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WO1999042349A1 - Unite de commande hydraulique pourvu d'un attenuateur monte dans le meme alesage cylindrique qu'une vanne de regulation - Google Patents

Unite de commande hydraulique pourvu d'un attenuateur monte dans le meme alesage cylindrique qu'une vanne de regulation Download PDF

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Publication number
WO1999042349A1
WO1999042349A1 PCT/US1999/003538 US9903538W WO9942349A1 WO 1999042349 A1 WO1999042349 A1 WO 1999042349A1 US 9903538 W US9903538 W US 9903538W WO 9942349 A1 WO9942349 A1 WO 9942349A1
Authority
WO
WIPO (PCT)
Prior art keywords
bore
attenuator
control unit
fluid
control valve
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.)
Ceased
Application number
PCT/US1999/003538
Other languages
English (en)
Inventor
Joseph A. Starr
Wendell D. Tackett
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 Active Safety US Inc
Original Assignee
Kelsey Hayes Co
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 Kelsey Hayes Co filed Critical Kelsey Hayes Co
Priority to AU26870/99A priority Critical patent/AU2687099A/en
Publication of WO1999042349A1 publication Critical patent/WO1999042349A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • 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
    • B60T8/36—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 including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, 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
    • 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

Definitions

  • This invention relates in general to vehicular brake systems and in particular is concerned with an attenuator located in the same bore as a control valve in a hydraulic control unit.
  • a typical system includes a master cylinder, fluid conduit arranged into a desired circuit, and wheel brakes.
  • the master cylinder generates hydraulic forces in the circuit by pressurizing brake fluid when the driver steps on the brake pedal.
  • the pressurized fluid travels through the fluid conduit in the circuit to actuate brake cylinders at the wheel brakes and slow the vehicle.
  • Electronically-controlled hydraulic brake systems also include a hydraulic control unit (HCU) containing control valves and other components located between the master cylinder and the wheel brakes. Through an electronic controller, the control valves and other components selectively control pressure to the wheel brakes to provide a desired braking response of the vehicle, including anti-lock braking, traction control, and vehicle stability control.
  • An attenuator can be provided in the HCU between an outlet of a pump and an inlet of an isolation valve. During a controlled event, fluid exits the pump in pressurized pulses and enters a fluid chamber of the attenuator. Fluid is released from the fluid chamber through an orifice having a relatively small diameter. High pressure pulses are damped by the orifice and thus reduce undesirable noise associated with such pulses.
  • Conventional attenuators have been formed by providing a separate bore in the hydraulic control unit and sealing the bore with an end cap.
  • An elastomeric plug can be placed in the fluid chamber for performance improvement.
  • This invention includes a hydraulic control unit of a vehicular brake system.
  • the hydraulic control unit includes an attenuator provided in the same bore as a fluid control valve.
  • the attenuator includes an element located in the bore.
  • the element and side and end walls of the bore define a fluid chamber.
  • An orifice is formed in the element for directing fluid to an inlet of the control valve. High pressure fluid pulses passing through the orifice are damped prior to reaching the control valve.
  • This invention reduces the costs of a hydraulic control unit by reducing components and the overall size of a hydraulic control unit.
  • a hydraulic control unit for a vehicular brake system includes a housing.
  • a bore is formed in the housing.
  • a control valve is mounted in the bore.
  • FIG. 1 is a schematic circuit diagram of a vehicular brake system according to this invention illustrating an attentuator positioned between a pump and an isolation valve in a hydraulic control unit.
  • FIG. 2 is a partial sectional view of the hydraulic control unit of FIG 1. illustrating the attenuator mounted in series with the isolation valve in a bore formed in the hydraulic control unit according to this invention.
  • FIG. 3 is a partial sectional view of a second embodiment of an attenuator mounted in series with the isolation valve of FIG. 2 in a bore formed in the hydraulic control unit according to this invention.
  • FIG. 4 is a partial sectional view of a third embodiment of an attenuator mounted in series with the isolation valve of FIG. 2 in a bore formed in the hydraulic control unit according to this invention.
  • FIG. 5 is a partial sectional view of an attentuator in series with and integrated into an isolation valve in a hydraulic control unit according to this invention.
  • a vehicular brake system according to this invention is indicated generally at 10 in FIG. 1.
  • System 10 includes valves and other components described below to provide anti-lock braking functions.
  • system 10 can also include components to provide traction control functions and/or vehicle stability control functions.
  • a brake pedal 12 is connected to a master cylinder 14 to provide pressurized brake fluid to a wheel brake 16.
  • the wheel brake 16 is illustrated as a disc assembly; however, wheel brake 16 may be any type found on vehicles.
  • a hydraulic control unit (HCU) 18 includes a housing 19 (see FIG 2) having bores for receiving control valves and other components described below. Fluid passageways or conduits are provided between the bores to provide fluid communication between the valves and other components. For purposes of clarity of illustration, only one set of components are illustrated in the schematic of FIG. 1. However, it is understood that the HCU 18 can also house corresponding components for other circuits and/or wheels of the vehicle.
  • the HCU 18 includes a normally open control valve 20, commonly referred to as an isolation valve, and a normally closed control valve 22, commonly known as a dump valve, disposed between the master cylinder 14 and the wheel brake 16.
  • a low pressure accumulator 24 is disposed between the dump valve 22 and a reciprocating hydraulic pump 26.
  • the pump 26 is driven by an electric motor (not illustrated) in a well known manner.
  • An attenuator 28 is provided in the HCU 18 downstream of an outlet of the pump 26.
  • An orifice 30 located in the HCU 18 provides a restricted flow path between the attenuator 28 and an inlet of the isolation valve 20. The attenuator 28 and restrictive orifice 30 dampen fluid pulses exiting the pump 26.
  • the isolation valve 20 is preferably formed as a solenoid valve switchable between two positions.
  • the dump valve 22 is preferably formed as a solenoid valve switchable between two positions. Valves 20 and 22, as well as pump 26, are electrically connected to an electronic control module (not illustrated) and operated to provide desired anti-lock braking in a well known manner.
  • FIG. 2 A sectional view of a portion of the HCU 18 is presented in FIG. 2.
  • the HCU 18 includes a housing 19 containing valves and other components described below.
  • the housing 19 includes a stepped bore 130 for receiving the isolation valve 20.
  • the attenuator 28 and restricted orifice 30 are fitted in series with the isolation valve 20 adjacent an end wall BOA of bore 130.
  • the isolation valve 20 includes a generally cylindrical valve body 132 fitted into the bore 130.
  • the valve body 132 includes a radial flange 134, a coaxial inlet passage 136, and outlet passages 138.
  • a conical valve seat 140 is formed at the upper end of the inlet passage 138.
  • a ball valve 142 is pressed into a cavity 144 formed in a lower end of an armature 146.
  • the unenergized position of the isolation valve 20 (not illustrated), the ball valve 142 is spaced away from the valve seat 140 so that fluid flows through the isolation valve 20.
  • the ball valve 142 rests on the valve seat 140 to block fluid flow through the isolation valve 20.
  • the armature 146 is slidably received in a cup-shaped sleeve 148 sealed at its open end to the valve body 132.
  • the sleeve 148 is laser welded to the valve body 132, thereby forming a fluid tight seal therebetween.
  • a coil spring 152 is mounted about a lower end of the armature 146 and engages an annular flange 153 formed on the armature 146. The spring 152 pushes the armature 146 away from the valve body 132 so that the ball valve 142 is spaced from the valve seat 140 in the unenergized position.
  • a solenoid coil assembly 154 is received over the sleeve 148.
  • the coil assembly 154 When energized, the coil assembly 154 generates a magnetic field that attracts the armature 146 toward the valve body 132, thereby pulling the ball valve 142 into the valve seat 140 as shown in Fig. 2. In this position, fluid flow through the isolation valve 20 is blocked.
  • the coil assembly 154 includes an annular flux ring 156 to enhance the strength of the magnetic field in the vicinity of the armature 146.
  • a compressible seal 160 such as an O-ring is received in a groove formed about the valve body 132 between the flange 134 and the outlet passages 138.
  • a lip seal 162 is preferably received in a groove formed about the valve body 132 between the outlet passages 138 and a lower end of the valve body 32. Lip seal 162 preferably has a relatively low-pressure differential that permits fluid to travel to the inlet passage 136 at predetermined fluid pressures.
  • a filter assembly 163 is mounted at an opening to the inlet passage 136.
  • An annular lip 164 is formed from material of the housing 19 adjacent the bore 130.
  • the lip 164 is formed by deforming the adjacent material in any desired manner, including swaging and orbital riveting.
  • the attenuator 28 includes a fluid chamber 200 bounded by sides of a lower portion of the bore 130 and the end wall 130A.
  • a disc 202 is pressed into a shoulder 131 formed in a lower portion of the bore and retained by an interference fit.
  • the disc 202 is spaced a predetermined distance from a lower end of the valve body 132 and a predetermined distance from the end wall 130A.
  • the disc 202 forms an upper boundary of the fluid chamber 200 and includes the orifice 30 for directing fluid from the fluid chamber 200 to the inlet passage 136.
  • the orifice 30 has a predetermined, relatively reduced diameter.
  • the disc 202 can be formed from any suitable material including a moldable and/or flexible material. If desired, a resilient plug (not illustrated) can be fitted in the fluid chamber 200 for additional displacement greater than displacement of brake fluid having an equivalent volume.
  • a fluid conduit 170 is formed in the housing 19 that leads from an outlet of the pump 26 to the fluid chamber 200. Fluid conduits 172 and 174 are formed in the housing 18 that lead from the master cylinder 14 to the bore 130 so that fluid can travel from the master cylinder 14 to the inlet passage 136.
  • a fluid conduit 176 is formed in the housing 19 that leads from the outlet passages 138 to the wheel brake 16.
  • a fluid conduit 178 is formed in the housing 19 that leads from orifices of the outlet passages 138 to the dump valve 22.
  • the isolation valve 20 is energized so that the ball valve 142 is forced into the valve seat 140 to block fluid flow.
  • the pump 26 is activated so that fluid is pumped the low-pressure accumulator 24 to the attenuator 28 via conduit 170.
  • the fluid chamber 200 receives and stores such fluid. High pressure fluid exits the fluid chamber 200 through orifice 30 and is damped, thereby reducing noise associated with undamped pulses.
  • the press fit of the disc 202 in the stepped bore 130 provides a safety benefit when compared to prior art attenuators that utilize an end cap to seal the attenuator.
  • an end cap Under extreme high-pressure fluid, an end cap may be forced out of the HCU 18, thereby causing a failure of a brake system.
  • pressurized fluid may build until an end cap is forced from a HCU 18. Losing an end cap can mean loss of brake fluid and braking functions in such prior art systems. If debris clogged orifice 30 of disc 202, extreme high pressure fluid may build in fluid chamber 200 until disc 202 is forced from its press fit in the stepped bore 130.
  • FIG. 3 A second embodiment of an attenuator 28' according to this invention is illustrated in FIG. 3. The attenuator 28' is received in stepped bore 130 of the housing 19 in lieu of the attenuator 28 of FIG. 2.
  • the attenuator 28' includes a cup-shaped element 300 having an end wall
  • the cup-shaped element 300 can be pressed onto a shoulder 131 formed in a lower portion of the bore 130 and retained by an interference fit. Alternatively, any other suitable means can be used to position the element 300 in the bore 130.
  • the element 300 can be formed from a metal, plastic, or other suitable material.
  • the element 300 includes the orifice 30.
  • the orifice 30 is formed at the center of the end wall 302.
  • the orifice 30 has a predetermined, relatively reduced diameter.
  • a seal 308 can be located in a groove 310 formed in an outer surface of the cylindrical wall 304.
  • the seal 308 prevents fluid flow between the fluid chambers formed in the unoccupied volume of the bore 130 on each side of the element 300 except fluid flow through the orifice 30.
  • a bumper 312 can be provided between the rim 306 and a lower surface of the isolation valve 20.
  • the bumper 312 can be formed from a resilient material (such as an elastomer) and bonded to either the rim 306 or the lower surface of the isolation valve 20.
  • the bumper 312 can be positioned by a groove in a desired element or any other suitable means.
  • At least one fluid conduit 314 is preferably formed in the cylindrical wall 304 to permit fluid to flow from the master cylinder 14 through conduits 172 and 174 to the isolation valve 20.
  • the bumper 312 may enhance the attenuating effect of the attenuator 28'. If the fit between the element 300 and the housing 19 is such that the element 300 is urged toward the isolation valve 20 during pressure pulses from the pump 26, the bumper 312 can transfer a resistance force from the isolation valve 20, which is retained in the housing 19 via the lip 164. Furthermore, the bumper 312 may permit the isolation valve 20 to be loaded under a compressive force when it is retained in the bore 130.
  • fluid from the pump 26 is received and stored in fluid chamber 200 via conduit 170. Fluid exits the fluid chamber 200 through orifice 30 in a damped condition to reach the inlet passage 136 of the isolation valve 20.
  • FIG. 4 A third embodiment of an attenuator 28" according to this invention is illustrated in FIG. 4.
  • the attenuator 28" is received in stepped bore 130 of the housing 19 in lieu of the attenuator 28 of FIG. 2.
  • the attenuator 28" can be formed as a cylindrical or disc-like insert 400.
  • the cylindrical insert 400 can be pressed onto a shoulder 131 formed in a lower portion of the bore 130 and retained by an interference fit.
  • any other suitable means can be used to position the insert 400 in the bore 130.
  • the insert 400 can be formed from a porous material, such as a sintered material, so that the voids 30' in the insert 400 function like the orifice 30 of attenuators 28 and 28'. Fluid from fluid chamber 200 travels through the voids 30' and is damped before it reaches the inlet passage 136 of the isolation valve 20.
  • a fourth embodiment of an attenuator 28 " ' according to this invention is illustrated in FIG. 5.
  • the attenuator 28'" can be integrated into a modified isolation valve 20'.
  • the combined isolation valve 20' and attenuator 28 '" are 10
  • the attenuator 28'" can be formed as a generally cylindrical insert 500 having an end cap 502 and a cylindrical portion 504.
  • the insert 500 can be pressed into a counterbore 133 formed in the isolation valve 20' at the beginning of the inlet passage 136 and retained by an interference fit.
  • any other suitable means and configurations can be used to secure the insert 500 to the isolation valve 20'.
  • the insert 500 can be formed from any suitable material including a moldable material.
  • a filter (not illustrated) can be provided at the entrance of the inlet passage 136.
  • the insert 500 includes the orifice 30.
  • the orifice 30 is formed at the center of the end cap 502.
  • the orifice 30 has a predetermined, relatively reduced diameter. Fluid from fluid chamber 200 travels through the orifice 30 and is damped before it reaches the inlet passage 136 of the isolation valve 20'.
  • the isolation valve 20' includes a fluid passage 135 that permits fluid communication between conduits 172 and 174 and an annular chamber 506 provided between the cylindrical portion 504 and the counterbore 133.
  • Conduits 508 are provided in the cylindrical portion 504 to permit fluid to flow from the annular chamber 506 to the inlet passage 136 in a relatively unrestricted flow path.
  • the interference fit described above for elements 202, 300, and 400 in the bore 130 can be designed to function as a relief valve.
  • the fit can be constructed to yield at a predetermined pressure range. In this manner, an undesired high pressure in fluid chamber 200 can blow off or force the element 202, 300, and 400 out of its seat prior to causing failure elsewhere in the HCU 18 at a point that may cause loss of braking. 1 1

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)

Abstract

La présente invention concerne une unité de commande (18) hydraulique d'un système de freinage automobile (10) comprenant un atténuateur (28, 28', 28'', 28''') monté dans le même alésage cylindrique (130, 130A) qu'une vanne de régulation (20) hydraulique. L'élément (202, 300, 400, 500) et les parois latérales et terminales de l'alésage cylindrique (130, 130A) forment une chambre (200) hydraulique. Un orifice (30) est formé dans cet élément pour diriger le fluide vers un passage d'entrée (172) de la vanne de régulation (20) hydraulique. Les impulsions du fluide haute pression traversant l'orifice précité (30) sont amorties avant d'arriver à la vanne de régulation (20).
PCT/US1999/003538 1998-02-20 1999-02-19 Unite de commande hydraulique pourvu d'un attenuateur monte dans le meme alesage cylindrique qu'une vanne de regulation Ceased WO1999042349A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU26870/99A AU2687099A (en) 1998-02-20 1999-02-19 Hydraulic control unit having attenuator located in same bore as control valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US7537498P 1998-02-20 1998-02-20
US60/075,374 1998-02-20

Publications (1)

Publication Number Publication Date
WO1999042349A1 true WO1999042349A1 (fr) 1999-08-26

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PCT/US1999/003538 Ceased WO1999042349A1 (fr) 1998-02-20 1999-02-19 Unite de commande hydraulique pourvu d'un attenuateur monte dans le meme alesage cylindrique qu'une vanne de regulation

Country Status (2)

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AU (1) AU2687099A (fr)
WO (1) WO1999042349A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10107814A1 (de) * 2000-11-21 2002-05-23 Continental Teves Ag & Co Ohg Drucksensorbaugruppe
WO2016070169A1 (fr) * 2014-10-31 2016-05-06 Kelsey-Hayes Company Soupape de dérivation d'atténuateur de pompe
CN109383470A (zh) * 2017-08-08 2019-02-26 株式会社万都 制动系统用电磁阀

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3608984A (en) * 1968-08-01 1971-09-28 Philips Corp Restriction device for an antilock brake system
US5035469A (en) * 1989-01-23 1991-07-30 Lucas Industries Public Limited Company Pressure control device for anti-lock or anti-skid systems in motor vehicles
DE4030971A1 (de) * 1990-10-01 1992-04-02 Bosch Gmbh Robert Elektromagnetbetaetigtes ventil
DE4111201A1 (de) * 1991-04-06 1992-10-08 Bosch Gmbh Robert Hydroaggregat zum einsetzen in eine bremsleitung
DE4241095A1 (de) * 1992-12-07 1994-06-09 Teves Gmbh Alfred Druckversorgung, insbesondere für eine hydraulische Bremsanlage
US5531513A (en) * 1994-12-16 1996-07-02 Kelsey-Hayes High pressure accumulator/bypass valve with stationary high pressure seal
JPH08216852A (ja) * 1995-02-14 1996-08-27 Unisia Jecs Corp アンチロックブレーキ装置のアクチュエータ
US5683151A (en) * 1993-09-24 1997-11-04 Robert Bosch Gmbh Hydraulic unit for traction-controlled motor vehicle brake systems

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3608984A (en) * 1968-08-01 1971-09-28 Philips Corp Restriction device for an antilock brake system
US5035469A (en) * 1989-01-23 1991-07-30 Lucas Industries Public Limited Company Pressure control device for anti-lock or anti-skid systems in motor vehicles
DE4030971A1 (de) * 1990-10-01 1992-04-02 Bosch Gmbh Robert Elektromagnetbetaetigtes ventil
DE4111201A1 (de) * 1991-04-06 1992-10-08 Bosch Gmbh Robert Hydroaggregat zum einsetzen in eine bremsleitung
DE4241095A1 (de) * 1992-12-07 1994-06-09 Teves Gmbh Alfred Druckversorgung, insbesondere für eine hydraulische Bremsanlage
US5683151A (en) * 1993-09-24 1997-11-04 Robert Bosch Gmbh Hydraulic unit for traction-controlled motor vehicle brake systems
US5531513A (en) * 1994-12-16 1996-07-02 Kelsey-Hayes High pressure accumulator/bypass valve with stationary high pressure seal
JPH08216852A (ja) * 1995-02-14 1996-08-27 Unisia Jecs Corp アンチロックブレーキ装置のアクチュエータ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 096, no. 012 26 December 1996 (1996-12-26) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10107814A1 (de) * 2000-11-21 2002-05-23 Continental Teves Ag & Co Ohg Drucksensorbaugruppe
WO2016070169A1 (fr) * 2014-10-31 2016-05-06 Kelsey-Hayes Company Soupape de dérivation d'atténuateur de pompe
CN109383470A (zh) * 2017-08-08 2019-02-26 株式会社万都 制动系统用电磁阀

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