JPS598021Y2 - hydraulic clutch - Google Patents

Description

[Detailed explanation of the idea] The present invention relates to an improvement of a hydraulic clutch.

Conventional hydraulic clutches operate by moving a single piston that is slidably fitted to the input shaft and operated by hydraulic pressure to move the friction plate that is engaged with the clutch housing to the friction plate that is engaged with the driven shaft. A method in which power is transmitted through pressure contact with a plate, and the piston is returned by the force of a return spring installed between the input shaft and the piston to release the pressure contact between the friction plate and the friction presser plate. ◎Integrated with or around the clutch switching valve. A method in which the hydraulic pressure acting on the piston is adjusted using a pressure reducing valve installed in the piston to cause slip between the friction presser plate and the friction plate. By combining the protrusions and dividing the chamber into a primary hydraulic pressure chamber and a secondary hydraulic chamber, the chambers are communicated with a small guide hole or a small gap to adjust the hydraulic oil supplied to the chambers. There is a method that applies pressure to the friction plate in stages to prevent shock when the clutch is inserted.

However, in the case of ■, when the clutch is disengaged, the piston is returned to its pre-activation position by a return spring, so the piston will not start unless the hydraulic pressure in the operating hydraulic chamber exceeds the return spring force when the clutch is engaged. Inevitably, there will be a delay in operation, and since the spring force of the clutch engagement return spring is acting against the hydraulic pressure in the hydraulic pressure chamber, the pressure against the friction plate of the piston will be reduced accordingly, and a portion of the hydraulic pressure in the hydraulic pressure chamber will be reduced. Moreover, when the power transmission is cut off, the force to return the piston is only the preset spring force, so the frictional resistance in the sliding part and the residual hydraulic oil in the hydraulic pressure chamber are eliminated, and the piston is returned. It has drawbacks such as being time consuming.

In the case of ◎, the pressure reducing valve lowers the hydraulic pressure in the hydraulic pressure chamber to reduce the pressure on the friction plate and cause slippage between the pressure plate and the friction plate, so the pressure generated by the hydraulic pump is significantly lowered to reduce the hydraulic pressure. Most of the hydraulic oil is discarded to obtain the hydraulic pressure in the chamber, and since the pressure reducing valve and the hydraulic pressure chamber are connected through a combination of long pores, the connection is unstable due to pulsation in the valve part. It has some drawbacks such as being too easy to get used to.

In the case of O, since there is a throttling effect on the hydraulic oil even at the initial stage of clutch engagement, the piston starts late, and furthermore, the resistance during the movement of the piston is large and the operation time is increased.

Also, when power transmission is cut off, the only force that causes the piston to retreat is the preset spring force of the return spring, and in addition to the frictional resistance of the sliding parts, there is also a large amount of friction between the primary working hydraulic chamber and the secondary working hydraulic chamber. Since it takes time to remove the remaining hydraulic oil through the constriction part, there are disadvantages such as difficulty in clutch disengagement.

The present invention has been made in order to eliminate the above-mentioned drawbacks, and it forms a return hydraulic chamber that faces the working hydraulic chamber by sandwiching a piston in the clutch housing, and also forms a return hydraulic chamber that faces the working hydraulic chamber. At the end of the forward stroke of the piston, a device is installed that increases the hydraulic pressure by regulating the amount of hydraulic oil delivered and forms a hydraulic damper, resulting in excellent responsiveness when engaging and disengaging the clutch. Our aim is to provide a hydraulic clutch that causes less shock, facilitates trolling operations, and is energy efficient.

FIG. 1 showing a first embodiment of the present invention will be described below.

1 is an operating hydraulic chamber 3 provided in the clutch housing 2
The piston is fitted externally to the input shaft 4 and internally to the clutch housing 2 in an oil-tight and slidable manner, and a stepped portion 5 is provided on the inside on the friction plate 14 side so that a part of the outside and inside pistons are connected. 6 and 7 are provided.

Reference numeral 8 denotes a return housing which is oil-tightly fixed to the input shaft 4 and slidably and oil-tightly engaged with the outer pilot part 6 of the piston 1; It dominates room 10.

Reference numeral 9 denotes a protrusion of a return housing 8 that is slidably provided in the inner pilot part 7, and includes a hydraulic oil throttle hole 11 and a relief hole 1.
2 is drilled.

The return hydraulic chamber 10 is connected to the outer and inner hydraulic chambers 1 by the protrusion 9.
Divided into 0' and 10", with aperture hole 11 and relief hole 12
It is communicated with.

The relief hole 12 is set at a position where it is closed by the piston 1 just before the friction presser plate 13 comes into contact with the friction plate 14 and power transmission begins slightly, and the throttle hole 11 is provided near the base of the protrusion 9.

Reference numerals 15 and 16 indicate oil holes in the operating hydraulic chamber 3 and the return hydraulic chamber 10 that communicate with the switching valve 18 provided on the input shaft 4;
7 is the friction plate 14 facing the friction plate holding plate 13 in the axial direction?
It is a driven shaft that is movably engaged and rotatably fitted to the input shaft 4, and includes a gear (not shown) that meshes with a thrust shaft gear (not shown).

The switching valve 18 shown in FIG. 1 has a notch 19 on the outer periphery. , 1
9.

, 193 and a hollow rotating body 22 provided with an oil passage hole 21 that communicates with a hydraulic oil pump (not shown) via a hollow portion 20, and oil passages 15, 152, 16, 162.
It is equipped with

The notch 19 communicates with the oil hole 21, and the notch 19. , 1
93 communicates with an oil pan (not shown), and the oil passage 15 connects to the working hydraulic chamber 3 through the oil hole 15, and the oil passage 16 communicates with the oil pan (not shown).

are in communication with the return hydraulic pressure chamber 10 via oil holes 16, respectively.

Although not shown, the oil passages 15 and 16 communicate with an operating hydraulic chamber and a return hydraulic chamber of the reverse clutch, respectively.

Notches 19, 19. , 193 and oil passages 15, 15, 16,
16.

is arranged so that you can switch between the five types shown in the table below with a single operation.

? The dash is for hydraulic oil delivery, and the off is for hydraulic oil discharge.

In the above configuration, when the clutch is rapidly engaged from neutral to forward, when the switching valve 18 is operated as shown in Figure 1, Port-C, the hydraulic oil flows into the oil passage 21 completely cut out section 19.

The hydraulic oil in the return hydraulic chamber 10 is sent to the hydraulic pressure chamber 3 through the first oil passage 15 and the first oil hole 15, and the hydraulic oil in the return hydraulic chamber 10 is sent to the outer hydraulic pressure chamber 1.
0' - relief hole 12 and throttle hole 11 - inner return hydraulic chamber 10
"The oil is returned to the oil pan through the oil hole 16, oil passage 16, and all cutouts 19, and the pressure inside the return hydraulic chamber 10 decreases rapidly, causing the piston 1 to move quickly.

When the piston 1 approaches the end of its forward stroke, the piston 1 closes the relief hole 12 of the protrusion 9, and only the throttle hole 11 communicates between the outer return hydraulic chamber 10' and the inner return hydraulic chamber 10'', and the piston 1 Since the outflow of hydraulic oil corresponding to the moving speed of is reduced, the oil pressure in the outer return hydraulic chamber 10' increases rapidly, and the outer return hydraulic chamber 10' acts as a hydraulic damper.
A friction plate 14 applies a brake to the forward movement of the piston 1.
And a friction plate? Since the contact with the cover plate 13 is made very gradually, the impact at the beginning of power transmission is reduced.

When returning the clutch from forward to neutral, the switching valve 18 is
By operating as shown in Figure '0-a, the hydraulic oil in the hydraulic pressure chamber 3 is discharged to the oil pan through the oil hole 15 and the oil passage 15 cutout 193, contrary to the case of forward movement, and the hydraulic pressure is rapidly increased. The piston 1 becomes smaller in size, and hydraulic oil is sent into the inner return hydraulic chamber 10'' through the oil passage 21 cut-out part 19, the oil passage 16, and the oil hole 16, the oil pressure increases, and the piston 1 begins to retreat.

In this case, since hydraulic oil is supplied to the outer return hydraulic chamber 10' from the throttle hole 11, the supply amount is small, and when the piston 1 begins to move, the outer return hydraulic chamber 10' becomes slightly negative pressure and resists the movement of the piston 1. However, when the piston 1 moves slightly, the relief hole 12 opens, so the piston 1 quickly retreats without causing too much trouble.

In this case, the return of the piston 1 is done by hydraulic pressure instead of the conventional return spring, so the piston 1 starts immediately as the hydraulic pressure in the operating hydraulic chamber 3 increases when the clutch is engaged, and conversely, when the power is cut off, such as when in neutral. Since the piston 1 is returned by the hydraulic pressure in the return hydraulic chamber 10, the return is quick.
Since the hydraulic oil distribution in the return hydraulic chamber 10 is carried out in conjunction with one switching valve 18, failures such as simultaneous fitting do not occur.

Trolling is carried out by applying hydraulic pressure to both the return hydraulic chamber 10 and the working hydraulic chamber 3, and applying the differential pressure between them to the friction plate 14, so that the pressure generated by the hydraulic pump remains almost the same.
10, less oil is discarded by the pressure regulating valve, and the oil pressure connection is stable, and by reducing the oil pressure in both chambers 3 and 10, the pressure on the friction plate 14 can be finely adjusted. It is possible.

Furthermore, each structural component is basically cylindrical and can be easily manufactured using existing equipment.

In the first embodiment described above, the protrusion 9 of the return housing 8 is provided with the throttle hole 11, but instead of this, a small gap may be provided between the protrusion 9 and the inner pilot part 7.

FIG. 2 showing a second embodiment of the present invention will be described below.

1 is an operating hydraulic chamber 3 provided in the clutch housing 2
The piston is fitted externally to the input shaft 4 in an oil-tight and slidable manner and fitted internally to the clutch housing 2, and has a pilot part 6 on the inside on the friction plate 14 side, and an inner bottom part 1'. A ring-shaped protrusion 23 is provided on.

? is a return housing that is oil-tightly fixed to the human-powered shaft 4 and slidably engaged with the spigot part 6 of the piston 1,
A return hydraulic chamber 10 facing the working hydraulic chamber 3 with the piston 1 in between is defined.

24 is a ring-shaped groove into which the protrusion 23 provided on the return housing 8 is fitted with a slight gap.

The positions of the protrusion 23 and the groove 24 are such that the friction plate holding plate 13 comes into contact with the friction plate 14 and power transmission begins slightly.
4 so that the protrusion 23 starts to fit in.

Also, the number of protrusions 23 and grooves 24, the height of protrusions 23 and the grooves 2
4 and the gap between the protrusion 23 and the groove 24 are set so as to function as a diaphragm, which will be described later.

30 is a gear that meshes with the thrust shaft gear 31 and is fitted onto the driven shaft 17.

The names and structures for other symbols are the same as in the first embodiment.

Further, the switching valve for operating the clutch is the same as that in the first embodiment, and is designed so that the five types of switching shown in the preceding table can be performed with one operation.

In the second embodiment, the effects of the throttle hole 11 and relief hole 12 provided in the protrusion 9 of the return housing 8 in the first embodiment are replaced by the effects of the protrusion 23 of the piston 1 and the groove 2 of the return housing 8.
This embodiment differs from the first embodiment in that the second embodiment is made to perform the following operations.

That is, when the clutch is engaged rapidly from neutral to forward, the operating oil in the return hydraulic chamber 10 is returned to the oil pan via the oil hole 16 and the switching valve by operating the switching valve, and the hydraulic oil is returned to the oil pan through the switching valve overnight hole 15. is sent to the hydraulic pressure chamber 3, and the piston 1 starts moving forward and moves quickly.

As the piston 1 approaches the end of its forward movement, the protrusion 23 of the piston 1 begins to fit into the groove 24 of the return housing 82, and only the small gap between them communicates with the protrusion 23.
3 and the groove 24 and in isolated parts of the return hydraulic chamber 10, these parts form a hydraulic damper and brake the forward movement of the piston 1.
As in the case of the first embodiment, the impact at the beginning of power transmission is reduced.

When switching the clutch from forward to neutral, the piston 1 quickly retreats by operating in the opposite manner to when switching from neutral to forward, as in the first embodiment.

In this case, should the protrusion 23 be returned until it comes out from the groove 24? Pressure chamber 10
Negative pressure acts within the piston 1, creating some resistance when the piston 1 begins to move, but this negative pressure is small and for a short time, so it does not hinder the piston 1's retreat much.

In the second embodiment, since the protrusion 23 and the groove 24 are basically non-contact, the dimensional accuracy is low and the durability is high, and furthermore, the groove 24 and the outer return hydraulic chamber 10 are continuous in the circumferential direction. Therefore, the resistance against the piston 1 is average.

FIG. 3 showing a third embodiment of the present invention will be described below.

A piston 13 is provided in an operating hydraulic chamber 3 provided in the clutch housing 2, and is fitted externally to the input shaft 4 in an oil-tight and slidable manner, and is fitted internally into the clutch housing 2.
A pilot part 63 is provided inside the friction plate 14 side.

Reference numeral 83 denotes a return housing which is oil-tightly fixed to the input shaft 4 and slidably engaged with the spigot part 63 of the piston 13, and the return housing faces the hydraulic pressure chamber 3 across the piston 13. A plurality of fitting holes 26 are provided in the shape of the chamber 10, into which a cylindrical small piston 25 whose piston 13 side is closed is slidably fitted in an oil-tight manner.

Furthermore, the throttle hole 1 is returned to the fitting hole 26 and communicates with the hydraulic chamber 10.
13 and a relief hole 123 are provided.

The small piston 25 is provided with a return spring 27 inside, and the spring force of the return spring 27 is set to be as small as possible within a range in which the hydraulic oil enters the inside through the throttle hole 113 within a prescribed time.

The dimensions of the small piston 25 coming out from the fitting hole 26 of the piston 13 to the return hydraulic chamber 10 are the same for each small piston 25.
Set by one side or a separate positioning plate.

The relief hole 123 is provided at a position where it is closed by the small piston 25 when the friction plate 14 and the friction plate holding plate 13 come into contact and a slight power transmission begins, and the throttle hole 113 is provided at a position where the small piston 25 is fitted. It is provided at a position where it will not be blocked by the small piston 25 in the final state of fitting into the mating hole 26.

The names and structures of other symbols are the same as in the first embodiment.

Further, the structure and operation of the switching valve for operating the clutch are the same as in the first embodiment.

The third embodiment replaces the action performed by the throttle hole 11 and relief hole 12 provided in the protrusion 9 of the return housing 8 in the first embodiment with a fitting hole provided with the throttle hole 113 and relief hole 123 of the return housing 83. 26 and the small piston 25 are different from the first embodiment.

That is, when the clutch is rapidly engaged from neutral to forward, the operating oil in the fitting hole 26 is drained into the relief hole 123 by operating the switching valve.
The hydraulic oil returns through the hydraulic chamber 10, oil hole 16, and is returned to the oil pan via the switching valve, and the hydraulic pressure in the fitting hole 26, the small piston 25, and the return hydraulic chamber 10 decreases, and the hydraulic oil flows into the hydraulic hydraulic chamber 3. flows in and the piston 13 starts moving forward and moves quickly.

Near the end of the forward stroke of piston 13, small piston 25
closes the relief hole 123, leaving only the throttle hole 113 open, and the hydraulic pressure in the fitting hole 26 and piston 25 rises rapidly, forming a hydraulic damper and applying a brake to the forward movement of the piston 13. to reduce the impact at the beginning of power transmission.

When switching the clutch from forward to neutral, the piston 13 quickly retreats by operating in the opposite manner to when switching from neutral to forward, as in the first and second embodiments.

In this case, unlike the first and second embodiments, when the piston 13 retreats, it can move away from the small piston 25.
It is completely unaffected by the negative pressure generated in the small piston 25.

In the third embodiment, the fitting of the return housing 83 {L2
6 is provided with a throttle hole 113 and a relief hole 123, and the small piston 25 is fitted into the fitting hole 26, but conversely, the piston 13 may be provided with a similar structure as described above.

FIG. 4 showing a fourth embodiment of the present invention will be described below.

Reference numeral 84 denotes a return housing that is oil-tightly fixed to the input shaft 4 and slidably engaged in an oil-tight manner to the spigot part 63 of the piston 13. The return housing 84 is a return hydraulic chamber that faces the working hydraulic chamber 3 across the piston 13. 10, and is provided with a plurality of ring grooves 29 into which the ring 28 is slidably inserted in an oil-tight manner.

Further, a throttle hole 114 and a relief hole 124 which return to the ring groove 29 and communicate with the hydraulic chamber 10 are provided.

A return spring 32 made of a bent leaf spring is provided between the lower part of the ring 28 and the bottom of the groove 29, and the spring force of the return spring 32 is within a range that allows the hydraulic oil to pass through the throttle hole 114 and enter the ring groove 29 within a specified time. Set it as small as possible within the spring 3 and return it again.
The relief hole 124 is made open in the free state of 2.

Throttle hole 114 and escape hole 12 provided in ring groove 29
Position 4 is the throttle hole 113 and relief hole 12 of the third embodiment.
It is established to satisfy the same conditions as 3.

The names and structures of other symbols are the same as in the third embodiment.

Further, the structure and operation of the switching valve for operating the clutch are the same as in the first embodiment.

In the fourth embodiment, the action of the fitting hole 26 provided with the throttle hole 113 and the escape hole 123 provided in the return housing 83 in the third embodiment and the small piston 25 that fits into the hole 26 is similar to that of the return housing 83 in the third embodiment. This is done by a ring groove 29 with a crest hole 114 and a relief hole 124 provided in the ring groove 29 and a ring 28 that fits into the ring groove 29, when the clutch is inserted from neutral to forward movement or when the clutch is returned from forward movement to neutral position. The operating principle is the same as that of the third embodiment.

In the fourth embodiment, the throttle hole 114 was provided near the bottom of the ring groove 29, but instead of this, several notches may be provided on the side surface of the ring 28 so that the outside and the inside of the hydraulic chamber 10 communicate with each other. .

Although the return housing 84 is provided with a ring 28 and a ring groove 29, in the second to fourth embodiments, a similar arrangement may be provided on the piston 13 side. Since it is based on hydraulic pressure, the piston starts and moves quickly, and returns quickly, and there is no failure such as fitting due to the switching valve, and the operation during trolling is the same as in the first embodiment.

Furthermore, since each structure or part is basically cylindrical, it can be easily manufactured using existing equipment.

The present invention relates to a clutch device that transmits rotational power to a driven shaft by pressing a friction plate by moving a hydraulic piston that is slidably fitted on an input shaft. A return housing that is slidably engaged in an oil-tight manner inside the piston is provided to form a return hydraulic chamber that faces the working hydraulic chamber across the piston. , a hydraulic damper is formed between the return housing and the hydraulic piston near the end of the forward stroke of the piston to increase the hydraulic pressure by regulating the amount of hydraulic fluid delivered. Since it is a clutch, it has the following effects.

(1) Shorten the clutch starting time when the clutch is inserted,
A clutch with excellent responsiveness can be provided.

(2) The impact generated when the clutch is engaged can be reduced.

(3) When the power is cut off, such as when in neutral, the piston is returned by hydraulic pressure, so a clutch that returns quickly and has good engagement can be provided.

(4) Since the hydraulic pressure in the hydraulic pressure chamber directly becomes pressure against the friction plate, there is little waste during the process, so a clutch with good energy efficiency can be provided.

(5) Since hydraulic oil is supplied and discharged using a single switching valve, malfunctions such as simultaneous insertion can be prevented.

(6) Trolling operations can be easily and delicately adjusted.

(7) It is possible to combine it with a ready-made pressure reducing valve, and it is possible to provide a clutch with excellent versatility.

[Brief explanation of the drawing]

Figure 1 shows the first embodiment of the present invention, where A is a cross-sectional view of the main part (the upper part from the center of the input shaft is the clutch engaged state, the lower part is the clutch non-engaged state), and the opening is a diagram for explaining the operation of the switching valve. The simplified cross-sectional views and FIGS. 2 to 4 are cross-sectional views of main parts of the second to fourth embodiments of the present invention (the upper part from the center of the input shaft is in the clutch-fitted state, and the lower part is in the clutch-unfitted state). . 1, 1, 13... Piston, 2... Clutch housing, 3... Operating hydraulic chamber, 4...
...Input shaft, 8, 8, 8. , 8.・・・・・・
... Return housing, 10 ... Return hydraulic chamber, 1
4... Friction plate, 17... Driven shaft.

Claims (1)

[Scope of utility model registration request] In a clutch device that transmits rotational power to a driven shaft by pressing a friction plate against a friction plate by movement of a hydraulic piston that is slidably fitted on the input shaft, the hydraulic piston is oil-tightly fixed to the input shaft within the clutch housing and is attached to the inside of the piston. a return housing slidably engaged in an oil-tight manner to form a return hydraulic chamber opposite the actuating hydraulic chamber across the piston;
A hydraulic clutch characterized in that a hydraulic damper is provided between the return housing and the hydraulic piston to increase the hydraulic pressure by regulating the amount of hydraulic oil to be delivered at the end of the forward stroke of the piston.