JPH045849B2 - - Google Patents

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to a hydraulic multiple disc clutch.

(Prior Art) As a conventional hydraulic multi-plate clutch, there is one shown in FIG. 5, for example (Japanese Unexamined Patent Publication No. 59-6427).
In Fig. 5, 1 is a gear that rotates in synchronization with the crankshaft (input shaft), 2 is a transmission main shaft (hereinafter referred to as the main shaft) which is a transmission shaft, and 3 and 4 are a clutch outer and its shaft. A friction disk is supported to be slidable in the direction, 5 and 6 are a clutch center and a clutch plate is supported to be movable in the axial direction, and 7 is a clutch pressure plate (hereinafter referred to as a plate) that presses the friction disk 4. 8 and 9 are hydraulic chambers and oil passages that apply hydraulic pressure to the pressure plate 7, and 10 is a sleeve 11 movable in the axial direction with respect to the pressure plate 7 by a certain clearance h. A clutch lifter plate (hereinafter referred to as a lifter plate) is attached by a through bolt 12, 13 is a central member receiving the pressing force of the release arm 14, and 15 is a lifter plate 10 supported by the clutch center 5.
16 is a reed valve that closes a relief hole for releasing the hydraulic pressure in the hydraulic chamber 8; 17 is a distal end portion fixed to the lifter plate 10; This is a control pin that opens the reed valve 16.

In such a hydraulic multi-disc clutch, when the clutch is connected, high pressure oil is supplied from the oil pump to the hydraulic chamber 8 through the oil passage 9, and this oil pressure causes the pressure plate 7 to move the clutch plate 6 against the friction disk 4. The clutch is connected. Next, when the clutch is in the disengaged state, the release arm 14 rotates clockwise and presses the central member 13 axially inward.
The lifter plate 10 moves toward the clutch center 5 together with the central member 13 overcoming the reaction force of the clutch spring 15 constituted by a diaphragm spring, thereby releasing the biasing force of the clutch spring 15. Furthermore, the lifter plate 10 moves inward in the axial direction by the clearance h and comes into contact with the pressure plate 7, directly pressing the pressure plate 7 inward in the axial direction, so that the clutch plate 6 and friction disk 4 are The pressing force is released. At the same time, control pin 17
moves inward in the axial direction together with the lifter plate 10 and opens the reed valve 16 at its tip.
Pressure oil in the hydraulic chamber 8 is discharged to the outside. Then, only the residual pressure in the hydraulic chamber 8 acts on the pressure plate 7, and due to the action of this residual pressure, the clutch becomes in a half-clutch state. Note that the residual pressure in the hydraulic chamber 8 is controlled by the diameter of the orifice at the inlet of the hydraulic chamber 8.

(Problems to be Solved by the Invention) However, in the conventional hydraulic multi-disc clutch described above, the half-clutch operation when the clutch is driven is controlled by the residual pressure of the hydraulic pressure in the high pressure chamber. The set point for the clutched state was affected by the oil temperature in the hydraulic chamber, making it difficult to set the clutch to a partially engaged state.

SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a hydraulic multi-disc clutch which enables a mechanically stable setting of a half-clutched state without the set point of the half-clutched state being affected by oil temperature.

(Means for Solving Problems) The hydraulic multi-plate clutch of the present invention includes a clutch outer that slidably supports a friction disk in the axial direction of a transmission shaft, and clutch plates that are arranged alternately with the friction disk. a clutch center slidably supporting the transmission shaft in the axial direction; a clutch pressure plate disposed on the clutch center so as to be slidable in the axial direction of the transmission shaft and pressing the friction disk and the clutch plate; a hydraulic chamber having a pressure-receiving surface substantially perpendicular to the transmission axis of the clutch pressure plate as part of its inner wall; a clutch lifter plate mounted so as to be spaced apart from the clutch pressure plate by a certain clearance; a first clutch spring that is supported by the clutch center and biases the clutch lifter plate in the direction in which the friction disk is pressed; a relief valve for discharging the pressure oil;
The second clutch spring has a set load smaller than that of the clutch spring.

(Example) An example of the present invention will be described below based on the accompanying drawings.

The hydraulic multi-plate clutch of this embodiment is shown in FIG. In the figure, 21 is a gear that rotates in synchronization with the crankshaft that is the input shaft, 22 is a main shaft that is rotatably supported by the gear 21 via a bearing 23 and serves as a transmission shaft, and 24 is the gear 21.
A friction disk 25 is supported on the clutch outer 24 so as to be slidable in the axial direction of the main shaft 22 and rotatable therewith. A clutch center 26 is fixed to the main shaft 22 by spline connection, and clutch plates 27 alternately arranged with friction disks 25 are supported on the clutch center 26 so as to be slidable in the axial direction and rotatable together. ing. Further, a pressure plate 28 has a pressing portion 28a that presses the friction disks 25 and the clutch plate 27, which are arranged alternately, toward the clutch center 26.
is disposed on the clutch center 26 so as to be able to slide in the axial direction and rotate integrally therewith, and a hydraulic type 30 is defined by a wall plate 29 and a pressure plate 28 that are fixed to the main shaft 22. A pressure receiving surface 28b of the pressure plate 28, which is substantially orthogonal to each other, forms a part of the inner wall. Hydraulic chamber 3
0 is connected to an oil pump (not shown) through a communication path 31 and an oil path 32. A pressure oil relief hole 3 is provided in the pressure receiving surface 28b of the pressure plate 28.
4 and a reed valve (relief valve) 35 that closes this when the clutch is engaged. In addition, in the figure, 33 is an oil passage for lubrication, 36 and 37
is an oil-tight O-ring, and 38 is a tightening nut.

Further, a lifter plate 40 is supported on the pressure plate 28 by a bolt 42 via a bush 41 having a flange 41a so as to be movable in the axial direction with respect to the pressure plate 28 by a certain clearance h. Lifter plate 40
A bearing 43 and a bearing holder 44 are fixed to the center hole. Lifter plate 4
A first clutch spring 45 is interposed between the clutch center 26 and the clutch center 26.
The inner peripheral edge of the pressure plate 28 is supported by the lifter plate 40, and the pressure plate 28 is connected to the clutch center 2 via the lifter plate 40 and bolts 42.
The set load of the first clutch spring 45 is biased outward in the axial direction relative to the first clutch spring 45.
shall be. In addition, the web portion 2 of the clutch center 26
A control pin 47 is inserted along the axial direction into the mounting portion 46 of the pressure plate 28, which is inserted into the hole 26b formed in the pressure plate 6a.
The base end of the control pin 47 is fixed to the lifter plate 40 and moves together with the lifter plate 40 to push open the reed valve 35 with its tip and release pressure oil from the relief hole 34. Further, a second clutch spring 48 in the shape of a disc spring is interposed between the lifter plate 40 and the bolt 42.
The set load of this second clutch spring 48
F ₁ is the set load of the first clutch spring 45
The relationship is set to F ₀ > F ₁ with respect to F ₀ . Further, a release arm 50 is disposed on the open end surface of the holder 44, and this release arm 50 is biased counterclockwise by a spring 51, and the holder 44 is rotated clockwise by a clutch cable (not shown). The structure is such that it is pressed toward the left in the figure.

In such a hydraulic multi-plate clutch, when the clutch is in a connected state, the first clutch spring 4
5 biases the lifter plate 40 to the right side in the figure, while high pressure oil is supplied to the hydraulic chamber 30 through the oil passage 32 and the communication passage 31, the hydraulic pressure F ₂ of the high pressure oil and the application of the first clutch spring 45 are reduced. power
F ₀ is applied to the pressure plate 28, the friction disk 25 and the clutch plate 27 are connected by the pressure plate 28, and the rotational force on the input side is transmitted to the main shaft 22, which is a transmission shaft.

Next, when a clutch pedal (not shown) is operated, the release arm 50 rotates clockwise against the biasing force of the spring 51 via a clutch cable (not shown), and the holder 44 is pushed toward the left in the drawing. Accordingly, the lifter plate 40 moves to the left in the axial direction against the biasing force of the first clutch spring 45 constituted by a diaphragm spring, and the biasing force of the first clutch spring 45 is released. Therefore, as shown in FIG. 4, which shows the relationship between the stroke amount of the release arm 50 and the pressing force of the pressure plate 28, when the first clutch spring 45 is released, the second clutch out of the total pressing force F is A biasing force F ₁ of the spring 48 and a hydraulic pressure F ₂ of the hydraulic chamber 30 are applied. In addition, in Figure 4, D ₁
is the play of the release arm 50.

When the release arm 50 further rotates and the lifter plate 40 moves to the left in the axial direction, the reed valve 35 is opened at the tip of the control pin 47 as shown in FIG. 2, and the pressure oil in the hydraulic chamber 30 is released to the outside. It is discharged to the outside through the hole 34 and the hydraulic chamber 3
The oil pressure F ₂ in 0 gradually decreases. When the lifter plate 40 further moves in the axial direction through a predetermined clearance h, the second clutch spring 48 is deflected.
Along with this, the pressing force _F1 by the second clutch spring 48 gradually decreases as shown in FIG. Then, when the lifter plate 40 moves by the clearance h, the lifter plate 40 comes into contact with the flange 41a of the bush 41 as shown in FIG. 3, the pressing force _F1 by the second clutch spring 48 is released, and the pressure plate 28 is displaced to the left in the axial direction by _D4 in FIG. 4 together with the lifter plate 40, the pressure plate 28 is completely separated from the friction disk 25, and a disengaged state of the clutch is ensured.

Therefore _, in the range indicated by the stroke _D3 of the lifter plate ₄₀ in FIG. state, and the half-clutch state can be set mechanically. Therefore, the setting point for the half-clutch state is stable without being affected by the oil temperature in the hydraulic chamber 30.

(Effects of the Invention) As is clear from the above description, according to the present invention, in addition to the first clutch spring interposed between the clutch center and the lifter plate, the second clutch spring is interposed between the pressure plate and the lifter plate. By installing a clutch spring, the set point for the half-clutch state can be set mechanically, and unlike conventional systems, it is not controlled solely by the residual pressure in the hydraulic chamber, so it is not affected by oil temperature. Therefore, the set point in the half-clutch state can be made stable.

[Brief explanation of drawings]

Figures 1 to 4 show an embodiment of the present invention, with Figure 1 being a longitudinal sectional view of a hydraulic multi-plate clutch, and Figures 2 and 3 explaining the operations of the reed valve and lifter plate, respectively. A vertical cross-sectional view of the main part, FIG. 4 is a diagram showing the relationship between the stroke amount of the lifter plate and the pressing force of the pressure plate,
FIG. 5 is a longitudinal sectional view showing a conventional hydraulic multi-plate clutch. In addition, in the drawing, 22 is the transmission shaft (main shaft),
24 is a clutch outer, 25 is a friction disk, 26 is a clutch center, 27 is a friction disk, 28, 28b is a clutch pressure plate and its pressure receiving surface, 30 is a hydraulic chamber, 35
40 is a clutch lifter plate, 45, F ₀ is a first clutch spring and its set load, 48, F ₁ is a second clutch spring and its set load, and h is a clearance.

Claims (1)

[Claims] 1. A clutch outer 24 that supports the friction disk 25 so as to be slidable in the axial direction of the transmission shaft, and a clutch plate 27 that is arranged alternately with the friction disk 25 so as to be slidable in the axial direction of the transmission shaft. a clutch center 26; a clutch pressure plate 28 that is slidably disposed on the clutch center 26 in the axial direction of the transmission shaft and presses the friction disk 25 and the clutch plate 27; and the clutch pressure plate 28. a hydraulic chamber 30 having a pressure-receiving surface 28b as part of its inner wall, which is substantially perpendicular to the transmission axis of the clutch; A first clutch spring 45 supported by the center 26 biases the clutch lifter plate 40 in the pressing direction of the friction disk 25, and when the clutch lifter plate 40 moves in the pressing release direction of the friction disk 25. and a relief valve 35 for discharging pressure oil from the hydraulic chamber 30, the first clutch spring 45 is provided between the clutch lifter plate 40 and the clutch pressure plate 28. Clutch pressure plate 2 with smaller set load compared to
8. A hydraulic multi-disc clutch characterized in that a second clutch spring 48 is inserted to bias the clutch spring 8 in the direction in which the friction disc 25 is pressed.