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EP0893607A1 - Electrovanne de décharge - Google Patents

Electrovanne de décharge Download PDF

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Publication number
EP0893607A1
EP0893607A1 EP98108825A EP98108825A EP0893607A1 EP 0893607 A1 EP0893607 A1 EP 0893607A1 EP 98108825 A EP98108825 A EP 98108825A EP 98108825 A EP98108825 A EP 98108825A EP 0893607 A1 EP0893607 A1 EP 0893607A1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
seat
main valve
solenoid
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
Application number
EP98108825A
Other languages
German (de)
English (en)
Other versions
EP0893607B1 (fr
Inventor
Martin Heusser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP0893607A1 publication Critical patent/EP0893607A1/fr
Application granted granted Critical
Publication of EP0893607B1 publication Critical patent/EP0893607B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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

Definitions

  • the invention relates to a solenoid operated drain valve according to the preamble of Claim 1.
  • Magnetic poppet valves are from data sheet D 7490/1 from Heilmeier & Weinlein, March 1996 (Types EM 11 to 31) are known, which are leak-free in the closed position.
  • These drain valves are inexpensive and reliable, but as pure Black / white valves unable to control a clear ramp function i.e. regulate the flow rate depending on the stroke and pressure.
  • a ramp function when in use of these known drain valves, for example electronically, with considerable Effort is brought about to the need for an expensive and elaborate To bypass two-way current regulator, which would also not be leak-tight.
  • a drain control valve known from EP-A-0 291 140 is in the main valve no pressure compensator provided, but a differential pressure generator arranged downstream, the spring-loaded is pushable in a bell-shaped cavity to reduce the current to make.
  • a hydraulic system known from EP-A-0 279 315 Control device e.g. for a lifting cylinder, a two-way flow controller is one Pressure compensator with a poppet valve function assigned in the shut-off position Control pressure keeps leakage free.
  • a main seat valve is not provided, but one adjustable orifice plate, which should keep the load pressure. Since it is difficult to use the orifice plate to use for load holding is a in most embodiments Black / white switching valve designed to hold the load pressure.
  • the invention has for its object a structurally simple, small-sized magnet-actuated To improve the drain valve of the construction 50 known from DE-U-29 61 7922, that the ramp function is independent of the load pressure.
  • the structurally simple combination of the black / white drain valve with the pressure compensator leads to load pressure independence, making a real two-way flow regulator is created, which is small and inexpensive.
  • the one provided in the pressure compensator Seat valve function in combination with the seat valve function in the main valve and in Pilot valve ensure that the drain valve is leak-tight in the closed position. Because the load pressure is shut off in the main valve and in the pilot valve without leakage oil, and additionally also in that which is then rendered inoperative by means of the poppet valve function Pressure compensator.
  • the seat valve function is eliminated in the regulating play of the pressure compensator.
  • the lowering valve of a lift truck has the advantage that the ramp function is load-dependent to control, either with a proportional magnet or even with a conventional one, in its characteristic to the hard spring characteristic customized magnets. Even when there is a long break in operation, the Load or a component of the forklift under load is held. It will so to speak, the trick made according to DE-U-29 61 7922, a black and white drain valve by using a hard spring and a special design of the main seat valve to a ramp function, added profitably through the pressure compensator to the ramp function or quantity control can be controlled independently of the load pressure and in the pressure compensator in the closed position Prevent leakage through the poppet valve function. This can be done with little construction Doing effort and simple components leads to small size a drain valve, which is particularly useful for simple forklifts.
  • the pressure compensator is expediently downstream of the main valve seat arranged.
  • the downstream of the main valve set pressure is tapped on one side of the pressure compensator while the load pressure is brought to the other side of the pressure compensator, on which the poppet valve function is provided for oil-free shut-off.
  • the drain valve can be in the accommodate the same installation space as a conventional black / white drain valve.
  • the diaphragm piston as a slide part is simple in terms of production technology designed with an integrated cone sealing surface.
  • the orifice piston works with its control end except for one Throttle opening or a control notch slide-tight together with the outflow opening.
  • the throttle opening or the control notch ensures, among other things, the correct Close the main valve and can also be used for volume control become.
  • the two-sided loading surfaces of the diaphragm piston same size.
  • the piston is structurally simple in direct extension of the Main valve seat arranged.
  • the sleeve provided for the main valve seat anyway extended to the bore for the piston and the valve seat for the additional To accommodate the sealing function.
  • the connecting channel that brings the load pressure to the pressure compensator can be provided in the sleeve. But it is also conceivable that Lead the load pressure to the pressure compensator in a different way.
  • the sleeve contains the main valve seat and the throttle, via which the pilot valve the opening and closing movements of the main valve controls.
  • This throttle is expediently smaller than or at most as large as the passage of the pilot valve, the passage of the pilot valve expediently at most the size of a bore with a diameter of 0.6 mm.
  • the spring of the piston of the pressure compensator can alternatively outside the piston or be housed inside the piston, in the latter case to reduce the size.
  • the pilot valve is also leak-tight (seat valve)
  • the spring is a hard spring with a steep characteristic curve, with the appropriate tuning of the magnet to control the ramp function.
  • the main valve with a quantity setting device provided that the black / white valve similar to a control valve be let that works with the pressure compensator independent of the load pressure.
  • a drain valve A in Fig. 1 is designed as a two-way flow controller Z and has between a line 2, the pressure to be controlled P or a quantity to be regulated leads, and a leading to a tank T drain line 3 designed as a seat valve Main valve H open.
  • a housing 4 designed as a screw-in insert a magnet M, suitably proportional magnet or one in its characteristic Modified simple switching magnet for a pilot valve arranged in the main valve H. V arranged with which the main valve H is actuated.
  • a pressure compensator W is expediently provided downstream of the main valve H.
  • the magnet M are a stationary part 6 and one when current is applied Magnetic coil 8 upward adjustable magnet armature 7 included.
  • One supported on part 6 hard spring 9 with a steep characteristic curve acts on a tappet 10, the for example, the conical end forms a closing member 11 for the pilot valve V and with a valve seat of a passage 14 in a seat closing element 13 of the Main valve H works together.
  • the pilot valve V is a seat valve, which in its The closed position is leak-tight.
  • the pilot valve V monitors the connection between a control chamber 12 and the discharge line 3. Between the control chamber 12 and the line 2 is one Throttle D provided.
  • the seat closing element 13 of the main valve H has one conical or spherical sealing surface 15, which cooperates with a main valve seat 17, arranged like the throttle D in a sleeve 5 inserted into the line 3 is.
  • the sleeve 5 is screwed to the housing 4.
  • the area of action of the seat closing element 13 in the control chamber 12 is larger than the cross section of the main valve seat 17 of the main valve H. downstream of the Main valve seat 17, a bore section 18 is provided, which has an annular flange 16 of the seat closing element 13 forms a quantity setting device.
  • the ring flange 16 is connected to the sealing surface 15 of the seat closing element 13 provided such that when the main valve H is closed, the annular flange 16 in the Bore section 18 dips.
  • the main valve H is leak-free in the closed position tight.
  • the bore section 18 is extended in Fig. 1 by a bore 19, of which lateral outflow openings 20 (in the form of orifices or orifices) lead to line 3.
  • a piston K is after the pressure compensator B.
  • Kind of a slide led This has a control end facing the main valve H. 21 and the main valve H facing away from a conical or spherical sealing surface 23rd on, which has a seat 22 in the sleeve 5 with a seat valve function (leak oil-free tight) cooperates when the piston K of the pressure compensator W in that shown in Fig. 1 Shut-off position, in which its control end 21 e.g. with a positive Cover U closes the outflow openings 20.
  • the poppet valve function K of the pressure compensator W is indicated with S.
  • a lower end 24 of the piston K is located in a chamber 28 which is connected to line 2 via a channel 27.
  • the end 24 is urged downwards by a spring 25 in FIG the spring 25 is supported in the sleeve 5.
  • the spring 25 surrounds the piston K on the outside.
  • a weak closing spring 29 for the seat closing element can be located in the control chamber 12 13 may be provided.
  • a tax notch or chamfer F be provided, the predetermined, small outflow cross-section to the outflow opening 20 also leaves open in the shut-off position of the piston K.
  • the spring 9 keeps the pilot valve V closed when the magnet M is de-energized and the operating area of the seat closing element 13 in the control chamber 12 is larger than the cross-sectional area of the main valve seat 17, is when de-energized Solenoid the main valve H kept closed. Since the pilot valve V and that If the main valve H is leak-tight in its closed positions, the piston K also becomes tight the pressure compensator W held in its shut-off position and the sealing surface 23 is on Seat 22 on, so that the chamber 28 is blocked leakage-free. In the closed position (In Fig. 1 when the magnet is de-energized) the drain valve is thus leak-free tight.
  • the magnet armature 7 pulls the plunger 10 against the force of the spring 9 up.
  • the pilot valve V is opened.
  • the control pressure in the control chamber 12 changes via passage 14 in a predetermined manner.
  • the pressure in line 2 lifts the seat closing element when the control pressure drops accordingly 13 from the main valve seat H, due to a slow response and the quantity setting device in the main valve H, the pressure P in the line 2 is not suddenly relieved, but with a predetermined ramp function.
  • the quantity would, however, without pressure compensator W depending on the height of the pressure P vary.
  • the Pressure compensator W the quantity is then regulated independently of pressure, with the control cycle of the piston K, the seat valve function S between the sealing surface 23 and the Sealing seat 22 is canceled.
  • the pressure compensator keeps the pressure difference accordingly the current strength constant.
  • the spring 9 is a hard spring with a steep characteristic is that the quantity setting device is present in the main valve H. and that the passage 14 of the pilot valve is relatively small, for example not larger than a hole with a diameter of 0.6 mm.
  • the throttle D is on the Passage cross section of the passage 14 matched so that it is maximum is the same size.
  • the pilot valve V increases again the control pressure in the control chamber 12 so that the main valve H the passage reduced in volume setting, the pressure compensator W still for the pressure independence worries.
  • the spring 9 closes the pilot valve V.
  • the control pressure in the control chamber 12 presses the seat closing element 13 on the main valve seat H.
  • the pressure P in the chamber 28 pushes the piston K in its shut-off position.
  • the pilot valve, the main valve H and the sealing surface 23 seated on the sealing seat 22 provide the desired leakage-free Tightness ago. The pressure P is maintained.
  • the drain valve A is, for example, in a lifting module of a lift truck (or for a tipper) is used, in which a consumer can be pressurized with the pressure P. works against a load to this with predetermined and by energizing the Magnet M set speed to move and in the closed position hold.
  • the drain valve A is located in the lifting module between the supply line of the consumer and the tank (see DE-A-42 39 321) and can be used for lifting and Lowering control or only used for lowering control.
  • the drain valve is A closed when the magnet M is de-energized, it can be used, for example, for lowering control use to lower a load independently of pressure, for example was raised by controlling the pump. When lowering is used Pump the rate of lowering through the drain valve A outflowing amount controlled, in the present case independently from the prevailing pressure P.
  • the drain valve A has the same function as in Fig. 1 (two-way flow controller Z) modified with respect to the pressure compensator W compared to FIG. 1.
  • Piston K is a pot piston and the spring 25 is arranged inside the pot piston in such a way that they are with their lower end on the piston K and with their upper end is supported on a stop 32 which is arranged on a pin 31 which is in the Piston K can be moved.
  • the stop 32 can be in the bore 19 on a Transition to the smaller bore section 18 in diameter in the printing direction support upwards.
  • the piston K has e.g. a larger exposure area than the cross section of the main valve seat 17.
  • the control notch F of Fig. 1 is in the piston K of FIG. 2 at least one throttle opening F 'to the outflow opening 20 provided.
  • the spring space of the piston K is indicated at 30.
  • the drain valve A operating as a two-way flow regulator is under construction the embodiment of FIG. 1 is the same, designed so that when the magnet is de-energized M the connection between the line 2 and the outflow line 3 is open.
  • the stationary Part 6 of the magnet M is below the armature 7 which can be moved downwards arranged.
  • the hard spring 9 with a steep characteristic curve is supported in part 6 and below acts on the plunger 10 and thus the armature 7 upwards, so that when de-energized Magnet M opened the pilot valve V and the seat closing element 13 of the Main valve H is lifted off the main valve seat 17.
  • the piston K of the pressure compensator is moved down from the shut-off position shown when the main valve H is open, to clear the flow path.
  • the drain valve A of Fig. 3 can e.g. for lifting and lowering control be used.
  • the pressure medium flows over the open drain valve A from.
  • Main valve H With full power and closed Main valve H becomes the total available quantity to the consumer guided. If the load is to be stopped, the supply pump is switched off and the Load pressure kept leak-free.
  • the lowering control is carried out while reducing the Current supply to the magnet M by regulating the quantity which, thanks to the pressure compensator W flows to tank T regardless of load pressure.
  • the spring 25 of the piston K can be arranged in the interior of the piston as in FIG. 2.
  • the piston is K without chamfer or notch.
  • Fig. 4 illustrates in a symbolic representation the drain valve A as a two-way flow controller in the design according to Figs. 1 and 2, i.e. without energizing the magnet M closed.
  • the pilot valve V is not shown in FIG. 4 for the sake of simplicity shown. Thanks to the seat valve function in the main valve H and the seat valve function S the pressure compensator A in the shut-off position of the piston K, the pressure P becomes leak-free kept, although the pressure compensator W for the clean control only slide-tight needs to be.
  • the drain valve A is a two-way flow controller Z according to the embodiment 3 symbolically represented, i.e. open when de-energized.
  • the poppet valve function In the main valve H there is also the seat valve function S of the pressure compensator P (the sealing surface 23 is then lifted off the seat 22).
  • the main valve H blocks the pressure P without leakage and the seat valve function S of the pressure compensator W comes into play.
  • Fig. 6 illustrates in a diagram of the current I over the amount Q with the solid curve P, like the amount Q regardless of the pressure P only over the Current I is regulated, either the amount to the consumer flows or the amount that flows out of the consumer.
  • the dashed curves P 'and P' ' indicate how the drain valve A without that directly associated with the main valve and a pressure compensator arranged downstream of the main valve, the quantity Q only could set depending on the pressure. This meant that at a certain current I the amount Q would be smaller at lower pressure P 'than the same Current I and higher pressure P '', and also that despite the same current different Speeds occurred.
  • the solid curve P shows clearly however, that the quantity Q and thus the speed of the consumer can be controlled independently of the pressure with the current intensity I.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Driven Valves (AREA)
EP98108825A 1997-07-25 1998-05-14 Electrovanne de décharge Expired - Lifetime EP0893607B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29713293U 1997-07-25
DE29713293U DE29713293U1 (de) 1997-07-25 1997-07-25 Magnetbetätigtes Ablaßventil

Publications (2)

Publication Number Publication Date
EP0893607A1 true EP0893607A1 (fr) 1999-01-27
EP0893607B1 EP0893607B1 (fr) 2003-04-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98108825A Expired - Lifetime EP0893607B1 (fr) 1997-07-25 1998-05-14 Electrovanne de décharge

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EP (1) EP0893607B1 (fr)
DE (2) DE29713293U1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002014696A3 (fr) * 2000-08-16 2002-07-18 Hydac Fluidtechnik Gmbh Soupape
EP1331199A2 (fr) * 2002-01-24 2003-07-30 Hydac Fluidtechnik GmbH Dispositif de commande, utilisé en particulier dans des dispositifs de levage hydraulique
EP1369598A1 (fr) 2002-06-03 2003-12-10 HAWE Hydraulik GmbH & Co. KG Dispositif électro-hydraulique de commande de levage pour véhicules de manutention
FR2848526A1 (fr) * 2002-12-17 2004-06-18 Tech D Etudes Realisations Et Dispositif d'amarrage d'un aeronef
DE10323595A1 (de) * 2003-05-16 2004-12-09 Hydac Fluidtechnik Gmbh Ventil
EP2466152A1 (fr) 2010-12-17 2012-06-20 HAWE Hydraulik SE Dispositif de commande hydroélectrique
WO2018068876A1 (fr) * 2016-10-13 2018-04-19 Hydac Fluidtechnik Gmbh Balance manométrique d'écoulement et dispositif de levage-abaissement comprenant une telle balance manométrique d'écoulement

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19849877A1 (de) * 1998-02-28 1999-09-02 Continental Teves Ag & Co Ohg Elektromagnetventil
DE19837207A1 (de) * 1998-03-03 1999-09-09 Itt Mfg Enterprises Inc Elektromagnetventil
JP2002505408A (ja) 1998-03-03 2002-02-19 コンティネンタル・テーベス・アクチエンゲゼルシヤフト・ウント・コンパニー・オッフェネ・ハンデルスゲゼルシヤフト 電磁弁
DE19843911A1 (de) * 1998-09-24 2000-03-30 Mannesmann Rexroth Ag Vorgesteuertes Sperrventil
US6409145B1 (en) 2000-02-28 2002-06-25 Delphi Technologies, Inc. Plunger assembly having a preset spring force pre-load
DE102006027859B4 (de) * 2006-04-28 2015-05-21 Continental Teves Ag & Co. Ohg Elektromagnetventil
DE102009019554B3 (de) * 2009-04-30 2010-09-09 Hydac Fluidtechnik Gmbh Proportional-Drosselventil
DE102012015356A1 (de) 2012-08-03 2014-05-15 Hydac Fluidtechnik Gmbh Ventil, insbesondere vorgesteuertes Proportional-Wegesitzventil

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0041247A2 (fr) 1980-06-03 1981-12-09 Backé, Wolfgang, Prof. Dr.-Ing. Dispositif asservi pour réglage de débit indépendant de la charge
DE3537760A1 (de) 1984-10-29 1986-04-30 Kawasaki Jukogyo K.K., Kobe, Hyogo Proportionaldurchflussregelventil
EP0279315A2 (fr) 1987-02-18 1988-08-24 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
EP0291140A2 (fr) 1987-05-14 1988-11-17 Hitachi Construction Machinery Co., Ltd. Appareil de soupape à commande d'écoulement
EP0548513A1 (fr) 1991-12-10 1993-06-30 Robert Bosch Gmbh Dispositif de commande du courant d'un fluide de travail
DE4239321A1 (de) 1992-11-23 1994-05-26 Heilmeier & Weinlein Elektrohydraulisches Hubmodul
DE29617922U1 (de) 1996-10-15 1996-11-28 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Magnetbetätigtes Ablaßventil eines elektrohydraulischen Hubmoduls

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0041247A2 (fr) 1980-06-03 1981-12-09 Backé, Wolfgang, Prof. Dr.-Ing. Dispositif asservi pour réglage de débit indépendant de la charge
DE3537760A1 (de) 1984-10-29 1986-04-30 Kawasaki Jukogyo K.K., Kobe, Hyogo Proportionaldurchflussregelventil
EP0279315A2 (fr) 1987-02-18 1988-08-24 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Dispositif de commande hydraulique
EP0291140A2 (fr) 1987-05-14 1988-11-17 Hitachi Construction Machinery Co., Ltd. Appareil de soupape à commande d'écoulement
EP0548513A1 (fr) 1991-12-10 1993-06-30 Robert Bosch Gmbh Dispositif de commande du courant d'un fluide de travail
DE4239321A1 (de) 1992-11-23 1994-05-26 Heilmeier & Weinlein Elektrohydraulisches Hubmodul
DE29617922U1 (de) 1996-10-15 1996-11-28 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Magnetbetätigtes Ablaßventil eines elektrohydraulischen Hubmoduls

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Title
"2/2-WEGE-MAGNET-SITZVENTILE TYPE EM11... 31 ZUM EINSCHRAUBEN FUER OELHYDRAULISCHE ANLAGEN, LECKOELFREI NACHFOLGEVENTIL ZU TYPEN EM1..3 NACH D 7490", DATENBLATT, vol. D7490/1, March 1996 (1996-03-01), pages 1 - 4, XP002030878 *
"datenblatt d 7490/1 der fa. heilmeier und weinlein", March 1996, article "magnetsitzventile ( typen em 11 bis 31)"

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6799599B2 (en) 2000-08-16 2004-10-05 Hydac Fluidtechnik Gmbh Valve
WO2002014696A3 (fr) * 2000-08-16 2002-07-18 Hydac Fluidtechnik Gmbh Soupape
EP1331199A2 (fr) * 2002-01-24 2003-07-30 Hydac Fluidtechnik GmbH Dispositif de commande, utilisé en particulier dans des dispositifs de levage hydraulique
EP1331199A3 (fr) * 2002-01-24 2004-05-12 Hydac Fluidtechnik GmbH Dispositif de commande, utilisé en particulier dans des dispositifs de levage hydraulique
US6837045B2 (en) 2002-06-03 2005-01-04 Hawe Hydraulik Gmbh & Co. Kg Electrohydraulic lifting control device for industrial trucks
EP1369598A1 (fr) 2002-06-03 2003-12-10 HAWE Hydraulik GmbH & Co. KG Dispositif électro-hydraulique de commande de levage pour véhicules de manutention
FR2848526A1 (fr) * 2002-12-17 2004-06-18 Tech D Etudes Realisations Et Dispositif d'amarrage d'un aeronef
EP1431179A1 (fr) * 2002-12-17 2004-06-23 Societe Technique d'Etudes, Realisations et Maintenances Energetiques Dispositif d'amarrage d'un aéronef
US6805321B2 (en) 2002-12-17 2004-10-19 Societe Technique D'etudes, Realisations Et Maintenances Energetiques Device for mooring an aircraft
DE10323595A1 (de) * 2003-05-16 2004-12-09 Hydac Fluidtechnik Gmbh Ventil
US7740224B2 (en) 2003-05-16 2010-06-22 Hydac Fluidtechnik Gmbh Valve
EP2466152A1 (fr) 2010-12-17 2012-06-20 HAWE Hydraulik SE Dispositif de commande hydroélectrique
WO2018068876A1 (fr) * 2016-10-13 2018-04-19 Hydac Fluidtechnik Gmbh Balance manométrique d'écoulement et dispositif de levage-abaissement comprenant une telle balance manométrique d'écoulement
CN109844325A (zh) * 2016-10-13 2019-06-04 Hydac流体技术有限公司 排出压力天平和具有这种排出压力天平的升降设备
CN109844325B (zh) * 2016-10-13 2020-09-22 Hydac流体技术有限公司 排出压力补偿阀和具有这种排出压力补偿阀的升降设备
EP3751153A1 (fr) * 2016-10-13 2020-12-16 Hydac Fluidtechnik GmbH Balance de pression d'écoulement et dispositif de levage-abaissement comprenant une telle balance de pression d'écoulement
US10871177B2 (en) 2016-10-13 2020-12-22 Hydac Fluidtechnik Gmbh Discharge pressure scale and lifting-lowering device having a discharge pressure scale of this type

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DE59807932D1 (de) 2003-05-22
EP0893607B1 (fr) 2003-04-16

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