JP2840986B2 - Hydraulic operated clutch - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulically operated clutch interposed between an engine and a transmission in an automobile.

[0002]

2. Description of the Related Art FIG. 3 is a side sectional view showing a conventional hydraulically operated clutch. A clutch disc 4a is connected to an input shaft 4 of a transmission (not shown).
The pressure receiving body 6 is screwed to a flywheel body 5 directly connected to an engine (not shown), and a cylinder body 5 d fitted to the pressure receiving body 6 so as to be slidable in the axial direction is attached to the flywheel body 5. fitted to Kezu設the splines 5b, plexes petri plate 5a is screwed into the cylinder body 5d, the ring-shaped piston 7 between the pressure receiving body 6 and the cylinder body 5d, possible sliding in the axial direction Mated, thereby displacing chamber B
And C are formed. The illustration of the pressure oil passages to the respective displacement chambers B and C is omitted.

Hereinafter, the operation in FIG. 3 will be described.
In a state where the engine, that is, the flywheel body 5 is rotating, and the rotation of the input shaft 4 in the transmission is stopped, the pressurized oil is supplied to the displacement chamber B, and the displacement chamber C is illustrated. When slide into open non reservoir, the hydraulic pressure generated in the displacement chamber B, the piston 7 slide into pressing migrate pressure over the plate 5a to the left. As a result, the clutch disk 4a is moved to the clutch surface 5e.
And grip by the pressure plate 5a (gri)
p) It will be done. Then, the rotational force of the flywheel body 5, that is, the output torque from the engine, is applied to the clutch surface 5e.
And transferred from plexes petri plate 5a in the clutch disk 4a, i.e. Yuki engaged clutch engagement, the torque is transmitted to the input shaft 4, Yuku by starting the motor vehicle.

[0004] The operation of releasing the clutch engagement is the reverse of the above-described case, in which the displacement chamber B is opened to the reservoir and the pressure oil is supplied to the displacement chamber C. Then, the hydraulic pressure generated in the displacement chamber C is pressed to shift the cylinder member 5d to the right relative to the pressure receiver 6, Yuku return the plexes petri plates 5a rightward. As a result, the engagement between the clutch disc 4a and the flywheel body 5 is released, and the power transmission between the engine and the drive wheels of the vehicle is cut off. Further, the operation for engaging or disengaging the clutch during the shifting of the transmission is performed in the same manner.

[0005] In the above operation, the operation of the plexes petri plate 5a, as described above, the pressure oil in the displacement chamber B is supplied done engagement of the clutch, the pressure oil in the displacement chamber C is supplied The clutch is disengaged. In this case, the displacement chambers B and C are
Since it rotates integrally with the flywheel body 5, the hydraulic oil in the displacement chambers B and C has a hydraulic component generated by the rotational centrifugal force. Therefore, if there is a difference between the hydraulic components generated from the rotational centrifugal force in each of the displacement chambers B and C, disturbance will be given to the control of the clutch engagement.

However, in FIG. 3, each of the outer shape d and the inner diameter e in the displacement chamber B coincides with each of the outer shape d and the inner diameter e in the displacement chamber C.
Therefore, the hydraulic components due to the centrifugal force generated in both the displacement chambers B and C are equal.

[0007]

SUMMARY OF THE INVENTION FIG.
Is such that the hydraulic components due to the centrifugal force generated in the two displacement chambers B and C are equal. However, for the purpose of equalizing the centrifugal force components, the cylinder body 5d that slides in the axial direction and the displacement chamber C having the same size as the displacement chamber B are configured, which complicates the configuration and increases the displacement. The result is an increase in weight. SUMMARY OF THE INVENTION It is an object of the present invention to provide a hydraulically operated clutch in which the complexity and weight of such a configuration are improved.

[0008]

The present invention SUMMARY OF THE INVENTION comprises a plexes petri plates to allow sliding to and axially rotate together with the flywheel body rotating integrally with the engine output shaft, in that the flywheel body A clutch disk interlocked with the input shaft is interposed between the clutch surface and the axial direction.
ing.

[0009] Then, the sliding of the opposite side of the clutch disc in the axial direction of the plexes petri plates were Kezu設the cylinder to the flywheel body in a state of Tsutsumi設radial about the input shaft, the axial direction on the cylinder The piston is fitted so that A pressure oil passage is communicated from a bearing portion to the displacement chamber formed by the cylinder and the piston via the flywheel body. That is, the clutch can be engaged by forcing the pressure oil from the pressure oil passage to the displacement chamber, and the engagement is released by opening the displacement chamber to the reservoir or the atmosphere.

In addition, the flywheel body forms a chamber in which the hydraulic oil is always present in a state where the clutch disk is wrapped, and between the chamber and the bearing portion , apart from the pressure oil passage, The first feature is that an oil passage formed in the flywheel body is provided. This means the following. In the engagement or disengagement of the clutch, the operation of the piston pushes the space in the chamber. Therefore, the displaced hydraulic oil requires exchange of the hydraulic oil with any space. In this case, the exchange is performed with an external reservoir or the like via the oil passage.

A second feature is that the oil passage is opened to the chamber in the radial direction so as to open to both sides of the cylinder in the radial direction. Means The displacement chamber rotates with the flywheel body, which rotates integrally with the engine, so that even when the displacement chamber is open to the reservoir, the displacement chamber is formed in the displacement chamber. A hydraulic pressure is generated due to the rotating centrifugal force. Since the above-mentioned chamber also rotates by the rotation of the flywheel body, the hydraulic oil in the chamber also generates hydraulic pressure due to the rotational centrifugal force. Therefore, the force for pushing the piston toward the chamber by the oil pressure of the centrifugal force component generated in the displacement chamber and the force for pushing back the piston by the oil pressure of the centrifugal force component generated in the chamber are as follows. The direction of cancellation is in a direction in which the hydraulic component of the rotational centrifugal force in the displacement chamber and the hydraulic component of the rotational centrifugal force in the chamber are balanced.

However, a clutch disk having a different rotation speed when the clutch is disengaged exists in the above chamber. Therefore, the rotational speed of the hydraulic oil in the chamber is different from the rotational speed of the displacement chamber, and the pressure of the rotational centrifugal force component cannot be balanced. Therefore, in the present invention, an oil passage that rotates completely integrally with the flywheel body, and the oil passage at the position of the displacement chamber is opened to the chamber to perform the pressure equilibrium. . That is, the equilibrium is performed by blowing out the oil pressure of the oil passage having the same rotational speed component as the displacement chamber at the displacement chamber position in the radial direction of the chamber.

[0013]

FIG. 1 is a side sectional view of a hydraulic operating clutch according to the present invention. A clutch disk 1a is connected to an input shaft 1 of a transmission (not shown).
The illustrated have no spline 2m flywheel body 2 directly connected to the engine, the pressure plate 2a is fitted, the shaft 2f fixed to the flywheel body 2, bearing portions 3
Rotation slidably fitted into the axial 2f is to Kezu設each groove 2h and 2g on its periphery, the bearing portion 3 is fixed in the housing of the transmission. A piston 2c is fitted in the cylinder 2b cut in a ring shape on the flywheel body 2 so as to be slidable in the axial direction, and a displacement chamber 2d has a perforation 2e.
It is connected to a hydraulic switching valve (not shown) through a groove 2h and a hole 3a cut on the circumference of the shaft 2f.

The chamber A containing the clutch disk 1a is always filled with hydraulic oil, and the chamber A is opened with the two perforations 2k and 2j through the perforations 3b and 2i communicating with the external reservoir. The open position is a position to open to both sides in the radial direction of the cylinder 2b. A spring 2p is interposed between the pressure plate 2a and the flywheel body 2.

The operation of the above embodiment will be described below. When the transmission is set to the first speed and the hydraulic switching valve is switched so that the hydraulic source communicates with the perforation 3a, the pressure oil at the hydraulic source is supplied to the perforation 3a, the groove 2h and the perforation 2e.
And is pressure-fed to the displacement chamber 2d. This means that the pressure oil fed to the displacement chamber 2d presses and shifts the piston 2c to the right and urges the pressure plate 2a toward the clutch surface 2n. As a result, the clutch disk 1 is formed by the clutch surface 2n and the pressure plate 2a.
a is in the engaged clutch engagement state, the rotational force of the flywheel body 2, that is, the power from the engine is transmitted to the gripped clutch disc 1a and the input shaft 1, and the vehicle starts moving. . Also, as the piston 2c moves to the right, the hydraulic oil in the chamber A is displaced, and the displaced hydraulic oil moves from the perforations 2j and 2k to the perforations 2i,
It is opened to an external reservoir via the groove 2g and the perforation 3b.

Conversely, when the clutch engagement is disengaged, the hydraulic switching valve is switched to open the displacement chamber 2d to the reservoir. G is pushed back to the left, and the clutch engagement is released. The above explanation is
Although the clutch engagement and disengagement at the time of starting the automobile have been described, the operation of engaging or disengaging the clutch at the time of shifting the transmission is the same.

In the above operation, the spring 2p
Has a function of pushing back the pressure plate 2a when the clutch is disengaged. However, even if the spring 2p is omitted, the clutch can be basically disengaged. When the displacement chamber 2d is opened to the reservoir, the pressure plate 2a is
a cannot be gripped, and the clutch can be disengaged. However, if the pressure plate is kept in contact during the disengagement, a drag torque to the clutch disk 1a due to the rotation of the pressure plate 2a is generated on the transmission side, and the speed change during the transmission shift is performed. It becomes necessary to increase the operating force. From such a thing,
If it is necessary to reduce the shift operation force, the spring 2p is provided as such. Therefore, the spring 2p for pushing back may be pushed back by a hydraulic piston or the like.

The hydraulic operation clutch shown in FIG. 1 is operated as described above, but the following phenomena occur in the operation during the operation. For example, as described above, the clutch disc 1
a is stopped at the beginning of its start.
Therefore, the end face a of the pressure plate 2a
FIG. 2 shows the flow velocity distribution of the hydraulic oil in the rotational circumferential direction between the clutch oil and the end face b of the clutch disk 1a.
That is, the rotational circumferential flow velocity of the hydraulic oil in contact with the end surface a of the pressure plate 2a matches the rotational speed of the pressure plate 2a, and the rotational circumferential flow speed of the hydraulic oil in contact with the end surface b of the clutch disc 1a. The flow rate is the clutch disc 1a
Is equal to the stopped zero rotation speed. In addition, the flow velocity distribution of the hydraulic oil during that time becomes a state in which the flow velocity uniformly changes in proportion to the distance between the end faces a and b from the state of zero flow velocity of the end face b toward the rotation speed of the end face a. ing.

[0019] For this reason, the average velocity between the end face a and the end surface b is that corresponds to half the rotational speed of the plexes petri plate 2a. In contrast, the hydraulic oil in the displacement chamber 2d is plexes petri plates 2a
It rotates at the same rotation speed as. Here, temporarily
Perforations 2j and 2k are not open to chamber A,
Further, it is assumed that even if the hydraulic oil in the chamber A is displaced by the compression or expansion of the chamber A, the displaced hydraulic oil can enter and leave the external reservoir. In this case, the average flow velocity of the hydraulic oil in the rotation direction between the end face a and the end face b is の of the rotation speed n in the displacement chamber 2 d as described above, and The pressure increase due to the rotational centrifugal force of the hydraulic oil on the same radius has a property proportional to the square of the rotation speed n at which the hydraulic oil rotates around the input shaft 1. Therefore, the average pressure rise due to the rotational centrifugal force of the hydraulic oil between the end surfaces a and b becomes 1/4 of the pressure increase due to the rotational centrifugal force in the displacement chamber 2d. Become.

However, in FIG. 1, the perforations 2j and the perforations 2j are formed on both sides in the radial direction with respect to the outer and inner diameters of the cylinder 2b.
k is opened to the chamber A, so that the displacement chamber 2
The pressure rise of the hydraulic oil due to the centrifugal rotational force of d and the pressure rise due to the rotational centrifugal force of the hydraulic oil between the end surfaces a and b are substantially equal. The reason is as follows. The perforations 2j and 2k are located on both sides in the radial direction with respect to the outer and inner diameters of the cylinder 2d and communicate with the perforations 2i. The hydraulic pressure is blown out from the perforations 2i to the chamber A, and the hydraulic pressure at the radial position of the perforations 2j generated by the rotational centrifugal force is blown out from the perforations 2i to the chamber A.

From the above, in the chamber A, in the radial direction, the oil pressure at the radial position corresponding to the hole 2k is equal to the oil pressure at the radial position corresponding to the hole 2k, and at the radial position corresponding to the hole 2j. Is perforated 2
i is equal to the oil pressure at the radial position of the perforation 2j. In addition, the hydraulic pressure distribution in the radial direction of the hydraulic oil in the chamber A between the position of the outlet of the perforation 2k to the chamber A and the position of the outlet of the perforation 2j to the chamber A uniformly changes along the radial direction. Should be doing. Further, in this case, since the perforation 2i rotates integrally with the flywheel body 2 or the displacement chamber 2b, the rotation and centrifugation of each hydraulic oil in the perforation 2i and the displacement chamber 2d on the same radius from the input shaft 1. The pressure rise due to the force becomes the same value, and the pressure distribution in the perforation 2i is also 2j from the 2k position.
The pressure changes uniformly toward the position. Also in the displacement chamber 2d, from the inner diameter side (perforation 2k side) to the outer diameter side (perforation 2j side), the pressure distribution is the same as the radial pressure distribution of the perforation 2i.

Therefore, between the radial position of the perforation 2k and the radial position of the perforation 2j, the hydraulic component due to the rotational centrifugal force in the displacement chamber 2d and the hydraulic pressure in the chamber A are substantially equal. As a result, the component of the increase in hydraulic centrifugal force due to the rotation of the flywheel body 2 in the displacement chamber 2d and the component of pushing back the piston 2c by the hydraulic pressure in the chamber A are substantially balanced. In addition, as for the configuration of the perforations 2i and the perforations 2j and 2k communicating with the perforations 2i, a plurality of sets are disposed at equally dividing positions in the circumferential direction of the cylinder 2b.

[0023]

As is apparent from the above description, the hydraulically operated clutch according to the present invention does not require the provision of an auxiliary displacement chamber for canceling out the hydraulic component due to the rotational centrifugal force, and simply pierces the flywheel body. 2i, 2j and 2k
With a simple configuration in which only a hole is bored, the hydraulic pressure can be balanced by the rotational centrifugal force. In addition, the fact that there is no need to provide such an auxiliary displacement chamber reduces the weight of the flywheel body 2, and the weight reduction does not require the rotational inertia moment of the flywheel body 2. This also solves the problem of increasing the size.
Also, enabling the equilibrium of the hydraulic pressure by the rotational centrifugal force makes it possible to prevent disturbance due to the rotational centrifugal force component when automatically transmitting the hydraulic pressure to the displacement chamber 2d. Control becomes easy.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing a hydraulic operating clutch according to the present invention.

FIG. 2 shows a chamber A between end faces a and b in FIG.
2 shows the distribution of the flow velocity of the working oil in the rotation direction.

FIG. 3 is a side sectional view showing a conventional hydraulic operating clutch.

[Explanation of symbols]

1 input shaft, 1a clutch disc, 2 flywheel body, 2a pressure plate, 2b
Cylinder, 2c piston, 2d displacement chamber,
2e drilling, 2i, 2j and 2k drilling, 2n
Clutch surface, 2p spring.

Claims (1)

(57) [Claims] 1. A and plexes petri plates allow sliding and rotating integrally with the flywheel body rotating integrally with the engine output shaft to the axial direction, the axial direction of the clutch surface of the fly-wheel body during and through setting the clutch discs in conjunction with the input shaft, said at the clutch disc in the axial direction of the plexes petri plates opposite, cutting into the flywheel body in a state of Tsutsumi設radial about said input shaft A piston is fitted to the installed cylinder so that it can slide in the axial direction, and a pressure oil passage communicates with the displacement chamber formed by the cylinder and the piston from the bearing via the flywheel body. , The flywheel body forms a chamber in which the clutch disc is wrapped and hydraulic oil is always present,
An oil passage formed in the flywheel body is interposed between the bearing and the bearing, and the oil passage is opened to the chamber on both sides of the cylinder in the radial direction. Hydraulic clutch