JPH04140519A - Clutch releasing structure - Google Patents

Abstract

PURPOSE:To prevent an O-ring from breakage and a locking part of a wedge collar from drop-out by providing a predetermined clearance and a release bearing locking part extendedly outward of a position orthogonal to a load from the center of the O-ring in the shift of the center of a spring washer. CONSTITUTION:Predetermined clearances Z1 and Z2 are provided respectively in the axial direction X and radial direction of an input shaft between a wedge collar 64 in an annular recess 62 and an inner race 23b of a release bearing 23. Between the wedge collar 64 in a locking part 64a of the wedge collar 64 and an O-ring 63 is provided with a predetermined clearance Z3 in the axial direction X of the input shaft. A release bearing locking part 66 for locking the wedge collar 64 in the annular recess 62 is provided radially outward of a position orthogonal to a load W through the wedge collar 64 from the center of the O-ring 63 in the shift of first and second nipping members 65a, 65b in the clutch releasing direction.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a clutch release system that operates to disconnect the output shaft of an engine and the input shaft of a transmission in response to the action of hydraulic pressure based on depression of a clutch pedal. It's about structure.

(Prior art) Conventionally, this type of clutch has been disclosed in, for example, Japanese Patent Application Laid-open No. 60
As shown in Fig. 0 disclosed in Japanese Patent No. 157519, in a clutch case a, a flywheel C fixed to the end of a crankshaft b serving as an output shaft of an engine, and a transmission. The upper 51 flywheel C includes a clutch life e provided at the end of the input shaft d, and a disc spring h that presses the facing f of the clutch disc e against the wall 1 wheel C via the pressure plate g. The engine output is transmitted to the input shaft d through the clutch disc e. and,
A middle fulcrum type release fork i is provided on the outside of the input shaft d, and the release fork i is supported by the inner wall of the clutch case a corresponding to the transmission side. Due to the action of the oil tank that is affected by the depression of the pedal, the bushing rod j attached to the rear surface of the clutch case a moves clockwise as it moves to the left in the figure, and is supported so as to be able to slide freely outward from the input shaft d. Insert the inner race l of the release bearing into the disc spring h.
A disc spring h is attached which presses the facing f of the clutch disc e against the flywheel C via the pressure plate g by sliding (pulling) it in the right direction as shown in the figure together with the outer race n which is locked at the center of the disc spring h. The force is cut off to perform a disconnection operation between the crankshaft b and the input shaft d of the transmission. It constitutes a so-called pull-type clutch release structure.

Then, as shown in Fig. 11, the release bearing k
A wedge collar p and an O-ring q are interposed between the outer race n and the center of the disc spring h. 1. A locking member having a substantially V-shaped cross section that approximately matches the cross-sectional shape of the annular recess r, protrudes toward the input shaft d side, and is recessed so that the O-ring q is slidably locked therein. A section S is provided.

In this case, the input shaft d is relative to the release bearing k supported outwardly. The assembly of the disc spring h with the clutch disc e and pressure plate g assembled is O.
Once the ring q is locked in the locking part S, move the disk spring locking part at the center of the disc spring h on the wedge collar p to the right side as shown in the figure, and then move it to the end of the wedge collar p (the left end in the figure). Department)
to have a degree of freedom in the radial direction. After that, the locking part S of the wedge collar p is locked in the annular recess r of the 17 Lees bearing, and the center part of the disc on the wedge collar p is moved to the left side as shown in the figure, and the locking part S is moved to the left side as shown in the figure. This is completed by locking the O-ring q inside S.

(Issue 8 to be solved by the invention) However, in the conventional device described above, the locking portion S of the wedge collar p substantially matches the cross-sectional shape of the annular recess r in the release bearing, and does not slide over the O-ring q. If there is a machining error Z in at least one of the locking part S of the wedge collar p and the four annular parts of the release bearing, the center part of the disc spring h and A high stress is applied to the O-ring q between the two, and there is a risk that the O-ring q will be compressed and damaged.

The present invention has been made in view of the above points, and the object thereof is to create a gap between the wedge collar and the O-ring in the locking part of the wedge collar, and between the wedge collar and the release bearing in the annular recess. A clearance in a predetermined direction is appropriately provided to reliably prevent damage to the O-ring between it and the center of the surface spring without being compressed by high stress acting on the O-ring after assembly. It is.

Also, according to the above clearance. Another purpose is to prevent the locking portion of the wedge collar from coming off from within the annular recess of the release bearing.

(Means for Solving the Problem) In order to achieve the above object, the solving means of the present invention connects the output shaft of the engine and the input shaft of the transmission with a wedge collar to a release bearing provided outside the input shaft. and O
The clutch is connected by the biasing force of a disc spring whose center portion is locked through a ring, and the clutch is connected to the center portion of the disc spring via a wedge collar and an O-ring as the release bearing moves in the axial direction. The present invention is based on a clutch release structure in which the biasing force of the disc spring is cut off and disconnected by the movement of the disc spring. The wedge collar has an abbreviated cross section that protrudes toward the input shaft so that the wedge collar is locked in an annular recess provided in the release bearing, and that is recessed inside thereof so that the O-ring is locked therein. A V-shaped locking portion is provided, and a predetermined clearance is provided between the wedge collar and the release bearing in the annular recess in the axial direction and radial direction of the input shaft, and a V-shaped locking portion is provided in the wedge collar locking portion. A predetermined clearance is provided between the wedge collar and the O-ring in the axial direction of the input shaft. Furthermore, the release bearing locking portion that locks the wedge collar in the annular recess is moved from a position orthogonal to the load from the O-ring center via the wedge collar when the center of the disc spring moves in the clutch disengagement direction. The structure also extends outward.

(Function) With the above configuration, in the present invention, a predetermined clearance is provided in the axial direction and radial direction of the input shaft between the wedge collar and the release bearing in the annular recess provided in the release bearing. In addition, there is a space between the wedge collar and the O-ring in the locking part of the wedge collar provided on the wedge collar.
Since a predetermined clearance is provided in the axial direction of the input shaft, even if a machining error occurs in at least one of the locking part of the wedge collar and the annular recess of the release bearing, the engagement within the annular recess and the wedge collar will be maintained. Machining errors are absorbed by the respective clearances within the stop portions, and high stress will not be applied to the O-ring between it and the center of the disc spring after assembly.

In addition, the release bearing locking part that locks the wedge collar in the annular recess is located outside the position perpendicular to the load from the center of the O-ring through the wedge collar when the center of the disc spring moves in the clutch disengagement direction. Since the wedge collar and the release bearing are extended in the opposite direction, a predetermined clearance provided in the radial direction of the input shaft between the wedge collar and the release bearing in the annular recess allows the release bearing locking part in the annular recess and the locking part of the wedge collar to close together. This eliminates the problem of the locking portion between the two and the locking portions being reduced, and the release bearing locking portion effectively absorbs the load from the center of the O-ring through the wedge collar when the center of the disc spring moves in the direction of clutch disengagement. Is it possible to stop Nuke?

(Example) Embodiments of the present invention will be described below based on the drawings.

FIG. 2 shows a clutch using a release structure according to an embodiment of the present invention, in which 1 is an engine, 2 is a transmission, and 3 is a cylinder block 1a of the engine 1 and a transmission casing 2a of the transmission 2. This is the clutch case installed between the two. In this clutch case 3, the flywheel 4
is provided at the end of the output shaft 5 of the engine 1 so as to rotate together with the output shaft 5. A clutch cover 6 is fastened to the flywheel 4 with bolts 7, and a disc spring 8, a pressure plate 10, etc. are assembled into the clutch cover 6.

The input shaft 11 of the transmission 2 is rotatably supported with its tip fitted into the center of the flywheel 5 with a thrust bearing 12 interposed therebetween.

A hub 14 of a clutch disc 13 is splined to the outer periphery of the tip end of the input shaft 11 (behind the thrust bearing 12). The facing 15 of the clutch disc 13 is located between the flywheel 4 and the pressure plate 10, and based on the mounting load of the clutch cover 6, that is, the elasticity set on the engine 1 side by the disc spring 8, The facing 15 is strongly held between the flywheel 4 and the pressure plate 10, and the engine output is transmitted between the flywheel 4 (clutch cover 6, pressure plate 10, etc.) and the input shaft 11 through the clutch disc 13. . Further, a bolt 21 is fixed to the inner wall of the clutch case 3 and extends toward the engine 1 side. A release bearing 23 is provided on the outer periphery of the cylindrical member 22 disposed coaxially with the input shaft 11, and its outer race 23a can freely slide in the axial direction with respect to the outer periphery of the cylindrical member 22 by a support member 24. On the other hand, the inner race 23b is attached to the support member 2 with respect to the outer periphery of the cylindrical member 21.
4 and is supported in a loosely fitted state. The central peripheral edge of the disc spring 8 is locked to the front end (end on the engine l side) of the inner race 23b of the release bearing 23.

Further, as shown in FIGS. 3 to 7, a fork support 3 is provided on the inner wall of the clutch case 3 to support a release fork 31 that slides the outer race 23a of the release bearing 23 in the axial direction.
The fork support 32 provided with the fork support 2 protrudes from the inner wall of the clutch case 3 toward the engine 1 side. A fastening bolt 33 for fastening the transmission casing 2a and the clutch case 3. In order to avoid interference with the clutch case 3 as much as possible, the fastening bolts 33. Two bolts 35 are placed on the boss portion 34 and 34 located closer to the engine 1 than...
．． It is fixed by 35.

Further, the release fork 31 has one end branched into two arms 31a, 31a, and a protrusion that protrudes toward the engine 1 at approximately the middle of the fork support 32 located between the two bolts 35 and 35. When the portion 32a is held between the base ends of the two arms 31a and 231a from the left and right, the fork support 32 is held by the support pin 36 inserted between the 7-L31a and 31a.
It is swingably supported with respect to the protruding part 32a. The support pin 36 is fixed to the proximal end of one arm 31a by a spring pin 37 that is driven in from a diagonal direction of about 45'' on the side opposite to the fork support 32 with respect to the axial direction of the bolt 35. , the support pin receiving portion 38 in the protruding portion 32a of the fork support 32 is arranged in the left-right direction of the release fork 31 (support pin 3
In order to eliminate backlash caused by displacement in six directions), the arm 3 is formed around the entire circumference only in the center.
A recessed portion 32b recessed toward the transmission 2 side (inner wall side of the clutch case 3) is formed on the surface of the fork support 32 on the release fork 31 side corresponding to the base end portion 1a.

32b is provided. Further, the fork support 32 has a release fork 31 of the fork support 32.
The lower surface (the surface on the release fork 31 side excluding the recesses 32b and 32b) is positioned closer to the inner wall of the clutch case than the upper surface of the boss portion 34 so as not to cause a decrease in rigidity due to the recesses 32b and 32b on the side surfaces. This ensures wall thickness. In this case, the fork support 32 is connected to the fastening bolt 3
Although it is provided in a position where interference with 33°... is avoided as much as possible, by locating the lower surface closer to the transmission 2 than the tip of the boss portion 34, some of the fastening bolts 33°... There is no denying that there will be interference, so interference avoidance recesses 32c, 32c are provided on the lower surface of the fork support 32 to avoid interference with the respective fastening bolts 33.

Two arms 31a, 31 of the release fork 31
At the tip of a, there is a protrusion 41 provided at the rear end (transmission 2 side) of the outer race 2Ba of the release bearing 23.
(Only one side is shown in the figure) Abutting part 42 that comes into contact with the front surface of
42 are provided. In addition, the above release fork 3
1 is provided with a receiving recess 43 for receiving and stopping the front end of a bushing rod 44, which will be described later. On the rear surface of the clutch case 3 located on the left side with respect to the input shaft 11 of the transmission 2, a bushing rod 44 that penetrates the rear surface and extends substantially parallel to the input shaft 11 of the transmission 2 is slid in the axial direction. A cylinder 45 is provided for flexible support. The cylinder 45 has an oil injection hole 45.
The oil injection hole 45a is open, and the oil injection hole 45a is opened by the action of hydraulic pressure, which makes it difficult to press the clutch pedal (not shown).
Oil is injected into the cylinder 45 through the cylinder 45. In FIG. 2, 46 is a dust boot whose one end is connected to the front end of the bushing rod 44 and the other end is connected to the cylinder 45.

Further, as shown in FIGS. 8 and 9, the cylinder 45 is attached via a spacer 51 to the rear surface of the clutch case 3 located on the left side with respect to the input shaft 11 of the transmission 2. There is. The rear surface of the spacer 51 is inclined by α° with respect to an orthogonal line Y that is orthogonal to the axis X (axis center) of the input shaft 11 of the transmission 2 so that the inner end is located in front of the outer end. It is formed on the surface 51H. The bushing rod 44 in the cylinder 45 attached to this inclined surface 51H is inclined by β° with respect to the axis X of the input shaft 11 of the transmission 2 so that the rear end approaches the transmission casing 2a along with the cylinder 45. It is arranged at an angle. Further, the bushing rod 44 in the cylinder 45 is connected to the cylinder 4.
5, it is located below the axis X of the input shaft 11 on the side of the transmission 2. Furthermore, the cylinder 4
An air vent hole 52 is provided at the rear end of the cylinder 45 so that air such as bubbles generated in the oil in the cylinder 45 can be discharged by an operator during maintenance. The clutch case 3 and the transmission casing 2a are provided inside a tunnel portion 53 (not shown) that protrudes into the vehicle interior, and the body line 53a of the tunnel portion 53 conforms to the shape of the clutch case 3 and the transmission casing 2a. It gradually becomes thinner as it goes backwards along the line.

Here, the movement of each part based on the depression operation of the clutch pedal will be described. When the clutch pedal is depressed, oil is injected into the cylinder 45 through the oil injection hole 45a, and the hydraulic action of this oil causes the bushing rod 44 to moves toward the engine 1 as shown by the imaginary line in FIG. The release fork 3 is pushed by the bushing rod 44 through the receiving recess 43.
1 rotates (swings) clockwise around the support pin 36 as shown by the imaginary line in the figure, and the release fork 3
The protruding portion 41 of the outer race 23a of the release bearing 23 is moved (pulled) rearward together with the inner race 23b to the position shown by the imaginary line in the same figure by each contact portion 42 of the arm 31a of the release bearing 23. Along with this, inner race 23
The center-type peripheral edge of the disc spring 8, which is locked to the b'rfJ end via a wedge collar 64 and an O-ring 6B (described later), is moved rearward, and the disc spring 8 is connected to the pressure plate 10.
The elasticity (biasing force) set on the engine 1 side is released, and the facing 15 is idled between the flywheel 4 and the pressure brakes 1 and 10, and the flywheel 4 and input shaft 1 are
The engine output is not transmitted through the clutch disc 13 or clutch disc 13. In this way, the output shaft 5 of the engine 1 and the input shaft 11 of the transmission 2 are connected intermittently,
When the clutch is disengaged, the release fork 31 moves the release bearing 23 rearward. This constitutes a so-called pull type clutch C.

As shown in FIG. 1, the front end of the inner race 23b of the release bearing 23 (engine 1 side end)
A locking member 61 that locks the central peripheral edge of the device spring 8 is locked in an annular four part 62 having a substantially trapezoidal cross section provided at the front end (end on the engine 1 side) of the inner race 23b of the release bearing 23. a wedge collar 64 which protrudes toward the input shaft 11 side so as to be stopped therein, and has a locking part 64a having a substantially V-shaped cross section at its front end, which is recessed so that the O-ring 63 is locked therein; It consists of first and second clamping members 65a and 65b, which serve as disc spring locking parts that sandwich and lock the central peripheral edge of the disc spring 8 from both sides. Corresponding first clamping member 6
The lower end of 5a connects to the front end of inner race 23b (four annular portions 62) via the O-ring 63 and wedge collar 64.
It is locked to. Between the wedge collar 64 and the inner race 23b of the release bearing 23 in the four annular portions 62, there is a predetermined clearance Z1 in the axis X direction of the input shaft 11, and a predetermined clearance Z1 in the radial direction (orthogonal line Y direction). A clearance z2 is provided respectively, and a predetermined clearance Z3 is provided in the direction of the axis X of the input shaft 11 between the wedge collar 64 and the O-ring 63 within the locking portion 64a of the wedge collar 64. There is. Further, a release bearing locking portion 66 that locks the wedge collar 64 within the four annular portions 62 is arranged so that the first and second clamping members 65 in the clutch disengagement direction
When moving a and 65b, the load from the center of the ring 63 via the wedge collar 64 extends radially outward from the position perpendicular to the load W! has been done.

Therefore, in the above embodiment, the annular concave portion (wedge collar 64 in the inner race 23b of the release bearing 23 and the inner race 23b of the release bearing 23) with a substantially trapezoidal cross section provided at the front end (engine side end)
) A predetermined 1 degree balance Z1 in the axis X direction and radial direction of the blade shaft 11. When Z2 is provided, a predetermined clearance Z is mainly provided between the wedge collar 64 and the O-ring 63 located in the locking portion 64a of the wedge collar 64 in the direction of the axis X of the input shaft 11. is provided. As a result, the locking portion 64a of the wedge collar 64 and the inner race 2 of the release bearing 23
Processing 24 on at least one of the annular recesses 62 of 3b.
;! Even if a
l, Z2. Processing errors are absorbed by Z3, and after assembly, the first and second clamping members 65a around the center hole of the disc spring 8.

65b and the O-ring 63 is not compressed due to high stress, and damage to the O-ring 63 can be reliably prevented.

Further, a release bearing locking portion 66 that locks the wedge collar 64 within the annular recess 62 of the inner race 23b of the release bearing 23 is configured to hold the wedge collar 64 at zero when the first and second holding members 65a, 65b move in the clutch disengagement direction. The wedge collar 64 in the annular recess 62 extends radially outward from the position perpendicular to the load W from the center of the ring 63 via the wedge collar 64.
A predetermined clearance z2 provided in the radial direction of the input shaft 11 between the input shaft 11 and the inner race 23b of the release bearing 23
The release bearing locking portion 6 in the annular recess 62
6 and the locking portion 64a of the wedge collar 64, the first and second clamping members 65a on the periphery of the center hole of the disc spring 8 in the clutch C disconnection direction are eliminated.
, 65b, the load from the center of the O-ring 63 through the wedge collar 64 is effectively stopped by the release bearing locking portion 66, and the wedge collar 64 is prevented from engaging from within the annular recess 62 of the release bearing. It is possible to reliably prevent the stop portion 64a from coming off.

(Effects of the Invention) As described above, according to the clutch release structure of the present invention, a predetermined clearance is provided between the wedge collar and the release bearing in the annular recess of the release bearing in the axial direction and radial direction of the input shaft. In addition, a predetermined clearance was provided in the axial direction of the input shaft between the wedge collar and the O-ring in the locking part of the wedge collar, so that the respective clearances in the annular recess and the locking part of the wedge collar This absorbs machining errors in at least one of the locking part of the wedge collar and the annular recess of the release bearing, and prevents stress from acting on the O-ring between it and the center of the disc spring and compressing it after assembly. Therefore, damage to the O-ring can be reliably prevented. Moreover, the release bearing locking part in the annular recess is extended outward from the position perpendicular to the load from the center of the O-ring via the wedge collar when the disc spring engaging part moves in the clutch disengagement direction. , a predetermined clearance in the radial direction between the wedge collar and the release bearing in the annular recess eliminates the reduction in the mutual engagement between the release bearing engagement part and the wedge collar engagement part, and the clutch disengagement direction When the center of the disc spring moves, the load from the center of the O-ring through the wedge collar is effectively stopped by the release bearing locking part, and the wedge collar is locked from within the annular recess of the release bearing. It is possible to reliably prevent the part from coming off.

[Brief explanation of the drawing]

The drawings show an embodiment of the present invention, and FIG. 1 is an enlarged sectional view showing the support relationship between the disc spring and the release bearing, FIG. 4 is a side view of the release fork and fork support, 5 is a plan view of the release fork, 6 is a plan view of the fork support, and 7 is a front view of the fork support. FIG. 8 is a rear view of the support, FIG. 8 is a side view of the clutch case and transmission casing, and FIG. 9 is a plan view of FIG. 8. Further, FIGS. 10 and 11 are views corresponding to FIGS. 2 and 1, respectively, showing a conventional example. 1... Engine 2... Transmission 5... Output shaft 8... Belleville spring 11... Input shaft 23... Release bearing 62... Annular four part 63... O-ring 64... Wedge collar 64a...Locking portions 65a, 65b=-1st. Second clamping member 66...Release bearing locking part C...Clutch X...Axis (shaft) Zl,,z2. Z3...Clearance W...Loading 1 person Figure Figure

Claims (1)

[Claims] (1) The output shaft of the engine and the input shaft of the transmission are connected by the biasing force of a disc spring whose center is locked to a release bearing provided outside the input shaft via a wedge collar and an O-ring. The clutch is configured to cut off the biasing force of the disc spring by moving the center of the disc spring via the wedge collar and the O-ring as the release bearing moves in the axial direction. In the clutch release structure, the wedge collar protrudes toward the input shaft so that the wedge collar is locked in an annular recess provided in the release bearing, and the O-ring is locked inside the wedge collar. A locking portion having a substantially V-shaped cross section is provided, and a predetermined clearance is provided in the axial direction and radial direction of the input shaft between the wedge collar and the release bearing in the annular recess. At the same time, a predetermined clearance is provided between the wedge collar and the O-ring in the locking portion of the wedge collar in the axial direction of the input shaft, and a release locking the wedge collar in the annular recess is provided. The bearing locking portion is characterized in that it extends outward from a position orthogonal to the load from the center of the O-ring via the wedge collar when the center of the disc spring moves in the clutch disengagement direction. Clutch release structure.