EP0000794B1 - Two-cycle control valve - Google Patents

Two-cycle control valve Download PDF

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Publication number
EP0000794B1
EP0000794B1 EP78200086A EP78200086A EP0000794B1 EP 0000794 B1 EP0000794 B1 EP 0000794B1 EP 78200086 A EP78200086 A EP 78200086A EP 78200086 A EP78200086 A EP 78200086A EP 0000794 B1 EP0000794 B1 EP 0000794B1
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EP
European Patent Office
Prior art keywords
valve
spring
separate
piston
balancing piston
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
EP78200086A
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German (de)
French (fr)
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EP0000794A1 (en
Inventor
Manfred Siebold
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
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Robert Bosch GmbH
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Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0000794A1 publication Critical patent/EP0000794A1/en
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Publication of EP0000794B1 publication Critical patent/EP0000794B1/en
Expired legal-status Critical Current

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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
    • 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
    • B60T15/04—Driver's valves
    • B60T15/043—Driver's valves controlling service pressure brakes
    • B60T15/045—Driver's valves controlling service pressure brakes in multiple circuit systems, e.g. dual circuit systems
    • B60T15/046—Driver's valves controlling service pressure brakes in multiple circuit systems, e.g. dual circuit systems with valves mounted in tandem

Definitions

  • the invention is based on a two-circuit control valve according to the preamble of the main claim.
  • a control valve is known (US-A-3 291 539).
  • the object of the invention is to keep the response behavior of the two individual valves and the pressure changes introduced into the two circuits by the same.
  • a two-circuit control valve is used as a two-circuit brake valve and has a housing 1, in which an actuating rod 2 is inserted from above.
  • the rod 2 presses on a sleeve 3 with a shoulder 4, under which a travel spring 5 lies.
  • the other end of the travel spring 5 engages a staging and reaction piston 6, which carries an outlet valve seat 7 of a first individual valve 8 at its other end.
  • a second valve seat 9 of the individual valve 8 is located on a fixed housing part, which limits a pressure change chamber 10 towards the piston 6 and which accommodates a storage chamber 11 on the inside.
  • the storage chamber 11 is connected via a threaded connection to a supply line of a brake circuit I, which is fed via the pressure swing chamber 10 and a threaded connection.
  • a closing body 13 works together with the two valve seats 7 and 9 and is pressed against the seats by a valve spring 12.
  • the other end of the valve spring 12 is supported on an inner shoulder 14 of a weighing piston 17 which on the one hand delimits the pressure change chamber 10 of the brake circuit I and on the other hand a pressure change chamber of the brake circuit 11.
  • the weighing piston has a coaxial tubular extension 15, one end of which seals penetrates an annular wall 16 inserted into the housing 1 and on which the closing body 13 with an annular sealing lip is placed so as to be axially movable.
  • the inner diameter of the annular wall 16 is equal to the diameter of the outlet valve seat 22 of the second individual valve 19, so that the weighing piston 17 has the same effective surfaces upwards and downwards.
  • the weighing piston 17 is provided with an axial through-bore 21 through the tube extension 15. On its circumference it carries two O-rings 24 and 25, between which an outside air chamber 17 'is arranged. This outside air chamber 17' is connected to the bore 21 via a radial channel 20.
  • the weighing piston 17 is also provided at its other end with the outlet valve seat 22, which projects into an inlet seat 18 of a second individual valve 19 which is fixed to the housing.
  • the inlet seat 18 lies between a pressure change chamber 26 and a storage chamber 27, in which a closing body 28 of the second individual valve for a brake circuit II is arranged.
  • the housing 1 is closed at the bottom by an inserted wall 1 ', on which both a valve spring 29 of the second individual valve 19 and a compression spring 30 acting on the weighing piston 17 are supported.
  • the wall 1 ' has a tubular cylindrical projection, on which the closing body 28 is placed with an annular sealing lip so as to be axially movable.
  • the closing body 13 of the first individual valve 8 and the closing body 28 of the second individual valve 19 are axially pierced to relieve their pressure.
  • a common connection of the two individual valves 8 and 19 to the outside air is established via these perforations in the closing body and via an outside air connection 23.
  • the spring 30 lies within the second individual valve 19. Its upper end engages under a spring plate 31 and tries to hold it on a radial wall 32 of the weighing piston 17.
  • This wall 32 is provided with several axially parallel openings 33 for the passage of air.
  • the wall 32 has a coaxial bore 34 which is penetrated by one end of a plunger 35 which is in contact with the spring plate 31.
  • the plunger 35 is screwed with its other end in the staging and reaction piston 6, which likewise has a plurality of axially parallel openings 36 for the air passage on the inside.
  • the screw connection is variable in length in order to adjust the distance between the outlet valve seat 22 of the second individual valve 19 and the outlet valve seat 7 of the first individual valve 8.
  • the actuating rod 2 runs into the brake valve and actuates the stepping element by pressing the travel spring 5. and reaction piston 6.
  • the plunger 35 With the piston 6, the plunger 35 also moves downward and lifts the spring plate 31 from the weighing piston 17. So that the action of the compression spring 31 on the weighing piston 17 is canceled, and the weighing piston 17 is now only subject to the force of the valve spring 12, so that it makes a way down until it abuts the closing body 28.
  • the outlet valve of the second individual valve 19 is then closed.
  • An inlet valve can first be opened on the individual valve 8. With an appropriate spring design, the inlet valve of the individual valve 19 can also be opened first. In both cases, the weighing piston 17 immediately compensates by opening the inlet valve of the other individual valve as well as simultaneously under the pressure introduced into the pressure change chambers 10 or 26. The brake cylinders of both brake circuits I and II are then supplied evenly with the same brake pressure. When the inlet valves are open, the forces of the compression spring 30 and the two valve springs 12 and 29 of the individual valves 8 and 19 are decisive for the restoring forces on the two individual valves 8 and 19. The spring force of the valve spring 12 is also decisive for the opening force on the second individual valve 19.
  • a rubber spring can also be used as a travel spring.
  • the connections for the reservoir and the brake cylinder are arranged at the same height on the housing 1 for each brake circuit I or II.
  • control valve according to the invention Due to the plunger 35 arranged inside the weighing piston 17 and the spring 30 arranged without taking up space, the control valve according to the invention is very compact, so that it takes up very little space when it is installed.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Zweikreis-Steuerventil nach der Gattung des Hauptanspruchs. Ein derartiges Steuerventil ist bekannt (US-A-3 291 539).The invention is based on a two-circuit control valve according to the preamble of the main claim. Such a control valve is known (US-A-3 291 539).

Bei diesem bekannten Steuerventil wird zuerst das dem Stößel benachbarte, erste Einzelventil umgeschaltet und dann wirkt der in den ersten Bremskreis eingesteuerte Druck auf den das zweite Einzelventil umschaltenden Kolben ein. Dadurch sind die Druckanstiege, wie überhaupt alle Druckänderungen in den beiden Bremskreisen nie gleichmäßig, was eine unterschiedliche Bremsung an den verschiedenen Gruppen von Bremszylindern nach sich zieht.In this known control valve, the first individual valve adjacent to the tappet is first switched over, and then the pressure applied to the first brake circuit acts on the piston switching over the second individual valve. As a result, the pressure increases, like all pressure changes in the two brake circuits, are never even, which results in different braking on the different groups of brake cylinders.

Des weiteren ist es durch die DE-A-19 35 537 bereits bekannt, bei einem Dreikreis-Steuerventil einen Stößel zu verwenden, der ein erstes Einzelventil des Steuerventils durchgreift.Furthermore, it is already known from DE-A-19 35 537 to use a tappet in a three-circuit control valve which passes through a first single valve of the control valve.

Aufgabe der Erfindung ist es, das Ansprechverhalten der beiden Einzelventile und die von diesen in die beiden Kreise eingesteuerten Druckänderungen durchaus gleich zu halten.The object of the invention is to keep the response behavior of the two individual valves and the pressure changes introduced into the two circuits by the same.

Diese Aufgabe wird gelöst durch ein Steuerventil mit den kennzeichnenden Merkmalen des Hauptanspruchs.This object is achieved by a control valve with the characterizing features of the main claim.

Beschreibung der ErfindungDescription of the invention

Ein Zweikreis-Steuerventil ist als Zweikreis-Bremsventil eingesetzt und hat ein Gehäuse 1, in das von oben eine Betätigungsstange 2 eingesetzt ist. Die Stange 2 drückt auf eine Hülse 3 mit einer Schulter4, unter der eine Wegfeder 5 liegt. Das andere Ende der Wegfeder 5 greift an einem Stufungs- und Rückwirkkolben 6 an, der an seinem anderen Ende einen Auslaßventilsitz 7 eines ersten Einzelventils 8 trägt. Ein zweiter Ventilsitz 9 des Einzelventils 8 befindet sich an einem feststehenden Gehäuseteil, der zum Kolben 6 hin eine Druckwechselkammer 10 begrenzt und der innen eine Vorratskammer 11 aufnimmt. Die Vorratskammer 11 ist über einen Gewindeanschluß an eine Vorratsleitung eines Bremskreises I angeschlossen, der über die Druckwechselkammer 10 und einen Gewindeanschluß gespeist wird. Mit den beiden Ventilsitzen 7 und 9 arbeitet ein Schließkörper 13 zusammen, der von einer Ventilfeder 12 gegen die Sitze gedrückt wird. Das andere Ende der Ventilfeder 12 stützt sich an einer Innenschulter 14 eines Wiegekolbens 17 ab, der einerseits die Druckwechselkammer 10 des Bremskreises I und andererseits eine Druckwechselkammer des Bremskreises 11 begrenzt. Der Wiegekolben hat einen koaxialen Rohransatz 15, dessen eines Ende eine in das Gehäuse 1 eingesetzte Ringwand 16 abgedichtet durchdringt und auf den der Schließkörper 13 mit einer Ringdichtlippe axialbeweglich aufgesetzt ist. Der Innendurchmesser der Ringwand 16 ist gleich dem Durchmesser des Auslaßventilsitzes 22 des zweiten Einzelventils 19, damit der Wiegekolben 17 nach oben und unten die gleichen Wirkflächen hat. Durch den Rohransatz 15 ist der Wiegekolben 17 mit einer axialen Durchgangsbohrung 21 versehen. An seinem Umfang trägt er zwei O-Ringe 24 und 25, zwischen denen eine Außenluftkammer 17' angeordnet ist Diese Außenluftkammer 17' ist über einen Radialkanal 20 mit der Bohrung 21 verbunden. Der Wiegekolben 17 ist außerdem an seinem anderen Ende mit dem Auslaßventilsitz 22 versehen, der in einen gehäusefesten Einlaßsitz 18 eines zweiten Einzelventils 19 hineinragt. Der Einlaßsitz 18 liegt zwischen einer Druckwechselkammer 26 und einer Vorratskammer 27, in der ein Schließkörper 28 des zweiten Einzelventils für einen Bremskreis II angeordnet ist. Nach unten wird das Gehäuse 1 durch eine eingesetzte Wand 1' abgeschlossen, an der sich sowohl eine Ventilfeder 29 des zweiten Einzelventils 19 als auch eine auf den Wiegekolben 17 einwirkende Druckfeder 30 abstützt. Die Wand 1' hat einen rohrzylindrischen Ansatz, auf den der Schließkörper 28 mit einer Ringdichtlippe axialbeweglich aufgesetzt ist. Der Schiießkörper 13 des ersten Einzelventils 8 und der Schließkörper 28 des zweiten Einzelventils 19 sind zu ihrer Druckentlastung axial durchbohrt. Über diese Durchbohrungen der Schließkörper und über einen Außenluftanschluß 23 ist eine gemeinsame Verbindung der beiden Einzelventile 8 und 19 zur Außenluft hergestellt.A two-circuit control valve is used as a two-circuit brake valve and has a housing 1, in which an actuating rod 2 is inserted from above. The rod 2 presses on a sleeve 3 with a shoulder 4, under which a travel spring 5 lies. The other end of the travel spring 5 engages a staging and reaction piston 6, which carries an outlet valve seat 7 of a first individual valve 8 at its other end. A second valve seat 9 of the individual valve 8 is located on a fixed housing part, which limits a pressure change chamber 10 towards the piston 6 and which accommodates a storage chamber 11 on the inside. The storage chamber 11 is connected via a threaded connection to a supply line of a brake circuit I, which is fed via the pressure swing chamber 10 and a threaded connection. A closing body 13 works together with the two valve seats 7 and 9 and is pressed against the seats by a valve spring 12. The other end of the valve spring 12 is supported on an inner shoulder 14 of a weighing piston 17 which on the one hand delimits the pressure change chamber 10 of the brake circuit I and on the other hand a pressure change chamber of the brake circuit 11. The weighing piston has a coaxial tubular extension 15, one end of which seals penetrates an annular wall 16 inserted into the housing 1 and on which the closing body 13 with an annular sealing lip is placed so as to be axially movable. The inner diameter of the annular wall 16 is equal to the diameter of the outlet valve seat 22 of the second individual valve 19, so that the weighing piston 17 has the same effective surfaces upwards and downwards. The weighing piston 17 is provided with an axial through-bore 21 through the tube extension 15. On its circumference it carries two O-rings 24 and 25, between which an outside air chamber 17 'is arranged. This outside air chamber 17' is connected to the bore 21 via a radial channel 20. The weighing piston 17 is also provided at its other end with the outlet valve seat 22, which projects into an inlet seat 18 of a second individual valve 19 which is fixed to the housing. The inlet seat 18 lies between a pressure change chamber 26 and a storage chamber 27, in which a closing body 28 of the second individual valve for a brake circuit II is arranged. The housing 1 is closed at the bottom by an inserted wall 1 ', on which both a valve spring 29 of the second individual valve 19 and a compression spring 30 acting on the weighing piston 17 are supported. The wall 1 'has a tubular cylindrical projection, on which the closing body 28 is placed with an annular sealing lip so as to be axially movable. The closing body 13 of the first individual valve 8 and the closing body 28 of the second individual valve 19 are axially pierced to relieve their pressure. A common connection of the two individual valves 8 and 19 to the outside air is established via these perforations in the closing body and via an outside air connection 23.

Die Feder 30 liegt innerhalb des zweiten Einzelventils 19. Ihr oberes Ende untergreift einen Federteller 31 und versucht, diesen an einer radialen Wand 32 des Wiegekolbens 17 festzuhalten. Diese Wand 32 ist zum Luftdurchgang mit mehreren achsparallelen Durchbrüchen 33 versehen. Außerdem hat die Wand 32 eine koaxiale Bohrung 34, die von einem Ende eines Stößels 35 durchgriffen wird, das mit dem Federteller 31 in Berührung steht. Der Stößel 35 ist mit seinem anderen Ende im Stufungs- und Rückwirkkolben 6 verschraubt, der ebenfalls innen mehrere achsparallele Durchbrüche 36 für den Luftdurchgang aufweist. Die Verschraubung ist längenveränderlich, um den Abstand des Auslaßventilsitzes 22 des zweiten Einzelventils 19 zum Auslaßventilsitz 7 des ersten Einzelventils 8 zu justieren.The spring 30 lies within the second individual valve 19. Its upper end engages under a spring plate 31 and tries to hold it on a radial wall 32 of the weighing piston 17. This wall 32 is provided with several axially parallel openings 33 for the passage of air. In addition, the wall 32 has a coaxial bore 34 which is penetrated by one end of a plunger 35 which is in contact with the spring plate 31. The plunger 35 is screwed with its other end in the staging and reaction piston 6, which likewise has a plurality of axially parallel openings 36 for the air passage on the inside. The screw connection is variable in length in order to adjust the distance between the outlet valve seat 22 of the second individual valve 19 and the outlet valve seat 7 of the first individual valve 8.

WirkungsweiseMode of action

Bei gelöster Bremse sind die Schließkörper 13 und 28 von den beiden Auslaßventilsitzen 7 und 22 abgehoben, und die Bremskreise I und II sind über den gemeinsamen Außenluftanschluß 23 entlüftet.When the brake is released, the closing bodies 13 and 28 are lifted off the two exhaust valve seats 7 and 22, and the brake circuits I and II are vented via the common outside air connection 23.

Wird gebremst, so läuft die Betätigungsstange 2 in das Bremsventil hinein und betätigt unter Durchdrücken der Wegfeder 5 den Stufungs-und Rückwirkkolben 6. Mit dem Kolben 6 bewegt sich auch der Stößel 35 nach unten, und hebt den Federteller 31 vom Wiegekolben 17 ab. Damit ist die Einwirkung der Druckfeder 31 auf den Wiegekolben 17 aufgehoben, und der Wiegekolben 17 unterliegt jetzt nur noch der Kraft der Ventilfeder 12, so daß er einen Weg nach unten macht, bis er am Schließkörper 28 anstößt. Das Auslaßventil des zweiten Einzelventils 19 ist dann geschlossen.If braking is carried out, the actuating rod 2 runs into the brake valve and actuates the stepping element by pressing the travel spring 5. and reaction piston 6. With the piston 6, the plunger 35 also moves downward and lifts the spring plate 31 from the weighing piston 17. So that the action of the compression spring 31 on the weighing piston 17 is canceled, and the weighing piston 17 is now only subject to the force of the valve spring 12, so that it makes a way down until it abuts the closing body 28. The outlet valve of the second individual valve 19 is then closed.

Beim Weiterbewegen der Betätigungsstange 2 in Bremsbetätigungsrichtung schließt dann das Auslaßventil des ersten Einzelventils 8, das einen größeren Öffnungshub aufweist als das andere Auslaßventil.When the actuating rod 2 moves further in the brake actuating direction, the outlet valve of the first individual valve 8 then closes, which has a larger opening stroke than the other outlet valve.

Ein Öffnen eines Einlaßventils kann zuerst am Einzelventil 8 stattfinden. Bei entsprechender Federauslegung kann aber auch zuerst das Einlaßventil des Einzelventils 19 geöffnet werden. In beiden Fällen sorgt der Wiegekolben 17 sofort für einen Ausgleich, indem er unter dem in die Druckwechselkammern 10 oder 26 eingesteuerten Druck so gut wie gleichzeitig das Einlaßventil des anderen Einzelventils aufmacht. Die Bremszylinder beider Bremskreise I und II werden dann gleichmäßig m:t gleichhohem Bremsdruck versorgt. Bei geöffneten Einlaßventilen sind die Kräfte der Druckfeder 30 und der beiden Ventilfedern 12 und 29 der Einzelventile 8 und 19 maßgebend für die Rückstellkräfte an den beiden Einzelventilen 8 und 19. Die Federkraft der Ventilfeder 12 ist außerdem bestimmend für die Öffnungskraft am zweiten Einzelventil 19.An inlet valve can first be opened on the individual valve 8. With an appropriate spring design, the inlet valve of the individual valve 19 can also be opened first. In both cases, the weighing piston 17 immediately compensates by opening the inlet valve of the other individual valve as well as simultaneously under the pressure introduced into the pressure change chambers 10 or 26. The brake cylinders of both brake circuits I and II are then supplied evenly with the same brake pressure. When the inlet valves are open, the forces of the compression spring 30 and the two valve springs 12 and 29 of the individual valves 8 and 19 are decisive for the restoring forces on the two individual valves 8 and 19. The spring force of the valve spring 12 is also decisive for the opening force on the second individual valve 19.

Anstatt der Stahlfeder 5 kann auch eine Gummifeder als Wegfeder verwendet werden. Die Anschlüsse für Vorratsbehälter und Bremszylinder sind für jeweils einen Bremskreis I bzw. II auf gleicher Höhe am Gehäuse 1 angeordnet.Instead of the steel spring 5, a rubber spring can also be used as a travel spring. The connections for the reservoir and the brake cylinder are arranged at the same height on the housing 1 for each brake circuit I or II.

Durch den innerhalb des Wiegekolbens 17 angeordneten Stößel 35 und durch die ohne Platzverbrauch angeordnete Feder 30 baut das erfindungsgemäße Steuerventil sehr kompakt, so daß es bei seinem Einbau sehr wenig Platz verbraucht.Due to the plunger 35 arranged inside the weighing piston 17 and the spring 30 arranged without taking up space, the control valve according to the invention is very compact, so that it takes up very little space when it is installed.

Claims (7)

1. Dual-circuit control valve, especially for a braking system of motor vehicles, having two separate valves (8, 19) which are disposed one after the other in a valve housing (1) and are equipped with valve springs (12, 29), also having an actuating rod (2) which enters the valve housing and co-operates therein mechanically with one portion of the first separate valve (8) by way of a travel spring (5) and a piston (6), and having a device for actuating the second separate valve (19) and having a balancing piston (17) which is subjected to the two brake pressures introduced into two brake circuits, and also having a stem (35) which can counteract the effect of a compression spring (30) inserted between the balancing piston and a fixed housing wall, characterised in that the valve spring (12) of the first separate valve (8) is supported, at the one end, against the balancing piston (17) and, at the other end, by way of a valve closure element (13) against the housing (valve seat 9), and its force support upon the balancing piston (17) when the control valve is unactuated is alleviated by the compression spring (30), also in that the stem (35) is secured to the piston (6), which is moved by the actuating rod (2), and reaches through the first separate valve (8) in a manner known per se, and in that the force of the valve spring (29), which acts upon the balancing piston (17), upon such an actuation, by way of a closure element (28) of the second separate valve (19), against the force of the valve spring (12) of the first separate valve (8) is compensated in a counterbalanced manner.
2. Dual-circuit control valve as claimed in claim 1, characterised in that the valve spring (12) of the first separate valve (8) is decisive for the opening forces at the second separate valve (19).
3. Dual-circuit control valve as claimed in claim 1 or 2, characterised in that a spring plate (31) is inserted between the balancing piston (17) and the end of the compression spring (30) facing the balancing piston and can be lifted from the end of the stem (35) by the balancing piston.
4. Dual-circuit control valve as claimed in one of claims 1 to 3, characterised in that the balancing piston (17) has a tubular projection (15) upon which a closure element (13) of the first separate valve (8) with a moulded-on annular sealing lip is slidably placed.
5. Dual-circuit control valve as claimed in one of claims 1 to 4, characterised in that the balancing piston (17) has an inner shoulder (14) which is the abutment for the valve spring (12) acting upon the closure element (13), of the first separate valve (8).
6. Dual-circuit control valve as claimed in claim 4 or 5, characterised in that the end of the tubular projection of the balancing piston (17) facing the first separate valve (8) reaches through an annular wall (16), whose internal diameter corresponds to the diameter of the outlet valve seat (22) of the second separate valve (19).
7. Dual-circuit control valve as claimed in one of claims 1 to 6, characterised in that the stem (35) is screwed in the piston (6) in a length-varying manner.
EP78200086A 1977-08-13 1978-07-07 Two-cycle control valve Expired EP0000794B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2736661 1977-08-13
DE19772736661 DE2736661A1 (en) 1977-08-13 1977-08-13 TWO-CIRCUIT CONTROL VALVE

Publications (2)

Publication Number Publication Date
EP0000794A1 EP0000794A1 (en) 1979-02-21
EP0000794B1 true EP0000794B1 (en) 1981-05-20

Family

ID=6016384

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78200086A Expired EP0000794B1 (en) 1977-08-13 1978-07-07 Two-cycle control valve

Country Status (3)

Country Link
EP (1) EP0000794B1 (en)
BR (1) BR7805161A (en)
DE (2) DE2736661A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2119464B (en) * 1982-03-17 1985-03-20 Lucas Ind Plc Improvements in dual brake valves
GB2133097B (en) * 1982-11-29 1986-09-03 Dewandre Co Ltd C Pneumatic brake valve
GB8324941D0 (en) * 1983-09-17 1983-10-19 Lucas Ind Plc Dual brake valves
IT1190559B (en) * 1986-04-02 1988-02-16 Magneti Marelli Spa DUPLEX TYPE PNEUMATIC DISTRIBUTOR FOR BRAKING SYSTEMS FOR VEHICLES
DE3830105A1 (en) * 1988-09-05 1990-03-15 Knorr Bremse Ag BRAKE VALVE FOR AIR BRAKE SYSTEMS OF VEHICLES

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1010942A (en) * 1961-06-26 1965-11-24 Dewandre Co Ltd C Improvements in or relating to fluid pressure-operated braking apparatus
US3291539A (en) * 1966-03-17 1966-12-13 Wagner Electric Corp Control valve
DE1943753C3 (en) * 1969-07-12 1978-07-13 Wabco Westinghouse Gmbh, 3000 Hannover Three-circuit brake valve for air brake systems in motor vehicles
DE1935537A1 (en) * 1969-07-12 1971-02-11 Westinghouse Bremsen U Appbau Brake valve for three-circuit air brake systems

Also Published As

Publication number Publication date
DE2736661A1 (en) 1979-02-22
EP0000794A1 (en) 1979-02-21
DE2860713D1 (en) 1981-08-27
DE2736661C2 (en) 1987-04-02
BR7805161A (en) 1979-05-02

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