GB2307525A - Electrically-operated disc brake assemblies for vehicles - Google Patents

Electrically-operated disc brake assemblies for vehicles Download PDF

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Publication number
GB2307525A
GB2307525A GB9621738A GB9621738A GB2307525A GB 2307525 A GB2307525 A GB 2307525A GB 9621738 A GB9621738 A GB 9621738A GB 9621738 A GB9621738 A GB 9621738A GB 2307525 A GB2307525 A GB 2307525A
Authority
GB
United Kingdom
Prior art keywords
disc brake
brake
disc
piston
screw device
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
GB9621738A
Other versions
GB2307525B (en
GB9621738D0 (en
Inventor
Anthony Eugene Martin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF International UK Ltd
Original Assignee
Lucas Industries Ltd
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 Lucas Industries Ltd filed Critical Lucas Industries Ltd
Publication of GB9621738D0 publication Critical patent/GB9621738D0/en
Publication of GB2307525A publication Critical patent/GB2307525A/en
Application granted granted Critical
Publication of GB2307525B publication Critical patent/GB2307525B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F16D65/72—Slack adjusters hydraulic
    • F16D65/74—Slack adjusters hydraulic self-acting in one direction
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/745—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive acting on a hydraulic system, e.g. a master cylinder
    • 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
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/005—Force, torque, stress or strain
    • 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
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/10—Plural pistons interacting by fluid pressure, e.g. hydraulic force amplifiers using different sized pistons
    • 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
    • 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
    • F16D2125/405—Screw-and-nut with differential thread

Description

2307525 1 IMPROVEMENTS IN ELECTRICALLY-OPERATED DISC BRAKE ASSEMBLIES FOR
VEHICLES This invention relates to improvements in electrically -operated disc brake assemblies for vehicles of the kind in which a friction member is adapted to be applied to a rotatable brake disc by brake-applying means including an electric motor, and a linear actuator means in the form of a screw device adapted to apply an axial ly-directed brake-applying force to the friction member in response to operation of the motor.
In brakes of the kind set forth normally the screw device has to be of a sufficient length not only to apply the friction member to the disc in a brake-apply movement, but also to accommodate additional displacement as a result of wear of the friction member. As a result the screw device must be of substantial length, which, in turn, increases the complexity and cost of the assembly.
According to our invention in an electrically-operated disc brake assembly of the kind set forth the screw device acts on the friction member through an hydraulic strut of which the effective volume is adapted to increase to accommodate wear of the friction member.
This enables us to provide a screw device of which the range of extension and contraction is sufficient to achieve movement of the friction member through a brake-apply distance with additional movement necessary to accommodate wear of the friction member being compensated for by increase in volume and, in consequence, in the effective length of the hydraulic strut.
1 2 We are therefore able to provide a relatively simple screw device with consequent conservation of cost.
The hydraulic strut may comprise of volume of fluid contained in a space defined between the screw device and a brake-applying piston adapted to act on the friction member, and a normally-open valve through which the space is supplied with fluid from a reservoir is adapted to close to trap fluid in the space in response to movement of the screw device towards the disc in a brake-apply direction.
In one construction the screw device includes an internally screw threaded intermediate piston which is axially moveable, is keyed against rotation and works in an internal bore in the brake-applying piston which, in turn, works in a bore in a brake housing, and acts on the friction member through a closed, outer end, the valve being adapted to control communication between the space defined between the two pistons and the reservoir, through passages in the intermediate piston and in an externally screw threaded drive member rotatable by the motor to alter the effective length of the screw device.
When the brake-applying piston works in a bore in a limb of a caliper adapted to straddle the periphery of the disc the reservoir comprises an annular chamber surrounding that limb of the caliper and defined by a flexible diaphragm enclosed within a cover and of which the outer face is vented to atmosphere through a port in the cover.
The drive member may be rotatably driven by the motor through a gear box.
3 In another construction the gear box may be omitted and the drive member may comprise differential screws adapted to translate rotation of the motor into axial movement of the drive member in a brake-applying direction.
One embodiment of our invention is illustrated in the single figure of the accompanying drawings which is a longitudinal section through an electrically -operated disc brake assembly comprising a caliper of the single sided sliding type.
The brake illustrated in the drawings comprises a housing in the form of a caliper 1 of generally U-shaped outline comprising opposed limbs 2 and 3 adapted to straddle the periphery of a rotatable disc 4 and interconnected by a bridge piece 5. The caliper 1 is mounted for sliding movement on a stationery mounting member adjacent to one face of the disc and in which the limb 2 is slidably mounted.
An electric motor 6 and a gear box 7 are mounted on the end of the limb 2 remote from the disc 4. Specifically a housing 9 accommodating the motor and the gear box is clamped against the end face of the limb 2 remote from the disc 4.
A pair of friction members 10 and 11 are mounted in the caliper 1. Specifically the friction member 10 is guided for movement towards and away from the disc between guide surfaces in the limb 2 which take the drag on the friction member 10 when the brake is applied and prevent it from rotating with respect to the caliper 1. The friction member 11 is carried by the inner face of the limb 3.
4 The friction member 10 is adapted to be applied to the disc 4 by means of an actuating mechanism 12 initiated by operation of the motor 6, and the friction member 11 is urged into engagement with the opposite face of the disc by sliding movement of the caliper 1 in the opposite 5 direction due to the reaction of the actuating mechanism 12 on the caliper 1.
The actuating mechanism 12 comprises an hydraulic brake applying piston 13 of cup shaped outline which works in a bore 14 in the limb 2 of the caliper 1 through a seal 15 of elasto-meric material and of which the closed end acts on the friction member 10. An intermediate piston 16, substantially of top-hat outline, works in an internal bore 17 of the brake applying piston 13 and an inner end portion 18 of increased diameter has a splined engagement with an enlarged portion of the bore 14 to prevent rotation of the piston 16. The intermediate piston 16 is screw threaded internally to receive in screw threaded engagement external screw threads on a drive member 20 coupled to an output shaft 21 from the gear box 7.
A space 25 between the closed end of the brake-applying piston 13 and the inner end of the intermediate piston 16 is connected through a normally open centre valve 26 to an annular reservoir 28 for fluid through the interior of the drive member 20 and radial ports 27 leading to the reservoir. The annular reservoir 28 is defined by an annular diaphragm 29 which encircles the limb 2 of the caliper and is enclosed within a cylindrical cover 30 provided with an atmospheric vent opening 31.
In the inoperative brakes-off position illustrated in the drawings the hydraulic valve 26 is open to provide communication between the hydraulic space 25 and the reservoir 28. When the motor 6 is operated to apply the brake, rotation of the drive member 20 causes the intermediate piston 16 to advance axially in the bore 17 of the brake-applying piston 13 initially to cause the valve 26 to close and isolate the space 25 from the reservoir 28. The volume of fluid trapped within the space 25 defines an hydraulic strut so that further movement of the intermediate piston 16 in a brake-applying direction is accompanied by a corresponding movement in the same direction of the brake-applying piston 13 which, in turn, acts to urge the friction member 10 into engagement with the disc 4. The reaction of the actuating mechanism 12 on the caliper 1 causes the caliper 1 to move axially in the opposite direction with the limb 3 urging the friction member 11 into engagement with the opposite face of the disc 4.
When the brake-actuating mechanism 12 is released and the motor 6 operates in the opposite direction to withdraw the intermediate piston 12 away from the disc 4, the valve 26 opens. This releases the fluid from the space 25 to enable it to return to the reservoir 28. The brake- applying piston 13 retracts a distance sufficient to enable the friction members 10 and 11 to adopt running clearances with respect to the disc 4 and with the retracted position of the brake-applying piston 13 being determined by the 'roll-back' characteristics of the seal 15.
As the linings of the friction members 10 and 11 wear due to brake applying movements the retracted position of the brake-applying piston 13 is progressively advanced with respect to and towards the disc 4. This means that during subsequent brake-applying operations the effective volume of the space 25 increases with consequent increase in the effective length of the hydraulic strut.
The provision of the hydraulic strut enables us to reduce substantially the thread length of the screw device defined by the 6 engagement of the drive member 20 with the intermediate piston 13, in comparison with the thread length which would otherwise be required.
A load transducer 35 may be accommodated between the gear box portion of the housing 9 and the drive member 20 to determine a feedback signal by means of which the motor 6 is regulated in the application of the brake.
In a modification the load transducer 35 can be replaced by a pressure transducer 36, in turn for measuring the pressure developed within the space 25 when the brake is applied.
A similar signal will be produced by either the load transducer 35 or the pressure transducer 36.
The hydraulic fluid comprises a material, suitably silicon oil, which not only defines the hydraulic strut but also acts as a lubricant for the sliding surfaces between the brake-applying piston 12 and the intermediate piston 16, and between the screw threads, the gears of the gear box 7 and the splines.
In the modification of the construction described above the gear box 7 may be omitted and differential screws may be incorporated to translate rotation of the motor 6 into axial movement of the friction member 10 in a brake-applying direction.
In the modified construction or in the construction described above with reference to the accompanying drawing the screws may comprise plain threads. In other modified constructions the screws may comprise ball screws, or roller screws.
7

Claims (7)

1. An electrical 1 y-operated disc brake assembly of the kind set forth in which the screw device acts on the friction member through an hydraulic strut of which the effective volume is adapted to increase to accommodate wear of the friction member.
2. A disc brake according to claim 1, in which the hydraulic strut comprises of volume of fluid contained in a space defined between the screw device and a brake-applying piston adapted to act on the friction member, and a normally-open valve through which the space is supplied with fluid from a reservoir is adapted to close to trap fluid in the space in response to movement of the screw device towards the disc in a brakeapply direction.
3. A disc brake according to claim 2, in which the screw device includes an internally screw threaded intermediate piston which is axially moveable, is keyed against rotation, and works in an internal bore in the brake-applying piston which, in turn, works in a bore in a brake housing and acts on the friction member through a closed, outer end, the valve being adapted to control communication between the space defined between the two pistons and the reservoir, through passages in the intermediate piston and in an externally screw threaded drive member rotatable by the motor to alter the effective length of the screw device.
4. A disc brake according to claim 2 or claim 3, in which the brakeapplying piston works in a bore in a limb of a caliper adapted to straddle the periphery of the disc and the reservoir comprises an annular chamber surrounding that limb of the caliper and defined by a flexible diaphragm 8 enclosed within a cover and of which the outer face is vented to atmosphere through a port in the cover.
5. A disc brake according to claim 3 or claim 4, in which the drive member is rotatably driven by the motor through a gear box.
6. A disc brake according to claim 3 or claim 4, in which the drive member comprises differential screws adapted to translate rotation of the motor into axial movement of the drive member in a brake-applying 10 direction.
7. An electrical ly-operated disc brake assembly substantially as described herein with reference to and as illustrated in the accompanying drawings.
GB9621738A 1995-10-25 1996-10-18 Improvements in electrically-operated disc brake assemblies for vehicles Expired - Fee Related GB2307525B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB9521868.1A GB9521868D0 (en) 1995-10-25 1995-10-25 Improvements in electrically-operated disc brake assemblies for vehicles

Publications (3)

Publication Number Publication Date
GB9621738D0 GB9621738D0 (en) 1996-12-11
GB2307525A true GB2307525A (en) 1997-05-28
GB2307525B GB2307525B (en) 1999-06-16

Family

ID=10782898

Family Applications (2)

Application Number Title Priority Date Filing Date
GBGB9521868.1A Pending GB9521868D0 (en) 1995-10-25 1995-10-25 Improvements in electrically-operated disc brake assemblies for vehicles
GB9621738A Expired - Fee Related GB2307525B (en) 1995-10-25 1996-10-18 Improvements in electrically-operated disc brake assemblies for vehicles

Family Applications Before (1)

Application Number Title Priority Date Filing Date
GBGB9521868.1A Pending GB9521868D0 (en) 1995-10-25 1995-10-25 Improvements in electrically-operated disc brake assemblies for vehicles

Country Status (2)

Country Link
DE (1) DE19644441B4 (en)
GB (2) GB9521868D0 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2329434A (en) * 1997-09-23 1999-03-24 Daimler Benz Ag Brake actuator
US6598714B1 (en) * 1998-01-27 2003-07-29 Sfk Engineering And Research Centre B.V. Actuator comprising flexible element, and brake calliper comprising such actuator
US6837342B1 (en) * 1999-11-18 2005-01-04 Skf Engineering & Research Centre B.V. Actuator having a central support and brake calliper comprising such actuator

Families Citing this family (17)

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DE19719510A1 (en) * 1997-05-09 1998-11-12 Schaeffler Waelzlager Ohg Motion conversion device
DE19741865C1 (en) * 1997-09-23 1998-06-18 Daimler Benz Ag Automobile brake actuator using electric motor
WO1999027272A1 (en) 1997-11-21 1999-06-03 Continental Teves Ag & Co. Ohg Electrically actuated brake device for motor vehicles
DE19817892A1 (en) * 1998-04-22 1999-10-28 Continental Teves Ag & Co Ohg Actuator for disc brake unit with new arrangement of hydraulically operated pistons
DE19843178C1 (en) * 1998-09-21 2000-03-16 Siemens Ag Braking system for motor vehicle
WO2000017537A1 (en) 1998-09-21 2000-03-30 Siemens Aktiengesellschaft Electromechanical vehicle braking device
DE10150803B4 (en) * 2001-10-15 2006-08-17 Lucas Automotive Gmbh Hydraulic vehicle brake with electrically operated locking device
DE112009004842B4 (en) 2009-06-02 2023-06-01 Harmonic Drive Systems Inc. Wave type linear motion mechanism
KR20110124818A (en) * 2010-05-12 2011-11-18 주식회사 만도 Electric disc brake
DE102011007772B4 (en) * 2011-04-20 2024-03-28 Robert Bosch Gmbh Method for adjusting the clamping force exerted by a parking brake
DE102012214509A1 (en) * 2012-05-10 2013-11-14 Continental Teves Ag & Co. Ohg Device for e.g. providing air clearance between brake lining and brake disk of electromechanical service brake in motor car, has ring element allowing balls to be moved away or inclined from ring in released position of ring element
WO2015149767A1 (en) * 2014-04-01 2015-10-08 Schaeffler Technologies AG & Co. KG Operation actuator
CN109424668B (en) * 2017-08-29 2020-08-25 比亚迪股份有限公司 Disc brake and vehicle
CN109990018B (en) * 2017-12-29 2020-11-06 比亚迪股份有限公司 Disc brake and vehicle with same
DE102018111126A1 (en) * 2018-05-09 2019-11-14 Ipgate Ag Brake system, especially for automated driving
CN110701215B (en) * 2019-09-29 2021-03-26 哈尔滨哈飞航空工业有限责任公司 Electric control electric rotor wing braking system
DE102022201451A1 (en) * 2022-02-11 2023-08-17 Robert Bosch Gesellschaft mit beschränkter Haftung Individual wheel braking unit and braking system for a vehicle

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GB1275241A (en) * 1970-01-05 1972-05-24 Toyota Motor Co Ltd Disk brake for vehicles

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US5348123A (en) * 1991-09-02 1994-09-20 Akebono Brake Industry Co., Ltd. Brake actuating apparatus for a vehicle
DE4312524A1 (en) * 1993-04-16 1994-10-20 Bosch Gmbh Robert Wheel brake for vehicles, in particular for motor vehicles
DE19519308C2 (en) * 1995-05-26 1999-01-21 Continental Ag Brake actuator with gear
DE19529791C2 (en) * 1995-08-12 1999-02-11 Continental Ag Brake actuator with adjuster

Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
GB1275241A (en) * 1970-01-05 1972-05-24 Toyota Motor Co Ltd Disk brake for vehicles

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2329434A (en) * 1997-09-23 1999-03-24 Daimler Benz Ag Brake actuator
GB2329434B (en) * 1997-09-23 1999-08-11 Daimler Benz Ag Brake actuator
US6098762A (en) * 1997-09-23 2000-08-08 Daimlerchrysler Ag Brake actuator
US6598714B1 (en) * 1998-01-27 2003-07-29 Sfk Engineering And Research Centre B.V. Actuator comprising flexible element, and brake calliper comprising such actuator
US6837342B1 (en) * 1999-11-18 2005-01-04 Skf Engineering & Research Centre B.V. Actuator having a central support and brake calliper comprising such actuator

Also Published As

Publication number Publication date
GB2307525B (en) 1999-06-16
DE19644441B4 (en) 2007-06-21
GB9621738D0 (en) 1996-12-11
DE19644441A1 (en) 1997-04-30
GB9521868D0 (en) 1996-01-03

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Legal Events

Date Code Title Description
732E Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977)
732E Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977)
PCNP Patent ceased through non-payment of renewal fee

Effective date: 20071018