WO2013088901A1 - クラッチのアクチュエータ - Google Patents
クラッチのアクチュエータ Download PDFInfo
- Publication number
- WO2013088901A1 WO2013088901A1 PCT/JP2012/079761 JP2012079761W WO2013088901A1 WO 2013088901 A1 WO2013088901 A1 WO 2013088901A1 JP 2012079761 W JP2012079761 W JP 2012079761W WO 2013088901 A1 WO2013088901 A1 WO 2013088901A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- output member
- screw shaft
- nut
- clutch
- release mechanism
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
- F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal or cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D28/00—Electrically-actuated clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
- F16D27/14—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H2025/2053—Screws in parallel arrangement driven simultaneously with an output member moved by the screws
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H2025/2062—Arrangements for driving the actuator
- F16H2025/2075—Coaxial drive motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
- F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
- F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
- Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
- Y10T74/18704—Means to selectively lock or retard screw or nut
Definitions
- the present invention relates to an actuator, and more particularly to an actuator for driving a release mechanism of a clutch.
- a device using an electric motor has been developed as a device for putting a vehicle clutch device in a power transmission state (clutch on) or a power cutoff state (clutch off).
- an apparatus disclosed in Patent Document 1 includes a motor, a motion conversion mechanism that converts the rotational motion of the motor into a linear motion, and a mechanism for driving the release mechanism of the clutch by the linear motion converted by the motion conversion mechanism. And.
- the clutch device generally has a configuration in which the clutch disc is pressed by a diaphragm spring to turn on the clutch, and the pressing force of the diaphragm spring is released by a release mechanism to turn the clutch off. Therefore, in the apparatus as described above, when the release mechanism is operated and the clutch is turned off, the driving force may be applied from the release mechanism side due to the pressing force of the diaphragm spring. If the motor can rotate with respect to such reverse drive from the release mechanism side, the release mechanism side member cannot be fixed.
- the motion conversion mechanism is composed of a worm gear and a worm wheel, and self-locking is applied to reverse driving from the release mechanism side.
- the driving force from the motor is transmitted to the release mechanism side via the worm gear and the worm wheel.
- the transmission efficiency between the worm gear and the worm wheel is about 40 to 50%, which is very low. For this reason, in order to obtain a desired release force, a motor with a large output is required.
- An object of the present invention is to improve efficiency in driving a release mechanism, particularly in a clutch actuator for operating a release mechanism.
- the clutch actuator according to the first invention is for driving a clutch release mechanism, and includes an electric motor, an output member, a first drive mechanism, and a second drive mechanism.
- the output member is connected to the release mechanism and is movable in the operating direction of the release mechanism.
- the first drive mechanism converts the rotation of the electric motor in one direction into the movement of the output member in the first axis direction.
- the second drive mechanism has a self-lock function with respect to the reverse drive force from the release mechanism, and converts the rotation of the electric motor in the other direction into the movement of the output member in the second axial direction.
- the rotation of the electric motor in one direction is converted into the movement of the output member in the first axis direction by the first drive mechanism.
- the release mechanism is driven by the movement of the output member in the first axial direction.
- the reverse driving force is transmitted to the second driving mechanism. Since the second drive mechanism has a self-locking function against the reverse drive force from the release mechanism, the output member can be prevented from moving in the second axial direction, and as a result, the release mechanism side member is fixed. . Further, the rotation of the electric motor in the other direction is converted into movement of the output member in the second axial direction by the second drive mechanism.
- One drive mechanism can be composed of a mechanism with good transmission efficiency.
- the clutch actuator according to the second invention is the actuator according to the first invention, wherein the first drive mechanism is a ball screw mechanism for pushing the output member in the first axial direction by rotating the electric motor in one direction.
- the ball screw mechanism can transmit power with high efficiency, it is possible to reduce the size of the electric motor for driving the release mechanism.
- the actuator of the clutch according to the third invention is the actuator of the first or second invention, wherein the second drive mechanism transmits the reverse drive force from the output member, and the output member is rotated by the rotation of the electric motor in the other direction. It is a trapezoidal screw mechanism for moving in the second axis direction.
- the cell lock function can be realized with a simple mechanism.
- a clutch actuator is the actuator according to any one of the first to third aspects, wherein the ball screw mechanism includes a first screw shaft, a first nut, and a plurality of balls.
- the first screw shaft has a thread groove on the outer peripheral surface and is connected to the output shaft of the electric motor.
- the first nut has a thread groove on the inner peripheral surface, contacts the output member when rotating in one direction of the electric motor and moves the output member in the first axial direction, and outputs when rotating in the other direction of the electric motor. Move away from the member.
- the plurality of balls are disposed in the threaded grooves of the first screw shaft and the first nut.
- the clutch actuator according to the fifth invention is the actuator according to the fourth invention, wherein the trapezoidal screw mechanism has a second screw shaft and a second nut.
- the second screw shaft is rotated by the rotation of the electric motor in the other direction.
- the second nut is screwed onto the second screw shaft and self-locks with the second screw shaft when receiving the reverse driving force from the output member, and the output member when receiving the driving force from the second screw shaft. At the same time, it moves in the second axis direction.
- the release mechanism side member when a reverse driving force is applied from the release mechanism side, the release mechanism side member is fixed by self-locking between the second nut and the second screw shaft.
- the second nut moves in the second axial direction by the rotation of the second screw shaft.
- the clutch actuator according to the sixth invention is the actuator of the fifth invention, wherein the first screw shaft and the second screw shaft are arranged in parallel.
- the first nut has a protruding portion protruding toward the second screw shaft, and the second nut is slidably disposed in the axial direction on the protruding portion of the first nut.
- Such a configuration makes it possible to prevent the first nut of the ball screw mechanism from rotating without using a special member or mechanism.
- the actuator of the clutch according to the seventh aspect is for driving the release mechanism of the clutch, and includes an electric motor, an output member, a drive mechanism, and a second nut.
- the output member is connected to the release mechanism and is movable in the operating direction of the release mechanism.
- the drive mechanism includes a screw shaft that is rotated by an electric motor, and a first nut that is screwed to the screw shaft and connected to the output member.
- the second nut is screwed onto the screw shaft and engageable with the output member, and has a self-locking function against the reverse driving force from the output member.
- the rotation of the electric motor is converted into the movement of the output member by the drive mechanism.
- the release mechanism is driven by the movement of the output member.
- the reverse driving force is transmitted to the second nut. Since the second nut has a self-locking function with respect to the screw shaft of the drive mechanism, it can be prevented from moving against the reverse driving force from the output member, and as a result, the release mechanism side member is fixed. .
- the release mechanism when the release mechanism is driven, it is driven via the drive mechanism, and when the reverse drive force is applied from the release mechanism, it is self-locked between the second nut and the screw shaft. It can be configured with a mechanism with good transmission efficiency.
- the efficiency when the release mechanism is driven can be improved.
- FIG. 2 is an enlarged partial view of FIG. 1.
- FIG. 2 is an enlarged partial view of FIG. 1.
- FIG. 1 shows a clutch actuator 1 and a release mechanism 2 according to a first embodiment of the present invention.
- FIG. 1A shows a cross-sectional configuration of the actuator 1
- FIG. 1B shows a front view of a power transmission portion.
- the clutch side mechanism is not shown in the figure, but is a general clutch device configuration. That is, the clutch device includes a clutch cover assembly and a clutch disk assembly.
- the clutch device includes a clutch cover assembly and a clutch disk assembly.
- the clutch disc is pressed against the friction surface of the flywheel by the diaphragm spring, and the clutch is in an on state.
- the release mechanism 2 is actuated by the actuator 1 shown in FIG. 1, the pressure plate of the clutch cover assembly is moved away from the flywheel against the pressing force of the diaphragm spring, and the clutch is turned off. Become.
- the actuator 1 includes an electric motor (hereinafter simply referred to as “motor”) 3, a power transmission mechanism 4, a ball screw mechanism 5 as a first drive mechanism, a trapezoidal screw mechanism 6 as a second drive mechanism, And an output member 7.
- motor an electric motor
- ball screw mechanism 5 as a first drive mechanism
- trapezoidal screw mechanism 6 as a second drive mechanism
- output member 7 an output member 7.
- the motor 3 is fixed to the support block 10. As shown in FIG. 2, the rotating shaft 3 a of the motor 3 is rotatably supported on the support block 10 by a bearing 11.
- the power transmission mechanism 4 includes a first gear 13 and a second gear 14, a phase switching plate 15, and a phase switching pin 16.
- the first gear 13 has a disc-shaped gear portion 13a and a boss portion 13b protruding from the gear portion 13a to the motor 3 side.
- the boss portion 13 b is rotatably supported by the support block 10 via a bearing 18.
- the first gear 13 has a hole 13c penetrating in the axial direction at the center.
- the output shaft 3a of the motor 3 is inserted into one end of the hole 13c and is connected so as not to be relatively rotatable.
- the second gear 14 has a disc-shaped gear portion 14a and a boss portion 14b protruding from the gear portion 14a to the motor 3 side.
- the boss portion 14 b is rotatably supported by the support block 10 via two bearings 19 and 20.
- the second gear 14 has a hole 14c penetrating in the axial direction at the center.
- the phase switching plate 15 is arranged coaxially with the second gear 14 as shown in FIG.
- the phase switching plate 15 includes an inner peripheral disc portion 15a and a semicircular portion 15b formed on the outer periphery of the disc portion 15a.
- a through hole 15c (see FIG. 2) penetrating in the axial direction is formed at the center of the disc portion 15a.
- abut with the phase switching pin 16 are formed in the circumferential direction both ends of the semicircle part 15b.
- the phase switching pin 16 is fixed to the side surface of the second gear 14 on the output member 7 side, and protrudes to the phase switching plate 15 side. As described above, the phase switching pin 16 can abut on the circumferential end faces 15d and 15e of the semicircular portion 15b of the phase switching plate 15.
- the ball screw mechanism 5 includes a ball screw shaft (first screw shaft) 21, a ball screw nut (first nut) 22, and a plurality of balls 23.
- the ball screw shaft 21 has a helical thread groove on the outer peripheral surface. Further, one end of the ball screw shaft 21 is inserted into the through hole 13c of the first gear 13 and is connected so as not to be relatively rotatable. That is, the ball screw shaft 21 is connected to the motor 3 via the first gear 13, and the ball screw shaft 21 and the first gear 13 rotate in synchronization with the rotation of the motor 3.
- the ball screw nut 22 includes a screw portion 22a through which the ball screw shaft 21 is inserted, and a protruding portion 22b provided protruding from the screw portion 22a toward the trapezoidal screw mechanism 5 side. ,have.
- a spiral thread groove is formed on the inner peripheral surface of the screw portion 22a.
- a through hole 22c penetrating in the axial direction is formed in the protruding portion 22b.
- the plurality of balls 23 are arranged to roll freely in the thread groove of the ball screw shaft 21 and the thread groove of the ball screw nut 22.
- the trapezoidal screw mechanism 6 includes a trapezoidal screw shaft (second screw shaft) 26 and a trapezoidal screw nut (second nut) 27.
- the trapezoidal screw shaft 26 has a trapezoidal thread on the outer peripheral surface. One end of the trapezoidal screw shaft 26 is inserted into the through hole 14 c of the second gear 14 and is rotatably supported by the second gear 14 via the bush 28. Further, one end portion of the trapezoidal screw shaft 26 is inserted through the through hole 15c of the phase switching plate 15 and is fixed so as not to be relatively rotatable. That is, the trapezoidal screw shaft 26 is rotatable relative to the second gear 14, but rotates in synchronization with the phase switching plate 15.
- the trapezoidal screw nut 27 is screwed to the trapezoidal screw shaft 26.
- the trapezoidal screw nut 27 is inserted into a through hole 22c formed in the protruding portion 22b of the ball screw nut 22 so as to be rotatable and axially movable.
- the output member 7 is a block-shaped member and has a first recess 7a and a second recess 7b as shown in FIG.
- the first end surface 7c on the motor 2 side of the portion where the first recess 7a is formed and the second end surface 7d on the motor 2 side of the portion where the second recess 7b is formed are formed in steps, The end surface 7c is closer to the motor 3 side.
- the connection part 7e with which the end of the release fork 29 which comprises the release mechanism 2 is rotatably connected is formed in the release mechanism 2 side of the 1st recessed part 7a.
- the ball screw shaft 21 and a part of the ball screw nut 22 are inserted into the first recess 7a.
- the end surface 22d of the ball screw nut 22 can abut on the first end surface 7c on the first recess 7a side.
- a trapezoidal screw shaft 26 is inserted into the second recess 7b.
- the end surface 27a of the trapezoidal screw nut 27 can come into contact with the end surface 7d on the second recess 7b side.
- the rotation of the first gear 13 is transmitted to the second gear 14.
- the first gear 13 rotates clockwise in FIG. 1, and the second gear 14 rotates counterclockwise. Therefore, the phase switching pin 16 rotates in the same manner.
- the phase switching plate 15 does not rotate during the idling angle range in which the phase switching pin 16 is separated from the first end surface 15d of the phase switching plate 15 and contacts the second end surface 15e. That is, the trapezoidal screw shaft 26 does not rotate.
- the ball screw nut 22 moves in the A direction and comes into contact with the first end face 7c of the output member 7.
- the trapezoidal screw shaft 26 does not rotate, the trapezoidal screw nut 27 does not move in the A direction.
- a predetermined gap G1 is formed between the end surface 27a of the trapezoidal screw nut 27 and the second end surface 7d of the output member 7 as shown in FIG. Arise. This gap G1 is maintained while the motor 3 rotates in the first direction, and therefore power is not transmitted from the trapezoidal screw mechanism 6 to the output member 7.
- the elastic force F (see FIG. 1) of the diaphragm spring constituting the clutch device acts on the output member 7 in the direction B in FIG. That is, a driving force opposite to that described above is acting on the output member 7.
- the second end surface 7 d of the output member 7 comes into contact with the end surface 27 a of the trapezoidal screw nut 27.
- the trapezoidal screw nut 27 does not rotate due to the self-locking function of the trapezoidal screw mechanism 6. That is, the trapezoidal screw shaft 26 and the phase switching plate 15 fixed thereto do not rotate. Therefore, the phase switching pin 16 separated from the second end surface 15e of the phase switching plate 15 stops at a position between the second end surface 15e and the first end surface 15d.
- phase switching pin 16 is positioned between the second end surface 15e and the first end surface 15d of the phase switching plate 15. ing.
- the ball screw nut 22 can be prevented from rotating with a simple configuration.
- the actuator 51 includes a cylindrical case 52, an electric motor 53, a drive mechanism 54, a fixing screw nut 55, and an output member 56.
- the motor 53 is fixed to the side surface on one end side of the case 52.
- a rotation shaft 53 a of the motor 53 is rotatably supported by the case 52 by a bearing 60.
- the drive mechanism 54 is housed inside the case 52 and includes a ball screw shaft 61, a ball screw nut 62, and a plurality of balls 63.
- the ball screw shaft 61 has a helical thread groove on the outer peripheral surface.
- one end of the ball screw shaft 61 is connected to the rotation shaft 53 a of the motor 53 through a joint 64.
- the joint 64 is rotatably supported by the case 52 via a bearing 65.
- the ball screw nut 62 has a ball screw shaft 61 inserted therethrough, and a spiral thread groove is formed on the inner peripheral surface.
- a spline shaft 62 a is formed at one end of the outer peripheral surface of the ball screw nut 62.
- the plurality of balls 63 are arranged so as to roll freely in the thread groove of the ball screw shaft 61 and the thread groove of the ball screw nut 62.
- the fixing screw nut 55 is screwed to the ball screw shaft 61 on the release mechanism side of the ball screw nut 62.
- the fixing screw nut 55 has a self-locking function with respect to the ball screw shaft 61. When power is applied from the fixing screw nut 55 side, the fixing screw nut 55 does not rotate with respect to the ball screw shaft 61. Self-locked.
- FIG. 6 is a front view showing the relationship between the fixing screw nut 55 and the output member 56.
- the output member 56 is a member extending in a direction along the axis of the ball screw shaft 61, and includes a cylindrical portion 68 formed on the motor 53 side and a connecting portion 69 formed on the release mechanism 2 side of the cylindrical portion 68. And have.
- a ball screw shaft 61, a ball screw nut 62, and a fixing screw nut 55 are accommodated.
- a spline hole 68a is formed at the end of the cylindrical portion 68 on the motor 53 side, and the spline shaft 62a of the ball screw nut 62 is engaged with the spline hole 68a.
- a slit 68b penetrating in the radial direction is formed in a portion of the cylindrical portion 68 on the motor 53 side.
- a pair of detent portions 55a and 55b of the fixing screw nut 55 are inserted into the slit 68b so as to be rotatable within a predetermined angle range.
- a groove 68 c is formed along the axial direction on the outer peripheral surface of the cylindrical portion 68, and a similar groove 52 a is formed in a corresponding portion of the case 52.
- a rod 70 is inserted into these grooves 68c and 52a.
- a collar 74 is provided inside the output member 56.
- the collar 74 can contact or separate from the side surface of the fixing screw nut 55.
- One end of a release fork 29 constituting the release mechanism 2 is rotatably connected to the connecting portion 69.
- the detent portion 55b of the fixing screw nut 55 is in contact with the end surface B (see FIG. 6) of the slit 68b. In this case, a gap is generated between the fixing screw nut 55 and the collar 74.
- the elastic force of the diaphragm spring constituting the clutch device acts on the output member 56 in the direction B in FIG.
- the output member 56 and the ball screw nut 62 move in the B direction.
- the collar 74 comes into contact with the end face of the fixing screw nut 55, and the detent portion 55 b of the fixing screw nut 55 moves to the position A in FIG. 6, and power is transmitted to the fixing screw nut 55.
- the detent portion 55b of the fixing screw nut 55 is in contact with the end face C (see FIG. 6) of the slit 68b. In this case, a gap is generated between the fixing screw nut 55 and the collar 74.
- the ball screw mechanism is adopted as the first drive mechanism or the drive mechanism, but the present invention is not limited to this.
- a planetary roller screw mechanism may be used.
- the mechanism for self-locking is not limited to the trapezoidal screw mechanism. Other types of screw mechanisms may be used.
- the efficiency at the time of driving the release mechanism can be improved in the clutch actuator for operating the release mechanism.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Transmission Devices (AREA)
- Mechanical Operated Clutches (AREA)
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
Abstract
Description
図1に本発明の第1実施形態によるクラッチのアクチュエータ1及びレリーズ機構2を示している。図1(a)はアクチュエータ1の断面構成を示し、図1(b)は動力伝達部分の正面図を示している。
このアクチュエータ1は、電動モータ(以下、単に「モータ」と記す)3と、動力伝達機構4と、第1駆動機構としてのボールねじ機構5と、第2駆動機構としての台形ねじ機構6と、出力部材7と、を備えている。
図1及び図2に示すように、動力伝達機構4は、第1ギア13及び第2ギア14と、位相切替板15と、位相切替ピン16と、を有している。
ボールねじ機構5は、ボールねじ軸(第1ねじ軸)21と、ボールねじナット(第1ナット)22と、複数のボール23と、を有している。
台形ねじ機構6は、台形ねじ軸(第2ねじ軸)26と、台形ねじナット(第2ナット)27と、を有している。
出力部材7は、ブロック状の部材であり、図3に示すように、第1凹部7a及び第2凹部7bを有している。第1凹部7aが形成された部分のモータ2側の第1端面7cと、第2凹部7bが形成された部分のモータ2側の第2端面7dとは、段違いに形成されており、第1端面7cの方がモータ3側に、より近い。また、図1に示すように、第1凹部7aのレリーズ機構2側には、レリーズ機構2を構成するレリーズフォーク29の一端が回動自在に連結される連結部7eが形成されている。
<クラッチオン→クラッチオフ(レリーズ)時>
クラッチオフ(動力切断)の場合は、レリーズ機構2のレリーズフォーク29を図1においてR1方向に回転させる必要がある。この場合は、モータ3を第1方向に回転する。モータ3の回転は第1ギア13を介してボールねじ機構5のボールねじ軸21に伝達される。このボールねじ軸21の回転は、ボール23を介してボールねじナット22に伝達される。ボールねじナット22は突出部22cに台形ねじナット27が設けられていることによって回り止めされており、したがって、ボールねじ軸21の回転は、図1においてボールねじナット22のA方向の軸方向移動に変換される。これにより、ボールねじナット22の端面22dが出力部材7の第1端面7cに当接し、出力部材7はA方向に移動させられる。したがって、レリーズフォーク29は図1においてR1方向に回転し、クラッチ装置はオフとなる。
クラッチオフの状態では、モータ3の駆動は停止される。すなわち、モータ3への電力の供給は停止される。
クラッチをオンにする場合は、レリーズ機構2のレリーズフォーク29を図1においてR2方向に回転させる必要がある。この場合は、モータ3を第2方向に回転する。これにより、第1ギア13は反時計回りに回転し、第2ギア14は時計回りに回転する。
(1)クラッチオフにするための駆動機構としてボールねじ機構5を用いているので、駆動力を効率良く伝達できる。したがって、モータを小型化することが可能になる。
第2実施形態によるアクチュエータ51を図5に示す。このアクチュエータ51は、筒状のケース52と、電動モータ53と、駆動機構54と、固定ねじナット55と、出力部材56と、を備えている。
駆動機構54は、ケース52の内部に収納されており、ボールねじ軸61と、ボールねじナット62と、複数のボール63と、を有している。
固定ねじナット55は、ボールねじナット62のレリーズ機構側において、ボールねじ軸61に螺合している。この固定ねじナット55は、ボールねじ軸61に対してセルフロック機能を有しており、固定ねじナット55側から動力が作用すると、固定ねじナット55はボールねじ軸61に対して回転せず、セルフロックされる。
出力部材56は、ボールねじ軸61の軸に沿った方向に延びる部材であり、モータ53側に形成された筒状部68と、筒状部68のレリーズ機構2側に形成された連結部69と、を有している。
<クラッチオン→クラッチオフ(レリーズ)時>
クラッチオフ(動力切断)の場合は、レリーズ機構2のレリーズフォーク29を図5においてR1方向に回転させる必要がある。この場合は、モータ53を第1方向に回転する。モータ53の回転はジョイント64を介してボールねじ軸61に伝達される。このボールねじ軸61の回転は、ボール63を介してボールねじナット62に伝達される。ボールねじナット62にはスプライン係合によって出力部材56が連結されているので、ボールねじ軸61の回転は、図5においてボールねじナット62及び出力部材56のA方向の軸方向移動に変換される。これにより、レリーズフォーク29は図5においてR1方向に回転し、クラッチ装置はオフとなる。
クラッチオフの状態では、モータ53の駆動は停止される。すなわち、モータ53への電力の供給は停止される。
クラッチをオンにする場合は、レリーズ機構2のレリーズフォーク29を図5においてR2方向に回転させる必要がある。この場合は、モータ53を第2方向に回転する。これにより、ボールねじ軸61は先とは逆に回転し、その回転はボールねじナット62及び出力部材56のB方向の移動に変換される。この結果、クラッチ装置において、プレッシャプレートがダイヤフラムスプリングによってフライホイール側に押され、クラッチが接続されたクラッチオン状態になる。
本発明は以上のような実施形態に限定されるものではなく、本発明の範囲を逸脱することなく種々の変形又は修正が可能である。
2 レリーズ機構
3,53 モータ
5 ボールねじ機構
6 台形ねじ機構
7,56 出力部材
21,61 ボールねじ軸(第1ねじ軸)
22,62 ボールねじナット(第1ナット)
23,63 ボール
26 台形ねじ軸(第2ねじ軸)
27 台形ねじナット(第2ナット)
55 固定ねじナット
Claims (7)
- クラッチのレリーズ機構を駆動するためのアクチュエータであって、
電動モータと、
前記レリーズ機構に連結され、前記レリーズ機構の作動方向に移動自在な出力部材と、
前記電動モータの一方向の回転を前記出力部材の第1軸方向の移動に変換するための第1駆動機構と、
前記レリーズ機構からの逆駆動力に対してセルフロック機能を有し、前記電動モータの他方向の回転を前記出力部材の第2軸方向の移動に変換するための第2駆動機構と、
を備えたクラッチのアクチュエータ。 - 前記第1駆動機構は、前記電動モータの一方向の回転によって前記出力部材を前記第1軸方向に押すためのボールねじ機構である、請求項1に記載のクラッチのアクチュエータ。
- 前記第2駆動機構は、前記出力部材からの逆駆動力が伝達されるとともに、前記電動モータの他方向の回転によって前記出力部材を前記第2軸方向に移動させるための台形ねじ機構である、請求項1又は2に記載のクラッチのアクチュエータ。
- 前記ボールねじ機構は、
外周面にねじ溝を有し、前記電動モータの出力軸に連結された第1ねじ軸と、
内周面にねじ溝を有し、前記電動モータの一方向の回転時には前記出力部材に当接して前記出力部材を前記第1軸方向に移動させるとともに、前記電動モータの他方向の回転時には前記出力部材から離れる第1ナットと、
前記第1ねじ軸及び前記第1ナットのねじ溝に配置された複数のボールと、
を有する、請求項1から3のいずれかに記載のクラッチのアクチュエータ。 - 前記台形ねじ機構は、
前記電動モータの他方向の回転によって回転する第2ねじ軸と、
前記第2ねじ軸に螺合し、前記出力部材からの逆駆動力を受けたときには前記第2ねじ軸との間でセルフロックし、前記第2ねじ軸から駆動力を受けたときには前記出力部材とともに前記第2軸方向に移動する、第2ナットと、
を有する、請求項4に記載のクラッチのアクチュエータ。 - 前記第1ねじ軸と前記第2ねじ軸とは平行に配置されており、
前記第1ナットは前記第2ねじ軸側に突出する突出部を有し、
前記第2ナットは前記第1ナットの突出部に軸方向にスライド自在に配置されている、
請求項5に記載のクラッチのアクチュエータ。 - クラッチのレリーズ機構を駆動するためのアクチュエータであって、
電動モータと、
前記レリーズ機構に連結され、前記レリーズ機構の作動方向に移動自在な出力部材と、
前記電動モータによって回転されるねじ軸と、前記ねじ軸に螺合し前記出力部材に連結された第1ナットと、を有する駆動機構と、
前記ねじ軸に螺合するとともに前記出力部材に係合可能であり、前記出力部材からの逆駆動力に対してセルフロック機能を有する第2ナットと、
を備えたクラッチのアクチュエータ。
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DE112012005237.4T DE112012005237T5 (de) | 2011-12-15 | 2012-11-16 | Kupplungsaktuator |
US14/360,909 US8991582B2 (en) | 2011-12-15 | 2012-11-16 | Clutch actuator |
CN201280059396.6A CN103975172B (zh) | 2011-12-15 | 2012-11-16 | 离合器驱动器 |
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JP2011274752A JP5431443B2 (ja) | 2011-12-15 | 2011-12-15 | クラッチのアクチュエータ |
JP2011-274752 | 2011-12-15 |
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JP (1) | JP5431443B2 (ja) |
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CN104343843A (zh) * | 2013-07-29 | 2015-02-11 | 舍弗勒技术有限两合公司 | 用于摩擦离合装置的操纵装置和具有操纵装置的摩擦离合装置 |
WO2015070850A1 (de) * | 2013-11-18 | 2015-05-21 | Schaeffler Technologies AG & Co. KG | Drehmomentabstützung eines aktors an einem kupplungsgehäuse/getriebegehäuse |
CN112334674A (zh) * | 2018-06-13 | 2021-02-05 | 康斯博格汽车部件集团股份公司 | 电驱动式离合器致动器 |
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US10487887B2 (en) | 2014-11-07 | 2019-11-26 | Means Industries, Inc. | Electromechanical apparatus for use with a controllable coupling assembly and coupling and electromechanical control assembly |
US9458895B2 (en) * | 2014-12-16 | 2016-10-04 | American Axle & Manufacturing, Inc. | Lead screw actuator having axially movable plunger with compliance in both axial directions |
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KR101767047B1 (ko) * | 2016-01-20 | 2017-08-10 | 이스트바이크 주식회사 | 레버크랭크기구를 이용한 무단변속기의 캠핀을 제어하는 장치 |
DE102017105101B4 (de) * | 2016-12-21 | 2019-05-29 | Schaeffler Technologies AG & Co. KG | Schaltaktuator |
JP2019113167A (ja) * | 2017-12-26 | 2019-07-11 | 日本精工株式会社 | 直動アクチュエータ及び直動アクチュエータの組立方法 |
US11168497B2 (en) | 2018-05-29 | 2021-11-09 | Magna Closures Inc. | Power actuator with self disengaging clutch unit |
CN108746709B (zh) * | 2018-06-20 | 2019-08-27 | 绍兴市秀臻新能源科技有限公司 | 一种延长摇臂钻床耐用程度的方法 |
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CN112334674A (zh) * | 2018-06-13 | 2021-02-05 | 康斯博格汽车部件集团股份公司 | 电驱动式离合器致动器 |
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CN103975172B (zh) | 2016-08-17 |
JP5431443B2 (ja) | 2014-03-05 |
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US20140353109A1 (en) | 2014-12-04 |
JP2013124743A (ja) | 2013-06-24 |
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DE112012005237T5 (de) | 2014-08-28 |
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