EP0565552B1 - Vanne de charge a accumulation exempte d'huile de fuite - Google Patents

Vanne de charge a accumulation exempte d'huile de fuite Download PDF

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Publication number
EP0565552B1
EP0565552B1 EP92901393A EP92901393A EP0565552B1 EP 0565552 B1 EP0565552 B1 EP 0565552B1 EP 92901393 A EP92901393 A EP 92901393A EP 92901393 A EP92901393 A EP 92901393A EP 0565552 B1 EP0565552 B1 EP 0565552B1
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EP
European Patent Office
Prior art keywords
connection
control
valve
piston
inlet
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
Application number
EP92901393A
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German (de)
English (en)
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EP0565552A1 (fr
Inventor
Rüdiger JUNG
Harald BÄR
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Flutec Fluidtechnische Geraete GmbH
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Flutec Fluidtechnische Geraete GmbH
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Publication of EP0565552A1 publication Critical patent/EP0565552A1/fr
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Anticipated expiration legal-status Critical
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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/0275—Installations or systems with accumulators having accumulator charging devices with two or more pilot valves, e.g. for independent setting of the cut-in and cut-out pressures
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2622—Bypass or relief valve responsive to pressure downstream of outlet valve
    • Y10T137/2625—Pilot valve

Definitions

  • the invention relates to an accumulator charging valve which is provided with a control piston for connecting an inlet feeding a hydraulic system to an outlet when an adjustable upper boost pressure is reached in the hydraulic system and for disconnecting this connection when an adjustable lower boost pressure is reached in the hydraulic system two switching positions separates the connection between inlet and outlet and in the other switching position establishes this connection, whereby a control connection connecting the hydraulic system with the accumulator charging valve is separated from the outlet by means of a separating device and a first and a second pilot valve are provided for setting the lower and the upper boost pressure is.
  • Accumulating store loading valves which are also referred to as shutdown valves, are usually used in Hydraulic systems or hydraulic circuits are used which have at least one hydraulic accumulator for keeping the pressure in the hydraulic system constant.
  • the respective hydraulic accumulator works in a range between a lower and an upper boost pressure, the respective pressure level of which can be adjusted, and is therefore freely selectable. If the charge pressure falls below or exceeds the lower or the upper charge pressure, the connection to the inlet ensuring the pressure oil supply is established or separated by means of the accumulator charge valve.
  • the adjustable difference between the lower and the upper boost pressure can be large but can also take very small values.
  • a storage charging valve of the same type has already been described in DE-PS 36 08 100.
  • this known accumulator charging valve has a control piston, the one piston part being designed as a separating device in each ingestible switching position of the control piston separating the connection between the control connection and the outlet which opens into the tank. Leakage occurs between the control connection and the outlet leading to the tank via an annular gap formed by this piston part. This reduces the boost pressure in the accumulator, which has the disadvantages described in DE-PS 36 08 100.
  • a non-generic embodiment of a hydraulic accumulator charging valve which has a main piston and a pilot control supplied with pressure medium from the inlet via a throttle point, with a pilot valve designed as a seat valve, which, after opening when the shutdown is reached, is released by an unlocking piston is held in the open position and so brings about the switch-off position of the main piston and this until it is reached of a lower cut-in pressure. Thanks to this training, there is no longer any loss of control oil, at least when the process is stressed.
  • the invention has for its object to provide a accumulator charging valve with freely adjustable switching points, which works with such a leak-free oil that the pressure in the hydraulic accumulator is kept constant even over a longer period of time.
  • the separating device has a closing piston with a closing surface which, when the adjustable upper boost pressure is reached, for leak-free closure of the connection between the control connection and the outlet forming a leak, a sealing seat with a forms a fixed seat, which is arranged in a travel space of the closing piston, there is no backflow of pressure oil from the "loaded" respective hydraulic accumulator, especially during the downtime of the hydraulic system, to the tank.
  • the accumulator charging valve according to the invention also fulfills all requirements for safe operation of the connected hydraulic system.
  • the separating device is formed from the first pilot valve and the shut-off valve located between the inlet and the control connection, which, when the adjustable upper boost pressure is reached, forms the leakage connection between the control connection and seal the drain tightly.
  • control piston which interacts with the closing piston, forms a pressure compensator with the latter. This enables safe switching of the accumulator charging valve, regardless of the prevailing volume flows and viscosities.
  • the closing piston with its active surface facing and facing away from the control piston can be exposed to the pressure prevailing in the inlet or in the control connection and has on its active surface facing the control piston the closing part which can be brought into contact with the fixed one Part that is arranged between the inlet and the control connection in the travel space of the closing piston.
  • This provides a defined sealing point, by means of which a leak-oil-free seal between the control connection and the drain is ensured when the adjustable upper boost pressure is reached.
  • at least the control piston can be completely decoupled from the actual storage circuit of the hydraulic system.
  • the separating device with its respective sealing part is formed from the first pilot valve and the shut-off valve located between the inlet and the control connection.
  • this type of accumulator charging valve has a passage on the control piston which opens into the control chamber and which can be connected to a drain line, it can be reached, in particular when the system is at a standstill or from parts of the system to always charge the respective hydraulic accumulator to the upper boost pressure when it is put back into operation, even if the actually prevailing accumulator pressure is greater than the predeterminable lower boost pressure.
  • a defined charge state is always produced in the hydraulic accumulator, which corresponds to the upper charge pressure, so that the full accumulator capacity is then available for the hydraulic system.
  • the memory charging valve according to the invention is explained in more detail below with reference to two exemplary embodiments according to FIGS. 1 and 2.
  • the first embodiment of the accumulator charging valve according to the invention according to FIG. 1 is connected via the control connection B to a hydraulic system 10, of which only the hydraulic accumulator 12 is shown schematically in FIG. 1 and the feed line that leads away from the branch point 14 is shown schematically.
  • control connection B which partly leads into the valve body 16 of the accumulator charging valve, it also has an outlet T, which leads to a tank, and an inlet P, which is more common to a hydraulic pump 18 that can be driven by a motor M and therefore not described in detail Type is connected.
  • pilot valves 22 and 24 are placed on the valve body 16, the pilot valve 22 performing a pressure closing function and the pilot valve 24 performing a pressure limiting function. With these two pilot valves 22 and 24, the lower or upper boost pressure or switching point in the hydraulic system 10 can therefore be set. The respective setting is done via an adjustable control spring 26, which is guided in the valve body of the respective pilot valve 22, 24.
  • the structure and the mode of operation of such pilot valves 22, 24 are generally known to those skilled in the art and are therefore not described again in detail.
  • the rear valve spaces 28 and 30 of the two pilot valves 22 and 24 are connected to one another via a transverse bore 32.
  • a leakage oil line L shown broken off, branches off from this transverse bore 32 and opens into a leakage oil collection point.
  • This leakage oil line L has at least at the end in the area of the leakage oil collection point essentially the atmospheric pressure, which facilitates the drainage of the leakage oil.
  • the leak oil line L can also be connected to the outlet T, which opens into the tank and which can accordingly have a higher pressure than the atmospheric pressure.
  • the two front valve spaces 34 and 36 of the two pilot valves 22 and 24 also communicate with one another via a cross connection 38 in the form of a bore.
  • a control piston 42 is arranged in a longitudinally displaceable manner in a piston chamber 40 extending transversely in the valve body 16.
  • the inlet P and the outlet T open into this piston chamber 40.
  • the interior of the control piston 42 together with the wall of the piston chamber 40, encloses a control chamber 44, in which a piston spring 46 is arranged, which cooperates with a valve ball 48 and is designated as a whole by 50 Check valve forms.
  • the check valve 50 when actuated by the pressure in the inlet P, serves to establish a connection between the inlet P and the control chamber 44, which has a branch 52 at the end, which opens into the front valve chamber 36 of the second pilot valve 24.
  • the piston chamber 40 is closed at its open-ended end by means of a hexagon screw 54 and opens with its other opposite end into a travel space 56 of comparable size.
  • a hexagon screw 54 instead of the valve ball 48, another correspondingly suitable closing element can be used, for example in the form of a conical or plate-shaped component or the like.
  • a displaceable piston 58 is arranged displaceably in this travel space 56 and, as part of the separating device according to the invention, cooperates with the control piston 42 and forms a pressure compensator with the latter.
  • the locking piston 58 which essentially consists of a steel material, has circumferential grooves 60 distributed along its circumference at predeterminable distances from one another, which act like lubrication grooves and permit a smooth movement of the locking piston 58.
  • the closing piston 58 In its position shown in FIG. 1, the closing piston 58 abuts with its one end on an end screw 62 which closes off the travel space 56 from the outside.
  • the closing piston 58 has a cylindrical connecting piece 64 which is connected in one piece to the closing piston 58 and which carries a web 66 at its end facing the control piston 42.
  • This web 66 engages over the through bore 68 arranged in the control piston 42, which creates the connection between the control chamber 44 and the inlet P and which, according to the basic position of the check valve 50 shown in FIG. 1, is closed by its valve ball 48.
  • the two free, opposite ends of the web 66 rest on the end face of the control piston 42, two opening regions of the bore 68 then separated from the web 66 being constantly connected to the inlet P.
  • the separating device in the closing piston 58 has a closing part in the form of a conically shaped closing surface 72 on its active surface 70 facing the control piston 42, which is seen to the left when the closing piston 58 is moved in FIG. 1 Can be brought into contact with a fixed part in the form of a conical seat surface 74 adapted to the closing surface 72, which is arranged in the travel space 56 and delimits it at the end.
  • the sealing part of the separating device therefore consists of the movable closing part in the form of the closing surface 72 and the seat surface 74 designed as a fixed part, both of which can be brought into sealing contact with one another.
  • the active surface 76 of the closing piston 58 facing away from the control piston 42 delimits a part 78 of the travel space 56 which is somewhat enlarged in diameter and into which a branch 80 lying between the check valve in the form of the check valve 20 and the control connection B and a connecting line 82 which leads to the first Pilot valve 22 leads.
  • the accumulator loading valve also has two further sealing parts in the two valve tappets 84 and 86 of the two pilot valves 22 and 24, which each have a conical closing surface 88 at the end, which has a fixed part in the form of a Seat edge 90 interact, which is part of the valve housing of the two pilot valves 22 and 24.
  • the valve lifter 84 of the first pilot valve 22 can open or block the path between the connecting line 82 to the front valve chamber 34.
  • the valve lifter 86 of the second pilot valve 24 establishes or separates the connection between the front valve chamber 36 and the rear valve chamber 30.
  • the hydraulic pump 18 drives pressure medium via the inlet P and the check valve 20, which then opens accordingly, pressure medium into the accumulator circuit and thus into the hydraulic system 10, in this case the control piston 42 and the closing piston 58 largely pressure-equalized and are held by the piston spring 46 in their position shown in FIG.
  • the inlet P is separated from the outlet T and the first pilot valve 22 is opened, whereas the second pilot valve 24 is closed.
  • a connection between the control connection B and the cross connection 38 is thus established via the first pilot valve 22, whereas the connection between the branch 52 and the cross bore 32 is prevented via the second pilot valve 24.
  • the first pilot valve 22 at the seat edge 90 closes first.
  • the pressure in the inlet P opens the check valve 50 and fluid, the second, flows through the bore 68, the control chamber 44 and the branch 52 Pilot valve 24 opens at the location of its seat edge 90.
  • the control chamber 44 of the control piston 42 is therefore limited by means of the second pilot valve 24 to its predeterminable pressure, which here differs from the value zero, which then drops when the second pilot valve 24 is actuated, the two-part pressure compensator formed from the control piston 42 and the closing piston 58 is no longer pressure equalized, so that the closing piston 58 moves the control piston 42 in FIG. 1 as seen under the influence of the upper boost pressure prevailing in the control connection B against the action of the piston spring 46 via the connecting piece 64 and the web 66. In this switching position assumed on the left, the closing piston 58 presses with its closing surface 72 against the seat surface 74 of the travel space 56 and thus seals the connection between the control connection B and the outlet T without leakage.
  • the control piston 42 itself releases the connection between inlet P and outlet T and the check valve 20 closes, so that the hydraulic accumulator 12 of the hydraulic system 10 is permanently charged to the upper boost pressure and the hydraulic pump 18 delivers hydraulic oil from inlet P immediately after a slight pressure difference Expiration T.
  • the piston spring 46 thus pushes the control piston 42 and thus the closing piston 58 back into the basic position shown in FIG. 1 when the adjustable boost pressure has fallen below its lower limit value, the control piston 42 again separating the inlet P from the outlet T and the charging cycle again from inlet P to control connection 3.
  • the control piston 42 and the closing piston 58 have approximately the same size ratios, in particular their outer diameter is the same. Furthermore, their longitudinal axes lie essentially on a common line.
  • the seat diameter formed by the seat surface 74 in the travel space 56 is smaller than the piston outer diameter of the closing piston 58 measured at the point where it is in contact with the travel space 56. This results in the described downshifting process in addition to the force of the piston spring 46, a force component that results from the specified diameter difference and the prevailing downshifting pressure that the release of the closing surface 72 from the seat surface 74 and thus the movement of the closing piston 58 in Fig.1 seen relieved to the right. As soon as the seat surface 72 has detached from the seat surface 74, the surface area ratio no longer plays a role and the two pistons are in turn pressure-balanced.
  • the second exemplary embodiment of a store loading valve according to the invention is only explained to the extent that it differs significantly from the first described embodiment.
  • Components relating to the second exemplary embodiment, which correspond to the components of the first exemplary embodiment, are reproduced with the same reference numerals, however, increased by 100 in each case.
  • the closing piston 58 has been omitted and only the control piston 142 has been used.
  • the piston spring 146 which is arranged in the interior of the control chamber 144, has one end directly on the control piston 142 and the other end on the second pilot valve 124.
  • the piston chamber 140 is installed longitudinally in the accumulator charging valve and the branch 52 is omitted because the control chamber 144 opens directly into the front valve chamber 136 of the second pilot valve 124.
  • a continuous nozzle 152 Arranged in the control piston 142 at the end is a continuous nozzle 152 which forms a throttle point and which constantly connects the inlet P to the control chamber 144.
  • the piston spring 146 tries to hold the control piston 142 in its basic position shown in FIG.
  • an annular groove 194 designed as a lubrication groove which runs along the outer circumference of the control piston 142, is at least partially in register with the outlet T.
  • a further second annular groove 196 is in this way between the annular groove 194 and the end of the control piston 142 facing the second pilot valve 124 arranged on its outer circumference that in the basic position shown in FIG. 2, this circumferential annular groove 196 is completely covered by the valve wall of the valve body 116.
  • control piston 142 If the control piston 142 is moved from its basic position shown in FIG. 2 in FIG. 2 from bottom to top into its other end position, a connection between the control chamber 144 is established via a transverse bore 198 which is arranged in the bottom of the second annular groove 196 and a connecting line 102 running in the valve body 116, which leads into the upper transverse bore 132.
  • the control piston 142 Through the transverse bore 198 and the second annular groove 196, the control piston 142 thus has a passage which opens into the control chamber 144 and which can be connected to the leakage oil line L via the connecting line 102.
  • the separating device with its respective sealing part is formed from the first pilot valve 122 and the check valve located between the inlet P and the control connection B in the form of the check valve 120.
  • the pump 118 in turn delivers via the built-in check valve 120 into the storage circuit of the hydraulic system 110.
  • the control piston 142 is pressure-balanced and is in the basic position shown in FIG. 2 caused by the piston spring 146.
  • Inlet P is separated from outlet T and first pilot valve 122 is opened, whereas second pilot valve 124 is closed.
  • the pilot valve 122 closes first and when the upper boost pressure is reached, the second pilot valve 124 opens due to the pressure in the control chamber 144, which results from the fluid supply through the inlet P behind the nozzle 192.
  • the pressure prevailing in the leakage oil line L is then mainly present on the spring side of the control piston 142, since the oil which is constantly flowing in through the nozzle 192 can flow back to the largely unpressurized side via the passage 196, 198 mentioned.
  • the hydraulic system 110 is then charged to the upper boost pressure and the pump 118 delivers from inlet P to outlet T with little pressure loss.
  • the accumulator pressure prevailing in the hydraulic system 110 then acts on the check valve 120 and the first pilot valve 122 does not have any connection to the control piston 142 and thus to the outlet T due to their sealing effect allows the hydraulic system 110 to be completely leak-free shut-off at the lower and the upper boost pressure.
  • the pump 118 conveys from P to T with a low pressure drop.
  • the pressure in the hydraulic system drops due to oil extraction, but remains constant above the lower boost pressure.
  • the piston spring 146 pushes the control piston 142 back into its starting position due to the lack of oil delivery by the pump.
  • the pump 118 is switched on again, it pumps via the check valve 120 into the hydraulic accumulator 112, which is charged to the upper boost pressure.
  • the respectively movable closing part is formed from the rounded closing surface of a valve ball, which can be sealingly brought into contact with a fixed annular seat edge on the valve body.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Check Valves (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Edible Oils And Fats (AREA)
  • Non-Volatile Memory (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Claims (8)

  1. Vanne de charge à accumulation pourvue d'un piston de commande (42) aux fins d'établir une communication entre une entrée (P) alimentant un circuit hydraulique (10) et une sortie (T) lorsqu'une pression de charge supérieure réglable est atteinte dans le circuit hydraulique (10) et pour interrompre ladite communication lorsqu'une pression de charge inférieure réglable est atteinte dans ledit circuit hydraulique (10), lequel piston, dans l'une de ses deux positions de commutation interrompt la communication entre l'entrée (P) et la sortie (T) et, dans l'autre position de commutation, établit la communication entre l'entrée (P) et la sortie (T), une entrée de commande (B) qui relie le circuit hydraulique (10) à la vanne de charge à accumulation étant isolée de la sortie (T) par l'intermédiaire d'un dispositif de coupure et une première vanne pilote (22) et une deuxième vanne pilote (24) étant prévues pour le réglage de la pression de charge inférieure et de la pression de charge supérieure, caractérisée par le fait que le dispositif de coupure comporte un piston (58) de fermeture pourvu d'une surface (72) de fermeture qui, lorsque la pression de charge supérieure réglable est atteinte vient en appui étanche sur une sur une surface (74) formant siège fixe, disposée dans une chambre (56) de guidage du piston de fermeture (58), aux fins de fermer sans fuites la communication entre l'entrée de commande (B) et la sortie (T), laquelle communication constitue un circuit de fuite.
  2. Vanne de charge à accumulation pourvue d'un piston de commande (142) aux fins d'établir une communication entre une entrée (P) alimentant un circuit hydraulique (110) et une sortie (T) lorsqu'une pression de charge supérieure réglable est atteinte dans le circuit hydraulique (110) et pour interrompre ladite communication lorsqu'une pression de charge inférieure réglable est atteinte dans ledit circuit hydraulique (110), lequel piston, dans l'une de ses deux positions de commutation interrompt la communication entre l'entrée (P) et la sortie (T) et, dans l'autre position de commutation, établit la communication entre l'entrée (P) et la sortie (T), une entrée de commande (B) qui relie le circuit hydraulique (110) à la vanne de charge à accumulation étant isolée de la sortie (T) par l'intermédiaire d'un dispositif de coupure et une première vanne pilote (122) et une deuxième vanne pilote (124) étant prévues pour le réglage de la pression de charge inférieure et de la pression de charge supérieure, caractérisée par le fait que le dispositif de coupure se compose de la première vanne pilote (122) et de la vanne de coupure (120) placée entre l'entrée (P) et l'entrée de commande (B) qui, lorsque la pression de charge supérieure réglable est atteinte, ferment de manière étanche la communication entre l'entrée de commande (B) et la sortie (T), laquelle communication constitue un circuit de fuite.
  3. Vanne de charge à accumulation selon la revendication 1 ou la revendication 2, caractérisée par le fait que la force d'un moyen de rappel (46, 146) maintient le piston de commande (42, 142) dans sa position qui interrompt la communication entre l'entrée et la sortie (P, T), par le fait qu'une communication peut être établie entre ladite entrée (P) et une chambre de commande (44, 144) du piston de commande (42, 142) et par le fait que la chambre de commande (44, 144) est maintenue à une pression prédéfinie au moyen de la deuxième vanne pilote (24, 124).
  4. Vanne de charge à accumulation selon la revendication 3, caractérisée par le fait que pour réaliser la communication entre l'entrée (P) et la chambre de commande, il est prévu dans le piston de commande (142) une buse (182) ou bien on actionne un clapet anti-retour (50) logé dans la chambre de commande (44).
  5. Vanne de charge à accumulation selon la revendication 3 ou la revendication 4, caractérisée par le fait qu'une vanne d'arrêt (20, 120) qui est blocante en direction de l'entrée (P) est insérée entre l'entrée (P) et l'entrée de commande (B) et par le fait qu'un piquage (80, 180) entre ladite vanne d'arrêt et l'entrée de commande (B) mène à la première vanne-pilote (22, 122).
  6. Vanne de charge à accumulation selon l'une des revendications 3, à 5, caractérisée par le fait que le piston de commande (142) présente un passage (196, 198) qui débouche dans la chambre de commande (144) et peut être connecté à une conduite d'évacuation des fuites (L, T).
  7. Vanne de charge à accumulation selon la revendication 1, caractérisée par le fait que le piston de commande (42) qui coopère avec le piston de fermeture (58) forme une balance de pression avec ce dernier.
  8. Vanne de charge à accumulation selon la revendication 7, caractérisée par le fait que le piston de fermeture (58), par l'intermédiaire de ses faces (70, 76) tournée vers et éloignée du piston de commande (42) peut être sollicité par la pression qui règne au niveau de l'entrée (P) ou de l'entrée de commande (B) et que la face (70) tournée vers le piston de commande (42) porte la partie de fermeture qui de préférence présente une surface de fermeture (72) conique ou arrondie.
EP92901393A 1991-01-04 1992-01-01 Vanne de charge a accumulation exempte d'huile de fuite Expired - Lifetime EP0565552B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4100071A DE4100071A1 (de) 1991-01-04 1991-01-04 Leckoelfreies speicherladeventil
DE4100071 1991-01-04
PCT/EP1992/000009 WO1992012350A1 (fr) 1991-01-04 1992-01-01 Vanne de charge a accumulation exempte d'huile de fuite

Publications (2)

Publication Number Publication Date
EP0565552A1 EP0565552A1 (fr) 1993-10-20
EP0565552B1 true EP0565552B1 (fr) 1995-04-12

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EP92901393A Expired - Lifetime EP0565552B1 (fr) 1991-01-04 1992-01-01 Vanne de charge a accumulation exempte d'huile de fuite

Country Status (6)

Country Link
US (1) US5373865A (fr)
EP (1) EP0565552B1 (fr)
JP (1) JPH06504355A (fr)
AT (1) ATE121168T1 (fr)
DE (2) DE4100071A1 (fr)
WO (1) WO1992012350A1 (fr)

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US9885373B1 (en) 2016-10-11 2018-02-06 Honeywell International Inc. Leak-free piston style accumulator

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FR1319685A (fr) * 1962-04-12 1963-03-01 Gury Const Hydromecaniques Sa Conjoncteur-disjoncteur hydraulique à pressions de conjonction et de disjonction réglables
DE1807436A1 (de) * 1968-11-07 1970-06-04 Gewerk Eisenhuette Westfalia Abschaltventil fuer hydraulische Pumpanlagen
US4114637A (en) * 1976-12-20 1978-09-19 Double A Products Company Variable differential pressure unloading valve apparatus
DE3334189C2 (de) * 1983-09-22 1986-04-10 Integral Hydraulik & Co, 4000 Düsseldorf Abschaltventil
DE3608100A1 (de) * 1986-03-12 1987-09-17 Integral Hydraulik Co Abschaltventil
DE3744178A1 (de) * 1987-12-24 1989-07-06 Integral Hydraulik Co Hydraulisches speicherladeventil

Also Published As

Publication number Publication date
ATE121168T1 (de) 1995-04-15
DE4100071A1 (de) 1992-07-09
DE59201918D1 (de) 1995-05-18
JPH06504355A (ja) 1994-05-19
EP0565552A1 (fr) 1993-10-20
WO1992012350A1 (fr) 1992-07-23
US5373865A (en) 1994-12-20

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