GB1590003A - Hydraulic systems - Google Patents

Hydraulic systems Download PDF

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Publication number
GB1590003A
GB1590003A GB4028477A GB4028477A GB1590003A GB 1590003 A GB1590003 A GB 1590003A GB 4028477 A GB4028477 A GB 4028477A GB 4028477 A GB4028477 A GB 4028477A GB 1590003 A GB1590003 A GB 1590003A
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GB
United Kingdom
Prior art keywords
damping chamber
pressure
pump
valve
brake
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.)
Expired
Application number
GB4028477A
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 GB1590003A publication Critical patent/GB1590003A/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • 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
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4068—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system the additional fluid circuit comprising means for attenuating pressure pulsations
    • 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
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
    • B60T8/4275—Pump-back systems
    • B60T8/4291—Pump-back systems having means to reduce or eliminate pedal kick-back
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
    • 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
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/04—Devices damping pulsations or vibrations in fluids

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Regulating Braking Force (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

(54) IMPROVEMENTS IN OR RELATING TO HYDRAULIC SYSTEMS (71) We, ROBERT BOSCH GMBH. a German Company, of Postfach 50, 7 Stuttgart 1, Federal Republic of Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement: The present invention relates to hydraulic systems.
In hydraulic systems equipped with a pump for producing hydraulic pressure, it is known to use a storage device in the form of a piston and spring storage device or a diaphragm storage device having a gas spring.
However, piston and spring storage devices are very expensive. Diaphragm storage devices with gas springs have an unsuitable characteristic for applications in which there is too great a variation of volume.
In hydraulic anti-lock systems for vehicle wheel braking systems, such as those described in German Offenlegungsschrift 2,010,484, there is the problem that hydraulic oscillations cause troublesome sounds and/or can be detected on the brake pedal in a troublesome manner. If the oscillations occur between a solenoid valve and a wheel brake cylinder, they influence the detection signals provided by sensors responsive to wheel rotation such that the anti-brake system can no longer operate satisfactorily.
According to the present invention there is provided a hydraulic system comprising a pressure oscillation producer and arranged in series and/or in parallel with the pressure oscillation producer a pressure-resistant damping chamber which has a stiffness made greater than the compressibility of the hydraulic fluid and which has an interior crosssection exceeding that of a conduit within which the pressure oscillations are to be damped.
A hydraulic system embodying the present invention has the advantage that the oscillations in the system can be damped such that they are no longer troublesome. Thus, noises in the system can be avoided and when applied to a vehicle braking system there are no troublesome oscillations on a brake pedal.
Furthermore, when applied to an anti-lock system for a vehicle braking system it can be ensured that sensors responsive to wheel rotation do not produce false signals which would jeopardize the operation of the antilock system.
The present invention will be further described by way of example, with reference to the accompanying drawings, in which: Fig. 1 shows diagrammatically a first embodiment of the invention incorporated in a portion of an hydraulic anti-lock system for a vehicle wheel braking system Fig. 2 is a section through a pump housing including a damping chamber, Fig. 3 shows diagrammatically a second embodiment of the invention incorporated in a portion of another hydraulic anti-lock system for a vehicle wheel braking system, Fig. 4 is a section through a damping chamber in the second embodiment of the invention shown in Fig. 3, Figs. 5 and 6 each show the second embodiment of the invention incorporated in a portion of a respective modification of the antilock system shown in Fig. 3, and Fig. 7 shows partly diagrammatically a further embodiment of the invention including a modified damping chamber.
In Fig. 1 there is shown a portion of a vehicle wheel braking system including an anti-lock system and comprising a feed pump 1 having a pump piston 1' for feeding hydraulic fluid to a master brake cylinder 34.
When in operation the pump 1 produces pressure oscillations in the hydraulic fluid.
The hydraulic fluid flows by way of a pump outlet valve 2 into a damping chamber 3 which has a stiffness much greater than the compressibility of the hydraulic fluid. Thus the damping chamber has a specific, relatively small volume change AV. The change depends upon the compressibility p of the fluid, the volume V of the damping chamber, and the pressure change Ap in the fluid. Consequently, a formula for the change in volume is AV = p . V. Ap.
A throttle 4 and the master brake cylinder 34 are located downstream of the damping chamber 3, Fluid is fed from the master cylinder 34 to a multi-position solenoid valve 6 which as part of the anti-lock system regulates brake pressure in a brake conduit 7 leading to a wheel brake cylinder 8. The solenoid valve 6 can be by-passed by means of a non-return valve 9 to release the brake, and a low-pressure store 10, from which the pump 1 receives fluid by way of an inlet valve 11, is connected to the solenoid valve 6.
Fig. 2 shows a section through a housing 12 which accommodates the damping chamber 3, the pump 1, the outlet valve 2 and, if required, the throttle 4. The solenoid valve 6, and a motor 13 for driving the pump 1, are secured to the housing 12.
It will be seen that the damping chamber 3 can be manufactured very simply. The damping chamber comprises a bore 14 in the bottom of which is fitted the outlet valve 2. The bore 14 has, as can be seen from Fig. 2, a cross-section exceeding that of a conduit within which oscillations are to be damped and is sealed towards the outside by means of a screw-threaded sealing cap 15. Thus, the damping chamber 3 has no moving parts and no dynamic seals and thus involves only low costs. The damping chamber is metallic and pressure-resistant, although it may be mentioned that "pressure resistant" can mean "not fully unresilient". However, the resilience of the chamber is negligible compared with the resilience of the fluid so that as previously mentioned the stiffness of the damping chamber is much greater than the responsibility of the fluid. Owing to the small volume of the chamber, it requires only a small amount of space. It can be satisfactorily bled and have great operational reliability.
Pressure oscillations produced in the hydraulic fluid by the pump 1 are suppressed by virtue of the arrangement of the damping chamber 3 which is connected downstream of the pump 1. Troublesome noises can be avoided as well as any oscillations which might confuse the driver by way of the brake pedal.
It is also important that the damping chamber 3 can be arranged in series and/or in parallel with the pressure oscillation producer as illustrated in Fig. 1.
Fig. 3 shows a portion of another hydraulic anti-lock system. In this instance, a solenoid valve 16 which can produce pressure oscillation is connected to a wheel brake cylinder 19 in series with a damping chamber 17 and a throttle 18. Alternatively, the throttle 18 may be omitted. The solenoid valve 16 may be by-passed in the brake release direction by means of a non-return valve 20.
A housing 21, accommodating the damping chamber 17, is shown in section in Fig. 4.
The damping chamber 17 is sealed towards the outside by means of a cap 22 having a screw-threaded connection 23 for a brake conduit 24 leading to the wheel brake cylinder 19. This damping chamber 17 is just as advantageous as the damping chamber 3 of Fig. 2.
Furthermore, by virtue of the arrangement of the damping chamber 17, the sensors associated with the wheels cannot produce false signals and jeopardize the operation of the anti-lock system as a result of irregular rotation of the wheels that could be caused by pressure oscillations occurring during rapid switching of the solenoid valves.
Figs. 5 and 6 show the same portion of a braking system as is shown in Fig. 3. The difference resides only in the arrangement of the respective solenoid valves. The embodiments of Figs. 5 and 6 have identical solenoid inlet valves 25; in the embodiment of Fig. 5, a solenoid outlet valve 26 is arranged in series with the damping chamber 17, while, in Fig.
6, a solenoid outlet valve 27 of different construction is arranged in parallel with the damping chamber 17. In the embodiments of Figs. 5 and 6 both the solenoid valves 25, 26 or 25, 27 can produce pressure oscillations and the damping chamber 17 is in each embodiment connected in series with both solenoid valves.
Fig. 7 shows a modification of the damping chamber. In this instance, a damping chamber 30 is provided with a non-return valve 31 which is controllable by means of a spring-loaded piston 32.
The non-return valve 31 controls communication between the pump 1 and the master brake cylinder 34 which is connected to a passage 33, a solenoid valve 36 being connected to a passage 35, and a brake cylinder 37 acting as a load being connected downstream of the solenoid valve 36.
The master cylinder 34 produces nonoscillating pressures, although the pump 1 when in operation produces pressure oscillations: these oscillations are damped by the damping chamber 30 which is connected downstream of the pump 1. The non-return valve 31 is normally open, and closes when the pressure in the damping chamber 30 has risen to approximately 5 bar. It opens automatically when the pressure in the damping chamber 30 is higher than the pressure of the master cylinder.
WHAT WE CLAIM IS: 1. A hydraulic system, comprising a pressure oscillation producer, and arranged in series and/or in parallel with the pressure
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (9)

  1. **WARNING** start of CLMS field may overlap end of DESC **.
    the damping chamber has a specific, relatively small volume change AV. The change depends upon the compressibility p of the fluid, the volume V of the damping chamber, and the pressure change Ap in the fluid. Consequently, a formula for the change in volume is AV = p . V. Ap.
    A throttle 4 and the master brake cylinder 34 are located downstream of the damping chamber 3, Fluid is fed from the master cylinder 34 to a multi-position solenoid valve 6 which as part of the anti-lock system regulates brake pressure in a brake conduit 7 leading to a wheel brake cylinder 8. The solenoid valve 6 can be by-passed by means of a non-return valve 9 to release the brake, and a low-pressure store 10, from which the pump 1 receives fluid by way of an inlet valve 11, is connected to the solenoid valve 6.
    Fig. 2 shows a section through a housing 12 which accommodates the damping chamber 3, the pump 1, the outlet valve 2 and, if required, the throttle 4. The solenoid valve 6, and a motor 13 for driving the pump 1, are secured to the housing 12.
    It will be seen that the damping chamber 3 can be manufactured very simply. The damping chamber comprises a bore 14 in the bottom of which is fitted the outlet valve 2. The bore 14 has, as can be seen from Fig. 2, a cross-section exceeding that of a conduit within which oscillations are to be damped and is sealed towards the outside by means of a screw-threaded sealing cap 15. Thus, the damping chamber 3 has no moving parts and no dynamic seals and thus involves only low costs. The damping chamber is metallic and pressure-resistant, although it may be mentioned that "pressure resistant" can mean "not fully unresilient". However, the resilience of the chamber is negligible compared with the resilience of the fluid so that as previously mentioned the stiffness of the damping chamber is much greater than the responsibility of the fluid. Owing to the small volume of the chamber, it requires only a small amount of space. It can be satisfactorily bled and have great operational reliability.
    Pressure oscillations produced in the hydraulic fluid by the pump 1 are suppressed by virtue of the arrangement of the damping chamber 3 which is connected downstream of the pump 1. Troublesome noises can be avoided as well as any oscillations which might confuse the driver by way of the brake pedal.
    It is also important that the damping chamber 3 can be arranged in series and/or in parallel with the pressure oscillation producer as illustrated in Fig. 1.
    Fig. 3 shows a portion of another hydraulic anti-lock system. In this instance, a solenoid valve 16 which can produce pressure oscillation is connected to a wheel brake cylinder 19 in series with a damping chamber 17 and a throttle 18. Alternatively, the throttle 18 may be omitted. The solenoid valve 16 may be by-passed in the brake release direction by means of a non-return valve 20.
    A housing 21, accommodating the damping chamber 17, is shown in section in Fig. 4.
    The damping chamber 17 is sealed towards the outside by means of a cap 22 having a screw-threaded connection 23 for a brake conduit 24 leading to the wheel brake cylinder 19. This damping chamber 17 is just as advantageous as the damping chamber 3 of Fig. 2.
    Furthermore, by virtue of the arrangement of the damping chamber 17, the sensors associated with the wheels cannot produce false signals and jeopardize the operation of the anti-lock system as a result of irregular rotation of the wheels that could be caused by pressure oscillations occurring during rapid switching of the solenoid valves.
    Figs. 5 and 6 show the same portion of a braking system as is shown in Fig. 3. The difference resides only in the arrangement of the respective solenoid valves. The embodiments of Figs. 5 and 6 have identical solenoid inlet valves 25; in the embodiment of Fig. 5, a solenoid outlet valve 26 is arranged in series with the damping chamber 17, while, in Fig.
    6, a solenoid outlet valve 27 of different construction is arranged in parallel with the damping chamber 17. In the embodiments of Figs. 5 and 6 both the solenoid valves 25, 26 or 25, 27 can produce pressure oscillations and the damping chamber 17 is in each embodiment connected in series with both solenoid valves.
    Fig. 7 shows a modification of the damping chamber. In this instance, a damping chamber 30 is provided with a non-return valve 31 which is controllable by means of a spring-loaded piston 32.
    The non-return valve 31 controls communication between the pump 1 and the master brake cylinder 34 which is connected to a passage 33, a solenoid valve 36 being connected to a passage 35, and a brake cylinder 37 acting as a load being connected downstream of the solenoid valve 36.
    The master cylinder 34 produces nonoscillating pressures, although the pump 1 when in operation produces pressure oscillations: these oscillations are damped by the damping chamber 30 which is connected downstream of the pump 1. The non-return valve 31 is normally open, and closes when the pressure in the damping chamber 30 has risen to approximately 5 bar. It opens automatically when the pressure in the damping chamber 30 is higher than the pressure of the master cylinder.
    WHAT WE CLAIM IS: 1. A hydraulic system, comprising a pressure oscillation producer, and arranged in series and/or in parallel with the pressure
    oscillation producer a pressure-resistant damping chamber which has a stiffness much greater than the compressibility of the hydraulic fluid and which has an interior crosssection exceeding that of a conduit within which the pressure oscillations are to be damped.
  2. 2. A hydraulic system as claimed in claim 1, forming part of a wheel anti-lock system for a vehicle braking system, and in which the pressure oscillation producer is brake fluid feed pump and the damping chamber is disposed in the housing of the pump.
  3. 3. A hydraulic system as claimed in claim 2, in which the damping chamber is arranged directly in series with an outlet valve of the pump.
  4. 4. A hydraulic system as claimed in claim 1, forming part of a wheel anti-lock system for a vehicle braking system, and in which the pressure oscillation producer is a solenoid valve the damping chamber is arranged in series with the solenoid valve of the anti-lock system and a brake cylinder.
  5. 5. A hydraulic system as claimed in any of claims 1 to 4, in which a throttle is arranged in series with the damping chamber.
  6. 6. A hydraulic system as claimed in claim 1, forming part of a wheel anti-lock system for a vehicle braking system, and in which the pressure oscillation producer is a brake fluid feed pump and the braking system has a master brake cylinder as a non-oscillating pressure producer, and in which there is provided in series with the damping chamber a nonreturn valve which controls communication between the pump and the vehicle braking system and is connected to a control piston which maintains the non-return valve in its open position when the damping chamber is non-pressurized.
  7. 7. A hydraulic system including a pressure oscillation producer and a pressure resistant damping chamber, constructed and arranged and adapted to operate substantially as hereinbefore particularly described with reference to and as illustrated in Figs. 1 and 2 of the accompanying drawings.
  8. 8. A hydraulic system including a pressure oscillation producer and a pressure resistant damping chamber, constructed and arranged and adapted to perate substantially as hereinbefore particularly described with reference to and as illustrated in Figs. 3 and 4, or Figs. 5, or Fig. 6 of the accompanying drawings.
  9. 9. A hydraulic system including a pressure oscillation producer and a pressure resistant damping chamber, constructed and arranged and adapted to operate substantially as hereinbefore particularly described with reference to and as illustrated in Fig. 7 of the accompanying drawings.
GB4028477A 1976-09-29 1977-09-28 Hydraulic systems Expired GB1590003A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19762643860 DE2643860A1 (en) 1976-09-29 1976-09-29 HYDRAULIC SYSTEM

Publications (1)

Publication Number Publication Date
GB1590003A true GB1590003A (en) 1981-05-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
GB4028477A Expired GB1590003A (en) 1976-09-29 1977-09-28 Hydraulic systems

Country Status (5)

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JP (1) JPS5343180A (en)
DE (1) DE2643860A1 (en)
GB (1) GB1590003A (en)
IT (1) IT1087621B (en)
SE (1) SE7710849L (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4988147A (en) * 1989-03-11 1991-01-29 Robert Bosch Gmbh Hydraulic high-pressure pump for a vehicle brake system
US4989924A (en) * 1988-03-31 1991-02-05 Aisin Seiki Kabushiki Kaisha Fluid pressure circuit
GB2235507A (en) * 1989-08-09 1991-03-06 Bosch Gmbh Robert Anti skid motor vehicle braking system
US5031969A (en) * 1989-02-11 1991-07-16 Robert Bosch Gmbh Apparatus for pressure regulation in a hydraulic system
US5172956A (en) * 1990-09-29 1992-12-22 Robert Bosch Gmbh Hydraulic system for a motor vehicle brake system having a pump with pulsation reduction
DE4213524A1 (en) * 1992-04-24 1993-10-28 Bosch Gmbh Robert Hydraulic brake and wheel slip control for vehicle - has reflection dampers in pipe lines to counteract pump pressure waves
US5401086A (en) * 1991-11-19 1995-03-28 Sumitomo Electric Industries, Ltd. Antilocking brake fluid pressure control unit for vehicle brake system
US5460438A (en) * 1993-04-06 1995-10-24 Robert Bosch Gmbh Damping device, particularly for hydraulic brake system
US8671680B2 (en) 2008-02-08 2014-03-18 Continental Teves Ag & Co. Ohg Hydraulic system with improved pulsation damping

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58176152A (en) * 1982-04-06 1983-10-15 タシケントスキ−・ナウチノ−・イスレドワ−チエルスキ−・イ・プロエクトヌイ・インスチツ−ト・ストロイチエルヌイフ・マテリアロフ「あ」ニイストロムプロエクト「あ」 Manufacture of cement clinker
JPH0732301Y2 (en) * 1988-09-14 1995-07-26 株式会社曙ブレーキ中央技術研究所 Anti-skid controller
JPH0771926B2 (en) * 1988-09-20 1995-08-02 株式会社ナブコ Anti-skid brake device
DE3902131C2 (en) * 1989-01-25 1997-02-20 Teves Gmbh Alfred Anti-lock hydraulic brake system for motor vehicles
US5209554A (en) * 1989-04-22 1993-05-11 Beilfuss Hans J Slip-controlled brake system, especially for use with automotive vehicles
DE3923282C2 (en) * 1989-07-14 1998-04-30 Bosch Gmbh Robert Device for damping pressure vibrations
DE4004316C2 (en) * 1989-08-09 2002-05-08 Bosch Gmbh Robert Hydraulic vehicle brake system with anti-lock device
US5249854A (en) * 1990-04-25 1993-10-05 Sumitomo Electric Industries, Ltd. Braking circuit provided with antilocking apparatus
DE4106790A1 (en) * 1990-07-26 1992-09-10 Teves Gmbh Alfred BLOCK-PROTECTED, HYDRAULIC BRAKE SYSTEM
US5445447A (en) * 1990-09-28 1995-08-29 Lucas Industries Public Limited Company Hydraulic anti-locking systems for vehicles
BR9106927A (en) * 1990-09-28 1993-07-27 Lucas Ind Plc ANTI-HYDRAULIC BRAKE BLOCKING SYSTEM FOR VEHICLES
DE4109450A1 (en) * 1991-03-22 1992-09-24 Teves Gmbh Alfred SLIP-CONTROLLED BRAKE SYSTEM, ESPECIALLY FOR MOTOR VEHICLES
US5385395A (en) * 1991-03-22 1995-01-31 Alfred Teves Gmbh Slip-controlled brake system, especially for automotive vehicles
JP2602155Y2 (en) * 1991-09-19 1999-12-27 日本エービーエス株式会社 Hydraulic pressure control device for anti-skid device
DE4142710A1 (en) * 1991-12-21 1993-06-24 Bosch Gmbh Robert STRAND FOR CARRYING A MEDIUM
US5379593A (en) * 1992-11-09 1995-01-10 Nabco Limited Liquid pressure source unit for liquid-operated booster
DE4319227A1 (en) * 1993-06-09 1994-12-15 Teves Gmbh Alfred Hydraulic brake system with slip control
DE4343678A1 (en) * 1993-12-21 1995-06-22 Teves Gmbh Alfred Vehicle hydraulic brake system with anti-locking and traction control
DE19536847A1 (en) * 1995-10-02 1997-04-03 Bosch Gmbh Robert Hydraulic unit for a slip-controlled motor vehicle brake system
DE102011089183A1 (en) * 2011-12-20 2013-06-20 Robert Bosch Gmbh Pressure pulsation damper for a vehicle brake system

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4989924A (en) * 1988-03-31 1991-02-05 Aisin Seiki Kabushiki Kaisha Fluid pressure circuit
US5031969A (en) * 1989-02-11 1991-07-16 Robert Bosch Gmbh Apparatus for pressure regulation in a hydraulic system
US4988147A (en) * 1989-03-11 1991-01-29 Robert Bosch Gmbh Hydraulic high-pressure pump for a vehicle brake system
GB2235507B (en) * 1989-08-09 1994-02-09 Bosch Gmbh Robert A hydraulic braking system for a vehicle
GB2235507A (en) * 1989-08-09 1991-03-06 Bosch Gmbh Robert Anti skid motor vehicle braking system
US5172956A (en) * 1990-09-29 1992-12-22 Robert Bosch Gmbh Hydraulic system for a motor vehicle brake system having a pump with pulsation reduction
US5401086A (en) * 1991-11-19 1995-03-28 Sumitomo Electric Industries, Ltd. Antilocking brake fluid pressure control unit for vehicle brake system
EP0543187B1 (en) * 1991-11-19 1996-09-11 Sumitomo Electric Industries, Limited A method of vacuum charging an antilocking brake system
DE4213524A1 (en) * 1992-04-24 1993-10-28 Bosch Gmbh Robert Hydraulic brake and wheel slip control for vehicle - has reflection dampers in pipe lines to counteract pump pressure waves
US5417481A (en) * 1992-04-24 1995-05-23 Robert Bosch Gmbh Hydraulic vehicle brake system with a hydraulic unit for wheel slop control
US5468057A (en) * 1992-04-24 1995-11-21 Robert Bosch Gmbh Hydraulic vehicle brake system with a hydraulic unit for wheel slip control
US5460438A (en) * 1993-04-06 1995-10-24 Robert Bosch Gmbh Damping device, particularly for hydraulic brake system
US8671680B2 (en) 2008-02-08 2014-03-18 Continental Teves Ag & Co. Ohg Hydraulic system with improved pulsation damping

Also Published As

Publication number Publication date
IT1087621B (en) 1985-06-04
JPS5343180A (en) 1978-04-19
SE7710849L (en) 1978-03-30
DE2643860A1 (en) 1978-03-30

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