JPS6237526A - Liquid pressure clutch device - Google Patents

Abstract

PURPOSE:To prevent occurrence of double gearing by separating the clutch piston at the connecting side of clutch prior to connection with clutch board. CONSTITUTION:Moving speed of clutch piston 10 to the piston housing 3 side is set higher than the moving speed of clutch piston 22 to the clutch hab 20 side. Consequently, the clutch piston 10 will separate from the clutch boards 7, 9 prior to connection of piston 22 thus to never cause double gearing when switching the clutch.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention relates to a separate hydraulic clutch device that is equipped with a plurality of clutch mechanisms and is used in an automatic transmission, in which one of the clutch mechanisms is not yet disengaged. The present invention relates to a hydraulic clutch device that prevents a so-called double transmission state in which the other clutch mechanism is connected.

(Prior Art) Conventional separate type hydraulic clutch devices include those shown in FIGS. 2 and 3. A clutch shaft 1 transmits engine power, and is rotatably attached to the clutch casing via a tapered bearing 2. 3 is a piston housing that is fixed to the clutch shaft 1 and rotates integrally with the clutch shaft 1, and on the left and right sides of the piston housing 3 in FIG. (not shown)
Two piston mechanisms are independently arranged to connect and disconnect between the clutch shaft 1 and the clutch shaft 1.

First, in the piston mechanism on the left, reference numeral 4 represents an output gear, which is attached to the clutch shaft 1 through a needle bearing 5 so as to be relatively rotatable, and has a tooth portion 4a that meshes with a gear group (not shown). There is.

A clutch drum 6 is fitted integrally with the output gear 4, and has an inner circumferential spline 6a formed on its inner circumference, and a plurality of external clutch plates 7 are disposed on the inner circumferential spline 6a. A clutch hub 8 is spline-fitted to the clutch shaft 1 inside the clutch drum 6 so as to rotate together with the clutch shaft 1. The clutch hub 8 is integrally formed with a flange portion 8a extending in the circumferential direction and a hub portion 8b extending in the axial direction, and an outer circumferential spline 8c is formed on the outer periphery of the hub portion 8b. This outer peripheral spline 8C has a plurality of internal clutch plates 9.
are arranged so as to be alternately located with respect to the external clutch, temporary 7.

Reference numeral 10 denotes a clutch piston fitted into a hydraulic pressure chamber 11 formed in the piston housing 3 so as to be able to move forward and backward. is being energized.

Reference numeral 13 denotes a first clutch oil supply passage formed in the axial direction of the clutch shaft 1, and this clutch oil supply passage 13 and the hydraulic pressure chamber 11 are connected through a hydraulic branch passage 14 and an auxiliary hydraulic pressure chamber 15.

Then, when clutch oil is supplied to the auxiliary hydraulic pressure chamber 15 and the hydraulic pressure chamber 11 via the clutch oil supply path 13 and the hydraulic branch path 14, the clutch piston 10 is moved to the spring 12 by the hydraulic pressure.
The pressing protrusion 10a of the clutch piston 10 strongly presses the clutch plates 7, 9 against the flange 8a of the clutch hub 8. At this time, since contact friction occurs between the clutch plates 7 and 9, the power of the clutch shaft 1 is transferred to the clutch hub 8. It is transmitted to the output gear 4 via the clutch plates 7 and 9 and the clutch drum 6.

On the other hand, when clutch oil is not supplied to the hydraulic pressure chamber 11 and the auxiliary hydraulic pressure chamber 15, the clutch piston 10 is pushed back toward the piston housing 3 side by the spring force of the spring 12 and separated from the clutch plates 7 and 9, and the clutch piston 10 is separated from the output gear 4. Power transmission with the clutch shaft 1 is cut off.

Next, in the hydraulic clutch mechanism disposed on the right side with respect to the piston housing 3, 16 is an output gear,
It is attached to the clutch shaft 1 via a needle bearing 17 so as to be relatively rotatable, and has a tooth portion 16a that meshes with another gear group (not shown).

Reference numeral 18 designates a clutch drum that is integrally fitted to the output key 716, and has an inner circumferential spline 18a formed on its inner circumference, and a plurality of external clutch plates 19 are arranged on the inner circumferential spline 18a.

A clutch hub 20 is provided inside the clutch drum 18 and is spline-fitted to the clutch shaft 1 and rotates together with the clutch shaft 1. The clutch hub 20 is integrally formed with a flange portion 20a extending in the circumferential direction and a hub portion 20b extending in the axial direction, and an outer circumferential spline 20C is formed on the outer periphery of the hub portion 20b. A plurality of internal clutch plates 21 are arranged on this outer circumferential spline 20G so as to be alternately positioned with respect to the external clutch plates 19.

Reference numeral 22 denotes a clutch piston fitted into the other hydraulic pressure chamber 23 formed in the piston housing 3 so as to be able to move forward and backward. Forced.

25 is the first clutch oil supply path 13 as shown in FIG.
A second clutch oil supply path is formed in the clutch shaft 1 in parallel with the clutch oil supply path 25 and the hydraulic pressure chamber 23.
A hydraulic branch passage 26 and an auxiliary hydraulic chamber 2 communicating with the hydraulic branch passage 26 are connected to
7 is connected.

Then, when the flange portion is supplied to the auxiliary hydraulic pressure chamber 27 and the hydraulic pressure chamber 23 via the clutch oil supply path 25 and the hydraulic branch path 26, the clutch piston 22 is moved to the spring 2 by the hydraulic pressure.
4 moves toward the clutch hub 20 side against the spring force of the clutch piston 22 or the clutch plate 19.
21 is strongly pressed against the flange portion 20a of the clutch hub 20.

At this time, since contact friction occurs between the clutch plates 19 and 21, the power of the clutch shaft 1 is transferred to the clutch hub 20.
．． It is transmitted to the output key 716 via the clutch plate 19.21 and the clutch drum 18.

On the other hand, when the flange portion is not supplied to the hydraulic pressure chamber 23 and the auxiliary hydraulic pressure chamber 27, the clutch piston 22
4 is pushed back toward the piston housing 3 side and separated from the clutch plate 19.21, so the output key 716
Power transmission between the clutch shaft 1 and the clutch shaft 1 is cut off.

The clutch oil supply passages 13, 25 and the stirring oil supply passage 28 formed in the clutch shaft 1 are arranged in an appropriate positional relationship as shown in FIG.

In this way, by independently controlling the connection and disconnection of the separately provided hydraulic clutch mechanisms, different reduction ratios can be set, and the power between the transmission gear group (not shown) and the clutch shaft 1 can be set. It is now possible to disconnect and disconnect.

In a hydraulic clutch device having piston mechanisms that can be operated independently, both clutch pistons 10 and 22 simultaneously operate the respective clutch hubs 8 and 22.
Clutch oil supply passages 13 and 25 so as not to move to the 20 side.
Hydraulic pressure supply control is performed.

That is, when one piston mechanism, for example, the piston mechanism on the right side in FIG. 2, is connected to the clutch hub 20 side and transmits the power of the clutch shaft 1 to the output key 716 to drive a speed change gear (not shown). does not supply hydraulic pressure to the left piston mechanism, the piston 10 is urged by the spring 12 and moves toward the piston housing 3, and therefore no power is transmitted from the clutch shaft 1 by the left clutch mechanism.

Conversely, when hydraulic pressure is supplied to the left hydraulic clutch device to transmit power, the piston 10 transmits the power of the clutch shaft 1 to the clutch hub 8, while the right hydraulic clutch device is supplied with hydraulic pressure. Leave it in a disconnected state without supplying it.

In addition, if hydraulic pressure is not supplied to both hydraulic clutch devices via the respective clutch oil supply channels 13.25, the clutch pistons 10.22 will be moved by the respective springs 12.24.
is urged to move toward the piston housing 3 side, and is set in a so-called neutral state.

(Problem to be Solved by the Invention) However, in the piston machine and groove of the hydraulic clutch device having such a configuration, the clutch piston is driven by hydraulic pressure supply and the clutch piston is moved toward the clutch hub side. The movement characteristics when the clutch piston is pushed back toward the piston housing by the spring force of the spring after the oil pressure supply is stopped are different.

For this reason, for example, if hydraulic pressure is supplied to the hydraulic clutch mechanism on the right side of FIG. 2 and hydraulic pressure is not supplied to the hydraulic clutch mechanism on the left side, and the hydraulic pressure supply is reversed, that is, the hydraulic pressure on the left side is When hydraulic pressure is supplied to the pressure clutch device and the hydraulic pressure supply to the right hydraulic clutch device is stopped to switch the transmission gear group, the clutch piston 22 of the right hydraulic clutch device is still sufficiently removed from the output key 716. Even though the clutch piston 10 of the left hydraulic clutch mechanism is not disengaged, the clutch piston 10 of the left hydraulic clutch mechanism is connected to the output gear 4, resulting in a so-called double chorus situation.

(Means for solving the problems) The present invention was made in view of the above problems, and
The purpose of the present invention is to provide a piston mechanism for a hydraulic clutch device that can prevent the occurrence of so-called double chorus,
To achieve this purpose, a clutch hub is provided integrally with a clutch shaft, a clutch piston is movable forward and backward toward the clutch hub, and a clutch plate is disposed between the clutch piston and the clutch hub. and a pair of piston mechanisms configured such that the clutch piston presses the clutch plate against the clutch hub,
A hydraulic mechanism that includes a first hydraulic mechanism that uses hydraulic pressure to move the clutch piston of one piston mechanism toward the clutch plate, and a second hydraulic mechanism that uses hydraulic pressure to move the clutch piston of the other piston mechanism toward the clutch plate. In the pressure clutch device, a third hydraulic pressure 1NG is applied to move the clutch piston of the one piston mechanism in a direction in which it is released from the clutch plate by the hydraulic pressure of the second hydraulic mechanism, and a third hydraulic pressure 1NG is applied to move the clutch piston of the other piston mechanism in the direction of releasing the clutch piston from the clutch plate. and a fourth hydraulic mechanism that moves the clutch plate in the releasing direction using the hydraulic pressure of the first hydraulic mechanism, and is characterized in that the clutch pistons of the respective piston mechanisms move quickly when they are separated from the clutch plate.

(Embodiment) FIG. 1 is a sectional view of a main part showing an embodiment of a piston mechanism of a hydraulic clutch device according to the present invention.

Note that the same or equivalent parts as in FIG. 2 are given the same reference numerals.

Clutch pistons 10.22 are fitted into hydraulic chambers 11.23 formed on both sides of a piston housing 3 integrally fixed to the clutch shaft 1 so as to be movable forward and backward.

A plurality of external clutch plates 7 are disposed on an inner circumferential spline 6a formed on the inner circumference of a clutch drum 6 that is integrally fitted to the output gear 4.

A clutch hub 8 disposed inside the ram 6 is integrally fixed to the clutch shaft 1 by spline fitting.
゜The clutch 18 has a flange portion 8 extending in the circumferential direction.
a, the hub portion 8b and the recessed portion 8d extending in the axial direction are -1,
3) at the axial end of the recess 8d.
A recessed step portion for locking one end of the turn spring 12 is formed.

Hydraulic pressure chamber 1 (, clutch piston installed in the river 10
A cylindrical portion -10b is formed at the end opposite to the recessed portion 8d in ih, and the cylindrical portion 10b is slidably fitted into the recessed portion 8d, and is formed between the recessed portion 8d and the cylindrical portion 10b. Sealed room 30
The clutch piston 10 is elastically biased toward the piston housing 3 by a return spring 2 provided therein. The sealed chamber 30 communicates with the clutch oil supply path 13 via a hydraulic branch path 31 formed in the clutch shaft 1 .

A lubricating oil branch passage 32a communicating with a lubricating oil branch passage 32 extending from the lubricating oil supply passage 28 of the clutch shaft 1 is formed in the recess 8d of the clutch hub 8, and a lubricating oil branch passage 32a is formed in the recess 8d of the clutch hub 8.
I'm looking forward to the supply of lubricating oil.

The hydraulic pressure chamber 11 is connected to a second clutch oil supply path 25 via an auxiliary hydraulic pressure chamber 15 and a hydraulic branch path 14 that communicates with the n1 hydraulic pressure chamber 15.
is connected to.

Next, in the hydraulic clutch mechanism disposed on the right side with respect to the piston housing 3, a plurality of external clutch plates 19 are disposed on an inner circumferential spline 18a formed on the inner circumference of the clutch drum 18. . A clutch hub 20 is integrally fixed to the clutch shaft 1 inside the clutch drum 18 by spline fitting.

The clutch hub 20 includes a flange portion 20a extending in the circumferential direction, a hub portion 20b and a recess portion 20d extending in the axial direction.
are integrally formed, and a recessed step portion for locking one end of a return spring 24 made of a coil spring is formed at the axial end of the recessed portion 20d.

The clutch piston 22 fitted into the hydraulic pressure chamber 23 includes
A cylindrical portion 22b is formed at an end opposite to the recess 20d, and the cylindrical portion 22b is slidably fitted into the recess 20d, and is inserted into a sealed chamber 33 formed between the recess 20d and the cylindrical portion 22b. The clutch piston 22 is elastically biased toward the piston housing 3 by a return spring 24 provided. The sealed chamber 33 is connected to the second clutch oil supply path 25 via a hydraulic branch path 34 formed in the clutch shaft 1 .

A lubricating oil supply path 28 is provided in the recess 20d of the clutch hub 20.
The lubricating oil branch path 3 that extends further and communicates with the lubricating oil branch path 35
5a is formed to supply lubricating oil to the clutch hub 20 side. The hydraulic pressure chamber 23 is connected to the first clutch oil supply path] 3 via an auxiliary hydraulic pressure chamber 27 and a hydraulic branch path 26 communicating with the auxiliary hydraulic pressure chamber 27.

Further, a pressure discharge hole 3a is formed in the side end of the piston housing 3, and valves 11a and 23a are provided between the hydraulic pressure chamber 11 and the pressure discharge hole 3a, and between the hydraulic pressure chamber 23 and the pressure discharge hole 3a, respectively. This prevents an unnecessary increase in pressure in the hydraulic chamber 11.23.

Next, the operation of the hydraulic clutch mechanism having such a configuration will be explained.

As shown in the figure, when no hydraulic pressure is supplied to either of the hydraulic pressures 11 and 23 via the clutch oil supply path 13.25, the clutch piston 10 is moved by the spring force of the return spring 12, and the clutch piston 22 is return spring 2
4 are moved toward the piston housing 3 side by the spring force of the clutch shaft 1, so that the power of the clutch shaft 1 is not transmitted to the clutch drum 6 and the clutch drum 18, which is a so-called neutral state.

Here, when hydraulic pressure is supplied to the auxiliary hydraulic pressure chamber 15 and the hydraulic pressure chamber 11 via the clutch oil supply path 25 and the hydraulic branch path 14, the clutch piston 10 resists the spring force of the return spring 12 and the clutch plate 7, 9 is pressed into contact with the clutch hub 8, and the power of the clutch shaft 1 is transmitted to the clutch drum 6 via the clutch hub 8 or the clutch plates 7, 9, and the clutch mechanism on the left side of the figure is brought into a connected state.

By the way, if hydraulic pressure is supplied through the clutch oil supply path 25 while no oil pressure is supplied to the clutch oil supply path 13,
Hydraulic pressure is not only supplied to the hydraulic pressure chamber 11 but also to the hydraulic branch path 3.
4 to the closed chamber 33, and the clutch piston 22 is urged toward the clutch housing 3 by the spring force of the return spring 24 and hydraulic pressure, and becomes stationary.

Next, in this state, if the hydraulic pressure supply from the clutch oil supply path 13° 25 is reversed, that is, the supply of hydraulic pressure from the clutch oil supply path 25 is stopped and, conversely, the oil pressure is supplied from the clutch oil supply path 13. Like 1;7JJ! In the case of A control, the clutch piston 22 is moved to the return spring 24 by the hydraulic pressure supplied from the clutch oil supply path 13 to the sub-hydraulic pressure chamber 27 and the hydraulic pressure chamber 23 via the hydraulic branch path 26.
The clutch shaft 1 moves toward the clutch hub 20 against the spring force, and the power of the clutch shaft 1 is transmitted to the output key 716 via the clutch piston 22 or the clutch hub 20, and the right clutch mechanism becomes connected.

Here, although hydraulic pressure is not supplied to the hydraulic pressure chamber 11 of the piston mechanism on the left side of the figure, hydraulic pressure is supplied from the clutch oil supply path 13 to the sealed chamber 30 via the hydraulic branch path 31.
The clutch piston 10 moves toward the piston housing 3 in response to the spring force of the return spring 12 and hydraulic pressure. At this time, the speed at which the clutch piston 22 moves toward the clutch hub 20 side and the speed at which the clutch piston 10 moves toward the piston housing 3 side are equal, or the speed at which the clutch piston 10 moves toward the piston housing 3 side is faster. It is set to be.

This movement characteristic is set by the spring force of the return springs 12 and 24 and the amount of hydraulic pressure supplied to the hydraulic chamber 23 and the sealed chamber 30 per unit time.

In this way, at least the clutch piston 10 is connected to the clutch and temporary 7 before the clutch piston 22 is connected.
, 9, so that so-called clutch double chorus does not occur during clutch switching.

Next, when the clutch mechanism on the right side of the figure is in a connected state and the clutch mechanism on the left side is in a disengaged state, conversely, when hydraulic pressure is supplied to the hydraulic pressure chamber 11 and the supply of hydraulic pressure to the hydraulic pressure chamber 23 is stopped. , the clutch piston 10 is the return spring 1
The other clutch piston 22 moves toward the clutch hub 8 side against the spring force of the second clutch hub 8 and becomes connected, and the other clutch piston 22 is moved toward the piston housing 3 side by the spring force of the return spring 24 and the action of the oil pressure in the sealed chamber 33. The clutch becomes disengaged. In this case as well, the clutch piston 22 is moved not only by the spring force of the return spring 24 but also by the hydraulic pressure in the sealed chamber 33, so it can move at a speed equal to or faster than the moving speed of the clutch piston 10. Therefore, a double clutch state does not occur.

As explained above, according to this embodiment, the hydraulic pressure supplied to the hydraulic pressure chamber of one piston mechanism is also supplied to the sealed chamber of the other piston mechanism, and the clutch piston on the side where the clutch is disengaged is operated by the spring of the clutch piston. Since it is driven by the action of force and hydraulic pressure in a sealed chamber, the clutch piston on the side to which the clutch is connected separates before it connects to the clutch plate, so it is possible to prevent a double chorus from occurring.

(Effects of the Invention) As explained above, according to the piston mechanism of the hydraulic clutch device of the present invention, the return operation of the clutch piston becomes faster, so it is possible to prevent the occurrence of a double chorus state of the clutch.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of essential parts of an embodiment of a hydraulic clutch device according to the present invention, FIG. 2 is a cross-sectional view of a conventional hydraulic clutch device, and FIG. 3 is a cross-sectional view taken along line A-A in FIG. It is a diagram. 1: Clutch shaft 3: Piston housing 7.19': External clutch plate 8.20: Clutch hub 8d, 20d: Recessed portion 9.21: Internal clutch plate 10.22: Clutch piston 10b, 22b: Cylindrical portion 11.23: Hydraulic pressure chamber 13: First clutch oil supply path 25: Second clutch oil supply path 30.33: Sealed chamber 31.34: Hydraulic branch path

Claims (1)

[Claims] A clutch hub integrated with the clutch shaft,
It has a clutch piston that can move forward and backward toward the clutch hub, and a clutch plate disposed between the clutch piston and the clutch hub, and the clutch piston presses the clutch plate against the clutch hub. A first piston mechanism is provided with a pair of piston mechanisms configured to move the clutch piston of one piston mechanism toward the clutch plate side using hydraulic pressure.
and a second hydraulic mechanism that moves the clutch piston of the other piston mechanism toward the clutch plate side using hydraulic pressure, the clutch piston of the one piston mechanism is moved by the second hydraulic pressure. a third hydraulic mechanism that moves the clutch piston of the other piston mechanism in the direction of release from the clutch plate using the hydraulic pressure of the mechanism; and a fourth hydraulic mechanism that moves the clutch piston of the other piston mechanism in the direction of release from the clutch plate using the hydraulic pressure of the first hydraulic mechanism. A hydraulic clutch device characterized by being equipped with a hydraulic mechanism.