US20120175943A1 - Pressure control valve arrangement having an eccentrically mounted double magnet - Google Patents

Pressure control valve arrangement having an eccentrically mounted double magnet Download PDF

Info

Publication number
US20120175943A1
US20120175943A1 US13/381,039 US201013381039A US2012175943A1 US 20120175943 A1 US20120175943 A1 US 20120175943A1 US 201013381039 A US201013381039 A US 201013381039A US 2012175943 A1 US2012175943 A1 US 2012175943A1
Authority
US
United States
Prior art keywords
pressure
mid
control valve
valve arrangement
valves
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.)
Abandoned
Application number
US13/381,039
Other languages
English (en)
Inventor
Jan Grebe
Dirk Brenner
Jochen Weippert
Wolfgang ROHN
Harald Jaehns
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge 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 Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Assigned to KNORR-BREMSE SYSTEME FUER NUTZFAHRZEUGE GMBH reassignment KNORR-BREMSE SYSTEME FUER NUTZFAHRZEUGE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WEIPPERT, JOCHEN, GREBE, JAN, ROHN, WOLFGANG, BRENNER, DIRK, JAEHNS, HARALD
Publication of US20120175943A1 publication Critical patent/US20120175943A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • B60T8/3605—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 wherein the pilot valve is mounted in a circuit controlling the working fluid system
    • 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
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B60T15/025—Electrically controlled valves
    • B60T15/027—Electrically controlled valves in pneumatic systems
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0263—Construction of housing; Use of materials therefor of lift valves multiple way valves
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K7/00—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves
    • F16K7/12—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm
    • F16K7/14—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm arranged to be deformed against a flat seat
    • F16K7/17—Diaphragm valves or cut-off apparatus, e.g. with a member deformed, but not moved bodily, to close the passage ; Pinch valves with flat, dished, or bowl-shaped diaphragm arranged to be deformed against a flat seat the diaphragm being actuated by fluid pressure

Definitions

  • the present invention relates to a pressure control valve arrangement for controlling the fluid pressure in an ABS brake system of a vehicle.
  • ABS antilock system
  • ABS brake system prevents the wheels from locking and comes into operation when greater adhesion than is transferable is demanded between a tire and the road, that is to say when the driver overbrakes.
  • the central electronic control apparatus of the ABS brake system detects from rotational speed sensor signals the tendency of one or more wheels to lock and from this calculates the activation of the pressure control valve arrangement acting upon the assigned brake cylinder.
  • the brake pressure is then set to optimal slip by the pressure control valve arrangement by lowering, holding or building up the brake pressure according to the wheel behavior and therefore the frictional conditions between the tire and road.
  • ABS pressure control valve arrangements without a relay action are used in vehicles, such as, for example, utility vehicles, omnibuses, tractors and trailers.
  • Pressure control valve arrangements without a relay action mostly have 3/2 way solenoid valves as the pilot control valves of diaphragm valves, an electronic control device activating the 3 / 2 way solenoid valves so that the “pressure holding”, “pressure reduction” and the “pressure build-up” functions necessary for ABS operation can be carried out.
  • the pressure medium mostly air, flows, unimpeded, through the pressure control valve arrangements in both directions when the brake cylinders are being ventilated and bled. This ensures that the functioning of the service brake system is not influenced by the ABS pressure control valve arrangement.
  • Pressure control valves of the generic type as 1-channel pressure control valves for antilock systems in motor vehicles, have in each case, inside the housing, a diaphragm valve as a holding valve and as an outlet valve and also in each case an electromagnetic control valve for the holding valve and the outlet valve.
  • the two diaphragm valves contain in each case a diaphragm capable of being acted upon by the pressure in a pilot control space, the pilot control space being closed outwardly by a cover fastened to the housing.
  • a generic pressure control valve arrangement of an ABS brake system is known, for example, from EP 0 266 555 A1 or from DE-A 2 855 876.
  • the housing has a pressure medium connection for the action of pressure and/or the relief of pressure, which is connected to a foot-operated brake valve. Furthermore, the two diaphragm valves are arranged laterally on the housing, the corresponding pilot control spaces being closed by covers fastened laterally to the housing, that is to say, there, surface normals on the diaphragms of both diaphragm valves are arranged perpendicularly to the mid-axis of the pressure medium connection.
  • a plane of symmetry of the mid-axes of the magnet coils of the double magnet of the two electromagnetic control valves is arranged centrically with respect to a mid-axis of the pressure medium connection (there, the pressure medium inlet).
  • the mid-axes of the two magnet coils at the same time also define the positions of the valve seats of the electromagnetic control valves of the pressure control valve arrangement, because the mid-axes of the magnet coils are arranged coaxially with the valve seats and with the magnet armatures.
  • the valve seats of the electromagnetic control valves are connected to the pressure medium connection or issue into this via pressure medium ducts.
  • pressure medium ducts may be made coaxially with the mid-axes of the magnet coils by cutting manufacture, such as drilling, in order for reasons of cost to avoid having to rechuck the housing in order to make obliquely running pressure medium ducts or housing bores.
  • the pressure medium ducts consequently run parallel to one another in a vertical direction.
  • the inside diameter of the pressure medium connection has to be relatively large, especially since the magnet coils also cannot undershoot a certain diameter.
  • a correspondingly large diameter of the pressure medium connection is unfavorable in flow terms, in practice a reducing sleeve which reduces the effective flow diameter is inserted into the pressure medium connection.
  • the subject on which the exemplary embodiments and/or exemplary methods of the present invention are based is to develop a pressure control valve arrangement of the type initially mentioned in such a way that it can be manufactured and assembled more simply and more cost-effectively.
  • the mid-axes of the magnet coils are coaxial with the valve seats of the electromagnetic control valves, and in each case one valve seat is formed at one end of a pressure medium duct which connects the respective valve seat to the pressure medium connection. Since two electromagnetic control valves are present, two pressure medium ducts formed in the housing must consequently lead from the respective valve seats coaxial with the mid-axes of the magnet coils into the pressure medium connection. In this case, pressure medium ducts running obliquely, that is to say deviatingly from a vertical or from a horizontal, are to be avoided, so as to avoid having to rechuck the housing during manufacture.
  • the exemplary embodiments and/or exemplary methods of the present invention achieve this object by providing that a plane of symmetry of the mid-axes of the magnet coils of the double magnet of the two electromagnetic control valves is arranged parallel and eccentrically with respect to a mid-axis of the pressure medium connection.
  • the distance between the mouth of the connecting duct, arranged in the housing, in the pressure medium connection between the valve seat of one of the electromagnetic control valves and the pressure medium connection, on the one hand, and the mid-axis of the pressure medium connection, on the other hand, is then reduced, as compared with the prior art, because the mid-axis of one of the magnet coils of the double magnet and therefore also the valve seat, coaxial thereto, of the respective electromagnetic control valve and, too, the respective pressure medium duct can then be moved nearer to the mid-axis of the pressure medium connection and consequently issue into the pressure medium connection at a shorter distance from this mid-axis.
  • the other pressure medium duct emanating from the valve seat of the other electromagnetic control valve then no longer needs to run parallel to the first, for example vertical pressure medium duct, but instead can issue, for example running in a horizontal direction, into an annular duct which is formed in a housing and which is connected in turn to the pressure medium connection.
  • the pressure medium ducts then run in a vertical and a horizontal direction, so that the housing does not have to be rechucked during manufacture.
  • the diameter of the pressure medium connection can thus be smaller and therefore more favorable in flow terms.
  • a reducing sleeve can be dispensed with.
  • the housing may be provided with at least one through bore which issues in side faces of the housing and which is intended as a holding arrangement for holding the pressure control valve arrangement on a carrier body, the plane of symmetry of the mid-axes of the magnet coils of the double magnet of the two electromagnetic control valves being arranged, offset by the amount of the eccentricity with respect to a plane of symmetry of the through bore, said plane of symmetry being arranged perpendicularly to a mid-axis of the through bore.
  • the eccentric arrangement of the double magnet acquires an additional reference to a relevant geometric quantity of the pressure control valve arrangement, because the length of the through, bore is fixed, for reasons of space, as a standardized installation dimension of the pressure control valve arrangement and is invariable. It defines the maximum width of the housing.
  • the surface normal running perpendicularly with respect to the assigned diaphragm is arranged parallel to the mid-axis of the through bore and perpendicularly to the mid-axis of the pressure medium connection, and, in the other diaphragm valve, the surface normal running perpendicularly with respect to the assigned diaphragm is arranged perpendicularly to the mid-axis of the through bore and perpendicularly to the mid-axis of the pressure medium connection.
  • This may be implemented, for example, in that one diaphragm valve is arranged laterally and the other diaphragm valve on the bottom side or head side on the housing.
  • a cover closing a pilot control space of one diaphragm valve for example arranged laterally on a housing, with respect to the outside and fastened to the housing is then composed of at least one plastic
  • the wall thickness of this cover can be greater than in the prior art, in which both diaphragm valves are arranged laterally on the housing and, because of the standardized overall width of the housing, the thickness of the covers has to be smaller.
  • the plastic cover which is thicker, as compared with the prior art, is then more rigid. The tendency of the cover to deformation therefore decreases, and so the safety of the respective diaphragm valve against leakage of the pilot control space is increased.
  • a cover closing a pilot control space of the other diaphragm valve with respect to the outside and fastened to the housing may likewise be composed of a plastic.
  • At least one of the covers may at the same time, with the effect of an advantageous double function, close a pressure medium duct formed in the housing and separated from the respective pilot control space.
  • the pressure medium connection may be provided, in particular, for connection to a service brake valve of a pressure medium-actuated brake apparatus of a vehicle.
  • FIG. 1 shows a basic illustration of an ABS brake system as a general diagram of a 4S/4C ABS brake system of a vehicle.
  • FIG. 2 a shows a diagrammatical illustration of a pressure control valve arrangement activating a brake cylinder, in the open state (pressure build-up).
  • FIG. 2 b shows a diagrammatic illustration of the pressure control valve arrangement of FIG. 2 a in the closed state (pressure reduction).
  • FIG. 3 shows a front view of an actual version of the pressure control valve arrangement of FIG. 2 a and FIG. 2 b according to an exemplary embodiment of the present invention.
  • FIG. 4 shows a side view of the pressure control valve arrangement of FIG. 3 .
  • FIG. 5 shows a sectional illustration along the line V-V of FIG. 4 .
  • FIG. 6 shows the other side view of the pressure control valve arrangement of FIG. 3 .
  • FIG. 7 shows a sectional illustration along the line VII-VII of FIG. 6 .
  • a vehicle equipped with an ABS brake system has a front axle 1 and a rear axle 2 .
  • Wheels 3 a and 3 b are arranged on the front axle 1 ; the rear axle 2 has, for example, wheels 4 a and 4 b in each case equipped with twin tires.
  • the ABS brake system serving for braking these wheels 3 a , 3 b and 4 a , 4 b is designed here in the manner of a 4S/4C system (four sensors, four channels). This means that, overall, four rotational speed sensors 5 a - 5 d and four pressure control valve arrangements 7 a - 7 d are available here.
  • the pressure control valve arrangements 7 a - 7 d serve for the activation of respectively assigned brake cylinders 6 a - 6 d . All the pressure control valve arrangements 7 a - 7 d are connected to a foot-operated brake valve 9 via a branching pneumatic brake pressure line 8 .
  • the driver when actuating the foot-operated brake valve 9 , generates a brake pressure which, passing through the pressure control valve arrangements 7 a - 7 d , is transferred by the pneumatic brake pressure line 8 to the brake cylinders 6 a - 6 d assigned to the wheels 3 a , 3 b and to the wheels 4 a , 4 b.
  • the pressure control valve arrangements 7 a - 7 d are activatable via integrated electromagnetic valves 15 a , 15 b shown in FIG. 2 a , FIG. 2 b and FIG. 4 and for this purpose are connected electrically to a central electronic control unit 10 .
  • the electronic control unit 10 is connected on the input side to the four rotational speed sensors 5 a - 5 b determining the wheel speeds.
  • the brake pressure selected by the driver via the foot-operated brake valve 9 is lowered correspondingly to an ABS control, according to the electronic control unit 10 , by the corresponding pressure control valve arrangements 7 a - 7 d until locking is eliminated.
  • the ABS brake system of the present exemplary embodiment comprises, furthermore, an ASR function which comprises an ASR unit 11 for reducing the engine torque, such as an ASR solenoid valve 12 and a shuttle valve 13 .
  • the pressure control valve arrangement 7 used according to FIG. 2 a within the framework of the ABS brake system for the purpose of ABS control is constructed here in the manner of a 1-channel pressure control valve arrangement and is composed essentially of two integrated diaphragm valves 14 a and 14 b and of two spring-loaded electromagnetic valves 15 a , 15 b activating these.
  • the diaphragm valves 14 a and 14 b are in each case loaded in the closing direction by spring elements 16 a , 16 b and are pilot-controlled via the respectively assigned electromagnetic valves 15 a and 15 b.
  • a pressure control valve arrangement 7 is shown in FIG. 2 a in its open position, in which a build-up of pressure to the connected brake cylinder 6 takes place.
  • neither of the solenoid valves 15 a and 15 b is activated electrically.
  • the compressed air coming from the foot-operated brake valve 9 presses onto the diaphragm valve 14 a designed as an inlet valve.
  • the normally closed electromagnetic valve 15 a prevents the assigned diaphragm valve 14 a from being closed again.
  • the brake pressure coming from the foot-operated brake valve 9 closes the second diaphragm valve 14 b serving as an outlet valve.
  • the compressed air thus runs, unimpeded, through the pressure control valve arrangement 7 .
  • the pressure control valve arrangement 7 is in this state even when ABS control does not take place.
  • a pressure reduction in a brake cylinder 6 a to 6 d is achieved in that current is applied to both electromagnetic valves 15 a and 15 b .
  • What was described above for holding the pressure applies to the electromagnetic valve 15 a and the assigned inlet-side diaphragm valve 15 a .
  • the other electromagnetic valve 15 b by having current applied to it, is closed. The pressure coming from the brake cylinder 6 therefore presses the outlet-side diaphragm valve 14 b open and the brake cylinder 6 is bled.
  • FIG. 3 to FIG. 5 show the pressure control valve arrangement 7 illustrated merely diagrammatically in FIG. 2 a and FIG. 2 b in an actual embodiment in the installation position, that is to say the components illustrated at the top are located at the top.
  • the two electromagnetic valves 15 a , 15 b for the pilot control of the diaphragm valves 14 a , 14 b are combined in a double solenoid valve, the function of which, however, is analogous to that of the individual valves 15 a , 15 b.
  • the two electromagnetic valves 15 a , 15 b have a double magnet 18 combined in a block 17 and having two magnet coils 19 a , 19 b which cooperate with two solenoid valves seats 20 a , 20 b .
  • magnet armatures 36 a , 36 b cooperating with the solenoid valves seats 20 a , 20 b of the electromagnetic valves 15 a , 15 b are actuated as valve closing members by current being applied to the magnet coils 19 a , 19 b.
  • the block 17 comprising the double magnet 18 is fastened, which may be on the front side, to a housing 21 of the pressure control valve arrangement 7 and has a plug connection 22 for supplying current to the double magnet 18 .
  • This housing 21 has, furthermore, a pressure medium connection 23 for the action of pressure upon and/or the relief of pressure of the pressure control valve arrangement 7 , and also a working connection 24 , as can be seen in FIG. 4 , for connecting the brake cylinder 6 .
  • the pressure medium connection 23 is connected via the brake pressure line 8 to the foot-operated or service brake valve 9 of the pressure medium-actuated brake apparatus and is ventilated or bled according to actuation of the foot-operated brake valve 9 .
  • the mid-axes 25 a , 25 b of the magnet coils 19 a , 19 b are coaxial with the solenoid valve seats 20 a , 20 b of the electromagnetic valves 15 a , 15 b , and in each case one solenoid valve seat 20 a , 20 b is formed at one end of a pressure medium duct 26 a , 26 b which connects the respective solenoid valve seat 20 a , 20 b to the pressure medium connection 23 .
  • a plane of symmetry 27 shown in FIG. 3 , of the mid-axes 25 a , 25 b of the magnet coils 19 a , 19 b of the double magnet 18 of the two electromagnetic valves 15 a , 15 b is arranged, offset eccentrically by the amount of an eccentricity e with respect to a mid-axis 28 of the pressure medium connection 23 .
  • the mid-axis 28 of the pressure medium connection 23 is parallel with respect to this plane of symmetry 27 .
  • the distance between the mouth of, for example, the pressure medium duct 26 in the pressure medium connection 23 and the mid-axis 28 of the pressure medium connection 23 is then reduced, because the mid-axis 25 a of one of the magnet coils 19 a of the double magnet 18 and consequently also the solenoid valve seat 20 a of the respective electromagnetic valve 15 a and also the respective pressure medium duct 26 a are then moved nearer to the mid-axis 28 of the pressure medium connection 23 , and consequently the pressure medium duct 26 a can then issue into the pressure medium connection 23 at a shorter distance from said mid-axis, as shown clearly in FIG. 5 .
  • the double magnet 18 may also be arranged, offset by the amount of an eccentricity e, in the other direction, in FIG. 3 to the right with respect to the mid-axis 28 of the pressure medium connection 23 .
  • the distance of the other pressure medium duct 26 b emanating from the solenoid valve seat 20 b of the other electromagnetic valve 15 b from the mid-axis 28 of the pressure medium connection 23 is increased.
  • This pressure medium duct 26 b therefore does not issue directly into the pressure medium connection 23 , but instead first, for example, into an annular duct 29 which is formed in the housing 21 and which is connected, in turn, to the pressure medium connection 23 .
  • the eccentricity may amount to more than 1 mm.
  • the housing 21 is provided with at least one, here, for example, two, through bores 31 a , 31 b which issue into the two side faces 30 a , 30 b of the housing 21 and through which a project holding arrangement, for example screws, for holding the pressure control valve arrangement on a carrier body, for example on a chassis of the vehicle.
  • the mid-axes 32 a , 32 b of the two through bores 31 a , 31 b may be parallel to one another.
  • the plane of symmetry 27 of the mid-axes 25 a , 25 b of the magnet coils 19 a , 19 b of the double magnet 18 of the two electromagnetic valves 15 a , 15 b is arranged eccentrically with respect to a plane of symmetry 33 arranged perpendicularly to the mid-axes 32 a , 32 b of the through bores 31 a , 31 b , as may be gathered from FIG. 3 .
  • the mid-axis 28 of the pressure medium connection 23 lies in this plane of symmetry.
  • the axial length of the through bores 31 a , 31 b is deemed a standardized installation dimension of the pressure control valve arrangement 7 and, for reasons of space, is fixed and invariable, and it defines the maximum permissible width B of the housing 21 .
  • One diaphragm valve 14 a may be arranged laterally and the other diaphragm valve 14 b may be arranged on the bottom side on the housing 21 , as shown in FIG. 4 and FIG. 7 .
  • Such a diaphragm valve 14 a , 14 b has, as a valve body, a diaphragm 34 a , 34 b which can be acted upon by pressure medium being introduced into a control chamber 38 a , 38 b which is covered in each case on the housing outside by a cover 35 a , 35 b which is produced by primary forming, such as injection molding, and which is fastened to the housing 21 .
  • the control chamber 38 a , 38 b is formed between the diaphragm 34 a , 34 b and the cover 35 a , 35 b .
  • the covers 35 a , 35 b may be composed of at least one plastic.
  • At least one of the covers 35 a , 35 b may be designed such that, in addition to its function as a closing body for the assigned control chamber 38 a , 38 b , it at the same time closes a bore which is formed in the housing 21 and is not intended for connection to the control chamber 38 a , 38 b and which issues into a side face 30 a , 30 b of the housing 21 .
  • the surface normal running perpendicularly with respect to the assigned diaphragm 34 a may be parallel to the mid-axes 32 a , 32 b of the through bores 31 a , 31 b and perpendicular to the mid-axis 28 of the pressure medium connection 23 , as can easily be imagined from FIG. 3 .
  • the surface normal running perpendicularly with respect to the assigned diaphragm 34 b is arranged perpendicularly to the mid-axes 32 a , 32 b of the through bores 31 a , 31 b and perpendicularly to the mid-axis 28 of the pressure medium connection 23 .
  • one diaphragm valve 14 a is then arranged laterally and the other diaphragm valve 14 b on the bottom side or, alternatively, on the head side on the housing 21 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Transportation (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Regulating Braking Force (AREA)
US13/381,039 2009-06-29 2010-06-24 Pressure control valve arrangement having an eccentrically mounted double magnet Abandoned US20120175943A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009030898.9 2009-06-29
DE102009030898A DE102009030898A1 (de) 2009-06-29 2009-06-29 Drucksteuerventilanordnung mit exzentrisch angeordnetem Doppelmagneten
PCT/EP2010/058985 WO2011000768A1 (de) 2009-06-29 2010-06-24 Drucksteuerventilanordnung mit exzentrisch angeordnetem doppelmagneten

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/058985 A-371-Of-International WO2011000768A1 (de) 2009-06-29 2010-06-24 Drucksteuerventilanordnung mit exzentrisch angeordnetem doppelmagneten

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US15/369,926 Continuation US10059317B2 (en) 2009-06-29 2016-12-06 Pressure control valve arrangement having an eccentrically mounted double magnet

Publications (1)

Publication Number Publication Date
US20120175943A1 true US20120175943A1 (en) 2012-07-12

Family

ID=42557534

Family Applications (2)

Application Number Title Priority Date Filing Date
US13/381,039 Abandoned US20120175943A1 (en) 2009-06-29 2010-06-24 Pressure control valve arrangement having an eccentrically mounted double magnet
US15/369,926 Active US10059317B2 (en) 2009-06-29 2016-12-06 Pressure control valve arrangement having an eccentrically mounted double magnet

Family Applications After (1)

Application Number Title Priority Date Filing Date
US15/369,926 Active US10059317B2 (en) 2009-06-29 2016-12-06 Pressure control valve arrangement having an eccentrically mounted double magnet

Country Status (4)

Country Link
US (2) US20120175943A1 (de)
EP (1) EP2448797B1 (de)
DE (1) DE102009030898A1 (de)
WO (1) WO2011000768A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120181852A1 (en) * 2009-06-29 2012-07-19 Jan Grebe Pressure control valve arrangement having pressure medium guiding surface integrally formed onto a projection of the cover
CN106488862A (zh) * 2014-08-27 2017-03-08 威伯科有限公司 用于压缩空气制动设备中进行压力调制的阀单元
US20180265061A1 (en) * 2015-11-28 2018-09-20 Wabco Gmbh Hydraulic brake system
US20190193706A1 (en) * 2016-09-05 2019-06-27 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Solenoid valve assembly for a braking system for a vehicle, braking system for a vehicle, and method for mounting a solenoid valve assembly for a braking system for a vehicle
CN113753226A (zh) * 2021-08-18 2021-12-07 西安航空制动科技有限公司 一种集成嵌入式飞机刹车系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013100778B3 (de) 2013-01-25 2014-03-13 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Rückschlagventil für Entlüftungs- oder Auslassöffnungen von Drucklufteinrichtungen von Fahrzeugen
DE102015108210A1 (de) * 2015-05-26 2016-12-01 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Gehäusebauteil eines Gehäuses einer Druckmittel führenden Vorrichtung eines Fahrzeugs

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3416843A (en) * 1966-12-14 1968-12-17 Berg Mfg & Sales Co Brake pressure regulator
US3826283A (en) * 1973-05-29 1974-07-30 Berg Manufacturing Co Inversion valve
US3853357A (en) * 1973-09-04 1974-12-10 Gen Motors Corp Vehicle pilot pressure controlled brake system with wheel lock control modulating means
US4230377A (en) * 1978-03-09 1980-10-28 Robert Bosch Gmbh Pressure control valve unit
JPS6045459A (ja) * 1983-08-20 1985-03-11 Nippon Air Brake Co Ltd ブレ−キ弁におけるヒステリシスの低減方法およびブレ−キ弁
US5374114A (en) * 1991-01-15 1994-12-20 Alfred Teves Gmbh Electrohydraulic pressure control device

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2224274C3 (de) * 1971-01-18 1981-05-14 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Blockiergeschützte Fahrzeugbremsanlage, insbesondere für Straßenfahrzeuge
DE2855876C2 (de) 1978-12-22 1986-10-23 Knorr-Bremse AG, 8000 München Schaltventil für Bremsblockierschutzeinrichtungen von Druckluftbremsanlagen in Kraftfahrzeugen
IT8553613V0 (it) * 1985-07-19 1985-07-19 Magneti Marelli Spa Gruppo elettropneumatico di controllo per impianti di frenatura anti slittamento per autoveicoli
DE3637415A1 (de) 1986-11-03 1988-05-05 Knorr Bremse Ag Drucksteuerventil, insbesondere fuer blockierschutzeinrichtungen von kraftfahrzeugen
DE4038575A1 (de) * 1989-12-22 1991-06-27 Bosch Gmbh Robert Drucksteuerventil fuer druckluftbetaetigte fahrzeugbremsanlagen
GB9102313D0 (en) * 1991-02-02 1991-03-20 Bendix Ltd Fluid pressure modulator valve device
JPH08175353A (ja) * 1994-12-27 1996-07-09 Nabco Ltd アンチスキッドブレーキ装置
DE4447305C2 (de) * 1994-12-31 2003-04-17 Knorr Bremse Systeme Verfahren zum Entlüften von Bremszylindern in schlupfgeregelten Druckluft-Bremsanlagen
DE10046977B4 (de) * 2000-09-22 2004-06-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kombinierte Ventilvorrichtung
DE102008028440A1 (de) * 2008-06-17 2009-12-31 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Drucksteuerventilanordnung mit Membranventilen zur Steuerung eines Fluiddrucks in einer ABS-Bremsanlage eines Fahrzeugs mit in einem Gehäuseteil einstückig integriertem Ventilsitz

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3416843A (en) * 1966-12-14 1968-12-17 Berg Mfg & Sales Co Brake pressure regulator
US3826283A (en) * 1973-05-29 1974-07-30 Berg Manufacturing Co Inversion valve
US3853357A (en) * 1973-09-04 1974-12-10 Gen Motors Corp Vehicle pilot pressure controlled brake system with wheel lock control modulating means
US4230377A (en) * 1978-03-09 1980-10-28 Robert Bosch Gmbh Pressure control valve unit
JPS6045459A (ja) * 1983-08-20 1985-03-11 Nippon Air Brake Co Ltd ブレ−キ弁におけるヒステリシスの低減方法およびブレ−キ弁
US5374114A (en) * 1991-01-15 1994-12-20 Alfred Teves Gmbh Electrohydraulic pressure control device

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120181852A1 (en) * 2009-06-29 2012-07-19 Jan Grebe Pressure control valve arrangement having pressure medium guiding surface integrally formed onto a projection of the cover
US9039103B2 (en) * 2009-06-29 2015-05-26 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Pressure control valve arrangement having pressure medium guiding surface integrally formed onto a projection of the cover
CN106488862A (zh) * 2014-08-27 2017-03-08 威伯科有限公司 用于压缩空气制动设备中进行压力调制的阀单元
US10112590B2 (en) * 2014-08-27 2018-10-30 Wabco Gmbh Valve unit for modulating pressure in an air-brake system
US20180265061A1 (en) * 2015-11-28 2018-09-20 Wabco Gmbh Hydraulic brake system
US10829100B2 (en) * 2015-11-28 2020-11-10 Wabco Gmbh Hydraulic brake system
US20190193706A1 (en) * 2016-09-05 2019-06-27 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Solenoid valve assembly for a braking system for a vehicle, braking system for a vehicle, and method for mounting a solenoid valve assembly for a braking system for a vehicle
US10988126B2 (en) * 2016-09-05 2021-04-27 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Solenoid valve assembly for a braking system for a vehicle, braking system for a vehicle, and method for mounting a solenoid valve assembly for a braking system for a vehicle
CN113753226A (zh) * 2021-08-18 2021-12-07 西安航空制动科技有限公司 一种集成嵌入式飞机刹车系统

Also Published As

Publication number Publication date
EP2448797A1 (de) 2012-05-09
DE102009030898A1 (de) 2010-12-30
EP2448797B1 (de) 2015-08-12
US10059317B2 (en) 2018-08-28
WO2011000768A1 (de) 2011-01-06
US20170120881A1 (en) 2017-05-04

Similar Documents

Publication Publication Date Title
US10059317B2 (en) Pressure control valve arrangement having an eccentrically mounted double magnet
US9637099B2 (en) Pressure control valve arrangement having diaphragm valves for controlling a fluid pressure in an ABS brake system of a vehicle, having a valve seat integrated in a unipartite fashion in a plastic housing part
US8672421B2 (en) Pressure control valve arrangement having diaphragm valves for controlling a fluid pressure in an ABS brake system of a vehicle, having diaphragms arranged in parallel planes or in coplanar fashion
CN102066169B (zh) 用于车辆制动系统的调节阀以及带有这种调节阀的车辆制动系统
US8979217B2 (en) Electro-pneumatic pressure regulation module comprising pressure regulation channels having separate pneumatic circuits
US11634109B2 (en) Method for decelerating a vehicle, in particular a commercial vehicle, electro-pneumatic brake system for decelerating a vehicle, and vehicle having an electro-pneumatic brake system
US9676378B2 (en) Valve device adaptable for brake control of a variety of pressure medium-operated vehicle brake systems
US4647114A (en) Hydraulic brake system
US9616866B2 (en) Vehicular brake hydraulic pressure control apparatus
EP3787942B1 (de) Redundantes bremssystem für schwerlastfahrzeuge
US7658453B2 (en) Service brake relay with integrated quick release valve
US9039103B2 (en) Pressure control valve arrangement having pressure medium guiding surface integrally formed onto a projection of the cover
US9180849B2 (en) Pressure control valve arrangement having a pressure medium channel of oval cross-section
US6846408B2 (en) Filter assembly for a control valve in a vehicular brake system
US9139178B2 (en) Pressure control valve arrangement having covers that are produced as a completely integral part with transverse channels by primary shaping
MXPA01007768A (es) Valvula rele con valvula de verificacion doble polarizada integral.
US11485333B2 (en) Diaphragm valve without a supporting ring and without a supporting plate
CN218367764U (zh) 挂车控制阀和商用车辆
US6766644B2 (en) Master cylinder with by-pass function and proportioning valve
JP3955312B2 (ja) ブレーキ装置
US20240270222A1 (en) Brake system and method for braking a vehicle having at least two axles
JP3382345B2 (ja) 液圧装置
US20240083405A1 (en) Relay Valve Arrangement for a Trailer Brake System
JP3898920B2 (ja) ブレーキ装置
JP3397016B2 (ja) リザーバ蓄液量検出装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: KNORR-BREMSE SYSTEME FUER NUTZFAHRZEUGE GMBH, GERM

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:GREBE, JAN;BRENNER, DIRK;WEIPPERT, JOCHEN;AND OTHERS;SIGNING DATES FROM 20120118 TO 20120124;REEL/FRAME:027974/0760

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION