JPH053776Y2 - - Google Patents

Description

[Detailed description of the invention] (Field of industrial application) This invention is a brake used in a hydraulic clutch with an inertia brake that prevents the clutch cover from spinning during clutch switching for vehicles (industrial construction machinery). This relates to pressure plates.

(Prior art and its problems) A conventional hydraulic clutch will be explained with reference to FIG. In FIG. 4, 10 is an input shaft. Input shaft 10
The hub 12 is spline-fitted to the hub 1.
A large number of clutch disks 16 are spline-fitted to the two spline external teeth 14 so as to be slidable in the axial direction. Friction facings 18 are fixed to both sides of the clutch disk 16, and a clutch plate 20 is interposed between adjacent friction facings 18. clutch plate 20
Lug 2 of clutch cover 22 will be described in detail later.
4 (protrusion) so as to rotate together with the clutch cover 22 in the circumferential direction.

A piston 26 is housed inside the clutch cover 22, and when the clutch is connected, the piston 26
The hydraulic pressure from 6 is transmitted to the clutch disk 16 and the clutch plate 20 by the plate 28, and
This is a structure in which the clutch cover 22 and the clutch cover 22 are fixed together. A back plate 30 is held on the lug 24 of the clutch cover 22 by a snap spring 32, and the back plate 30 is integrally engaged with the lug 24 in the circumferential direction. Spline internal teeth 34 are formed on the back plate 30, and power is output from the spline internal teeth 34.

Pins 40 are press-fitted into the approximately annular back plate 30 at, for example, four locations in the circumferential direction.
0 is provided with a return spring 42. When the clutch is disengaged and no hydraulic pressure is acting on the piston 26, the clutch cover 22 is rotatable relative to the hub 12, and as the clutch cover 22 rotates idly, the spring force of the return spring 42 is transferred through the plate 28 and the ring member 44. The brake force is transmitted to the brake disc 46 to apply a brake force to the clutch cover 22.

By the way, although the plate 28 and the ring member 44 are provided to transmit the hydraulic pressure of the piston 26 and the spring force of the return spring 42 to the brake disc 46 as described above, they are separate bodies from each other. Therefore, there are problems in that the number of parts increases and the axial length of the entire hydraulic clutch also increases.

(Purpose of the invention) The purpose of the invention is to provide a brake pressure plate for a hydraulic clutch that can transmit both the hydraulic pressure from the piston and the spring force from the return spring with a single brake pressure plate. There is.

(Structure of the invention) (1) Technical means The present invention provides a hydraulic clutch with an inertia brake that prevents a clutch cover 22 containing a piston 26 that slides under hydraulic pressure from idling when the clutch is disengaged. The rear surface 46b of the brake disc 46, which cannot rotate but presses the clutch cover 46a against the clutch cover 22, and the return spring 42.
One brake pressure plate 50 between
A brake surface 52 that presses against the rear surface 46b of the brake disc 46 is formed on the radially outer periphery of a brake pressure plate 50 having an integral substantially annular plate shape. A window hole 56 is formed in the radially intermediate portion through which the protrusion 24 of the clutch cover 22 passes, and a rear surface 54a behind the piston pressure contact surface 54 is connected to the friction facing of the clutch disk 16. 18 is a brake pressure plate of a hydraulic clutch, characterized in that the brake pressure plates are opposed to each other.

(2) Action Since the brake pressure plate has the brake surface, piston pressure contact surface, and window hole integrally formed, one brake pressure plate can handle the hydraulic pressure from the piston and the spring force of the return spring. communicated.

(Example) For example, the PTO of an agricultural tractor adopting the present invention
(Power Teke Off) In FIG. 1 showing a hydraulic clutch for driving, parts given the same reference numerals as in FIG. 4 indicate the same or equivalent parts.

In FIG. 1, the front surface 46a of the brake disc 46
is in sliding contact with the clutch cover 22. Further, a brake pressure plate 50, which is the gist of the present invention, is interposed between the brake disc 46 and the return spring 42, and the brake surface 50 of the pressure plate 50 is connected to the brake disc 46.
It is in sliding contact with the rear surface 46b of 6. Note that the brake disc 46 is fitted into a protrusion X on the inner surface of the housing H and is prevented from rotating.

The pressure plate 50 is formed of one substantially annular plate, and the radially outer peripheral portion of the pressure plate 50 facing the rear surface 46b serves as a braking surface 52. A radially inner circumferential portion of the pressure plate 50 forms a piston pressure contact surface 54 that comes into pressure contact with the piston 26. Furthermore, a window hole 56 through which the lug 24 of the clutch cover 22 passes and a through hole 60 into which the spring seat 58 of the return spring 42 is fitted are provided in the radially intermediate portion of the pressure plate 50.
They are alternately arranged at predetermined intervals in the circumferential direction of 0.

As shown in FIG. 2, which is a partial cross-sectional view of FIG.
A notch 66 is formed in the tab 64 that extends radially outward from the pin 4.
0, the return spring 42 has passed. The lug 24 of the clutch cover 22 extends so as to face the side surface 64a of the tab 64.
The side surface 24a of the clutch plate 20 collides with the side surface 64a to prevent rotation of the clutch plate 20 in the circumferential direction.

As shown in FIG. 3, when the pressure plate 50 is viewed from the direction of the arrow in FIG. It is formed into a substantially annular plate shape in which four sets of through holes 60 (Fig. 1) are fitted in are arranged alternately.

The piston 26 in FIG. 1 is supplied with pressure oil flowing from the passage 70 only when the clutch is engaged. In addition, the input shaft 10 has a lubricating oil passage 72.
The lubricating oil in the lubricating oil passage 72 is supplied from the hole 74 to the friction surfaces such as the friction facing 18 and the clutch plate 20 through the passage 76 and the hole 78.

Next, the effect will be explained. First, in the clutch disengaged state shown in FIG. 1, the piston 26 has returned to the most forward position due to the spring force of the return spring 42 transmitted from the piston pressure contact surface 54 of the pressure plate 50, and in this state, the clutch disk 16 and the clutch plate 20 are It's liberated. Therefore,
There is a risk that the clutch cover 22 will slip together with the clutch plate 20, but the spring force of the return spring 42 transmitted from the braking surface 52 of the pressure plate 50 will prevent the brake disc 46 from rotating.
The front surface 46a of the clutch cover 22 is pressed against the clutch cover 22 to apply a brake to the clutch cover 22 and prevent the clutch cover from idling.

On the other hand, when the clutch is connected with pressure oil supplied from the passage 70, the piston 26 moves rearward due to hydraulic pressure and pushes the pressure plate 50 rearward against the spring force of the return spring 42. When the pressure plate 50 moves rearward, the brake surface 52 separates from the rear surface 46b of the brake disc 46, and after the brake is released, the rear surface 54a of the pressure plate 50 moves toward the clutch disc 16.
The clutch disk 16 and the clutch plate 20 are fixed by pressing against the friction facings 18 of the clutch disk 16 and the clutch plate 20. In this state, the hub 12 and the back plate 30 are connected, and the power of the input shaft 10 is transferred to the back plate 30.
It is output from the spline internal teeth 34 of.

(Effect of the invention) As explained above, the brake pressure plate of the hydraulic clutch according to the invention has the front surface 46a
A single brake pressure plate 50 is interposed between the rear surface 46b of the brake disc 46, which is only non-rotatable and is in pressure contact with the clutch cover 22, and the return spring 42, and the brake pressure plate 50 is integrally formed into a substantially annular plate shape. A brake surface 52 that presses against the rear surface 46b of the brake disc 46 is formed on the outer periphery of the plate 50 in the radial direction, a piston pressure contact surface 54 that presses against the piston 26 is formed on the front surface of the inner periphery in the radial direction, and a brake surface 54 that presses against the piston 26 is formed on the front surface of the inner periphery in the radial direction. A window hole 56 through which the lug 24 (protrusion) of the clutch cover 22 passes is formed, and a rear surface 54a behind the piston pressure contact surface 54 is formed.
Friction facing 18 of clutch disk 16
Since the brake disk 46 is opposed to the brake disc 46 with one pressure plate 50, compared to the conventional structure shown in FIG. Pressure contact and transmission of the hydraulic pressure of the piston 26 can be performed, the number of parts can be reduced, and the structure can be simplified. In addition, since the pressure plate 50 has a substantially annular plate shape, the pressure plate 50 can be formed from a simple press-cut flat plate, and is lightweight and lightweight.
It has the advantage of being cheap to manufacture.

Further, since there is no need to overlap the two plates 28 and ring member 44 (FIG. 4) in the axial direction as in the conventional case, the axial length of the entire hydraulic clutch can be shortened.

[Brief explanation of the drawing]

Figure 1 is a vertical sectional view of a hydraulic clutch adopting the present invention, Figure 2 is a partial cross-sectional view of Figure 1, and Figure 3 is a partial cross-sectional view of Figure 1.
The figure is a front view of the brake pressure plate, and FIG. 4 is a longitudinal sectional view showing a conventional example. 10...Input shaft, 30...Back plate, 34...Spline internal teeth, 42...Return spring, 46...
... Brake disk, 50 ... Brake pressure plate, 52 ... Brake surface, 54 ... Piston pressure contact surface, 56 ... Window hole.

Claims (1)

[Scope of utility model registration request] In a hydraulic clutch with an inertia brake that prevents the clutch cover 22 containing a piston 26 that slides under hydraulic pressure from idling when the clutch is disengaged, a brake disc 46 that cannot rotate only has a front surface 46a pressed against the clutch cover 22. One brake pressure plate 50 is interposed between the rear surface 46b and the return spring 42,
A brake surface 52 that presses against the rear surface 46b of the brake disc 46 is formed on the radially outer circumference of a brake pressure plate 50 that is integrally formed into a substantially annular plate shape, and a piston that presses against the piston 26 on the front surface of the radially inner circumference. A pressure contact surface 54 is formed, a window hole 56 through which the protrusion 24 of the clutch cover 22 passes is formed in the radially intermediate portion, and a rear surface 54a behind the piston pressure contact surface 54 is opposed to the friction facing 18 of the clutch disk 16. A brake pressure plate for a hydraulic clutch characterized by: