WO2005078308A1 - Dispositif de freinage commandé par moteur - Google Patents

Dispositif de freinage commandé par moteur Download PDF

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Publication number
WO2005078308A1
WO2005078308A1 PCT/JP2005/002426 JP2005002426W WO2005078308A1 WO 2005078308 A1 WO2005078308 A1 WO 2005078308A1 JP 2005002426 W JP2005002426 W JP 2005002426W WO 2005078308 A1 WO2005078308 A1 WO 2005078308A1
Authority
WO
WIPO (PCT)
Prior art keywords
screw
shaft
brake
pressing
screw shaft
Prior art date
Application number
PCT/JP2005/002426
Other languages
English (en)
Japanese (ja)
Inventor
Ken Yamamoto
Original Assignee
Ntn Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn Corporation filed Critical Ntn Corporation
Publication of WO2005078308A1 publication Critical patent/WO2005078308A1/fr

Links

Classifications

    • 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
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • 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
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut

Definitions

  • the present invention relates to an electric brake device that converts rotation of an electric motor into linear motion by a ball screw mechanism and presses a brake member against a member to be braked.
  • Hydraulic-type brakes have been widely used as vehicle brake devices.
  • advanced brake controls such as ABS (Antilock Brake System)
  • ABS Antilock Brake System
  • These controls can be performed without complicated hydraulic circuits. Attention is being paid to electric brake devices that can be designed and compact.
  • the electric brake device operates an electric motor by a depression signal of a brake pedal, converts the rotation of the electric motor into a linear motion, and presses a brake member against a controlled member.
  • the electric brake device is mounted under the spring of the vehicle, so it is desired that a compact and lightweight design be possible.
  • a nut of a ball screw mechanism is rotated integrally with a rotor of an electric motor, and a screw shaft screwed to the nut via a ball is linearly moved to make a heavy weight.
  • a type that directly converts the rotation of an electric motor into linear motion by a ball screw mechanism without using a bulky gear reduction mechanism for example, see Patent Documents 1 and 2;).
  • the electric brake device described in Patent Document 1 has an elastic member such as a synthetic rubber material interposed between a shaft end of a screw shaft of a ball screw mechanism that moves linearly and a brake member, and the electric brake device is operated when the brake is operated.
  • an elastic member such as a synthetic rubber material interposed between a shaft end of a screw shaft of a ball screw mechanism that moves linearly and a brake member, and the electric brake device is operated when the brake is operated.
  • the brake member is pressed by the screw shaft via the elastic member, the electric motor is stopped when the brake is released, and the screw shaft is pushed back by the elastic restoring force of the elastic member.
  • the electric brake device described in Patent Document 2 rotates the electric motor forward when the brake is operated, moves the screw shaft of the ball screw mechanism to the brake member pressing side, and when the brake is released, the electric motor is rotated. Is rotated in the reverse direction to move the screw shaft to the side where the brake member force retreats. In this electric brake device, retract the screw shaft. After the movement, the electric motor is rotated forward to return the screw shaft to the standby position.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2002-213504 (Pages 2-4, FIG. 1-3)
  • Patent Document 2 Japanese Patent Application Laid-Open No. 2002-213505 (Pages 2-4, Fig. 12)
  • the electric brake device described in Patent Document 2 requires a reverse rotation of the electric motor when the brake is released, so that the timing of the brake release is delayed, giving the driver a feeling of strangeness.
  • a brake member such as a brake pad
  • the responsiveness of the braking effect is slowed down because the movement distance until the screw shaft presses the brake member becomes long.
  • a separate sensor and extra control algorithm are required, and the It becomes complicated.
  • an object of the present invention is to provide an electric brake device which is excellent in responsiveness of brake effect and brake release, and which does not decrease in responsiveness even when a brake member is worn.
  • the present invention includes an electric motor and a ball screw mechanism, and rotates a nut of the ball screw mechanism integrally with a rotor of the electric motor, and screws the nut to the nut via a ball.
  • the screw shaft of the ball screw mechanism is moved linearly, and the output of the electric motor, which is converted to linear movement of the screw shaft, causes the pressing member provided on the front end side of the screw shaft to convert the brake member to the member to be braked.
  • an axial through-hole is provided in the screw shaft of the ball screw mechanism, and a male screw is provided at the tip of the through-hole.
  • the shaft is fitted toward the front end of the screw shaft, and the male screw of the projecting shaft is screwed into a screw hole provided at the front end of the through hole.
  • Pressing means is provided for pressing and pushing the tensioning shaft toward the base end side, and the screw is loosened at the large lead angle ⁇ and rotated by the pressing means so as to rotate toward the base end side.
  • a structure with a stop to stop the projecting shaft that moves relative to the screw shaft is adopted.
  • the electric brake device rotates the electric motor when the brake is actuated.
  • the projecting shaft of the ball screw mechanism When the screw shaft of the ball screw mechanism is moved forward to the brake member pressing side, the projecting shaft also moves together with the screw shaft.However, the projecting shaft urged toward the base end by the pushing means is When the screw is separated from the stove, the screw with a large lead angle ⁇ is loosened and rotates, moves relatively to the screw shaft toward the base end, and makes contact with the stove again to support the screw shaft so that it does not return backward. Therefore, when the brake member wears, the pressing position changes gradually so as to move forward. With this change in the pressing position, the tensioning support position of the screw shaft by the tension shaft also changes forward, and the pressing portion of the screw shaft is pressed. Is always kept close to the pressing position of the brake member, and excellent responsiveness of the braking effect can be naturally ensured.
  • the male screw of the extension shaft is connected to the flank angle of the front surface of the thread facing the tip end side of the extension shaft.
  • the protruding shaft that is screwed with the saw-toothed screw has a large flank angle ⁇ .
  • the screw When engaging the female thread on the front face of the male thread facing the end, even if the lead angle ⁇ is large, the screw is locked without loosening, so it moves relative to the screw shaft of the ball screw mechanism only toward the base end. However, it does not relatively move to the tip side. Therefore, not only when the brake member is not worn, but also when the brake member is worn, the pressing portion of the screw shaft can be more securely stretched and supported so as not to return near the pressing position. Also, a tension shaft with a large flank angle ⁇ Since the axial clearance of the screw is further increased on the front side of the thread of the male screw that faces the distal end of the male screw, the pressing portion of the screw shaft can be sufficiently released from the brake member force when the brake is released.
  • the lead angle of the male screw is 8 to 20 °.
  • Grease force used for screw lubrication Force used for grease lubrication The friction coefficient of a screw is about 0.08 to 0.12.
  • Figure 5 is a graph in which the limit curve at which the screw starts to loosen when an axial force is applied is calculated for the friction coefficients of 0.08 and 0.12. The lower side of each limit curve is the loose area and the upper side is the lock area. It can be seen that the loose area increases as the lead angle ⁇ increases and the flank angle output S decreases.
  • the lead angle a is set to 8 ° or more so that there is a loose area even when the flank angle is 0 °.
  • the upper limit of the lead angle a was set to 20 ° in consideration of practicality as a screw.
  • flank angle 0 on the front surface of the thread and the flank angle 0 on the rear surface of the thread of the male screw are respectively
  • the pressing means has a compression elastic member disposed between a seat plate provided on the front end side of the through hole and a seat provided on the distal end surface of the projecting shaft, thereby achieving compactness.
  • the tension shaft can be pressed and urged.
  • the rotation restraining moment caused by the pressing force is reduced, and the rotation of the extension shaft due to loosening of the screw is reduced. Can be made smoother.
  • the pressing portion on the front end side of the screw shaft is formed by a separate pressing member, and the pressing member is provided with a screw hole into which a male screw of the protruding shaft is screwed, so that the protruding shaft and its pressing portion are pressed. It is possible to easily incorporate the protection means.
  • the electric brake device of the present invention when the electric motor is rotated during the operation of the brake to move the screw shaft of the ball screw mechanism forward to the brake member pressing side, the projecting shaft and the screw shaft are together. However, the projecting shaft urged against the proximal end by the pressing means moves relative to the screw shaft toward the proximal end while the screw with the large lead angle ⁇ is loosened and rotates, and again hits the stopper and Since the shaft is supported so that it does not return to the rear, even if the brake member wears and its pressing position changes, the pressing part of the screw shaft is always kept close to the pressing position, and excellent braking effect is obtained. Responsiveness can be naturally ensured. Also, when the brake is released, the electric motor is only stopped, and the screw shaft escapes the force on the brake member pressing side by the gap in the axial direction of the screw having the large lead angle ⁇ , so that excellent responsiveness can be secured.
  • the male screw of the projecting shaft is connected to the front end of the projecting shaft by a flank angle on the front surface of the thread.
  • the protruding shaft screwed with the serrated screw moves only relative to the screw shaft of the ball screw mechanism toward the base end side and does not move relative to the distal end side, and the brake member is worn.
  • the brake member is not worn, of course, even if the brake member is worn, the pressing portion of the screw shaft can be supported more securely so as not to return near the pressing position.
  • the clearance in the axial direction of the screw is further increased, so that the brake shaft can release the pressing part of the screw shaft when the brake is released.
  • the pressing means By providing the pressing means with a compression elastic member disposed between a seat plate provided on the front end side of the through hole and a seat provided on the tip end surface of the projecting shaft, a compact design is achieved. With this, the tension shaft can be pressed and urged. In addition, by forming the end surface of the compression elastic member on the side that comes into contact with the seat of the extension shaft into a small diameter, the rotational constraint moment caused by the pressing force is reduced, and the rotation of the extension shaft due to the loosening of the screw is reduced. It can be smooth.
  • the pressing portion on the front end side of the screw shaft is formed by a separate pressing member, and the pressing member is By providing a screw hole into which the male screw of the shaft is screwed, it is possible to easily incorporate the extension shaft and the pressing means therefor.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of an electric brake device.
  • FIG. 2 is an enlarged cross-sectional view showing a male screw of the extension shaft and a screw hole of a pressing member in FIG. 1.
  • FIG. 3 is a longitudinal sectional view showing a state in which the brake pad of FIG. 1 is worn.
  • FIG. 4 A longitudinal sectional view illustrating a procedure for replacing the worn brake pad of FIG.
  • FIG. 5 is a graph showing a loosening limit curve with respect to a screw lead angle and a flank angle.
  • this electric brake device is a disk brake in which brake pads 3a and 3b as brake members are arranged opposite to both sides of a disk rotor 2 as a member to be braked inside a caliper 1.
  • the stator 5 of the electric motor is fixed to the inner peripheral surface of the motor casing 4 attached to 1, and the nut 6 of the ball screw mechanism formed integrally with the rotor has a pair of bearings for the caliper 1 and the motor casing 4.
  • a separate pressing member 9 for pressing the brake pad 3a against the disk rotor 2 is attached to the front end side of a screw shaft 8 rotatably supported by 10 and screwed to the nut 6 via a ball 7.
  • the inside of the motor casing 4 is sealed with a boot 11 attached between the caliper 1 and the pressing member 9!
  • a through hole 12 is provided at the center of the screw shaft 8 of the ball screw mechanism.
  • a screw hole 13 is provided in the pressing member 9 so as to be continuous with the through hole 12.
  • a projecting shaft 14 fitted toward the front end side is screwed into a screw hole 13 with a male screw 15 provided at the tip end.
  • a seat plate 16 is attached to the front end surface of the pressing member 9, and a compression coil spring 18 as a compression elastic member is arranged between the pressing member 9 and a boring seat 17 provided on the front end surface of the extension shaft 14.
  • the compression coil spring 18 is formed with a small diameter at the end face in contact with the boring seat 17 to reduce the rotation restraining moment due to the pressing force, and to reduce the tension of the extension shaft 14 due to the loosening of the serrated screw described later.
  • the rotation is smooth.
  • the base end of the extension shaft 14 is fixed by a stopper screw 19 screwed to the motor casing 4.
  • a notch 16a is provided on the front surface of the seat plate 16 to engage with the projection on the brake pad 3a side to prevent the screw shaft 8 from rotating.
  • the male screw 15 of the projecting shaft 14 has a large lead angle a of 11 °, and is shown in FIG.
  • the flank angle ⁇ of the front surface 15a of the thread 15a facing the distal end of the threaded shaft 14 of the male screw 15 is 75 ° ( ⁇ 1.5 ⁇ + 50)
  • the flank angle 0 of the rear surface 15b of the thread 15b is 15 ° ( ⁇ 3. ⁇ ⁇ + 1
  • the serrated screw is grease-lubricated.
  • the screw that engages with the internal thread of the screw loosens and rotates relative to the screw shaft 8 and the pressing member 9 while rotating to the proximal end and hits the stopper screw 19.
  • the serrated screw is locked in the opposite direction in which 15a is engaged with the female screw of the screw hole 13, and does not move relatively. Also, since this serrated screw has a large lead angle, the axial gap is originally large due to the gap between the male and female threads, but the axial gap at the front face 15a of the thread with a large flank angle ⁇
  • the interval ⁇ is even larger.
  • FIG. 1 shows a case where the brake pads 3a and 3b are not worn
  • FIG. 3 shows a case where the brake pads 3a and 3b are worn.
  • the electric motor is started by the depression signal of the brake pedal (not shown), the nut 6 of the ball screw mechanism rotates, and the screw shaft 8 moves forward on the brake pad 3a side. I do.
  • the pressing member 9 on the front end side of the screw shaft 8 presses the brake pad 3a
  • the brake pad 3b attached to the caliper 1 is also pressed by the disk rotor 2 by the reaction force, and the brake is activated.
  • the extension shaft 14 When the screw shaft 8 moves forward during the brake operation, the extension shaft 14 also moves together with the screw shaft 8, but the extension shaft 14 urged toward the base end by the compression coil spring 18 is urged. Moves away from the stopper screw 19, the flank angle increases with a large lead angle ⁇ .
  • the serrated screw engaging with the female screw of the screw hole 13 is loosened, moves relative to the screw shaft 8 to the base end side while rotating, and hits the stop screw 19 again.
  • the projecting shaft 14, which has relatively moved to the base end, moves in a reverse direction in which the thread front surface 15a having a large flank angle ⁇ ⁇ engages with the female screw of the screw hole 13 even when the electric motor is stopped at the time of releasing the brake described later. Does not move relative,
  • the screw shaft 8 and the pressing member 9 are supported so that they do not return backward.
  • the electric motor when releasing the brake, the electric motor is stopped by the release signal of the brake pedal.
  • the electric motor is stopped and the rotational driving force of the nut 6 of the ball screw mechanism is lost, the screw shaft 8 and the pressing member 9 escape backward by the axial gap of the threaded front surface 15a of the serrated screw, and each brake pad The pressing of the disk rotor 2 by 3a and 3b is released. Therefore, in this electric brake device, the brake can be released with excellent responsiveness only by stopping the electric motor that does not need to reverse the electric motor.
  • the pressing portion of the screw shaft of the ball screw mechanism is formed by a separate pressing member, and the pressing member is provided with a screw hole that is screwed with the serrated male screw of the projecting shaft.
  • the pressing portion may be integrated with the screw shaft.
  • the male and female threads of the extension shaft may have a symmetrical front and rear face of the thread as long as the lead angle is large so that the thread is loosened by an axial load on the proximal end side.
  • the means for pressing the extension shaft and the stopper are not limited to those of the embodiment, and can be arbitrarily designed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

: Dispositif de freinage commandé par moteur ayant une excellente réactivité à l'application et au relâchement d'un frein et empêchant cette réactivité d'être diminuée même si un élément de frein est usé. Lorsque qu'une vis (8) est actionnée vers l'avant par la rotation d'un écrou (6) du mécanisme à vis à billes par un moteur électrique lorsque le frein est actionné, un arbre de tension (14) mis sous pression à sa base par un ressort hélicoïdal à compression (18) est actionné, tout en tournant, vers la base de la vis (8) dès lors qu'une vis cannelée avec un grand angle de filet α est libérée jusqu'à ce qu'elle touche une butée (19) pour supporter en pression la vis (8) de façon que celle-ci ne parte pas en marche arrière. En conséquence, même si des patins de frein (3a) et (3b) sont usés, l'excellente réactivité de l'action du frein peut être naturellement assurée en maintenant toujours un élément d'appui (9) proche de la position d'appui, et également lorsque le frein est lâché, une excellente réactivité peut être assurée en séparant l'élément d'appui (9) des patins de freins (3a) par le jeu axial de la vis cannelée en arrêtant simplement le moteur électrique.
PCT/JP2005/002426 2004-02-17 2005-02-17 Dispositif de freinage commandé par moteur WO2005078308A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-039746 2004-02-17
JP2004039746A JP4439284B2 (ja) 2004-02-17 2004-02-17 電動式ブレーキ装置

Publications (1)

Publication Number Publication Date
WO2005078308A1 true WO2005078308A1 (fr) 2005-08-25

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Application Number Title Priority Date Filing Date
PCT/JP2005/002426 WO2005078308A1 (fr) 2004-02-17 2005-02-17 Dispositif de freinage commandé par moteur

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JP (1) JP4439284B2 (fr)
WO (1) WO2005078308A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107208764A (zh) * 2015-01-26 2017-09-26 舍弗勒技术股份两合公司 滚珠螺杆传动装置和相关的电机执行器
WO2022106784A1 (fr) * 2020-11-20 2022-05-27 Hitachi Astemo France Frein équipé d'une pièce de guidage d'une vis à billes déplaçant une plaquette de freinage

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100812404B1 (ko) 2006-05-17 2008-03-11 신구오토모비스(주) 자전거 브레이크장치
JP4623316B2 (ja) * 2006-12-25 2011-02-02 日立オートモティブシステムズ株式会社 電動ディスクブレーキ
US8220594B2 (en) 2007-08-30 2012-07-17 Nippon Soken, Inc Electric brake device
JP5131502B2 (ja) * 2009-02-27 2013-01-30 トヨタ自動車株式会社 ブレーキ装置
KR20130067168A (ko) * 2011-12-13 2013-06-21 현대모비스 주식회사 전자식 주차 브레이크장치
JP6358657B2 (ja) * 2015-07-13 2018-07-18 新日本特機株式会社 キャリパ油圧制御ユニットおよびブレーキダイナモメータ
KR20210151371A (ko) * 2020-06-05 2021-12-14 주식회사 만도 전기 기계식 브레이크 및 이의 작동방법
KR20210151553A (ko) * 2020-06-05 2021-12-14 주식회사 만도 전기 기계식 브레이크 및 이의 작동방법
KR20220107460A (ko) * 2021-01-25 2022-08-02 주식회사 만도 전기 기계식 브레이크

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003156086A (ja) * 2001-11-21 2003-05-30 Nsk Ltd 電動ブレーキ装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003156086A (ja) * 2001-11-21 2003-05-30 Nsk Ltd 電動ブレーキ装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107208764A (zh) * 2015-01-26 2017-09-26 舍弗勒技术股份两合公司 滚珠螺杆传动装置和相关的电机执行器
US10626966B2 (en) 2015-01-26 2020-04-21 Schaeffler Technologies AG & Co. KG Ball screw drive and associated electromechanical actuator
WO2022106784A1 (fr) * 2020-11-20 2022-05-27 Hitachi Astemo France Frein équipé d'une pièce de guidage d'une vis à billes déplaçant une plaquette de freinage
FR3116576A1 (fr) * 2020-11-20 2022-05-27 Foundation Brakes France Frein équipé d’une pièce de guidage d’une vis à billes déplaçant une plaquette de freinage

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Publication number Publication date
JP4439284B2 (ja) 2010-03-24
JP2005233224A (ja) 2005-09-02

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