EP0815361A1 - Pipe breakage safety valve - Google Patents
Pipe breakage safety valveInfo
- Publication number
- EP0815361A1 EP0815361A1 EP96902996A EP96902996A EP0815361A1 EP 0815361 A1 EP0815361 A1 EP 0815361A1 EP 96902996 A EP96902996 A EP 96902996A EP 96902996 A EP96902996 A EP 96902996A EP 0815361 A1 EP0815361 A1 EP 0815361A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- piston
- pipe rupture
- consumer
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
- F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86718—Dividing into parallel flow paths with recombining
- Y10T137/86759—Reciprocating
- Y10T137/86767—Spool
Definitions
- the present invention relates to a pipe rupture valve, in particular a brake check valve according to the preamble of patent claim 1.
- Valves of this type are used, for example, as counterbalance shut-off valves for regulating the outflow of a consumer, for example a lifting cylinder, which is loaded by external forces, in order to prevent the consumer from leading the supply stream.
- a lifting cylinder which is loaded by external forces
- these valves take on the function of a leak-free, controlled check valve which firmly clamps the consumer in the respective position.
- a brake check valve is known from the prior art according to DE-OS 32 39 930, which in a special embodiment is designed with a non-return valve that is forced to open.
- This known brake / shut-off valve has a first hollow valve piston with an inner valve seat, which can be closed by means of a valve tappet pretensioned in the closed position.
- the inner valve seat is connected to a first pump-side valve pressure connection via a first radial bore provided in the valve piston.
- a second radial bore arranged behind the valve seat is connected via an annular channel to a further valve seat of the check valve, which blocks a second consumer-side valve pressure connection.
- a pressure relief valve is integrated in the check valve.
- the valve piston mentioned above also has additional small-diameter radial bores directly in front of the inner valve seat and is biased by a spring into a position in which a connection between the ring channel and the small-diameter radial bores is interrupted.
- a hydraulic fluid flows from the first valve pressure connection through the valve piston, the inner valve seat, the annular channel, the valve seat of the check valve to the second valve pressure connection and is conducted from there to the consumer. If the load is to be held in a certain position, the check valve is pressed onto the valve seat by a spring when the pump pressure is reduced, as a result of which the hydraulic pressure is clamped at the second valve pressure connection and thus in the consumer.
- valve piston and the piston of the check valve are moved by the pressure in a control pressure line against the respective biasing springs, with a fluid connection between the second valve pressure connection via the now positively opened valve seat of the check valve, the rink channel as well as the small-diameter radial bores and the first valve pressure connection, which in this case is connected to a tank via an external directional valve.
- This valve has a hollow valve piston which is biased against a valve seat connecting two valve pressure connections by means of a spring which is located in a spring chamber.
- a spring which is located in a spring chamber.
- the valve piston there is also an internal pilot seat valve, which is actuated by means of a control pressure. can be positively opened.
- the brake / shut-off valve is connected in parallel to a non-return valve arranged in a pressure line leading to the consumer with its two connections, the spring pressure being permanently applied to the Federau.
- the pressure connection located upstream of the check valve is acted upon by a pump pressure which is increased in relation to the load pressure prevailing in the connection downstream of the check valve in accordance with the force of the spring in the check valve, the valve piston being actuated both by the piston spring, as is pressed onto the valve seat by the load pressure prevailing in the spring chamber.
- the external check valve closes, while the valve piston of the brake / shut-off valve continues to be held in the closed position and the pump-side valve connection is essentially depressurized.
- the actuating ⁇ is actuated piston for opening the internal pilot seat valve, whereby the pressure is released in the spring chamber.
- the valve piston from the valve seat ⁇ is lifted and released the consumer pressure in a tank.
- the varying level of pressure at the pump-side valve connection has a disadvantageous effect on the control of the valve piston.
- the housing of the brake / check valve, in particular the spring chamber must be solid and particularly fluid-tight, since it is permanently exposed to the load pressure and must therefore withstand it.
- the pipe rupture protection valve has a servo valve which has at least two internal pressure connections and a valve piston which is prestressed by a prestressing spring into a first position which separates the pressure connections.
- the valve piston is designed with a first control edge, by means of which one of the pressure connections can be closed.
- a second control edge is provided at an axial distance from the first control edge, which seals the biasing spring against the pressure connections.
- the first control edge is formed by a valve plate which can be brought into contact with a valve seat forming a pressure connection by the spring prestressing force.
- the valve seat is formed by a sleeve which is inserted into a receiving bore drilled in the housing of the pipe rupture safety valve. This design enables the servo valve to be preassembled completely and therefore cost-effectively before it is inserted into the pipe rupture protection valve.
- the second control edge is formed by an annular collar formed on the valve piston, which serves as a sliding bearing, with a further annular collar between the first and the second control edge is provided directly adjacent to the first control edge and also serves to slide the valve piston.
- the second control edge which is formed in one piece on the valve piston, is assigned two functions, which simplifies the overall structure of the control piston.
- the pipe rupture safety valve has a valve connection which can be optionally connected to a pump or a tank, and a consumer connection which are connected to one another via a pressure supply channel with an intermediate pressure / feed valve to which a return channel is connected in parallel, in which the servo valve is interposed.
- the integral arrangement of the combined pressure / feed valve not only simplifies the duct routing within the pipe rupture safety valve but also its assembly, so that this also saves costs.
- the further measure is given to form a cavity on a side of the valve piston opposite the biasing spring, which cavity is separated from an annular collar arranged in one piece on the valve piston against a consumer chamber carrying the working pressure.
- the cavity is connected to the consumer chamber via a throttle point, preferably formed by the annular collar, wherein according to claim 12 the cavity is connected to a leakage line via a channel in which a pilot seat valve is located.
- the channel within the valve piston is designed as an axially extending through-bore, the valve piston for its axial displacement being engageable with an actuating piston which, prior to engagement, places the pilot seat valve arranged in the valve piston in an open position brings to relieve the pressure within the cavity in the leakage line.
- FIG. 1 shows the circuit diagram of a brake / check valve as a pipe rupture safety valve according to the invention
- FIG. 2 shows a first constructive embodiment of a brake / blocking valve according to the invention in a position which pressurizes the consumer, the valve piston being pressed onto its valve seat by a biasing spring as well as by the load pressure,
- FIG. 3 shows an alternative embodiment of the embodiment according to FIG. 1 in the same position
- Fig. 4 shows a second constructive embodiment of the invention in a position pressurizing the consumer, the valve piston being pressed onto the valve seat solely by the biasing spring.
- the basic design of the brake / shut-off valve as a pipe rupture safety valve has an integrated servo valve 1 with at least two internal pressure connections 2, 3 and a valve piston 4, which by means of a prestressing spring 5 into a first one two pressure connections 2, 3 separating position is biased.
- the valve piston 4 is provided for this purpose with a valve disc 6 designed as a conical section, which is pressed onto a valve seat 7 via the biasing spring 5.
- a seal in this case in the form of an annular collar 8, is provided on the valve piston 4 at an axial distance from the conical section 6 closing the first pressure connection 2, which seals the biasing spring 5 with respect to the two pressure connections 2, 3.
- a spring chamber 9 which receives the biasing spring 5 and is therefore pressure-free is connected to a separate tank connection L via an additional leak oil line 10.
- the servo valve 1 is interposed in a return channel 11 formed in the brake / blocking valve, which connects a valve connection V on the consumer side to a further valve connection A, which in turn An external, not shown directional control valve can optionally be connected to a pump or a tank.
- the servo valve 1 is designed for actuation by means of a control pressure which can be applied to the brake / shut-off valve via an external control connection P s _.
- a servo valve 1 in particular bypassing or bridging its pressure connection 2, is also formed, in which, according to the invention, a combined, pilot-controlled pressure / feed valve 13 is interposed, as described, for example, by the applicant under the Designation "MHDBN 22K" is distributed and thus belongs to the prior art.
- a measuring Termination M is provided for a pressure sensor which is connected directly to the connection V or can be used as a connection for a compensation line in double cylinders.
- FIG. 2 With regard to the structural design of the brake / blocking valve according to the invention, in particular its servo valve 1 according to a first exemplary embodiment, reference is now made to FIG. 2.
- the measurement connection M is connected via a first channel 14 to a consumer chamber 15 formed in a valve housing, from which a bore 16 leads to the consumer connection V according to FIG.
- the consumer chamber 15 or the bore 16 is penetrated essentially at right angles by a further valve housing bore for receiving the servo valve 1, which runs through the entire valve housing and is quasi divided into two by the consumer chamber 15.
- a sleeve 17 is fitted in a fluid-tight manner in the right-hand part of the bore according to FIG. 2, which serves for the sliding bearing of the valve piston 4 and which forms the valve seat 7 at its end opening into the consumer chamber 15.
- this sleeve 17 is pressed against a shoulder in the valve housing bore by means of a bushing 18 screwed into the valve housing with an inner bore diameter larger than the sleeve 17, as a result of which the sleeve 17 is axially fixed .
- the bushing 18 forms the spring chamber 9 mentioned at the outset, which is closed off from the outside by an end wall of the bushing 18.
- the control pressure connection P st is formed for a control pressure line, via which an actuating piston 19, which is mounted in the bushing 18, can be actuated via the control pressure.
- a sleeve 20 with an inside diameter equal to that of the right sleeve 17 is also screwed into the left-hand bore part according to FIG. 2 and is countered by a hollow screw 21, the left-hand bore part being inserted into the hollow screw by means of an adjusting screw.
- turned blind plug (not shown) is sealed from the environment.
- the valve piston 4 is extended through the consumer chamber 15 into the left-hand sleeve 20 and is slidably supported within the sleeve 20 via an annular collar 22 formed on the valve piston 4, a cavity 23 being formed between the blind plug and the left-hand annular collar 22 within the sleeve 20 .
- a connecting channel 24 provided with a throttle function is spirally screwed in on the lateral surface of the annular collar 22, which ensures that the pressure currently prevailing in the consumer chamber 15 gradually builds up in the cavity 23 via the connecting channel 24 and thus the valve tilkolben 4 and thus the opposite cone section 6 presses against the valve seat 7.
- valve piston 4 is also slidably supported in the right sleeve 17 according to FIG. 2, the support points here being due to the annular collar 8 serving as a seal and another annular collar 25 of the valve piston directly adjoining the cone section 6 4 are formed.
- This second annular collar 25 arranged on the conical section 6 has axial notches 26 on its outer surface, which are open in the direction of the sealing annular collar 8 and serve as so-called fine control grooves.
- the sleeve 17 is provided with a plurality of radial bores 27, which lie in a circular plane and can be separated by the conical section 6 from the consumer chamber 15, and which open into an outer annular channel 28 screwed into the sleeve 17, which is connected to the Valve connection A leading, schematically shown return channel 11 is fluid-connected.
- a further radial drain hole 29 is provided in the sleeve 17, which leads into the leak oil line 10 and thus the spring chamber 9 connects the leak oil line 10 and the leak oil connection L.
- the position of the drain hole 29 is selected such that in each position of the valve piston 4, a separation of the drain bore 29 from the return channel 11 leading to the valve port A through the sealing ring collar 8 and at the same time a permanent connection of the drain bore 29 to the spring chamber 9 is ensured.
- the right end portion of the valve piston 4 according to FIG. 2 is extended by an extension 30 axially screwed or screwed into the valve piston into the spring chamber 9 of the sleeve 18, which is radially expanded at the right outer extension end to form an annular spring seat 31 on which the biasing spring 5 arranged around the valve piston extension 30 is supported at one end.
- the other end of the spring 5 is supported on the right end face of the sleeve 17 itself, whereby the valve piston 4 is biased to the right with respect to the sleeve 17 according to FIG. 2 and thus the conical section 6 prevail with the support of the cavity 23 in the left-hand side the pressure on the valve seat 7 is pressed.
- the valve piston 4 and the extension 30 are provided with an inner, axial through bore 32 which connects the left-hand cavity 23 with the spring chamber 9.
- This through bore 23 is at the left end portion of the valve piston extension 30, i.e.
- a pilot valve 33 in seat construction with a closing element 34 is arranged, which is pressed by means of a spring, supported by the pressure in the left-hand cavity 23, onto an inner valve seat and by means of the actuating piston 19 via two in the Through hole 32 of the valve piston extension 30 additionally supported spacer pins 35 can be brought into an open position.
- the valve seat of the pilot valve 33 is connected to the spring chamber 9 via a radial bore in the valve piston extension 30.
- a further receiving bore (not shown in FIG. 2) for the commercially available combined pressure / feed valve 13 is formed in the valve housing For reasons of better comprehensibility, it is only shown as a switching symbol.
- the pilot-controlled pressure / feed valve 13 is interposed in the pressure feed channel 12, which branches off between the return port 11 between the valve connection A and the servo valve 1 and bypasses the pressure port 2 of the servo valve 1 opens into the consumer chamber 15.
- the pilot-controlled pressure / feed valve 13 accordingly forms a check valve opening towards the consumer chamber 15, which is held in the closed position on a control side by a biasing spring and can be brought into the open position by a pump pressure introduced via the valve connection A.
- this check valve is combined with a pilot-controlled pressure limiting valve which is controlled by the pressure in the consumer chamber via an internal control line and which releases the pressure in the consumer chamber 15 into the return line 11 when a predetermined limit value is exceeded.
- hydraulic fluid flows through the pressure connection A and opens the check valve of the combined pressure / Einspeisungsventil ⁇ 13 against the force of the biasing spring and passes through the Druck ⁇ supply channel 12 and the inner consumer chamber 15 of the brake / lock valve to the consumer port V, to which a consumer line, not shown, is connected.
- the conical section 6 of the valve piston 4 is firmly seated by the biasing force of its biasing spring 5 its valve seat 7, the ring collar 8 acting as a seal on the valve piston 4 separating the spring chamber 9 from the return channel 11, which is now also under pump pressure, so that no hydraulic fluid can escape through the spring chamber 9 and the subsequent leakage oil connection L.
- the pump pressure is simply reduced, as a result of which the check valve of the combined pressure feed valve 13 moves into the closed position.
- the consumer pressure from the consumer chamber 15 has built up in the left-hand cavity 23 according to FIG. 2 via the connecting channel 24 acting as a throttle, this now due to the pressure drop at the valve connection A and thus in the return channel 11 acts on the valve piston 4 and, owing to the force imbalance now prevailing, presses its cone section 6 onto its valve seat 7 in addition to the spring force. In this way it is ensured that the consumer remains in its position without oil leakage.
- the pressure / feed valve which now functions as a pilot-operated pressure relief valve opens 13 to release a certain amount of hydraulic fluid from the consumer chamber 15 into the now depressurized return duct 11. If the hydraulic pressure in the consumer is now to be reduced, for example for lowering a load, a control pressure is applied via the control pressure connection P s _ in the bush 18 arranged on the right-hand side according to FIG.
- the pressurizing surface on the cone section 6 is essentially identical to the ring collar 22 on the left side, so that the compressive forces acting thereon from the consumer chamber 15 virtually cancel each other out.
- the actuating piston now moves further to the left, it rests on the right-hand end face of the valve piston 4 or the extension 30 and displaces the valve piston 4 against the bias force of the biasing spring 5, which now acts alone.
- the cone section 6 is removed from its valve seat 7 lifted off, so that the pressure prevailing in the consumer and thus in the consumer chamber 15 can be released via the return duct 11 to the valve connection A and from there to the tank, not shown.
- the maximum displacement path of the valve piston 4 in the left-hand direction is limited by the blind plug designed as an adjusting screw. Furthermore, the dosage of the flowing hydraulic fluid can be exactly determined or set, since the force for displacing the valve piston 4 according to the above description, independent of the consumer pressure, is exclusively proportional to the spring force of the biasing spring 9. This metering accuracy is additionally improved by the arrangement of the fine control grooves 26, which allow a greater displacement tolerance.
- the formation of the cavity 23 on the left-hand end of the valve piston 4 according to FIG. 2 (on the valve piston side opposite the spring chamber) also offers the guarantee of the functional maintenance of the brake / blocking valve also in the event that the biasing spring 5 of the valve piston 4 is broken.
- the closing element 34 of the pilot control valve 33 arranged in the valve piston 4 is closed due to the biasing force of the seat valve internal biasing spring, whereby a pressure correspondingly gradually increases in the cavity 23 in question builds up the pressure in the consumer chamber 15.
- This pressure acts on the left-hand end face of the valve piston 4 and shifts it in the rightward direction due to the still existing force imbalance at the cone section 6.
- the cone section 6 can be brought back into the closed position and thus the connection of the consumer connection V to the valve connection A can be interrupted.
- the valve piston extension 30, because it is not loaded with a hydraulic pressure can be manufactured from a material that is less resilient and therefore less expensive.
- the pressure / feed valve 13 could be arranged externally or replaced by a separate check valve in connection with a pressure limiting valve.
- the collar 22 could simply have a larger play in the sleeve 20 are used, whereby a gap with a comparable effect would form between the two components. Similar change options are also available in the exemplary embodiments described below, so that this will not be discussed in more detail below.
- the inner pilot seat valve 33 in this embodiment according to the invention is located on the left end section of the valve piston 4 within the consumer chamber 15, with a push rod 36 in the inner through-bore for actuating the valve 33 by the adjusting piston 18 32 of the valve piston 4 is retracted and spring-biased to the right according to FIG. 3.
- the pilot seat valve 33 in this case consists of the closing element 34, which is preloaded on a valve seat and can be displaced in the opening direction by the push rod 36 via an interposed spacer pin 37.
- the closing element 34 is supported in an outer sleeve 38 forming the valve seat, which is in turn axially displaceably mounted in the valve piston 4 and can be actuated directly by the push rod 36.
- the sleeve 38 has an outer shoulder, which comes into engagement with a corresponding shoulder in the through bore 32 of the valve piston 4 for an axial displacement limitation in the spring preload direction.
- the sleeve 38 is pressed by a prestressing spring of the closing element 34 via the valve seat against the shoulder in the through bore 32 and can be lifted off the latter by an axial displacement of the push rod 36.
- the valve piston 4 is provided with radial bores 39 which connect between see the consumer chamber 15 and the inner through bore 32 of the valve piston 4.
- the closing element 34 of the pilot seat valve 33 is also held in the closed position, in which the connection between the left cavity 23 and the spring chamber 9 is interrupted.
- the outer sleeve 38 is also applied to the shoulder in the inner through bore
- valve seat 7 of the cone section 6, i.e. the inside diameter of the three ring bundles 8, 22, 25, which each have the same inside diameters of the right and left sleeves 17, 20 for mounting the valve piston 4, are radially expanded by a large-diameter boring, with the Valve seats 7 form an annular space 40 between the cone section 6 and the right sleeve 25 supporting the valve piston 4.
- annular space 40 lead a number of obliquely outwardly extending bores 41, which open into the inner through bore 32 of the valve piston 4 and in the closed state of the cone section 6 or the pilot seat valve
- This outer sleeve 38 has on its outer surface a recess 42 of a width corresponding to the axial spacing of the radial and oblique bores 39, 41 of the valve piston 4, however the recess 42 is arranged such that in closed position of the pilot seat valve 33 between the radial bores 39 and the oblique bores 41 there is no fluid connection.
- the functions for pressurizing and clamping a consumer essentially correspond to those of the first Embodiment of FIG. 2, so that a new description is omitted at this point.
- a control pressure is applied to the actuating piston 18 via the control pressure connection P st, as a result of which the push rod 36 within the valve piston 4 according to FIG. 3 is shifted to the left.
- the closing element 34 of the pilot seat valve 33 is first lifted off its valve seat, whereby the hydraulic pressure in the left-hand cavity 23 is released via the valve seat, the inner through bore 32 of the valve piston 4 and the spring chamber 9 into the leak oil line 10.
- the relevant pressure application area of the cone section 6 pointing towards the consumer chamber 15 is also larger than the corresponding contact area of the left-hand annular collar 22 formed on the valve piston 4, so that a resulting residual pressure force is dependent on the consumer pressure the cone section 6 acts in the closing direction.
- FIG. 4 A further exemplary embodiment of the invention is shown in FIG. 4, only the differences existing from the first exemplary embodiment being described in more detail below.
- the valve piston 4 has no internal pilot seat valve, whereas the left-hand cavity 23 has an anet connection with the right-hand spring chamber 9 via the through bore 32 in the valve piston 4.
- the reason for this is that the left-hand cavity 23 is kept depressurized, the contact pressure between the conical section 6 and the valve seat 7 being determined exclusively from the spring force of the biasing spring 5 of the valve piston 4.
- valve piston 4 has a first annular collar 43 with an outer spiral groove 44 on its left end section according to FIG. 4, which is slidingly supported in a sleeve 45 fixed in the valve housing.
- This sleeve 45 is closed at its end facing away from the consumer chamber 15 by a hollow truncated cone 46 which is fluid-tightly enclosed by a bushing 47 screwed into the valve housing and which is penetrated by the valve piston 4.
- a shaft nut 48 is screwed on, which fixes a shaft ring 49, which is mounted in the truncated cone 46 and sealed against it by means of a seal 56, on a corresponding shoulder 50 on the valve piston 4, the shaft ring 49 serving as a support for the truncated cone 46 against the Sleeve 45 biasing spring 51 is used.
- An annular space 52 formed between the truncated cone 46 and the valve piston 4 for receiving the biasing spring 51 is separated from the consumer chamber 15 by a second annular collar 53 of the valve piston 4, which is connected downstream of the first annular collar 43 mentioned above and which is located in the hollow cone butt 46 with sliding bearings and a spiral connecting groove 54 on its outer surface.
- valve piston 4 If the valve piston 4 is now shifted to the left to open the valve seat 7 as shown in FIG. 4, the left-hand first annular collar 43 abuts after only a slight sliding against the truncated cone 46 and lifts it from the left-hand sleeve 45. As a result, hydraulic fluid can flow through the annular groove 44 on the lateral surface of the first annular collar 43 directly into the sleeve 47 surrounding the truncated cone 46, as a result of which the leakage is increased slightly. 4 moves to the right again in the closed position, the truncated cone 46 gradually comes back into contact with the left-hand sleeve 45 in order to close it off and thus reduce the leakage losses again.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE1995110586 DE19510586A1 (en) | 1995-03-23 | 1995-03-23 | Pipe rupture valve |
DE19510586 | 1995-03-23 | ||
PCT/EP1996/000755 WO1996029517A1 (en) | 1995-03-23 | 1996-02-23 | Pipe breakage safety valve |
US08/935,736 US6027095A (en) | 1995-03-23 | 1997-09-23 | Pipe breakage safety valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0815361A1 true EP0815361A1 (en) | 1998-01-07 |
EP0815361B1 EP0815361B1 (en) | 2000-08-09 |
Family
ID=26013642
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96902996A Expired - Lifetime EP0815361B1 (en) | 1995-03-23 | 1996-02-23 | Pipe breakage safety valve |
Country Status (5)
Country | Link |
---|---|
US (1) | US6027095A (en) |
EP (1) | EP0815361B1 (en) |
JP (1) | JPH11505592A (en) |
DE (1) | DE19510586A1 (en) |
WO (1) | WO1996029517A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19642567C1 (en) * | 1996-10-15 | 1997-08-21 | Brueninghaus Hydromatik Gmbh | Combined hydraulic valve with switching and pressure reduction functions e.g. for holding brake |
DE102009038780B4 (en) | 2009-08-25 | 2011-12-01 | Airbus Operations Gmbh | Device for pipe burst protection |
CN102889261B (en) * | 2012-10-15 | 2015-02-04 | 常德中联重科液压有限公司 | Balancing valve, hydraulic cylinder telescoping control loop and hydraulic device |
DE102015225927A1 (en) * | 2015-12-18 | 2017-06-22 | Robert Bosch Gmbh | Valve piston and gate valve with a valve piston |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2187086A5 (en) * | 1972-05-31 | 1974-01-11 | Poclain Sa | |
DE2536106A1 (en) * | 1975-08-13 | 1977-02-24 | Hubert Odenthal | Safety valve for holding hydraulic motor under load - is biased into closed position by motor outlet pressure |
US4187870A (en) * | 1977-05-06 | 1980-02-12 | Baker International Corporation | Valve actuator and pilot assembly therefor |
GB2091383B (en) * | 1979-11-09 | 1985-07-24 | Bennes Marrel | Braking valve |
DE3239930A1 (en) * | 1982-10-28 | 1984-05-10 | Mannesmann Rexroth GmbH, 8770 Lohr | Hydraulically controllable shut-off valve, especially for securing a pipe fracture |
DE3319810C1 (en) * | 1983-06-01 | 1984-10-25 | Montan-Hydraulik GmbH, 4755 Holzwickede | Device for controlling hydraulic drives |
DE3683666D1 (en) * | 1985-04-11 | 1992-03-12 | Beringer Hydraulik Gmbh | LEAK-FREE BRAKE LOCK VALVE. |
DE4032420C2 (en) * | 1990-10-12 | 1994-04-14 | Wessel Hydraulik | Hydraulic safety valve |
US5381822A (en) * | 1993-11-26 | 1995-01-17 | Dana Corporation | Relief valve with hydraulic fuse |
-
1995
- 1995-03-23 DE DE1995110586 patent/DE19510586A1/en not_active Withdrawn
-
1996
- 1996-02-23 JP JP52801596A patent/JPH11505592A/en not_active Ceased
- 1996-02-23 WO PCT/EP1996/000755 patent/WO1996029517A1/en active IP Right Grant
- 1996-02-23 EP EP96902996A patent/EP0815361B1/en not_active Expired - Lifetime
-
1997
- 1997-09-23 US US08/935,736 patent/US6027095A/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO9629517A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP0815361B1 (en) | 2000-08-09 |
WO1996029517A1 (en) | 1996-09-26 |
DE19510586A1 (en) | 1996-09-26 |
US6027095A (en) | 2000-02-22 |
JPH11505592A (en) | 1999-05-21 |
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