JPH0313620Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a return pressure removal mechanism applied to a power transmission clutch or brake device of a large rotary power device.

(Prior Art) Conventionally, as shown in the vertical cross-sectional view of the rotating clutch in FIG. A plurality of mating plates 2 supported slidably in the axial direction are alternately disposed on the side, and hydraulic oil supplied from a hydraulic pump is supplied into the cylinder chamber 5 via a hydraulic pressure supply path 3. is applied to the annular hydraulic piston 4, and the protruding movement of the hydraulic piston 4 presses the friction plate 1 and the mating plate 2 in the axial direction, thereby transmitting the rotation of the driving shaft A' to the driven shaft B. was configured to do so.

Furthermore, when the hydraulic piston 4 is not in operation, in order to prevent the adverse effects of the return movement of the hydraulic piston 4 due to the hydraulic oil remaining in the gap between the cylinder chamber 5 and the hydraulic piston 4, the A hydraulic oil discharge passage 7 equipped with a so-called non-return valve 6 that communicates from the inside of the cylinder chamber 5 to the outside may be provided, or a hydraulic oil discharge path 7 may be provided that is connected to the head of the hydraulic piston 4 from the inside of the cylinder chamber 5 and pass through the inside of the hydraulic piston 4. A hydraulic oil discharge path 7' provided with a non-return valve 6' extending to the outside in the direction was provided.

That is, when not in operation, the centrifugal force caused by the rotation of the driving shaft side A moves the steel ball 6a or 6b to the position indicated by the chain line to communicate the discharge passage 7 or 7' with the cylinder chamber 5, and the above-mentioned hydraulic pressure caused by the spring 8 is The remaining hydraulic oil is discharged from the cylinder chamber 5 by using the return force of the piston 4 and the centrifugal force caused by the rotation of the driving shaft side A.

On the other hand, when the hydraulic piston 4 is activated, the steel ball 6a or 6b moves to the position shown by the solid line by the hydraulic pressure supplied from the hydraulic pressure supply path 3, thereby blocking the discharge path 7 or 7'. The hydraulic piston 4 was configured to make a predetermined protruding movement.

(Problems to be Solved by the Invention) In the rotary clutch having the above-mentioned conventional configuration, it is necessary to drill holes in order to arrange the non-return valves 6, 6', and the steel balls 6 and 6' are required to be provided.
Adjusting the relationship between the diameter and weight of a and 6b and the diameter of the hole is delicate, and depending on the degree of accuracy error, the non-return valve may not be able to perform its original function.

That is, when the hydraulic piston 4 is operated, the centrifugal force caused by the rotation of the driving shaft side A causes the steel ball 6a or 6b to move to the position indicated by the chain line, or the diameter of the hole in the non-return valve 6, 6' to change. If the steel balls 6a or 6b do not match, leakage of hydraulic oil will occur and the hydraulic piston 4 will
The rotating clutch mechanism was unable to perform its original function due to an operational failure.

Furthermore, when the hydraulic piston 4 is not operating, the discharge passages 7, 7' may remain closed. Therefore, the hydraulic oil remaining in the cylinder chamber 5 prevents the return movement of the hydraulic piston 4, causing the friction plate 1 and the mating plate 2 to come into contact with each other, resulting in wear and tear, which shortens the life of the rotating clutch mechanism. Problems such as the shortening of the lifespan were occurring.

(Means for solving the problem) In order to solve the above problem, the rotating clutch according to the present invention has a plurality of friction plates slidably supported in the axial direction on the driving shaft side, and a plurality of friction plates on the driven shaft side. A rotary clutch configured to alternately arrange a plurality of mating plates that are slidably supported in the axial direction, and press these mating plates and friction plates in the axial direction by an annular hydraulic piston, An annular protrusion is formed on the head portion of the hydraulic piston or inside the cylinder cover to delay the arrival of hydraulic oil to the outer periphery of the hydraulic piston at the start of operation, and an annular groove is formed on the outer periphery of the piston near the hydraulic piston head. A bypass passage is provided in the inner wall of the hydraulic cylinder, and the bypass passage is between the position of the slipper ring at the bottom dead center of the hydraulic piston and the position of the slipper ring at the upper stop point of the hydraulic piston. It is configured to have an outlet at an arbitrary position and an inlet on the inner wall of the hydraulic cylinder near the piston head at the top dead center of the hydraulic piston.

(Function) According to the rotating clutch according to the present invention, since the annular protrusion is formed inside the hydraulic piston head or cylinder cover, it is possible to delay the arrival of hydraulic oil to the outer periphery of the hydraulic piston at the start of operation, and to reduce the hydraulic pressure. An annular groove is formed on the outer periphery of the piston near the head of the piston and a slipper ring is attached thereto, and a bypass passage is provided on the inner wall of the hydraulic cylinder, so that the bypass passage is opened and closed at the contact surface of the slipper ring when the hydraulic piston reciprocates; Near the top dead center of the hydraulic piston, the discharge passage and the cylinder chamber can be communicated via the bypass passage.

(Example) An example of a rotary clutch equipped with a return pressure removal mechanism of the present invention will be described below with reference to the drawings.

FIG. 1 is a vertical cross-sectional view of the entire rotary clutch of the present invention, in which a driving shaft A' and a driven shaft B are rotatably coupled approximately concentrically via a bearing 9, and the driving shaft side A is A plurality of friction plates 1 are arranged to be slidably supported in the axial direction, and on the driven shaft B side,
A plurality of mating plates 2 supported slidably in the axial direction are arranged alternately with the friction plates 1.

FIG. 2 is an enlarged vertical sectional view showing an embodiment of the rotary clutch of the present invention, in which an annular protrusion 13 is formed on the pressure oil side head portion of the annular hydraulic piston 4, and the top dead center of the hydraulic piston 4 (hydraulic (in an unloaded state), separate spatial regions are formed at the outer and inner circumferences of the annular protrusion 13. The annular protrusion 13 may be provided inside the cylinder cover, or both on the hydraulic piston 4 and the cylinder cover.

Further, an annular groove is formed near the piston head on the outer peripheral sliding surface of the hydraulic piston 4, and a slipper ring 10 is mounted in the annular groove. The slipper ring 10 is composed of a back-up spring 10a and a seal ring 10b. That is, the back-up spring 10a has a circular cross-section, and a seal ring 10b whose sliding surface coincides with the inner wall of the cylinder is inserted along its outer circumference, so that the hydraulic piston 4 is attached to the inner circumferential wall of the cylinder chamber 5. It is constructed so that it slides smoothly.

Furthermore, an inlet 11a is provided on the inner circumferential wall of the cylinder chamber 5 near the top dead center of the head of the hydraulic piston 4.
A discharge port spaced apart from the inlet 11a by a predetermined distance in the pressing direction of the hydraulic piston 4 (any position between the position of the slipper ring 10 at the bottom dead center of the hydraulic piston 4 and the position of the slipper ring 10 at the top dead center of the hydraulic piston 4) 11b is formed.

Incidentally, it is also possible to provide a plurality of bypass paths 11.

Next, the operation of the return pressure removing mechanism of the rotary clutch of the present invention having the above structure will be explained based on FIGS. 2 and 3.

When the hydraulic piston 4 is pressed, as shown in FIG. 3, the hydraulic piston 4 is at the position I shown by the chain line at the beginning of operation, and the bypass passage 11 is closed by the annular protrusion 13. ing.

Therefore, as shown in FIGS. 1 and 2, hydraulic oil is supplied into the cylinder chamber 5 by the hydraulic pump P via the hydraulic pressure supply path 3, and acts on the head of the hydraulic piston 4, causing the hydraulic piston 4 to Spring 8
, and presses the friction plate 1 and the mating plate 2.

Subsequently, as the hydraulic piston 4 moves, when the hydraulic piston 4 moves to position (), the slipper ring 10 attached to the outer peripheral sliding surface of the hydraulic piston 4 moves to the position of the discharge port 11b. Since the discharge port 11 is closed, the pressure oil is sealed and the pressed state of the hydraulic piston 4 is maintained.

Therefore, the movement of the hydraulic piston 4 brings the friction plate 1 and the mating plate 2 into pressure contact, and the rotation of the driving shaft A' is smoothly transmitted to the driven shaft B.

On the other hand, when the hydraulic piston 4 returns, as shown in FIG. It enters the bypass passage 11 from there, passes through the discharge port 11b, and is discharged as indicated by the dotted arrow, and the hydraulic piston 4 is completely pushed back by the return force of the spring 8.

FIG. 4 is an enlarged longitudinal sectional view showing another embodiment of the rotary clutch of the present invention, in which the same parts as in the previous embodiment are given the same numbers.

The difference from the previous embodiment is that a vertical groove 11' is formed in the inner wall of the cylinder in the direction in which the hydraulic piston 4 presses, replacing the bypass passage 11.

In this case as well, when the hydraulic piston 4 is operated, the terminal end 11c of the longitudinal groove 11' is closed with the slipper ring 10 to maintain the pressed state of the hydraulic piston 4, and to keep the hydraulic piston 4 in the non-operating state. During operation, the hydraulic oil remaining in the cylinder chamber 5 can be discharged through the vertical groove 11' as shown by the dotted line.

(Effects) According to the rotary clutch equipped with the return pressure removal mechanism according to the present invention, the bypass passage is configured to communicate when the hydraulic piston is not in operation, and the slipper ring closes the bypass passage when the hydraulic piston is in operation. When the cylinder is not in operation, the return movement of the piston is not inhibited by hydraulic oil remaining in the gap between the cylinder chamber and the hydraulic piston. In other words, since the friction plate and the mating plate do not come into contact with each other when the hydraulic piston is not in operation, the friction plate and the mating plate do not suffer wear and tear, extending the life of the rotating clutch mechanism. It has many effects such as being able to fully fulfill the original function of the mechanism.

Furthermore, if the bypass passage of the present invention is installed in a fixed clutch having a large diameter, it will be effective in improving the responsiveness of clutch disengagement.

[Brief explanation of the drawing]

Fig. 1 is a vertical cross-sectional view of the entire rotating clutch of the present invention, Fig. 2 is an enlarged longitudinal cross-sectional view showing an embodiment of the rotating clutch of the present invention, and Fig. 3 illustrates the return pressure removal mechanism of the rotating clutch of the present invention. Enlarged vertical cross-sectional view of a part,
FIG. 4 is an enlarged longitudinal cross-sectional view of another embodiment of the rotary clutch of the present invention, and FIG. 5 is a longitudinal cross-sectional view of a conventional rotary clutch. A...driving shaft side, A'... driving shaft, B... driven shaft, 1... friction plate, 2... mating plate, 3... operating hydraulic pressure supply path, 4... hydraulic piston, 5... cylinder Chamber, 6, 6'... Non-return valve, 6a,
6b...Steel ball, 7,7'...Discharge path,
8...Spring, 9...Bearing, 10...
Slipper ring, 10a...Backup spring, 10b...Seal ring, 11...Bypass path, 11a...Inlet, 11b...Outlet, 1
1'... Vertical groove, 12... Fixed part, 13... Annular protrusion.

Claims (1)

[Scope of utility model registration request] A plurality of friction plates supported slidably in the axial direction on the driving shaft side and a plurality of mating plates supported slidably in the axial direction on the driven shaft side are alternately arranged,
In a rotary clutch configured to axially press a mating plate and a friction plate by an annular hydraulic piston, an annular protrusion is formed on the head portion of the hydraulic piston or inside the cylinder cover,
It is configured to delay the arrival of hydraulic oil to the outer periphery of the hydraulic piston at the start of operation, and an annular groove is formed on the outer periphery of the piston near the hydraulic piston head and a slipper ring is installed, and a bypass path is provided on the inner wall of the hydraulic cylinder. The bypass passage has an outlet at an arbitrary position between the position of the slipper ring at the bottom dead center of the hydraulic piston and the position of the slipper ring at the top dead center of the hydraulic piston, and A rotating clutch characterized by having an inlet in the inner wall of a nearby hydraulic cylinder.