GB1602820A - Pressure level regulating valve - Google Patents

Pressure level regulating valve Download PDF

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Publication number
GB1602820A
GB1602820A GB22841/78A GB2284178A GB1602820A GB 1602820 A GB1602820 A GB 1602820A GB 22841/78 A GB22841/78 A GB 22841/78A GB 2284178 A GB2284178 A GB 2284178A GB 1602820 A GB1602820 A GB 1602820A
Authority
GB
United Kingdom
Prior art keywords
valve seat
pressure
action
service
spring
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
GB22841/78A
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.)
Wabco Fahrzeugbremsen GmbH
Original Assignee
Wabco Fahrzeugbremsen 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 Wabco Fahrzeugbremsen GmbH filed Critical Wabco Fahrzeugbremsen GmbH
Publication of GB1602820A publication Critical patent/GB1602820A/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
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
    • B60T13/26—Compressed-air systems
    • B60T13/268—Compressed-air systems using accumulators or reservoirs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
    • B60T13/14—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using accumulators or reservoirs fed by pumps
    • B60T13/141—Systems with distributor valve
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/04—Control of fluid pressure without auxiliary power
    • G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
    • G05D16/101—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger the controller being arranged as a multiple-way valve

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Safety Valves (AREA)

Description

(54) PRESSURE LEVEL REGULATING VALVE (71) We, WABCO FAHRZEUGBREMSEN GmbH (formerly WABCO WEST1NGHOUsE GmbH), a German Company, of Am Lindener Hafen 21, 3000 Hannover 91, Germany, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- The invention relates to a regulating valve for the level control of a service pressure, especially brake pressure.
The purpose of regulating valves of this type is to prescribe and lower a service pressure of which the level is limited: one known form of regulating valve is described in German Offenlegungsschrift No. 22 60 799.
The present invention provides a pressure level regulating valve having a pressure medium inlet, a service pressure outlet and a pressure medium return, a first valve operable in dependence on the service pressure and in accordance with an applied control variable to block the service outlet from the inlet, and a second valve operable to connect the service outlet to the return when the inlet is closed, the second valve having a valve seat member slidably arranged on a tubular extension of a closure member of the first valve and displaceable by the said control variable, the valve seat member being exposed to the service pressure through a bore in the closure member and having a sealing face which is formed in a conical region of a recess in the valve seat member and is cooperable with an end face of the tubular extension.
An embodiment of the invention is described in detail in the following, with reference to the accompanying drawing which shows a longitudinal section through a regulating valve.
The regulating valve 1 illustrated has a housing 2 containing a through-bore 3, which is connected vi a bore 4 in the housing to a pressure medium inlet 5, of which the connection to a store is shown by symbols.
The through-bore 3 is provided at both ends with stepped portions 6 and 7.
In its end region adjacent the stepped portion 6 the bore 3 is tightly sealed by a plug 8, and is connected by means of a longitudinal bore 9 through the plug 8 to a service connection 10.
In its end region adjacent the stepped portion 7, the bore 3 is connected via a bore 11 in the housing to a return 12.
At the stepped portion 6 of the bore 3 a valve seat is formed, which co-operates with a closure member 15 acted upon in the direction of closure by a spring 14 supported against the plug 8. The closure member 15 has a conical portion providing a sealing face 16.
The closure member 15 has a longitudinal through-bore 17 and is arranged so as to slide in the bore 3 by means of a tubular portion 18 extending to the end region of the bore 3 adjacent the stepped portion 7.
Adjacent the conical portion of the closure member 15, the tubular portion 18 has an annular recess which forms, with the wall of the bore 3, an annular chamber 19 connected via the housing bore 4 to the pressure medium inlet 5.
There is arranged in the end region of the bore 3 adjacent the stepped portion 7, a valve seat 20 arranged to slide on the tubular portion 18: for this purpose, the valve seat is formed with a blind bore into which the portion 18 extends, being clearly spaced from the wall. The blind bore has, in the end portion, first of all an annular recess 22 which is connected via a trans verse bore 21 to the bore and furthermore via the housing bore 11 to the return 12; a conically tapered region, and finally a base region which is continued slightly and has a diameter smaller than that of the tubular portion 18. In the conically tapered region of the blind bore, a seaTing face 23 of the valve seat 20 is formed, co-operating with the outer edge of the tubular portion 18.
The tubular portion 18 has a sealing face 24 provided along its outer edge and cooperating with the valve seat 20 in a hysteresisfree manner 6r - with a corres pondingly-bevelled outer edge (not shown) with ft deliberate hysteresis.
The sealing face 24 along the unbevelled outer edge of the tubular portion 18 and the sealing face 16 in the conical region of the closure member 15 are, excluding installation tolerances, of the same size.
There is sealed and secured in the end region of the bore 3, adjacent the stepped portion 7. an actuating head 25 which has a sealed and slide-mounted thrust member 28 bearing with a bulge-shaped end face against the valve seat 20 under the action of a pressure spring 27 fixed in a spring support member 26. Through this thrust member 28, the valve seat 20 is acted upon by a control variable, in that the support member 26 is displaceable against the action of a spring 29, via a connecting rod 30 and an eccentric 31, by means of a handoperated lever 32, thus adjusting the action of the pressure spring 27.
The method of operation of the regulating valve shown in the drawing is as follows: In the drawing the regulating valve 1 is shown in its starting position, in which the hand lever 32 is in its outermost left-hand stop position and the spring support member 26, bears, under the action of the spring 29, against a stop arranged in the actuating head 25: the pressure spring 27 is then most active and acts with the maximum control via the thrust member 28 on the valve seat 20 against the action of the service pressure.
In the case of over action of the control variable, the valve seat 20 assumes a position displaced towards the service connection against the action of the service pressure and the spring 14, in which position the closure member 15 bears, with the sealing face 24 of the tubular portion 18, against the sealing face 23 of the valve seat 20 and so closes the connection betwen the service outlet and the return 12, and at the same time is lifted from the valve seat 13 as a result of which the service outlet 10 is connected to the pressure medium inlet 5.
As soon as the effects of the service pressure and the control variable are balanced, the closure member 15 moves under the action of the spring 14, taking along the valve seat 20, into the closed position thus blocking the connection between the service outlet 10 and the pressure medium inlet 5.
In the case of predominant action of the service pressure, (for example as a result of a reduction of the control variable acting on the valve seat 20, brought about by actuating the hand lever 32 in the direction of arrow A to advance the spring support 26 from the stop via the eccentric 31 and connecting rod 30 against the action of the spring 29) the valve seat 20 moves under the action of the service pressure against the action of the correspondingly relaxed pressure spring 27, the closure member 15 acted upon by the spring 14 being unable to follow beyond its closed position.As a result of the latter factor, the pressure medium inlet 5 is sealed off from the service outlet 10, and the service outlet 10 is connected via the transverse bore 21, the bore 3 and the housing bore 11 to the return 12 as a result of the valve seat 20 having been moved away from the sealing face 24 of the tubular portion 18.
As soon as the service pressure is reduced to balance the action of the reduced control variable acting on the valve seat 20, the valve seat 20 moves under the action of the pressure spring 27 against the reduced action of the service pressure, and, with its sealing face 23 adjacent to the sealing face 24 of the tubular portion 18, takes up its closure position so closing the connection between the service outlet 10 and the return 12.
In this manner it is possible to regulate as desired, continuously and with precision, the service pressure in the range of a predetermined maximum level to 0 bar, this being desired, for example, for hydraulic spring stores.
The advantages that can be achieved with a regulating valve designed as described above are especially that the sliding arrangement of the valve seat 20 of one valve on the closure member 15 of the other valve and the arrangement of the sealing face 23 of the valve seat 20 in a conical region of a recess together with the sealing face 24 that can be formed along the outer edge of the tubular portion 18 of the closure member provides a regulator that can be operated with precision and in a hysteresis-free manner or with deliberate hysteresis when the outer edge sealing face 24 is correspondingly sloped.Also, the valve seat 20 is arranged in a simple manner directly on the tubular portion 18 of the closure member 15 and is acted upon, via a spring 27 and a thrust member 26, by the control variable against the action, effected over a maximum working surface, of the service pressure: as a result, a problem-free cooperation of the two valves of the regulator can be achieved, which is not susceptible to malfunction, together with a favourable construction which, with respect to its manufacture, is comparatively simple.
Moreover, the arrangement of the blind bore in the valve seat 20, with the conicallytapered region, gives the advantage of being able to make the sealing faces 24 and 16 of the two valves of the regulator the same size - apart from installation tolerances.
WHAT WE CLAIM IS: 1. A pressure level regulating valve
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (8)

**WARNING** start of CLMS field may overlap end of DESC **. pondingly-bevelled outer edge (not shown) with ft deliberate hysteresis. The sealing face 24 along the unbevelled outer edge of the tubular portion 18 and the sealing face 16 in the conical region of the closure member 15 are, excluding installation tolerances, of the same size. There is sealed and secured in the end region of the bore 3, adjacent the stepped portion 7. an actuating head 25 which has a sealed and slide-mounted thrust member 28 bearing with a bulge-shaped end face against the valve seat 20 under the action of a pressure spring 27 fixed in a spring support member 26. Through this thrust member 28, the valve seat 20 is acted upon by a control variable, in that the support member 26 is displaceable against the action of a spring 29, via a connecting rod 30 and an eccentric 31, by means of a handoperated lever 32, thus adjusting the action of the pressure spring 27. The method of operation of the regulating valve shown in the drawing is as follows: In the drawing the regulating valve 1 is shown in its starting position, in which the hand lever 32 is in its outermost left-hand stop position and the spring support member 26, bears, under the action of the spring 29, against a stop arranged in the actuating head 25: the pressure spring 27 is then most active and acts with the maximum control via the thrust member 28 on the valve seat 20 against the action of the service pressure. In the case of over action of the control variable, the valve seat 20 assumes a position displaced towards the service connection against the action of the service pressure and the spring 14, in which position the closure member 15 bears, with the sealing face 24 of the tubular portion 18, against the sealing face 23 of the valve seat 20 and so closes the connection betwen the service outlet and the return 12, and at the same time is lifted from the valve seat 13 as a result of which the service outlet 10 is connected to the pressure medium inlet 5. As soon as the effects of the service pressure and the control variable are balanced, the closure member 15 moves under the action of the spring 14, taking along the valve seat 20, into the closed position thus blocking the connection between the service outlet 10 and the pressure medium inlet 5. In the case of predominant action of the service pressure, (for example as a result of a reduction of the control variable acting on the valve seat 20, brought about by actuating the hand lever 32 in the direction of arrow A to advance the spring support 26 from the stop via the eccentric 31 and connecting rod 30 against the action of the spring 29) the valve seat 20 moves under the action of the service pressure against the action of the correspondingly relaxed pressure spring 27, the closure member 15 acted upon by the spring 14 being unable to follow beyond its closed position.As a result of the latter factor, the pressure medium inlet 5 is sealed off from the service outlet 10, and the service outlet 10 is connected via the transverse bore 21, the bore 3 and the housing bore 11 to the return 12 as a result of the valve seat 20 having been moved away from the sealing face 24 of the tubular portion 18. As soon as the service pressure is reduced to balance the action of the reduced control variable acting on the valve seat 20, the valve seat 20 moves under the action of the pressure spring 27 against the reduced action of the service pressure, and, with its sealing face 23 adjacent to the sealing face 24 of the tubular portion 18, takes up its closure position so closing the connection between the service outlet 10 and the return 12. In this manner it is possible to regulate as desired, continuously and with precision, the service pressure in the range of a predetermined maximum level to 0 bar, this being desired, for example, for hydraulic spring stores. The advantages that can be achieved with a regulating valve designed as described above are especially that the sliding arrangement of the valve seat 20 of one valve on the closure member 15 of the other valve and the arrangement of the sealing face 23 of the valve seat 20 in a conical region of a recess together with the sealing face 24 that can be formed along the outer edge of the tubular portion 18 of the closure member provides a regulator that can be operated with precision and in a hysteresis-free manner or with deliberate hysteresis when the outer edge sealing face 24 is correspondingly sloped.Also, the valve seat 20 is arranged in a simple manner directly on the tubular portion 18 of the closure member 15 and is acted upon, via a spring 27 and a thrust member 26, by the control variable against the action, effected over a maximum working surface, of the service pressure: as a result, a problem-free cooperation of the two valves of the regulator can be achieved, which is not susceptible to malfunction, together with a favourable construction which, with respect to its manufacture, is comparatively simple. Moreover, the arrangement of the blind bore in the valve seat 20, with the conicallytapered region, gives the advantage of being able to make the sealing faces 24 and 16 of the two valves of the regulator the same size - apart from installation tolerances. WHAT WE CLAIM IS:
1. A pressure level regulating valve
having a pressure medium inlet, a service pressure outlet and a pressure medium return, a first valve operable in dependence on the service pressure and in accordance with an applied control variable to block the service outlet from the inlet, and a second valve operable to connect the service outlet to the return when the inlet is closed, the second valve having a valve seat member slidably arranged on a tubular extension of a closure member of the first valve and displaceable by the said control variable, the valve seat member being exposed to the service pressure through a bore in the closure member and having a sealing face which is formed in a conical region of a recess in the valve seat member and is cooperable with an end face of the tubular extension.
2. A regulating valve according to claim 1, in which the outer edge of the said end face of the tubular extension is formed as a sealing face.
3. A regulating valve according to claim 2, in which the sealing face along the outer edge of the tubular extension is bevelled.
4. A regulating valve according to any one of the preceding claims, in which the closure member has a conical closure portion providing a sealing face for the first valve.
5. A regulating valve according to claim 4 when appendant to claim 2, in which the sealing face of the conical closure portion and the sealing face along the outer edge of the tubular extension are substantially of the same size.
6. A regulating valve according to any one of the preceding claims in which the valve seat member is displaceable by the control variable via a thrust member and a first resilient member.
7. A regulating valve according to any one of the preceding claims, in which, when the service outlet is connected to the inlet the valve seat member is displaceable by a second resilient member urging the closure member in the direction of closure of the first valve.
8. A pressure level regulating valve substantially as described herein with reference to, and as illustrated by the accompanying drawing. ~~ ~ ~ ~
GB22841/78A 1977-06-25 1978-05-25 Pressure level regulating valve Expired GB1602820A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2728751A DE2728751C2 (en) 1977-06-25 1977-06-25 Control valve for modulating a consumer pressure, in particular brake pressure

Publications (1)

Publication Number Publication Date
GB1602820A true GB1602820A (en) 1981-11-18

Family

ID=6012382

Family Applications (1)

Application Number Title Priority Date Filing Date
GB22841/78A Expired GB1602820A (en) 1977-06-25 1978-05-25 Pressure level regulating valve

Country Status (3)

Country Link
DE (1) DE2728751C2 (en)
FR (1) FR2395542A1 (en)
GB (1) GB1602820A (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1122197B (en) * 1960-08-26 1962-01-18 Basf Ag Lubricating oil additive
DE3038797A1 (en) * 1980-10-14 1982-05-27 Herion-Werke Kg, 7012 Fellbach PRESSURE CONTROL VALVE

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2852316A (en) * 1955-09-01 1958-09-16 Ernest G Staley Spring energized braking systems
FR1404337A (en) * 1964-08-19 1965-06-25 Daimler Benz Ag Brake valve for hydraulic brake actuation systems, in particular for motor vehicles
GB1264478A (en) * 1968-09-23 1972-02-23
DE6606141U (en) * 1968-09-30 1970-08-20 Knorr Bremse Gmbh HAND BRAKE VALVE FOR COMPRESSED AIR BRAKE SYSTEMS, IN PARTICULAR FOR BUSES
GB1320752A (en) * 1970-04-01 1973-06-20 Dewandre Co Ltd C Control valves for spring brake units
FR2133495B1 (en) * 1971-04-15 1975-01-17 Bendix Corp
DE2260799A1 (en) * 1972-12-13 1974-06-20 Daimler Benz Ag CONTROL VALVE FOR ACCUMULATOR SYSTEMS, IN PARTICULAR FOR ACCUMULATOR BRAKES IN MOTOR VEHICLES
GB1430478A (en) * 1973-04-19 1976-03-31 Dewandre Co Ltd C Brake control vavles
GB1420149A (en) * 1973-04-19 1976-01-07 Dewandre Co Ltd C Dual hydraulic brake valves

Also Published As

Publication number Publication date
FR2395542B1 (en) 1984-05-25
DE2728751B1 (en) 1978-10-05
DE2728751C2 (en) 1981-03-26
FR2395542A1 (en) 1979-01-19

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Legal Events

Date Code Title Description
PS Patent sealed [section 19, patents act 1949]
PCNP Patent ceased through non-payment of renewal fee