push rod to interlock with a fork of a clutch; an outer member including a first insertion groove formed inside and a first thread formed on an inner circumferential surface of the first insertion groove, and connected to the push rod; a guide member including a second insertion groove into which the outer member is inserted in an axial direction of the push rod to be able to reciprocate; an inner member having a second thread formed on an outer circumferential surface correspondingly to the first thread, and inserting at least part of the second thread into the first insertion groove to be screw-coupled to the first thread; and a control rod including a wedge coupled to the inner member to be able to separate, and connected to an actuator to reciprocate the wedge in the axial direction of the push rod. The guide member includes a plurality of first wedges formed on one surface facing the inner member at predetermined first angular intervals, and the inner member is formed on a circumferential part surrounding a central part of one surface facing the guide member at the first angular intervals, wherein the inner member includes second wedges offset from the first wedges as much as predetermined second angular intervals.

Description

Technical Field [0001] The present invention relates to a wear compensating apparatus for a friction clutch,

The present invention relates to a wear compensation apparatus for a friction clutch.

The clutch is a device capable of engaging or disengaging a power transmission, and there are various kinds such as a friction clutch, a fluid clutch, a centrifugal clutch, an electromagnetic clutch, and the like.

Among these clutches, the friction clutch is configured to transmit its power by the frictional force of the two members (clutch disc and pressure plate), and this clutch can be engaged and disengaged by the actuator.

On the other hand, wear of the disk facings (clutch disk and / or pressure plate) occurs over time in the friction clutch, and the stroke of the diaphragm spring and the actuator may be changed by such wear, It may not be achieved.

Therefore, the clutch is provided with a wear compensation device for adequately compensating for the wear thereof, and the power transmission by the clutch can be smoothly matched with wear of the disk pacing suitably by such a wear compensation device.

However, the conventional wear compensation device has a complicated operation structure, and accordingly, a plurality of components are required, which is disadvantageous in that it is difficult to separate not only from the cost side but also to secure the operation reliability.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems of the conventional art, and it is an object of the present invention to provide a wear compensation apparatus for a friction clutch improved to have a short circulation structure.

Furthermore, it is an object of the present invention to provide a wear compensation apparatus for a friction clutch which is improved to reduce the manufacturing cost.

It is still another object of the present invention to provide a wear compensation apparatus for a friction clutch, which is improved to improve operational reliability.

According to a preferred embodiment of the present invention, there is provided a wear compensating apparatus for a friction clutch, comprising: a push rod interlocked with a fork of a clutch; An outer member having a first insertion groove formed therein and a first thread formed on an inner circumferential surface of the first insertion groove, the outer member being connected to the push rod; A guide member having a second insertion groove into which the outer member is inserted to be reciprocally movable along the axial direction of the push rod; An inner member having a second thread formed on the outer circumferential surface so as to correspond to the first thread, wherein at least a portion of the second thread is inserted into the first insertion groove so as to be screwed with the first thread; And a control rod having a wedge releasably coupled to the inner member, the control rod being connected to the actuator and reciprocally transferring the wedge along an axial direction of the push rod; Wherein the guide member further comprises a plurality of first wedges provided at a predetermined first angular interval on one surface of the guide member facing the inner member, And second wedges provided at the first angular interval and spaced apart from the first wedges by a predetermined second angular interval.

Preferably, the first wedges and the second wedges are formed to contact each other when the inner member is retracted toward the actuator by the wedge.

Preferably, the wedge is configured to be separated from the inner member when the first reaction force acting between the first wedges and the second wedges is greater than or equal to a predetermined reference reaction force when the inner member is moved back toward the actuator .

Preferably, the inner member is rotated in one direction by the second angle by the first reaction force when the wedge is separated from the inner member, and the outer member is rotated by the second angle When rotated in one direction, it is retracted toward the actuator by a distance corresponding to the second angle by the screwing.

Preferably, each of the first wedges includes a first vertical surface formed parallel to an axial direction of the push rod, and a second vertical surface extending from an end of the first vertical surface located on the fork side, And the second wedges each extend from a second vertical surface formed parallel to the axial direction of the push rod and an end of the second vertical surface located on the actuator side, And a second inclined surface inclined toward the fork toward the one direction, and the first reaction force acts between the first inclined surface and the second inclined surface.

Preferably, one of the inner circumferential surface of the first insertion groove and the outer circumferential surface of the outer member has a guide protrusion extending along the axial direction of the push rod, and the inner circumferential surface of the first insertion groove and the outer circumferential surface of the outer member A guide groove extending along the axial direction of the push rod is formed so that the guide projection is slidably inserted.

Preferably, the first wedges and the second wedges are arranged to conform to each other when the inner member is rotated by the second angle.

Preferably, the guide member further includes a support block provided on the inner side surface of the second insertion groove so as to face the inner member, and the support block includes a through hole drilled in the center portion to allow the wedge to pass therethrough Respectively.

Preferably, the first wedges are provided on one surface of the support block facing the inner member so as to surround the through holes.

Preferably, the inner member further comprises third wedges provided at the center of the one surface at the first angular interval, the third wedges being arranged to be shifted from the second wedges by the second angular interval, And fourth wedges provided on the one surface facing the inner member at the first angular interval and spaced apart from the third wedges by the second angular interval and detachably coupled to the third wedges.

Preferably, the third wedges and the fourth wedges are formed to contact each other when the wedge is advanced toward the fork.

Preferably, the third wedges and the fourth wedges are arranged such that when the second reaction force acting between the third wedges and the fourth wedges is less than a predetermined reference reaction force when the wedge is advanced toward the fork, And the inner member is advanced toward the fork by the wedge while being coupled with the wedge when the second reaction force is equal to or lower than the reference reaction force.

Preferably, the inner member is rotated in one direction by the second reaction force in the one direction if the second reaction force is equal to or greater than the reference reaction force, and the third wedges and the fourth wedges are rotated in the one direction by the second reaction force, Wherein when the inner member is rotated in one direction by the second angle, the outer member is rotated by the distance corresponding to the second angle, when the inner member is rotated in one direction by the second angle, Back to the actuator.

Preferably, each of the third wedges has a third vertical surface formed parallel to the axial direction of the push rod, and a second vertical surface extending from the end of the third vertical surface positioned on the actuator side so as to face toward the fork in the one direction And the fourth wedges each have a fourth vertical surface formed to be parallel to the axial direction of the push rod and a second vertical surface extending from an end of the fourth vertical surface located on the fork side, And the second reaction force is applied between the third inclined surface and the fourth inclined surface. The fourth inclined surface is inclined toward the actuator toward the other direction, and the second reaction force acts between the third inclined surface and the fourth inclined surface.

The wear compensation apparatus according to the present invention has the following effects.

First, since the present invention has an extremely simple structure as compared with the conventional wear compensation device, the manufacturing cost is extremely low and the operation reliability is greatly improved.

Second, the present invention can precisely compensate wear of the disk facings.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a view showing a state in which a friction clutch is engaged before abrasion of a disk face occurs in a wear compensation device for a friction clutch according to a preferred embodiment of the present invention. FIG.
Fig. 2 is a view showing a state in which the friction clutch is released before wear of the disc pacing occurs in the wear compensation device shown in Fig. 1; Fig.
Fig. 3 is a view for explaining the structure of the push rod shown in Fig. 1. Fig.
4 is a front view of the outer member shown in Fig.
5 is a front view of the guide member shown in Fig.
6 is a view showing a state in which the inner member and the control rod shown in Fig. 1 are separated. Fig.
Figure 7 is a rear view of the inner member shown in Figure 1;
8 is a front view of the wedge shown in Fig.
9 is a view showing a state where abrasion occurs in the disk facing.
Fig. 10 and Fig. 11 are views showing an aspect in which a wear compensation operation is performed by a reaction force acting between a guide member and an inner member in the wear compensation apparatus shown in Fig. 1; Fig.
12 is a view showing a state in which the inner member and the wedge shown in Fig. 1 are joined together; Fig.
13 is a view showing an aspect of a wear compensation device shown in Fig. 1 in which a wear compensation operation is performed by a reaction force acting between an inner member and a wedge;
14 is a view showing a state in which the friction clutch is released after the wear compensation operation is performed in the wear compensation device shown in Fig.

The terms and words used in the present specification and claims should not be construed as limited to ordinary or dictionary terms and the inventor may appropriately define the concept of the term in order to best describe its invention It should be construed as meaning and concept consistent with the technical idea of the present invention. Therefore, the embodiments described in this specification and the configurations shown in the drawings are only the most preferred embodiments of the present invention and do not represent all the technical ideas of the present invention. Therefore, It is to be understood that equivalents and modifications are possible.

In the drawings, the size of each element or a specific part constituting the element is exaggerated, omitted or schematically shown for convenience and clarity of description. Therefore, the size of each component does not entirely reflect the actual size. In the following description, it is to be understood that the detailed description of known functions and configurations incorporated herein will be omitted when it may make the subject matter of the present invention rather unclear.

FIG. 1 is a view showing a state in which a friction clutch is engaged before abrasion of a disc face occurs in a wear compensation device for a friction clutch according to a preferred embodiment of the present invention. FIG. 2 is a cross- In which the friction clutch is released before the wear of the disc pacing occurs.

1 and 2, the friction clutch 10 includes a clutch disc 11 connected to the shaft 1, a pressure plate 12 provided so as to be in frictional contact with or spaced from the clutch disc 11, A fork 17 that pivots to move the pressure plate 12, and an actuator 20 that pivots the fork 17.

The clutch disc 11 may be connected to the shaft 1. For example, when the friction clutch 10 is a vehicle clutch, the shaft 1 may be an input shaft of the transmission.

The clutch disc 11 may be coupled to a flywheel 13 and the flywheel 13 may be coupled to a crankshaft (not shown) of the vehicle. The clutch cover 14 may be coupled to the flywheel 13.

The pressure plate 12 may be installed to advance toward or away from the clutch disc 11. As shown in Fig. 1, as the pressure plate 12 advances toward the clutch disc 11, the engaging action of the friction clutch 10 can be made by frictional contact between the pressure plate 12 and the clutch disc 11. Conversely, as shown in Fig. 2, as the pressure plate 12 and the clutch disc 11 are separated from each other as the pressure plate 12 is retracted from the clutch disc 11, the disengagement operation of the friction clutch 10 can be performed have.

A diaphragm spring 15 is connected to the pressure plate 12 and a diaphragm spring 15 can be pivotably mounted on the clutch cover 14. [

A release bearing 16 may be connected to the diaphragm spring 15 and a lever or a fork 17 may be connected to the release bearing 16. The lever or fork 17 may also be pivotably mounted to one side pivot point 18 of the housing of the transmission or clutch.

The actuator 20 pivots the pressure plate 12 and the clutch disc 11 by pivoting the lever or the fork 17 (hereinafter referred to as "the fork 17") through the wear compensation device 100 They can be controlled to be in frictional contact with each other or spaced apart from each other.

1 and 2, a wear compensation device 100 (hereinafter, referred to as 'wear compensation device 100') according to a preferred embodiment of the present invention is provided between the fork 17 and the actuator 20, ) May be installed.

1 and 2, the wear compensation apparatus 100 includes a push rod 110, an outer member 120, a guide member 130, an inner member 140, a control rod (not shown) 150).

3 is a view for explaining the structure of the push rod shown in Fig.

First, the push rod 110 is a member for transmitting a force applied from the actuator 20 to the fork 17.

The push rod 110 may be provided to be interlocked with the fork 17 by hinging or contacting the fork 17 with the front end. The push rod 110 may include a coil spring 115, a push member 111, and a guide pin 113, as shown in FIG.

The coil spring 115 is installed along the axial direction of the push rod 110 on the outer circumferential surface of the push rod 110. Accordingly, the push rod 110 can be applied with elastic force (buffering force) by the coil spring 115. By this coil spring 115, the push rod 110 and the outer member 120 can not only be stably buffered at the time of movement but also can be easily returned to the home position.

3, the push member 111 is provided at the front end of the push rod 110, and the guide pin 113 extends from the push member 111 and slides into the inside of the push rod 110 As shown in FIG. Accordingly, the push member 111 can be biased from the front end of the push rod 110 outward by applying the elastic force of the coil spring 115 along the axial direction.

4 is a front view of the outer member shown in Fig.

Next, the outer member 120 is a member for transporting the push rod 110 by the wear amount of the disc face.

As shown in FIG. 1, the outer member 120 is connected to the rear end of the push rod 110. The push rod 110 can be moved along the outer member 120. 1, at least a part of the outer member 120 is inserted into the second insertion groove 131 of the guide member 130, which will be described later, so as to be able to reciprocate along the axial direction. The outer member 120 may include a first insertion groove 121, a first screw thread 123, and a guide groove 125, as shown in FIG.

The first insertion groove 121 is formed inside the outer member 120 to be opened toward the actuator 20. The first thread 123 is formed on the inner peripheral surface of the first insertion groove 121. The guide groove 125 is formed on the outer circumferential surface of the outer member 120 in parallel with the axial direction. As shown in FIG. 4, the pair of guide grooves 125 are preferably symmetrically formed, but the present invention is not limited thereto.

When the outer member 120 is inserted into the second insertion groove 131 of the guide member 130, the guide protrusion 132 of the guide member 130 to be described later is inserted into the guide groove 125. Accordingly, the push rod 110 connected to the outer member 120 and the outer member 120 can be reciprocally moved together along the axial direction.

5 is a front view of the guide member shown in Fig.

Next, the guide member 130 is a member for guiding the reciprocating movement of the outer member 120 and driving the inner member 140 to rotate.

The guide member 130 is installed to be positioned closer to the actuator 20 than the outer member 120. 1, the guide member 130 may include a second insertion groove 131, a guide protrusion 132, a first through hole 134, and a support block 133 have.

The second insertion groove 131 is formed inside the guide member 130 so as to open toward the fork 17 as shown in Fig. The second insertion groove 131 is formed to correspond to the outer member 120 so that the outer member 120 can be reciprocated axially along the second insertion groove 131.

The guide protrusion 132 protrudes from the inner side surface of the second insertion groove 131 and extends in the axial direction as shown in Fig. The guide protrusion 132 has a shape corresponding to the guide groove 125 so as to be slidably inserted into the guide groove 125. The guide protrusions 132 are formed in the same number as the guide grooves 125 so that the guide protrusions 132 can be inserted into the guide grooves 125.

The first through hole 134 is formed at the rear end of the guide member 130 so as to communicate with the second insertion groove 131. The first through hole 134 is smaller than the support block 133 but has a larger diameter than the control rod 150 and the wedge 151. [ The control rod 150 and the wedge 151 pass through the first through hole 134 and the second through hole 134. Thus, the support block 133 can be supported by the inner surface of the second insertion groove 131 to maintain the original position, Can be moved.

The support block 133 is provided on the inner surface of the second insertion groove 131 so as to face the inner member 140, as shown in Fig. The support block 133 may include a second through hole 135 and a plurality of first wedges 136, as shown in FIG.

The second through hole 135 is perforated to penetrate the center of the support block 133 and to communicate with the first through hole 134, as shown in FIGS. The second through-hole 135 preferably has the same diameter as the first through-hole 134. The control rod 150 and the wedge 151 may enter the first insertion hole 131 or enter the first insertion hole 131 through the second through hole 135. [

The first wedges 136 are formed to surround the second through holes 135 on the rear surface of the support block 133 toward the inner member 140, as shown in Figs. The first wedges 136 may have a first vertical surface 137 and a first inclined surface 138, as shown in FIG. The first vertical surface 137 may be formed parallel to the axial direction. The first inclined surface 138 extends from the end of the first vertical surface 137 located on the side of the fork 17 and can be inclined toward the actuator 20 toward the predetermined first direction. For example, the first direction may refer to a direction in which the axis of the push rod 110 is rotated in the counterclockwise direction when the wear compensation device 100 is viewed from the front of the push rod 110.

5, the first wedges 136 may be formed at a predetermined first angle? 1 around the second through-hole 135. The first angle? 1 is not particularly limited. For example, the first angle [theta] 1 may be 45 [deg.]. Then, as shown in FIG. 5, the first wedges 136 may be formed in total of eight at intervals of 45 degrees.

Fig. 6 is a view showing a state in which the inner member and the control rod shown in Fig. 1 are separated, and Fig. 7 is a rear view of the inner member shown in Fig.

Next, the inner member 140 is a member for transferring the outer member 120 and the push rod 110 in correspondence with the wear amount of the disk facings.

The inner member 140 is installed at least partially in the first insertion groove 121 of the outer member 120 so as to face the support block 133 and the wedge 151 as shown in Fig. This inner member 140 may have a second thread 141, second wedges 142 and third wedges 143, as shown in FIG.

The second thread 141 is formed on the outer peripheral surface of the inner member 140 to correspond to the first thread 123 of the outer member 120, as shown in Fig. The inner member 140 can be inserted into the first insertion groove 121 by screwing the second screw thread 141 to the first screw thread 123. Thus, the outer member 120 can be moved axially by the threading when the inner member 140 is rotated.

The second wedges 142 are formed to face the first wedges 136 of the support block 133 on the rear surface of the inner member 140, as shown in Fig. For example, the second wedges 142 are formed at the first angle? 1 in the circumferential portion surrounding the central portion of the rear surface of the inner member 140. 7, the second wedges 142 are spaced at intervals of 45 [deg.], Like the first wedges 136, so that a total of eight .

The second wedges 142 may have a second vertical surface 144 and a second inclined surface 145, as shown in FIG. The second vertical surface 144 may be formed parallel to the axial direction. The second inclined surface 145 may extend from the end of the second vertical surface 144 positioned on the side of the actuator 20 and be inclined toward the fork 17 toward a predetermined second direction. That is, the second vertical surface 144 and the second inclined surface 145 each have a first vertical surface 144 (see FIG. 9) such that the first wedges 136 and the second wedges 142 may be aligned, 137, and the first inclined surface 138. [0043] Here, the second direction refers to the direction opposite to the first direction described above. For example, the second direction is a direction in which the axis of the push rod 110 is rotated in the clockwise direction when the wear compensation device 100 is viewed from the front of the push rod 110, as shown in FIG. 1 .

The third wedges 143 are formed on the rear surface of the inner member 140 so as to face the fourth wedges 153 of the wedge 151 described later, as shown in Fig. For example, the third wedges 143 are formed at the center of the rear surface of the inner member 140 at the first angle? 1, 2 are spaced apart from each other by a predetermined second angle? 2. 7, when the first angle? 1 is 45 degrees, the third wedges 143 are spaced at intervals of 45 degrees like the second wedges 142, And the second angle [theta] 2 is 22.5 [deg.].

These third wedges 143 may have a third vertical surface 146 and a third inclined surface 147, as shown in FIG. The third vertical surface 146 may be formed parallel to the axial direction. The third inclined surface 147 extends from the end of the third vertical surface 146 located on the side of the actuator 20 and can be inclined toward the fork 17 toward the second direction.

1 and 2, the second wedges 142 are spaced apart from the first wedges 136 by a predetermined distance, and at the same time, the first wedges 136 and the second wedges 136 are separated from each other, Is inserted into the first insertion groove 121 of the outer member 120 so as to be shifted by two angles? 2.

8 is a front view of the wedge shown in Fig.

Next, the control rod 150 is a member for transmitting the force applied from the actuator 20 to the inner member 140.

1, the control rod 150 is installed to be positioned between the inner member 140 and the actuator 20, and one end thereof is axially coupled to the actuator 20. Such a control rod 150 may have a wedge 151, as shown in Fig.

The wedge 151 is formed to face the third wedges 143 of the inner member 140 at the other end of the control rod 150, as shown in Fig. The wedge 151 is configured to releasably engage the third wedges 143 of the inner member 140. To this end, the wedge 151 may have fourth wedges 153.

The fourth wedges 153 are formed to face the third wedges 143 of the inner member 140 on the front surface of the wedge 151, as shown in Fig. For example, the fourth wedges 153 are formed at the first angle? 1 on the front surface of the wedge 151, as shown in FIG. 8, when the first angle? 1 is 45 degrees, the fourth wedges 153 are spaced at intervals of 45 degrees in the same manner as the third wedges 143, .

The fourth wedges 153 may include a fourth vertical surface 155 and a fourth inclined surface 157, as shown in FIG. The fourth vertical surface 155 may be formed parallel to the axial direction. The fourth inclined surface 157 extends from the end of the fourth vertical surface 155 located on the side of the fork 17 and can be inclined toward the actuator 20 toward the first direction. That is, the fourth vertical surface 155 and the fourth inclined surface 157 are formed in the third vertical surface (the second vertical surface) so that the third wedges 143 and the fourth wedges 153 can be aligned with each other, 146, and the third inclined surface 147. [0060] The fourth vertical surface 155 and the fourth inclined surface 157 are formed by joining the third wedges 143 and the fourth wedges 153 to each other so that the inner member 140 and the wedge 151 have a predetermined binding force Or more.

1 and 2, the fourth wedges 153 are engaged with the third wedges 143, except when compensating for the wear amount of the disk facings, (151) is coupled to the inner member (140).

Hereinafter, a method of engaging and disengaging the friction clutch 10 using the wear-compensating apparatus 100 and a method of compensating wear of the disc face will be described.

First, with reference to FIG. 1, a method of engaging the friction clutch 10 before abrasion of the disc pacing occurs will be described.

When the control rod 150 is moved back toward the actuator 20 by the actuator 20, the inner member 140 wedged with the wedge 151, the outer member 120 screwed with the inner member 140, The push rod 110 connected to the member 120 is retracted together with the control rod 150. As the push rod 110 is thus retracted, the fork 17 can be pivoted rearward and positioned to be vertical, as shown in FIG. The release bearing 16 is then retracted by the fork 17 and the diaphragm spring 15 is pivoted forward by the release bearing 16 to urge the pressure plate 12 toward the clutch disc 11. As a result, the pressure plate 12 and the clutch disc 11 are brought into frictional contact with each other, so that the friction clutch 10 can be engaged. When the engaging operation of the friction clutch 10 is performed as described above, the distance between the actuator 20 and the fork 17 is set to 'L1', the distance between the actuator 20 and the inner member 140 is set to ' L2 ', and the distance between the inner member 140 and the fork 17 is referred to as' L3'.

Next, with reference to Fig. 2, a method of releasing the friction clutch 10 before wear of the disk pacing occurs will be described.

When the control rod 150 advances toward the fork 17 by an amount of X by the actuator 20 in a state in which the engagement operation of the friction clutch 10 is performed before the abrasion of the disk facings occurs, The push rod 110 connected to the outer member 120 and the outer member 120 threadedly coupled to the inner member 140 are advanced together with the control rod 150. [ As the push rod 110 is advanced in this way, the fork 17 is pivoted by the push rod 110 forward by 'X', as shown in FIG. Then, the release bearing 16 is advanced by the fork 17, and the diaphragm spring 15 is pivoted backward by the release bay ring to move the pressure plate 12 backward. As a result, the disengagement operation of the friction clutch 10 can be performed by separating the pressure plate 12 and the clutch disc 11 from each other. When the friction clutch 10 is released, the distance between the actuator 20 and the fork 17 is extended by 'X' relative to 'L1', and the distance between the actuator 20 and the inner member The distance between the inner member 140 and the fork 17 is maintained at 'L3'.

9 is a view for explaining a state where abrasion occurs in the disk facing.

9, when abrasion occurs in the disk facings, the push rod 110 is moved so that the distance between the actuator 20 and the fork 17 becomes 'L1' as before the abrasion occurs in the disk facings, The frictional contact between the pressure plate 12 and the clutch disc 11 can not be smoothly performed. As a result, the power transmission by the friction clutch 10 can not be performed smoothly. Hereinafter, the wear amount of the disk facings will be referred to as 'Y'.

The wear compensation apparatus 100 rotates the inner member 140 using the reaction force acting between the inner member 140 and the guide member 130 and the reaction force acting between the inner member 140 and the wedge 151, It is possible to compensate wear of the disk facings.

Figs. 10 and 11 are diagrams showing the manner in which the wear compensation operation is performed by the reaction force acting between the guide member and the inner member in the wear compensation apparatus shown in Fig. 1. Fig.

Hereinafter, with reference to FIGS. 10 and 11, a description will be given of a method for compensating wear of the disk facings by using the reaction force between the inner member 140 and the guide member 130. FIG.

The control rod 150 moves the actuator 20 until the second wedges 142 of the inner member 140 are in contact with the first wedges 136 of the guide member 130. [ Lt; / RTI > 10, the inner member 140 is inserted into the first insertion groove 121 such that the second wedges 142 are shifted from the first wedges 136 by the second angle? 2 The second inclined surfaces 145 of the second wedges 142 and the first inclined surfaces 138 of the first wedges 136 are brought into contact with each other by a second angle? As a result, a first reaction force acts between the first inclined surface 138 and the second inclined surface 145. This first reaction force can be divided into an axial component parallel to the axial direction and a cylindrical component parallel to the second direction. When the axial component of the first reaction force is larger than the coupling force between the third wedges 143 and the fourth wedges 153, the fourth wedges 153 are separated from the third wedges 143, 151 are separated from the inner member 140. When the wedge 151 is separated from the inner member 140, the inner member 140 is rotated by the second angle? 2 in the first direction by the circumferential component of the first reaction force, as shown in FIG. 11 , And the second wedges (142) coincide with the first wedges (136). 11, the outer member 120 screwed with the inner member 140 is moved backward by a distance corresponding to the second angle? 2 together with the push rod 110. As shown in Fig. The backward distance between the outer member 120 and the push rod 110 due to the rotation of the inner member 140 is determined by the diameter of the first insertion groove 121 and the inner member 140, The pitch interval of the light guide plate 141, and the like. Further, the wedge 151 is retracted by the control rod 150 so as to sequentially pass through the second through-hole 135 and the first through-hole 134. The backward distance between the outer member 120 and the push rod 110 as the inner member 140 is rotated by the second angle? 2 will be referred to as 'Z'.

Fig. 12 is a view showing a state in which the inner member and the wedge shown in Fig. 1 are coupled together, Fig. 13 is a view showing the wear compensation device shown in Fig. 1, Fig.

12, since the inner member 140 is separated from the wedge 151 due to the backward movement of the control rod 150 and is rotated in the first direction by the second angle? 2, The third wedges 143 of the wedge 151 and the fourth wedges 153 of the wedge 151 are shifted from each other by the second angle? 2. In this state, when the control rod 150 is advanced by the actuator 20, as shown in FIG. 12, the third wedges 143 and the fourth wedges 153 are moved by the second angle? 2 And are connected in a state in which they are shifted. A second reaction force is applied between the third inclined face 147 of the third wedges 143 and the fourth inclined face 157 of the fourth wedges 153 and the inner member 140 acts on the wedge 151 And is advanced by the wedge 151 in a coupled state. In addition, the outer member 120 and the push rod 110 are advanced by the inner member 140.

The second reaction force can be divided into an axial component parallel to the axial direction and a cylindrical component parallel to the first direction. 13, when the circumferential component of the second reaction force is equal to or greater than a predetermined reference value, the inner member 140 is rotated by the second angle? 2 in the first direction by the circumferential component of the second reaction force , And the third wedges 143 are joined with the fourth wedges 153 to be tightly coupled. 13, the outer member 120 screwed with the inner member 140, which has been moved backward by 'Z' by the first reaction force, moves together with the push rod 110 by the second reaction force, Z '.

On the other hand, the outer member 120 and the push rod 110 are stepped backward by '2Z' every time the wear compensation operation including the forward and backward movement of the wedge 151 is performed once. The wear compensation apparatus 100 can compensate for wear of the disk facings by gradually reducing the distance between the inner member 140 and the fork 17 by '2Z' using this principle. That is, the wear compensation apparatus 100 can compensate for wear of the disk facings by reducing the distance between the inner member 140 and the fork 17 by '2nZ' corresponding to the amount of wear of the disk facings 'Y' It is. Where n is the total number of times the wear compensation operation has been performed and is proportional to the amount of wear of the disk facing 'Y'.

13, after the wear compensation operation is performed n times to reduce the distance between the inner member 140 and the fork 17 by '2nZ', the inner member 140 and the actuator 20 The control rod 150 is advanced by using the actuator 20 so that the distance between the control rod 150 and the control rod 150 becomes 'L2'. Then the distance between the actuator 20 and the fork 17 is reduced by 2nZ compared to when the friction clutch 10 is engaged before the wear of the disk pacing occurs and the distance between the fork 17 and the release bearing 16) are deflected backward by a distance corresponding to '2nZ'. The diaphragm spring 15 is biased forward by the amount Y of wear of the disc face facing the friction disc 10 before the wear of the disc pacing is generated, . As a result, the engagement of the friction clutch 10 can be achieved by frictionally contacting the pressure plate 12 and the clutch disk with each other.

14 is a view showing a state in which the friction clutch 10 is released after the wear compensation operation is performed in the wear compensation device shown in Fig.

The actuator 20 is driven to advance the control rod 150 by 'X' in a state where the engaging operation of the friction clutch 10 is performed after the wear of the disc pacing occurs. Then, as shown in Fig. 14, the diaphragm spring 15 is pivoted rearward by the release bearing 16 to move the pressure plate 12 backward. As a result, the disengagement operation of the friction clutch 10 can be performed by separating the pressure plate 12 and the clutch disc 11 from each other.

Since the wear compensation apparatus 100 has a very simple structure as compared with the conventional wear compensation apparatus, the manufacturing cost is extremely low and the operation reliability is greatly improved. In addition, the wear compensation apparatus 100 can precisely compensate wear of the disk facings.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not to be limited to the details thereof and that various changes and modifications will be apparent to those skilled in the art. And various modifications and variations are possible within the scope of the appended claims.

10: Friction clutch
11: clutch disc
12: Pressure plate
13: Flywheel
14: Clutch cover
15: diaphragm spring
16: Release bearing
17: Fork
18: One side pivot point
20: Actuator
100: wear compensation device
110: push rod
111: push member
113: Guide pin
115: coil spring
120: outer member
121: first insertion groove
123: First thread
125: Guide groove
130: Guide member
131: second insertion groove
132: Guide protrusion
133: Support block
136: 1st wedge
140: inner member
141: Second thread
142: 2nd wedge
143: 3rd wedge
150: control load
151: Wedge
153: fourth wedge

Claims (14)

A push rod operatively associated with the fork of the clutch;
An outer member having a first insertion groove formed therein and a first thread formed on an inner circumferential surface of the first insertion groove, the outer member being connected to the push rod;
A guide member having a second insertion groove into which the outer member is inserted to be reciprocally movable along the axial direction of the push rod;
An inner member having a second thread formed on the outer circumferential surface so as to correspond to the first thread, wherein at least a portion of the second thread is inserted into the first insertion groove so as to be screwed with the first thread; And
And a control rod having a wedge detachably coupled to the inner member, the control rod being connected to the actuator and reciprocally transferring the wedge along the axial direction of the push rod;
Wherein the guide member further comprises a plurality of first wedges provided at a predetermined first angular interval on one surface toward the inner member,
Wherein the inner member has second wedges provided at the first angular interval around the central portion of one surface toward the guide member and provided so as to be shifted from the first wedges by a predetermined second angular interval Wherein the frictional clutch is a friction clutch. The method according to claim 1,
Wherein the first wedges and the second wedges are formed to contact each other when the inner member is retracted toward the actuator by the wedge. 3. The method of claim 2,
Wherein the wedge is separated from the inner member when a first reaction force acting between the first wedges and the second wedges is greater than a predetermined reference reaction force when the inner member is moved back toward the actuator Of the friction clutch. The method of claim 3,
Wherein the inner member is rotated in one direction by the second reaction force when the wedge is separated from the inner member,
Wherein the outer member is retracted toward the actuator by a distance corresponding to the second angle by the thread engagement when the inner member is rotated in one direction by the second angle. . 5. The method of claim 4,
Wherein each of the first wedges has a first vertical surface formed parallel to an axial direction of the push rod and a second vertical surface extending from an end of the first vertical surface positioned on the fork side, The first inclined surface inclined to the first inclined surface,
Each of the second wedges includes a second vertical surface formed parallel to an axial direction of the push rod and a second inclined surface extending from an end of the second vertical surface positioned on the actuator side and inclined toward the fork toward the one direction 2 inclined surfaces,
Wherein the first reaction force acts between the first inclined surface and the second inclined surface. 6. The method of claim 5,
A guide protrusion extending along the axial direction of the push rod is formed on the inner circumferential surface of the first insertion groove and the outer circumferential surface of the outer member,
Wherein a guide groove extending along an axial direction of the push rod is formed in the other of the inner circumferential surface of the first insertion groove and the outer circumferential surface of the outer member so that the guide projection is slidably inserted. Wear compensation device. 6. The method of claim 5,
Wherein the first wedges and the second wedges are provided such that when the inner member is rotated by the second angle, the first wedges and the second wedges coincide with each other. The method according to claim 1,
The guide member
Further comprising a support block provided on an inner surface of the second insertion groove to face the inner member,
Wherein the support block includes a through hole formed at a central portion thereof to allow the wedge to pass therethrough. 9. The method of claim 8,
Wherein the first wedges are provided on one surface of the support block facing the inner member so as to surround the through holes. The method according to claim 1,
Wherein the inner member further comprises third wedges provided at the first angular interval at the central portion of the one surface and provided so as to be shifted from the second wedges by the second angular interval,
The wedge is provided on one surface of the wedge facing the inner member at the first angular interval and is provided so as to be shifted from the third wedges by the second angular interval, Wherein the wedges are provided with wedges. 11. The method of claim 10,
Wherein the third wedges and the fourth wedges are formed to contact each other when the wedge is advanced toward the fork. 12. The method of claim 11,
Wherein the third wedges and the fourth wedges are configured such that when the second reaction force acting between the third wedges and the fourth wedges when the wedge is advanced toward the fork is less than a predetermined reference reaction force, As shown in FIG.
Wherein the inner member is advanced toward the fork by the wedge while being coupled with the wedge when the second reaction force is less than the reference reaction force. 13. The method of claim 12,
The inner member is rotated in one direction by the second angle by the second reaction force when the second reaction force is equal to or greater than the reference reaction force,
Wherein the third wedges and the fourth wedges are joined together when the inner member is rotated in one direction by the second angle,
Wherein the outer member is retracted toward the actuator by a distance corresponding to the second angle when the inner member is rotated in one direction by the second angle. 14. The method of claim 13,
Each of the third wedges includes a third vertical surface formed parallel to the axial direction of the push rod and a second vertical surface extending from the end of the third vertical surface positioned on the actuator side, 3 inclined surfaces,
Each of the fourth wedges includes a fourth vertical surface formed parallel to the axial direction of the push rod and a second vertical surface extending from an end of the fourth vertical surface positioned on the fork side, And a fourth inclined surface inclined toward the first inclined surface,
And the second reaction force acts between the third inclined surface and the fourth inclined surface.

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