EP3548347A1 - Maître-cylindre et système de freinage - Google Patents

Maître-cylindre et système de freinage

Info

Publication number
EP3548347A1
EP3548347A1 EP17784250.7A EP17784250A EP3548347A1 EP 3548347 A1 EP3548347 A1 EP 3548347A1 EP 17784250 A EP17784250 A EP 17784250A EP 3548347 A1 EP3548347 A1 EP 3548347A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
hydraulic
piston
brake
master
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.)
Withdrawn
Application number
EP17784250.7A
Other languages
German (de)
English (en)
Inventor
Simon Hansmann
Dirk Foerch
Matthias Kistner
Florent Yvonet
Raynald Sprocq
Chris Anderson
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3548347A1 publication Critical patent/EP3548347A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • B60T13/10—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 fluid assistance, drive, or release
    • B60T13/12—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 fluid assistance, drive, or release the fluid being liquid
    • B60T13/14—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 fluid assistance, drive, or release the fluid being liquid using accumulators or reservoirs fed by pumps
    • B60T13/142—Systems with master cylinder
    • 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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • 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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/20—Tandem, side-by-side, or other multiple master cylinder units
    • 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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/165—Single master cylinders for pressurised systems
    • 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
    • B60T13/10—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 fluid assistance, drive, or release
    • B60T13/12—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 fluid assistance, drive, or release the fluid being liquid
    • B60T13/16—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 fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
    • B60T13/161—Systems with master cylinder
    • B60T13/165—Master cylinder integrated or hydraulically coupled with booster
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/81—Braking systems

Definitions

  • the invention relates to a master brake cylinder for a brake system of a brake master cylinder
  • Hydraulic cylinder in which at least one hydraulic piston is mounted axially displaceable in an actuating direction and in a discharge direction, wherein the hydraulic piston is displaceable in the actuating direction against the force of a spring element, and wherein the spring element is assigned a bondage, which limits the maximum spring relief.
  • the invention relates to a brake system for a motor vehicle with such a master cylinder.
  • Hydraulic piston in the hydraulic cylinder a volume in the interior of the hydraulic cylinder is reduced, whereby a fluid located thereon is pressurized and through at least one of the hydraulic connections from the
  • Main cylinder is fed out to actuate at least one of the wheel brakes. If the driver removes his foot from the brake pedal, that sums it up tensioned spring element by its inherent elasticity of the hydraulic piston back to its original position, at the same time hydraulic medium passes through the hydraulic connections in the hydraulic cylinder, so that then the master cylinder is prepared for a further braking operation available.
  • the master cylinder according to the invention with the features of claim 1 has the advantage that the bondage has an ankle cylinder and an in the ankle cylinder axially displaceably mounted restoring piston, wherein the restraint cylinder has at least one jacket wall opening, so that a
  • Interior of the tether cylinder communicates with an interior of the master cylinder. Through the casing wall opening, a connection is created between the interior of the hydraulic cylinder and the interior of the tether cylinder, through which the fluid in the hydraulic cylinder also flows into the interior of the tether cylinder.
  • the movement of the restraining piston in the restraining cylinder is also determined as a function of the pressure conditions in the interior of the restraining cylinder which result from the inflow or outflow of fluid. This will be a
  • Hydraulic piston is limited to a permissible value in a movement in the discharge direction. This will be a hard stop of
  • the master cylinder is also a
  • pedal force simulator which at least one
  • Hydraulic accumulator has or forms, which the actuation of the
  • the damped spring throttling reduces the acceleration of the brake pedal when the actuation force is removed, so that the brake pedal can move into its rest position without any further acceleration, whereby the brake pedal is prevented from oscillating or an acoustically perceptible striking of the brake pedal in its rest position.
  • shell wall opening is arranged in the anvil cylinder in such a way that the damping operation
  • Mantle wall opening opens into a section in the tether cylinder, in which the tether piston in a displacement of the hydraulic piston in
  • Bonding cylinder which is formed free of mantle, so that in the remaining chamber, a fluid counteracts the movement of the piston, thereby ensuring the damping.
  • Mantle wall opening or shell wall openings is thus adjustable in a simple manner, the damping effect of the bondage.
  • the tether piston is guided radially at least substantially close to the tether cylinder. This ensures the effect described above, that the fluid in the closed chamber between
  • Tether piston and ankle cylinder movement in the unloading direction is essentially locked and the movement of the tether piston counteracts.
  • the spring element is held axially biased between the end plates.
  • the bondage is thus formed at their ends by the end plates, between which the spring element is held axially biased.
  • the spring element always urges the captive piston away from the front disk of the tether cylinder.
  • the front disk of the tether piston is arranged on a piston rod, which leads through an end wall of the tether cylinder into the tether cylinder and is fixedly connected there to the tether piston.
  • the ratio of the outer diameter of the piston rod to the inner diameter of the opening in the end face of the tether cylinder further affects the damping of the bondage when the piston is moved away in the direction of the front side of the forelock piston.
  • Piston rod and end wall opening to form a defined leakage gap thus the damping of the bondage can be influenced advantageously.
  • the spring element is designed as a helical spring and arranged coaxially to captive piston and ankle cylinder. This form the
  • Bonding piston, the anvil cylinder and the clamped between the end plates of this coil spring an advantageous assembly unit, which can be prefabricated and easily arranged in the hydraulic cylinder.
  • At least one of the end plates is fixedly connected to the hydraulic piston.
  • the piston rod is fixedly connected to the hydraulic piston, which then forms the front plate for the tether piston.
  • Acceleration of the brake pedal or the hydraulic piston is attenuated or limited in the discharge, but that actively the movement of the brake pedal and the hydraulic piston are braked. This is particularly advantageous in terms of the pedal, because this prevents too fast running back of the brake pedal and the user
  • the feeling of a conventional brake pedal is simulated, which is given in conventional brake systems with vacuum brake booster.
  • the other of the end discs with the hydraulic cylinder, in particular with an end wall of the hydraulic cylinder is firmly connected.
  • the master cylinder as
  • Tandem cylinder formed with a further hydraulic piston, which is arranged axially displaceable in the master cylinder against the force of another spring element and between the hydraulic piston and a front end of the hydraulic cylinder. Tandem cylinders are already known from the prior art, so that at this point should not be discussed in detail on its structure. It is important that a tandem cylinder has not one, but two hydraulic pistons arranged in series in the
  • Hydraulic cylinders are arranged.
  • the further hydraulic piston ensures that a further brake circuit is operated independently of a first brake circuit actuated by the hydraulic piston through the master brake cylinder.
  • the further hydraulic piston associated with a further bondage which is formed as described above bondage. This ensures that the total of the tandem cylinder, the pressing movement of the
  • Brake pedal dampens and optionally brakes, especially if the other bondage is also firmly connected to the other hydraulic piston on the one hand and the front side of the hydraulic cylinder on the other.
  • the former restraint is expediently firmly connected to the one hydraulic piston and the other hydraulic piston and thus lies axially between them.
  • the brake system according to the invention with the features of claim 10 is characterized by the inventive design of the master cylinder. This results in the already mentioned advantages. Furthermore, the invention relates to a brake system for a motor vehicle, with a master cylinder, which is connected to at least one hydraulic circuit having at least one hydraulically actuated wheel brake.
  • Figure 1 is a brake system of a motor vehicle in a simplified
  • FIG 3 shows the master cylinder according to a second embodiment, each in a simplified longitudinal sectional view.
  • Figure 1 shows a simplified illustration of a brake system 1 for a motor vehicle, not shown in detail.
  • the brake system 1 has a
  • Master brake cylinder 2 which is designed as a tandem cylinder and can be actuated by a brake pedal 3 by a driver of the motor vehicle.
  • Master brake cylinder in this case has a hydraulic cylinder 4, in which a hydraulic piston 5, which is mechanically fixedly connected to the brake pedal 3, and a further hydraulic piston 6 are each mounted axially displaceable. Between the hydraulic piston 5 and the hydraulic piston 6 is a hydraulic piston 5, which is mechanically fixedly connected to the brake pedal 3, and a further hydraulic piston 6 are each mounted axially displaceable. Between the hydraulic piston 5 and the hydraulic piston 6 is a hydraulic piston 5, which is mechanically fixedly connected to the brake pedal 3, and a further hydraulic piston 6 are each mounted axially displaceable. Between the hydraulic piston 5 and the hydraulic piston 6 is a hydraulic piston 5, which is mechanically fixedly connected to the brake pedal 3, and a further hydraulic piston 6 are each mounted axially displaceable. Between the hydraulic piston 5 and the hydraulic piston 6 is a hydraulic piston 5, which is mechanically fixedly connected to the brake pedal 3, and a further hydraulic piston 6 are each mounted axially displaceable. Between the hydraulic piston 5 and the hydraulic piston 6 is a hydraulic piston 5, which is mechanically fixedly connected to
  • Hydraulic cylinder 4 are formed, with hydraulic connections of the
  • Brake system 1 communicate.
  • two brake circuits 9 and 10 are connected to the master cylinder 2 by the hydraulic connections such that one of the brake circuits 9 with one of the hydraulic chambers and the other the brake circuits 10 is fluidly connected to the other hydraulic chamber.
  • the two brake circuits 9 and 10 are constructed substantially identical to each other.
  • Each brake circuit 9, 10 has two wheel brakes LR, RF
  • LF, RR which can be actuated by intake valves 11 and exhaust valves 12 in the respective brake circuit 9, 10.
  • the brake circuits 9, 10 are connected by high-pressure switching valves 13 each with one of the chambers of the master cylinder 2.
  • Brake circuits 9, 10 can be penetrated by actuation of the master cylinder 2.
  • the present brake system 1 is provided that on a
  • Vacuum brake booster is omitted. Therefore, the brake pedal 3 is also directly connected mechanically to the hydraulic piston 5.
  • the brake system 1 also has a brake pedal feel simulator 15, which has a switching valve 16 and a pressure accumulator 17.
  • the brake pedal feel simulator 15 functions to influence the pedal movement of the brake pedal 3 so as to correspond or nearly correspond to that of a brake pedal connected to a vacuum booster. This provides the driver with the accustomed brake pedal feel available.
  • an electromechanical brake booster 18 having a pump 19, in this case piston pump, which is driven by an electric motor 20 to increase a hydraulic pressure in the brake circuits 9, 10, if necessary.
  • the brake circuits 9, 10 are connected by a respective switching valve 21 to the brake booster 18.
  • Each of the spring elements 7, 8 is associated with a bond 22 or 23.
  • the two bondings 22, 23 are the same design, so that in the following structure and function of the two bonds with reference to the bond 22 will be explained in more detail.
  • the bondage 22 has an ankle cylinder 24, in which a
  • Tether piston 25 is mounted axially displaceable.
  • the anvil cylinder 24 is aligned coaxially with the hydraulic cylinder 4, so that the
  • Hydraulic piston 5, 6 corresponds.
  • the tether cylinder 24 has on a first end face an end plate 25 and on its second end face a
  • Bonding piston 25 is connected.
  • the piston rod 28 carries at her the
  • the spring element 7, 8 is designed as a helical spring which extends coaxially to the anvil cylinder 24 and the piston rod 28. Because the tether piston 25 is formed larger than the passage openings of the end wall 27, the tether piston 25 can be displaced maximally to the end wall 27. This limits the maximum
  • the tether piston 25 is radially sealing or at least substantially sealingly on the
  • a leakage gap remains.
  • piston rod 28 and through hole are formed such that a leakage gap is formed between them, so that a fluid from the chamber between the captive piston 25 and the end wall 27 in the ankle cylinder 24 through the leakage gap either directly into the interior of the Hydraulic cylinder 4 can enter, or in the hydraulic chamber between the captive piston 25 and end plate 26th
  • tether cylinder 24 In the tether cylinder 24 a plurality of shell wall openings 30 are formed, which are arranged close to the end plate 26. Through the jacket wall openings 30, the chamber is in the restraint cylinder 24 (between end plate 26 and restraint piston 25) in fluid communication with the interior of the
  • Hydraulic cylinder between the two hydraulic pistons 5 and 6
  • Movement speed of the tether piston 25 is limited in the anvil cylinder 24 and thus slows down the expansion behavior of the respective spring element 7, 8. This ensures that the respective spring element 7, 8 initially expands quickly and then only slowly to his
  • Mantle wall openings 30 is also the bondage 22 or 23 upon actuation of the brake pedal 3 when the hydraulic piston 5 in
  • Actuating direction as shown by an arrow 31, are shifted, within the tether cylinder 24 slightly slidable until the
  • Ankle cylinder 24 is formed.
  • Federfesselung 22 and 23 is also the accelerating moment of the spring elements 7, 8 limited, whereby the brake pedal 3 can run without further acceleration in its rest position, without causing a noise and / or vibrations on the pedal when reaching the selbigen.
  • Figure 3 shows an advantageous development of the master cylinder 3, wherein from Figure 2 already known elements are provided with the same reference numerals and insofar reference is made to the above description.
  • welds 32 are shown in FIG. 3 by way of example.
  • Vacuum brake booster is achieved.
  • impact sounds and / or generated by a hard impact are used in the brake system 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Braking Elements And Transmission Devices (AREA)
  • Braking Systems And Boosters (AREA)

Abstract

L'invention concerne un maître-cylindre(2) pour un système de freinage (1) d'un véhicule à moteur, comprenant un vérin hydraulique (4) présentant plusieurs raccords hydrauliques, dans lequel est logé au moins un piston hydraulique (5, 6) de manière à pouvoir se déplacer axialement dans un sens d'actionnement et dans un sens de décharge, le piston hydraulique (5, 6) pouvant être déplacé dans le sens d'actionnement à l'encontre de la force d'un élément ressort (7, 8), l'élément ressort (7, 8) étant associé à un élément de retenue (22, 23) qui limite la décharge maximale du ressort. Selon l'invention, l'élément de retenue (22, 23) présente un cylindre de retenue (24) et un piston de retenue (25) monté de manière à pouvoir coulisser axialement dans le cylindre de retenue (24), le cylindre de retenue (24) présentant au moins une ouverture de paroi extérieure (30) de sorte qu'un espace intérieur du cylindre de retenue (24) communique avec un espace intérieur du vérin hydraulique (4).
EP17784250.7A 2016-11-30 2017-10-05 Maître-cylindre et système de freinage Withdrawn EP3548347A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016223760.8A DE102016223760A1 (de) 2016-11-30 2016-11-30 Hauptbremszylinder, Bremsanlage
PCT/EP2017/075335 WO2018099638A1 (fr) 2016-11-30 2017-10-05 Maître-cylindre et système de freinage

Publications (1)

Publication Number Publication Date
EP3548347A1 true EP3548347A1 (fr) 2019-10-09

Family

ID=60083965

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17784250.7A Withdrawn EP3548347A1 (fr) 2016-11-30 2017-10-05 Maître-cylindre et système de freinage

Country Status (8)

Country Link
US (1) US20200079337A1 (fr)
EP (1) EP3548347A1 (fr)
JP (1) JP2019535595A (fr)
KR (1) KR102410780B1 (fr)
CN (1) CN109996708B (fr)
DE (1) DE102016223760A1 (fr)
GB (1) GB2558413A (fr)
WO (1) WO2018099638A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102668949B1 (ko) * 2019-04-26 2024-05-24 현대모비스 주식회사 차량용 제동장치

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DE3040562A1 (de) * 1980-10-28 1982-05-27 Alfred Teves Gmbh, 6000 Frankfurt Fremdenergiegespeiste bremsschlupfregelanlage eines hydraulischen fahrzeugbremssystems
DE3523372A1 (de) * 1985-06-29 1987-01-02 Teves Gmbh Alfred Bremsdruckgeber fuer eine hydraulische bremsanlage, insbesondere fuer kraftfahrzeuge
DE3533255A1 (de) * 1985-09-18 1987-03-19 Teves Gmbh Alfred Fremdenergiegespeiste bremsschlupfregelanlage eines hydraulischen fahrzeugbremssystems
DE3725249A1 (de) * 1987-07-30 1989-02-09 Teves Gmbh Alfred Hydraulischer kraftverstaerker
EP1686028A2 (fr) * 1995-12-20 2006-08-02 Kelsey-Hayes Company Maître-cylindre avec butée pour piston
JP2000177576A (ja) * 1998-12-14 2000-06-27 Bosch Braking Systems Co Ltd 液圧発生装置
JP2002002475A (ja) * 2000-06-23 2002-01-09 Bosch Braking Systems Co Ltd マスタシリンダ
JP2005112188A (ja) * 2003-10-08 2005-04-28 Advics:Kk マスタシリンダ
JP4563343B2 (ja) * 2006-05-31 2010-10-13 日立オートモティブシステムズ株式会社 マスタシリンダ
JP4537435B2 (ja) * 2007-09-05 2010-09-01 日信工業株式会社 シリンダ装置
JP5126039B2 (ja) * 2008-12-09 2013-01-23 株式会社アドヴィックス ストロークシミュレータ内蔵マスタシリンダ
DE102009054695A1 (de) * 2009-12-15 2011-06-16 Continental Teves Ag & Co. Ohg Hauptzylinder für ein geregeltes Bremssystem
JP2012210905A (ja) * 2011-03-31 2012-11-01 Advics Co Ltd マスタシリンダ
DE102011075359A1 (de) * 2011-05-05 2012-11-08 Continental Teves Ag & Co. Ohg Hauptzylinder insbesondere für ein geregeltes Bremssystem
CN202294757U (zh) * 2011-09-22 2012-07-04 余姚市安统五金有限公司 汽车液压总泵
DE102011083827A1 (de) * 2011-09-30 2013-04-04 Robert Bosch Gmbh Primärkolbenbaugruppe für einen Hauptbremszylinder eines Bremssystems eines Fahrzeugs, Herstellungsverfahren für ein Bremsgerät und Verfahren zum Betreiben eines Bremsgeräts
KR101302617B1 (ko) * 2011-10-07 2013-09-03 주식회사 만도 차량용 마스터 실린더
EP2832596B1 (fr) * 2012-03-30 2017-04-19 Honda Motor Co., Ltd. Dispositif de freinage
CN104110452A (zh) * 2013-04-16 2014-10-22 京西重工（上海）有限公司 制动系统中的主缸总成以及活塞止挡件
US9393942B2 (en) * 2013-11-01 2016-07-19 Beijingwest Industries, Co., Ltd. Composite spring retainer and method of assembly in a brake master cylinder
JP6209147B2 (ja) * 2014-09-30 2017-10-04 オートリブ日信ブレーキシステムジャパン株式会社 シリンダ装置および車両用ブレーキシステム
JP6209148B2 (ja) * 2014-09-30 2017-10-04 オートリブ日信ブレーキシステムジャパン株式会社 シリンダ装置および車両用ブレーキシステム
CN105459988B (zh) * 2014-09-30 2019-06-07 日本奥托立夫日信制动器系统株式会社 液压缸装置及车辆用制动系统
CN204915654U (zh) * 2015-08-27 2015-12-30 芜湖玉泰汽车制动有限公司 汽车制动总泵的活塞总成

Also Published As

Publication number Publication date
KR102410780B1 (ko) 2022-06-20
GB201719772D0 (en) 2018-01-10
US20200079337A1 (en) 2020-03-12
JP2019535595A (ja) 2019-12-12
DE102016223760A1 (de) 2018-05-30
KR20190087587A (ko) 2019-07-24
GB2558413A (en) 2018-07-11
CN109996708B (zh) 2022-04-15
WO2018099638A1 (fr) 2018-06-07
CN109996708A (zh) 2019-07-09

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