JPH02221721A - Release bearing driving mechanism for clutch - Google Patents

Abstract

PURPOSE:To prevent losses and deviation of operating forces to exactly control operations of a release bearing by employing a direct-drive type commutatorless motor as a motor to provide a stator fixed to a stationary member and a rotor fixed directly to a rotary member. CONSTITUTION:A thrust roller 10 is rotated monolithically with a rotor 19, its rotary motion is transmitted as an axial motion to a sleeve piston 8 by a ball cam mechanism 20, and the sleeve piston 8 moves a release bearing 35 linearly. In such operations, since the ball cam mechanism 20 is incorporated in a power transmission path from a motor 14 to the release bearing 35, kinetic torque required for the motor 14 is small. Further, since the motor 14 is direct- drive type and directly transmits the motion of the rotor 19 to the thrust roller 10, the motor can operate the thrust roller 10 exactly and positively in response to the action of the rotor 19.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a release bearing displacement mechanism used in friction clutches of vehicles such as automobiles, and in particular improves the structure for driving the release bearing. be.

[Prior Art] Generally, in a friction clutch for an automobile, a release bearing for controlling the connection/disconnection operation of the clutch is connected to a clutch pedal via a mechanical connection mechanism such as a link mechanism or a lever mechanism.

Further, in some clutches, a hydraulic cylinder whose operating state can be controlled by a clutch pedal is provided outside the clutch housing, and the cylinder is mechanically connected to the release bearing via a connecting mechanism.

Further, JP-A-61-180028 discloses a structure in which a hydraulic cylinder is provided inside a clutch housing and the hydraulic cylinder is directly connected to a release bearing.

[Problems to be Solved by the Invention] However, in a structure using a mechanical coupling mechanism such as a link as described above, the release bearing may not be accurately controlled due to friction and deformation of various parts. Further, the friction and deformation described above also cause a loss of force transmitted to the release bearing, which causes a problem of reduced clutch operation efficiency, especially in a structure that combines a hydraulic cylinder and a mechanical coupling mechanism.

On the other hand, with a structure in which the hydraulic cylinder is directly connected to the release bearing as in the above-mentioned Japanese Patent Application Laid-Open No. 61-180028, the above problems regarding the connection mechanism can be solved, but it is necessary for the hydraulic cylinder to generate a large force that can directly drive the release bearing. As a result, the hydraulic cylinder becomes larger, and it is necessary to arrange such a cylinder in the axial direction of the clutch. As a result, the clutch becomes large in size, particularly in its axial dimension. Furthermore, it is necessary to extend the hydraulic line for the hydraulic cylinder to the inside of the clutch housing, and the structure becomes complicated due to measures such as hydraulic seals on sliding parts.

The present invention aims to provide a structure that solves the above problems.

[Means for Solving the Problems] In order to achieve the above object, the present invention provides a rotating member connected to a motor, an axially moving member supported by a stationary member so as to be movable only in the axial direction, a motion conversion mechanism that transmits the rotational motion of the rotating member as the axial motion to the axially moving member; and a release bearing coupled to the axially moving member; the motor is a direct drive type non-commutator motor; a stator fixed to the stationary member;
The rotor is directly fixed to the rotating member.

[Operation] According to the above structure, the rotating member is directly driven by the motor, and more specifically, by rotating the rotating member integrally with the rotor, the rotational movement is converted into axial movement by the motion conversion mechanism. is transmitted to the axially moving member, which causes the release bearing to move linearly.

In the above operation, since a motion conversion mechanism is interposed in the power transmission path from the motor to the release bearing, the driving torque required of the motor is small.

Furthermore, in the above operation, the motor is of a direct drive type, and the motion of the rotor is directly transmitted to the rotating member, so that the rotating member can be operated accurately and reliably in response to the operation of the motor.

[Embodiment] In FIG. 1, the input side end of the input shaft 2 (only the center line is shown) of the transmission projects from the clutch housing 1 to the left in FIG. A housing sleeve 3 is arranged concentrically around the protruding end of the human power shaft 2.

The housing sleeve 3 is provided on the inner periphery of the housing 1, and the fixed sleeve 5 is fixedly fitted on the outer periphery of the housing sleeve 3. A cylindrical slave piston 8 is fitted onto the outer periphery of the fixed sleeve 5 as will be described later.
A cylindrical thrust roller 10 is fitted onto the outer periphery of the roller as will be described later.

There are two or three phases on the radially outer side of the thrust roller 10.
A matching brush smoke 14 is arranged. Motor 1
4 is a direct drive type non-commutator motor, and thrust roller 10
directly driven. That is, the thrust roller 10 is configured to function as an output shaft of the motor 14,
Specifically, it is structured as follows. An annular stay 16 of the motor 14 has an inner circumferential portion fixed to an inner circumferential portion of the clutch housing 1 with a plurality of bolts. Stator 1
A ball bearing 12 is disposed between the radially intermediate portion of the thrust roller 6 and the end of the thrust roller 10. On the radially outer side of the ball bearing 12, the stator 16
A fill winding 17 is attached to the surface on the thrust roller 10 side. In the illustrated embodiment, the separate coil winding 17 is a 4-pole 6-coil winding, as shown in FIG. A stator structure having shaped magnetic poles and a coreless winding structure can be formed using a plastic mold. Although not shown, a control circuit is provided outside the housing 1 to operate in conjunction with the clutch pedal. The control circuit is electrically connected to the coil winding 17 and controls the excitation state of the coil winding 17.

A permanent magnet 18 (for example, a ferrite, rare earth, or alnico magnet) is arranged on the opposite side of the stator 16 with respect to the coil winding 17 . The back surface of the permanent magnet 18 (the surface opposite to the coil winding 17) is fixed to an annular rotor 19 (magnetic yoke).

The inner circumference of the rotor 19 is fixed to the outer circumference of the thrust roller 10 by welding or the like. Therefore, when the motor 14 is operated to rotate the rotor 19, the thrust roller 10 rotates together with the rotor 19. The motor 14 is of a direct drive type, and has a characteristic of generating large torque at a low rotational speed.More specifically, the motor 14 is set to a characteristic that can control the connection/disconnection operation of the clutch, as will be described later.

The outer cylindrical portion of the rotor 19 extends to the vicinity of the outer periphery of the stator 16, and a magnetic sensor 50 (Hall element) is provided between the two. The magnetic sensor 50 is connected to an external control device and sends a detection signal regarding the rotational angular position of the rotor 19 to the control device.

On the radially outer side of the magnetic sensor 50, the rotor 19
A dust cover 51 made of a soft rubber film is attached to the outer periphery of the stator 16.

When the motor 14 is operated as described above, the thrust roller 10 rotates around the input shaft 2. In order to transmit the rotational motion to the slave piston 8 as an axial motion parallel to the input shaft 2, the slave piston 8 A ball cam mechanism 20 (motion transmission mechanism) is located between the thrust roller 10 and the thrust roller 10.
A rotation prevention mechanism 21 is provided between the slave piston 8 and the fixed sleeve 5.

The ball cam mechanism 20 includes three or more balls 22 (only one is shown) arranged at intervals in the circumferential direction of the slave piston 8. Each ball 22 is partially rotatably accommodated in a hemispherical ball holding hole 25 provided on the inner peripheral surface of the thrust roller 10, and partially accommodated in a cam groove 26 provided on the outer peripheral surface of the slave piston 8. They are properly mated.

FIG. 3 is a developed view of the outer peripheral surface of the slave piston. As is clear from FIG. It is set appropriately depending on the desired operating characteristics of the bearing mechanism.

As shown in Figure 1, slave piston 8 and thrust roller 1
An annular retainer 24 is disposed between the balls 22, and the plurality of balls 22 are held by the retainer 24 to maintain a constant relative positional relationship.

The rotation prevention mechanism 21 includes a plurality of rollers 28 (only one is shown) arranged at intervals in the circumferential direction of the fixed sleeve 5. Each roller 28 includes a short shaft 29 extending in the radial direction of the fixed sleeve 5, and an outer race 31 that fits around the shaft 29 via a plurality of small diameter rollers 30. The shaft 29 projects further inward in the radial direction than the roller 30 and the outer race 31, and its projecting portion fits into the hole of the fixing sleeve 5 and is fixed. The outer race 31 is a groove 32 provided on the inner peripheral surface of the slave piston 8.
is fitted. The groove 32 extends in the axial direction of the slave piston 8.

The rotation prevention mechanism 21 connects the slave piston 8 to the fixed sleeve 5 so as to be movable only in the axial direction. Therefore, when the thrust roller 10 is rotated by the motor 14, the slave piston 8 is moved in the axial direction by the action of the ball cam mechanism 20.

A release bearing 35 is connected to the slave piston 8. The release bearing 35 is connected to the inner circumference of a diaphragm spring of a clutch (not shown). When the release bearing 35 moves in the same direction due to the axial movement of the slave piston 8, the diaphragm spring is deformed and the connection/disconnection operation of the clutch is controlled, similar to a numerical latch. In a pull type clutch, the clutch is disconnected by pulling the inner circumference of the diaphragm spring toward the housing 1 side by the release bearing 35. However, when adopting the structure shown in the figure for such a latch, the inclination of cam #26 The direction is set in reverse.

The release bearing 35 is located on the opposite side of the housing 1 with the slave piston 8 interposed therebetween, and includes an outer race 36, a ball 37, and an inner race 38. The slave piston 8 is integrally provided with an outward flange 40 at the end adjacent to the outer race 36, and the end face of the outer race 36 is in contact with the end face of the flange 40 so as to be slidable in the radial direction.

A cylindrical bearing cover 41 is provided around the outer race 36. Both ends of the cover 41 are bent inward in the radial direction, and one of the bent ends engages with the flange 40 from the side opposite to the outer race 36. The other bent end of the cover 41 faces the other end surface of the outer race 36, and a self-aligning spring 42 is interposed between the two in a compressed state in the axial direction. The action of the cover 41 and the spring 42 connects the outer race 36 to the slave piston 8 in the axial direction. Furthermore, if the release bearing 35 and the slave piston 8 are assembled in a relatively eccentric state, when the release bearing 35 rotates together with the diaphragm spring during operation, the outer race 36
automatically slides in the radial direction with respect to the slave piston 8, and quickly assumes a concentric positional relationship with the slave piston 8.

The inner lace 38 is the outer lace 36 and the cover 41
It protrudes to the side opposite to the housing 1, and its protruding end is connected to the diaphragm spring.

[Effects of the Invention] As described above, according to the present invention, the rotational force of the motor 14 disposed near the release bearing 35 is converted into axial movement by the ball cam mechanism 20 and transmitted to the release bearing 35. Therefore, unlike the conventional structure in which a mechanical coupling mechanism consisting of a lever mechanism or a link mechanism is placed between the driving force and the release bearing, this mechanism uses a circular balanced force to directly drive the mechanism. The operation of the release bearing 35 can be accurately controlled by preventing loss or deviation of operating force due to wear or deformation.

Further, according to the present invention, since the motor 14 is a direct drive motor, its characteristics (low rotational speed and large torque) are fully utilized to achieve the response speed (
approximately 1-2 rps).

Further, when an electric motor is used as the motor 14 as shown in the drawing, there is no need to extend the hydraulic line to the inside of the clutch housing, so the structure can be simplified and there is no fear of oil leakage.

[Brief explanation of the drawing]

′! 1S1 is a sectional view of an embodiment of the present invention, FIG. 2 is a schematic cross-sectional view taken along the line 1--2 in FIG. 1...Clutch housing, 5...Fixing sleeve,
8...Slave piston, 10...Thrust roller, 14...Motor, 16...Stator, one...
Rotor, 20... Ball cam mechanism, 35... Release bearing Patent applicant Daikin Seisakusho Co., Ltd.

Claims (1)

[Claims] 1. A rotating member connected to a motor, an axially movable member supported by a stationary member so as to be movable only in the axial direction, and the rotational movement of the rotating member as the axial movement. a motion converting mechanism for transmitting data to the axially moving member; and a release bearing coupled to the axially moving member, the motor being a direct-drive non-commutator motor, and a stator fixed to the stationary member; A clutch release bearing drive mechanism characterized by comprising a rotor directly fixed to a rotating member. 2. The clutch release bearing drive mechanism according to claim 1, wherein the stator of the motor has flat disk-shaped magnetic poles and a coreless winding structure, and is fixed to the clutch housing. 3. The clutch release bearing drive mechanism according to claim 1, wherein a dust cover made of a soft rubber film for dustproofing is provided on both outer peripheries of the rotor and stator of the motor. 4. The clutch release bearing drive mechanism according to claim 1, wherein the motor is a two-phase or three-phase brushless motor.