EP0815361B1 - Rohrbruchsicherungsventil - Google Patents
Rohrbruchsicherungsventil Download PDFInfo
- Publication number
- EP0815361B1 EP0815361B1 EP96902996A EP96902996A EP0815361B1 EP 0815361 B1 EP0815361 B1 EP 0815361B1 EP 96902996 A EP96902996 A EP 96902996A EP 96902996 A EP96902996 A EP 96902996A EP 0815361 B1 EP0815361 B1 EP 0815361B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- consumer
- piston
- chamber
- 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 - Lifetime
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- 239000012530 fluid Substances 0.000 claims description 12
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 230000036316 preload Effects 0.000 description 10
- 230000001419 dependent effect Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 125000006850 spacer group Chemical group 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000002996 emotional effect Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000001609 comparable effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
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 safety valve in particular a brake check valve according to the Preamble of claim 1.
- Valves of this type are used, for example, as counterbalance check valves to regulate the discharge current by an external
- loads of a consumer cylinder of a lifting cylinder used to lead the consumer ahead to prevent the feed flow.
- these valves take over at the same time these valves in the event that they are designed as seat pistons are, the function of a leak-free, shutting off the consumer controlled clamping in the respective position Check valve.
- a Brake check valve known which in a particular embodiment with a positive check valve is trained.
- This known brake / check valve has one first hollow valve piston with an inner valve seat, the by means of a valve plunger preloaded in the closed position is closable.
- the inner valve seat has a Valve piston provided first radial bore connection with a first pump-side valve pressure connection.
- One behind the second radial bore arranged over the valve seat an annular channel with a further valve seat of the check valve connected, which is a second consumer side Valve pressure connection blocks.
- the above Valve piston also has additional small diameters Radial holes immediately before the inner one Valve seat on and is in a spring Biased position in which a connection between the Ring channel and the small-diameter radial holes interrupted is.
- Hydraulic fluid flows from the first to lift a load Valve pressure connection through the valve piston, the inner valve seat, the ring channel, the valve seat of the check valve to the second valve pressure connection and becomes a consumer from there headed.
- the load should be in a certain position will be held when the pump pressure decreases the check valve is pressed onto the valve seat by a spring, whereby the hydraulic pressure at the second valve pressure connection and thus clamped in the consumer.
- valve piston In this embodiment and the piston of the check valve through the Pressure in a control pressure line against the respective preload springs moves, with a fluid connection between the second valve pressure connection via the now positively opened Check valve seat, the rink channel and the small-diameter radial bores and the first valve pressure connection is produced, which in this case has a external directional valve is connected to a tank.
- 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 can be positively opened by means of a control piston which can be actuated by control pressure.
- the brake / shut-off valve is connected in parallel to a check valve arranged in a pressure line leading to the consumer with its two connections, the spring space being permanently subjected to the load pressure.
- 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 downstream of the check valve in accordance with the force of the spring in the check valve, the valve piston being affected by both the piston spring and by the load pressure prevailing in the spring chamber is pressed onto the valve seat. If the load is to be held in one position, the external non-return 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. To lower the load, the control piston is actuated to open the internal pilot seat valve, which relaxes the pressure in the spring chamber.
- the valve piston When the actuating piston is actuated further, the valve piston is lifted off the valve seat and the consumer pressure is thus released into a tank. It has been shown that with this valve design, the varying level of pressure at the pump-side valve connection has an adverse 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.
- a brake / check valve preferably as a pipe rupture safety valve create which is a simpler and cheaper Has structure.
- Pipe rupture safety valve with the in claim 1 specified features solved.
- it has Pipe burst safety valve according to the invention, a servo valve, that at least two internal work connections and one Has valve piston, which by a bias spring in a first position separating the work connections is biased.
- the valve piston is with a formed first control edge, by means of which one of the Pressure connections can be closed.
- an annular collar provided which the biasing spring against the Seals pressure connections.
- Valve seat formed by a sleeve which in one in the Pipe rupture valve housing drilled Location hole is inserted. This construction enables quasi a complete and therefore inexpensive Pre-assemble the servo valve before putting it in the Pipe burst safety valve is used.
- the development according to claim 5 further provides that the pipe rupture safety valve, optionally with a pump or a tank connectable valve connection, as well as a Has consumer connection with a pressure supply channel an intermediate pressure / feed valve with each other are connected 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 channel routing within the Pipe burst safety valve but also its assembly, so that this also saves costs.
- the further measure is specified on a the biasing spring opposite side of the valve piston form a cavity by one on the valve piston Additional ring collar arranged in one piece against the working pressure leading consumer chamber is separated.
- the Cavity according to claim 10 preferably through the additional ring collar trained throttle point with the consumer chamber connected, wherein according to claim 11, the cavity Leakage line is connected via a channel in which the Pilot seat valve sits.
- the brake / check valve as a pipe rupture safety valve in its basic structure an integrated Servo valve 1 with at least two internal pressure connections 2, 3 and a valve piston 4, which by a Preload spring 5 in a first, the two pressure connections 2, 3rd separating position is biased.
- the valve piston 4 is for this with a provided as a cone section valve plate 6, the pressed on a valve seat 7 via the biasing spring 5 becomes.
- the valve piston 4 is at an axial distance to the cone section closing the first pressure connection 2 6 a seal, in this case in the form of an annular collar 8 provided that the biasing spring 5 relative to the seals two pressure connections 2, 3.
- a the bias spring 5 receiving and thus pressure-free spring chamber 9 is there via an additional leak oil line 10 with a separate one Tank connection L connected.
- the servo valve 1 is interposed in a return channel 11 formed in the brake / check valve, which connects a consumer-side valve connection V with a further valve connection A, which in turn can be optionally connected via an external directional valve, not shown a pump or a tank can be connected.
- 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 st .
- 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 therefore belongs to the state of the art.
- a measuring port M is also provided for a pressure sensor, which is connected directly to the port V or can be used as a connection for a compensating line in double cylinders.
- the measuring 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. 2.
- 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 thereby divided into two parts 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. As can be seen from FIG.
- this sleeve 17 is pressed against a shoulder in the valve housing bore by means of a bush 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 beginning, which is closed to the outside by an end wall of the bushing 18.
- the control pressure connection P st is designed 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.
- FIG. 2 In the left part of the bore according to FIG. 2 there is also one Sleeve 20 with an inner diameter equal to the right sleeve 17 screwed in and countered by a hollow screw 21, the left-hand bore part by means of an as Adjusting screw trained, screwed into the hollow screw Blind plug (not shown) opposite the Environment is closed.
- the valve piston 4 is through the Consumer chamber 15 into the left-hand sleeve 20 extended and is there within the sleeve 20 via a Valve piston 4 formed collar 22 slide-bearing, wherein a cavity 23 between the sleeve 20 Blind plug and the left-hand collar 22 forms.
- valve piston 4 furthermore also in the right sleeve 17 according to FIG. 2 plain bearing, here the support points on the one hand by the ring collar 8 serving as a seal and a further, ring collar 25 directly adjacent to the conical section 6 of the valve piston 4 are formed.
- This second, on the cone section 6 arranged collar 25 has on it Shell surface axial notches 26 which in the direction of Sealing ring collar 8 are open and as so-called fine control grooves serve.
- the position the drain hole 29 is selected such that in each position of the valve piston 4 a separation of the drain hole 29 from the return duct leading to valve connection A. 11 through the sealing collar 8 and at the same time one permanent connection of the drain hole 29 to the spring chamber 9 guaranteed is.
- valve piston extension 30 extended into the spring space 9 of the sleeve 18, the one on the right outer end of the extension into an annular collar Spring seat 31 is radially expanded, on which the Valve piston extension 30 arranged bias spring 5 on her supports one end.
- the other end of the spring 5 is on supported the right end of the sleeve 17 itself, whereby the valve piston 4 with respect to the sleeve 17 according to FIG. 2 biased to the right and thus the cone section 6 below Support of the one in the left-hand cavity 23 Pressure is pressed on the valve seat 7.
- the valve piston 4 and the extension 30 is provided with an inner axial through hole 32 provided which the left-hand side Cavity 23 connects to the spring chamber 9.
- this through hole 32 is at the left end portion of the valve piston extension 30, i.e. between valve piston 4 and extension 30 a pilot valve 33 in seat design with a closing element 34 arranged, supported by a spring by the pressure in the left-hand cavity 23, on an inner Valve seat is pressed and by means of the adjusting piston 19th via two in the through bore 32 of the valve piston extension 30 additionally stored spacer pins 35 in an open position is feasible.
- the valve seat of the pilot valve 33 is attached via a valve piston extension 30 Radial bore connected to the spring chamber 9.
- valve housing Location hole there is another one in FIG. 2 in the valve housing Location hole, not shown, for the commercially available combined Pressure / feed valve 13 formed, which from For the sake of clarity, only as a symbol is shown.
- the pilot operated pressure / feed valve 13 accordingly forms a to the consumer chamber 15 opening check valve, which on a Control side held in the closed position by a preload spring and through one introduced via valve port A. Pump pressure can be brought into the open position.
- a lifting cylinder for lifting a load When pressure is supplied to a consumer, not shown for example, a lifting cylinder for lifting a load Appropriate actuation of an upstream of the brake / check valve conventional directional valve (not shown) flows Hydraulic fluid through pressure port A, opens the check valve of the combined pressure / feed valve 13 against the force of the biasing spring and passes through the pressure supply channel 12 and the inner consumer chamber 15 of the brake / check valve to the consumer connection V, at which one is not shown consumer line is connected.
- the pump pressure simply reduced, which causes the check valve of the combined pressure feed valve 13 in the closed position emotional.
- the connection channel 24 acting as a throttle the consumer pressure built from de consumer chamber 15
- pressurizing area on the cone section 6 is substantially identical to the left-hand collar 22, so that each one on it mutually acting pressure forces from the consumer chamber 15 almost cancel.
- the actuating piston moves further to the left, it lays the right-hand end face of the valve piston 4 or extension 30 and moves the valve piston 4 against the now acting biasing force of the biasing spring 5.
- This causes the cone section 6 of its Valve seat 7 lifted off, so that in the consumer and thus in the pressure prevailing in the consumer chamber 15 via the return duct 11 to the valve connection A and from there to the not shown Tank can be relaxed.
- the maximum displacement of the valve piston 4 in the left-hand direction limits the blind plug designed as an adjusting screw becomes. Furthermore, the dosing of the flowing can Determine or adjust hydraulic fluids exactly because the force to move the valve piston 4 as described above Independently of consumer pressure, only proportional to the spring force of the biasing spring 9. This dosing accuracy is additionally determined by the arrangement of the Fine control grooves 26 improved, the greater displacement tolerance allow.
- the formation of the cavity 23 on the 2 left end of the valve piston 4 (on the valve piston side opposite the spring chamber) furthermore the guarantee of the functional maintenance of the Brake / check valve also in the event that the bias spring 5 of the valve piston 4 is broken.
- pilot seat valve 33 in this embodiment according to the invention at the left end portion of the valve piston 4 within the Consumer chamber 15, wherein for actuating valve 33 through the adjusting piston 18 a push rod 36 in the inner Through bore 32 of the valve piston 4 retracted and according Fig. 3 is spring biased to the right.
- the pilot seat valve 33 here consists of the biased on a valve seat Closing element 34, which by means of the push rod 36 an interposed spacer pin 37 in the opening direction is movable.
- the closing element 34 is stored in a outer sleeve 38 forming the valve seat, which in turn axially displaceably mounted in the valve piston 4 and immediately can be operated by the push rod 36.
- the sleeve 38 has an outer shoulder, which with a corresponding Heel in the through bore 32 of the valve piston 4 for an axial displacement limitation in the spring preload direction comes into engagement.
- the sleeve 38 by a bias spring of the closing element 34 over the valve seat against the shoulder in the through hole 32 pressed and can by an axial displacement the push rod 36 are lifted off.
- the valve piston 4 is in the area of the outer sleeve 38 provided with radial bores 39 which connect between the consumer chamber 15 and the inner through hole 32 of the valve piston 4.
- the closing element 34 of the pilot seat valve 33 in the closed position held in the connection between the left cavity 23 and the spring chamber 9 is interrupted.
- Closing element 34 acting bias also becomes the outer Sleeve 38 on the paragraph in the inner through hole 32 pressed, the radial bores 39 from the sleeve wall be closed.
- this annulus 40 lead a number of obliquely outwards extending holes 41, which in the inner through hole 32 of the valve piston 4 open and in closed State of the cone section 6 or the pilot seat valve 33 from the outer sleeve 38 of the pilot seat valve 33 as well be closed.
- This outer sleeve 38 has on its outer surface a recess 42 of a width according to the axial distance between the radial and oblique holes 39, 41 of the valve piston 4, but with the screwing 42 is arranged such that in the above closed position of the pilot seat valve 33 between the radial bores 39 and the oblique bores 41 there is no fluid connection.
- a control pressure is applied to the actuating piston 18 via the control pressure connection P st at a regulated pressure voltage, whereby 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 control valve 33 is first lifted from its valve seat, as a result of which 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 leakage 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.
- valve piston 4 no internal pilot seat valve, whereas the left-hand one Cavity 23 through the through hole 32 in the valve piston 4 permanently connected to the spring chamber on the right 9 Has.
- the reason for this is that the left side Cavity 23 is kept depressurized, the contact pressure between the cone section 6 and the valve seat 7 exclusively from the spring force of the biasing spring 5 of the Valve piston 4 determined.
- valve piston 4 points according to its Fig. 4 left end portion with a first collar 43 an outer spiral groove 44 in one in the valve housing fixed sleeve 45 is slidably mounted.
- This sleeve 45 is at its end facing away from the consumer chamber 15 closed by a hollow truncated cone 46, which by a sleeve 47 screwed into the valve housing in a fluid-tight manner is and which is penetrated by the valve piston 4.
- valve piston 4 If the valve piston 4 is used to open the valve seat 7 4 now moved to the left, the left side bumps first ring collar 43 already after a small displacement against the truncated cone 46 and lifts it off the left-hand sleeve 45. This can cause hydraulic fluid through the annular groove 44 on the lateral surface of the first ring collar 43 flow directly into the sleeve 47 surrounding the truncated cone 46, which increases the leakage slightly. Emotional meanwhile the valve piston 4 according to FIG the truncated cone 46 gradually comes to the right in the closed position again in contact with the left-hand sleeve 45 to complete this and thus reduce leakage losses again.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
Description
Beim Heben einer Last wird der stromauf des Rückschlagventils befindliche Druckanschluß von einem Pumpendruck beaufschlagt, der gegenüber dem in dem stromab des Rückschlagventils befindlichen Anschluß herrschenden Lastdruck entsprechend der Kraft der Feder im Rückschlagventil erhöht ist, wobei der Ventilkolben sowohl durch die Kolbenfeder, wie auch durch den im Federraum herrschenden Lastdruck auf den Ventilsitz gepreßt wird. Soll die Last in einer Position gehalten werden, schließt sich das externe Rückschlagventil, während der Ventilkolben des Brems-/Sperrventils weiterhin in Schließstellung gehalten und damit der pumpenseitige Ventilanschluß im wesentlichen drucklos wird. Für das Senken der Last wird der Stellkolben zum Öffnen des internen Vorsteuersitzventils betätigt, wodurch sich der Druck im Federraum entspannt. Bei weiterer Betätigung des Stellkolbens wird der Ventilkolben vom Ventilsitz abgehoben und damit der Verbraucherdruck in einen Tank entlassen.
Es hat sich gezeigt, daß sich bei dieser Ventilausführung die variierende Höhe des Drucks an dem pumpenseitigen Ventilanschluß nachteilig auf die Steuerung des Ventilkolbens auswirkt. Außerdem muß das Gehäuse des Brems-/Sperrventils insbesondere der Federraum massiv und besonders fluiddicht ausgebildet sein, da er permanent dem Lastdruck ausgesetzt ist und demnach diesem standhalten muß.
Claims (14)
- Rohrbruchsicherungsventil zur Absicherung eines hydraulischen Verbrauchers mit einem integrierten Servoventil (1), das zumindest zwei interne Arbeitsanschlüsse (2, 3), von denen ein erster (2) zu einem Verbraucheranschluß (V) offen ist, sowie einen Ventilkolben (4) hat, der durch eine Vorspannfeder (5) in eine die Arbeitsanschlüsse (2, 3) trennende Schließstellung vorgespannt ist und in dieser Schließstellung mit einem Ventilteller (6) auf einem Ventilsitz (7) aufsitzt, der in Richtung Schließstellung außerdem vom Verbraucherdruck beaufschlagbar ist, wobei der Verbraucherdruck in einem Steuerraum (23) ansteht, der über eine Drosselstelle (24) mit dem ersten Arbeitsanschluß (2) fluidisch verbunden und über einen axial durch den Ventilkolben (4) führenden Kanal (32) und über ein als Sitzventil ausgebildetes Vorsteuerventil (33) von Druck entlastbar ist, und wobei der Ventilkolben (4) für seine axiale Verschiebung in Öffnungsrichtung mit einem Stellkolben (19) in Eingriff bringbar ist, der zeitlich vor dem Ineingriffkommen mit dem Ventilkolben (4) das im Ventilkolben (4) angeordnete Vorsteuerventil (33) öffnet, um den Steuerraum (23) vom Verbraucherdruck zu entlasten,
dadurch gekennzeichnet, daß die Vorspannfeder (5) in einem dem Steuerraum (23) bezüglich des Ventilkolbens (4) gegenüberliegenden Federraum (9) untergebracht ist, der druckfrei ist, daß am Ventilkolben (4) in einem Axialabstand zu dem Ventilteller (6) ein Ringbund (8) ausgebildet ist, durch den ein zwischen ihm und dem Ventilteller befindlicher und zum zweiten Arbeitsanschluß (3) hin offener Ringraum gebildet ist und der (8) den Federraum (9) gegen den zweiten Arbeitsanschluß (3) abdichtet und als ein Gleitlager des Ventilkolbens (4) dient, und daß der Steuerraum (23) in den Federraum (9) hinein von Druck entlastbar ist. - Rohrbruchsicherungsventil nach Anspruch 1, dadurch gekennzeichnet, daß der Ventilsitz (7) durch eine Hülse (17) ausgebildet wird, die in eine in ein Gehäuse des Rohrbruchsicherungsventils gebohrte Aufnahmebohrung eingesetzt ist.
- Rohrbruchsicherungsventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß zwischen dem Ventilteller (6) und dem Gleitlager ein weiterer Ringbund (25) unmittelbar an den Ventilteller (6) angrenzend vorgesehen ist, der ebenfalls zur Gleitführung des Ventilkolbens (4) dient.
- Rohrbruchsicherungsventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Federraum (9) permanent mit einem Leckageanschluß (L) des Rohrbruchsicherungsventils Verbindung hat.
- Rohrbruchsicherungsventil nach einem der vorstehenden Ansprüche, gekennzeichnet durch
einen wahlweise mit einer Pumpe oder einem Tank verbindbaren Ventilanschluß (A), der mit dem Verbraucheranschluß (V) über einen Druckzuführkanal (12) mit einem zwischengeschalteten Druck-/Einspeiseventil (13) verbunden ist, zu dem ein Rückführkanal (11) parallelgeschaltet ist, in den das Servoventil (1) zwischengeschaltet ist. - Rohrbruchsicherungsventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Ventilkolben (4) auf einem dem Ventilteller (6) gegenüberliegenden Endabschnitt mit einem zusätzlichen Ringbund (22) versehen ist, dessen Außendurchmesser im wesentlichen dem des Ventiltellers (6) entspricht und der in der Aufnahmebohrung des Rohbruchsicherungsventilgehäuses gleitgelagert ist.
- Rohrbruchsicherungsventil nach Anspruch 6, gekennzeichnet durch eine Gleithülse (20), die zwischen dem zusätzlichen Ringbund (22) und dem Gehäuse angeordnet und in der Aufnahmebohrung im Ventilgehäuse fixiert ist.
- Rohrbruchsicherungsventil nach Anspruch 6 oder 7, dadurch gekennzeichnet, daß der Ventilkolben (4) eine einen Verbraucherdruck führende Verbraucherkammer (15) innerhalb des Rohrbruchsicherungsventils durchdringt, wobei eine Eintrittsstelle durch den Ventilteller (6) und eine Austrittsstelle durch den zusätzlichen Ringbund (22) verschließbar ist.
- Rohrbruchsicherungsventil nach Anspruch 8, dadurch gekennzeichnet, daß
innerhalb der Aufnahmebohrung auf einer der Vorspannfeder (5) gegenüberliegenden Seits des Ventilkolbens (4) ein Hohlraum ausgebildet ist, der vom zusätzlichen Ringbund (22) gegen die Verbraucherkammer (15) abgetrennt ist und den Steuerraum (23) bildet. - Rohrbruchsicherungsventil nach Anspruch 9, dadurch gekennzeichnet, daß die Drosselstelle durch den zusätzlichen Ringbund (22) ausgebildet und direkt mit der Verbraucherkammer (15) verbunden ist, in welche der erste Arbeitsanschluß (2) mündet.
- Rohrbruchsicherungsventil nach Anspruch 9 oder 10, dadurch gekennzeichnet, daß der Hohlraum (23) mit einer Leckageleitung (10) über den Kanal (32) verbunden ist, in dem das Vorsteuersitzventil (33) angeordnet ist.
- Rohrbruchsicherungsventil nach Anspruch 11 dadurch gekennzeichnet, daß der Ventilteller (6) durch einen Kegelstumpf gebildet wird, an dessen kleindurchmessriger Stirnseite der zylinderförmige Ringbund (25) anschließt, wobei der Ventilsitz (7) in seinem Durchmesser bezüglich dem Ringbund (25) radial aufgeweitet ist, sodaß zwischen dem Ventilteller (6), dem Ventilsitz (7) und dem Ringbund (25) in geschlossenem Zustand des Druckanschlusses (2) der abgeschlossene Ringraum (40) entsteht.
- Rohrbruchsicherungsventil nach einem der Ansprüche 11 und 12, dadurch gekennzeichnet, daß das Vorsteuersitzventil (33) einen durch ein Schließelement (34) verschließbaren Ventilsitz hat, der in einer in dem Kanal (32) axial verschiebbaren Hülse (38) ausgebildet ist.
- Rohrbruchsicherungsventil nach Anspruch 13, dadurch gekennzeichnet, daß die verschiebbare Hülse (38) durch den Stellkolben (18) über eine Druckstange (36) betätigbar ist und zeitlich nach dem Schließen des Ventilsitzes (7) durch den Ventilteller (6) einen Verbindungskanal (39, 41) zwischen der Verbraucherkammer (15) und dem Ringraum (40) sperrt.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19510586 | 1995-03-23 | ||
DE1995110586 DE19510586A1 (de) | 1995-03-23 | 1995-03-23 | Rohrbruchsicherungsventil |
PCT/EP1996/000755 WO1996029517A1 (de) | 1995-03-23 | 1996-02-23 | Rohrbruchsicherungsventil |
US08/935,736 US6027095A (en) | 1995-03-23 | 1997-09-23 | Pipe breakage safety valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0815361A1 EP0815361A1 (de) | 1998-01-07 |
EP0815361B1 true EP0815361B1 (de) | 2000-08-09 |
Family
ID=26013642
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96902996A Expired - Lifetime EP0815361B1 (de) | 1995-03-23 | 1996-02-23 | Rohrbruchsicherungsventil |
Country Status (5)
Country | Link |
---|---|
US (1) | US6027095A (de) |
EP (1) | EP0815361B1 (de) |
JP (1) | JPH11505592A (de) |
DE (1) | DE19510586A1 (de) |
WO (1) | WO1996029517A1 (de) |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19642567C1 (de) * | 1996-10-15 | 1997-08-21 | Brueninghaus Hydromatik Gmbh | Kombiniertes Hydraulikventil mit einer Schalt- und einer Druckminderfunktion |
DE102009038780B4 (de) | 2009-08-25 | 2011-12-01 | Airbus Operations Gmbh | Vorrichtung zur Rohrbruchsicherung |
CN102889261B (zh) * | 2012-10-15 | 2015-02-04 | 常德中联重科液压有限公司 | 平衡阀、液压缸伸缩控制回路以及液压设备 |
DE102015225927A1 (de) * | 2015-12-18 | 2017-06-22 | Robert Bosch Gmbh | Ventilkolben und Schieberventil mit einem Ventilkolben |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2187086A5 (de) * | 1972-05-31 | 1974-01-11 | Poclain Sa | |
DE2536106A1 (de) * | 1975-08-13 | 1977-02-24 | Hubert Odenthal | Lastabsicherungsventil |
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 (de) * | 1982-10-28 | 1984-05-10 | Mannesmann Rexroth GmbH, 8770 Lohr | Hydraulisch steuerbares sperrventil, insbesondere fuer die rohrbruchsicherung |
DE3319810C1 (de) * | 1983-06-01 | 1984-10-25 | Montan-Hydraulik GmbH, 4755 Holzwickede | Einrichtung zum Steuern von Hydroantrieben |
EP0197467B1 (de) * | 1985-04-11 | 1992-01-29 | Beringer-Hydraulik AG | Leckfreies Brems-Sperrventil |
DE4032420C2 (de) * | 1990-10-12 | 1994-04-14 | Wessel Hydraulik | Hydraulisches Sicherheitsventil |
US5381822A (en) * | 1993-11-26 | 1995-01-17 | Dana Corporation | Relief valve with hydraulic fuse |
-
1995
- 1995-03-23 DE DE1995110586 patent/DE19510586A1/de not_active Withdrawn
-
1996
- 1996-02-23 JP JP52801596A patent/JPH11505592A/ja not_active Ceased
- 1996-02-23 WO PCT/EP1996/000755 patent/WO1996029517A1/de active IP Right Grant
- 1996-02-23 EP EP96902996A patent/EP0815361B1/de not_active Expired - Lifetime
-
1997
- 1997-09-23 US US08/935,736 patent/US6027095A/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE19510586A1 (de) | 1996-09-26 |
EP0815361A1 (de) | 1998-01-07 |
WO1996029517A1 (de) | 1996-09-26 |
US6027095A (en) | 2000-02-22 |
JPH11505592A (ja) | 1999-05-21 |
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