EP1574720A1 - Elektrohydraulische Steuervorrichtung - Google Patents
Elektrohydraulische Steuervorrichtung Download PDFInfo
- Publication number
- EP1574720A1 EP1574720A1 EP20040026604 EP04026604A EP1574720A1 EP 1574720 A1 EP1574720 A1 EP 1574720A1 EP 20040026604 EP20040026604 EP 20040026604 EP 04026604 A EP04026604 A EP 04026604A EP 1574720 A1 EP1574720 A1 EP 1574720A1
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- EP
- European Patent Office
- Prior art keywords
- line
- pressure
- working
- seat valve
- valve
- 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
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Classifications
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- 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
- F15B11/003—Systems with load-holding valves
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- 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
- F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
- F15B2211/30515—Load holding valves
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
- F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and a single output member
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/46—Control of flow in the return line, i.e. meter-out control
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
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- 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
- Y10T137/86574—Supply and exhaust
- Y10T137/86622—Motor-operated
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- 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
- Y10T137/87169—Supply and exhaust
- Y10T137/87193—Pilot-actuated
- Y10T137/87209—Electric
-
- 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
- Y10T137/87169—Supply and exhaust
- Y10T137/87217—Motor
Definitions
- the invention relates to an electro-hydraulic control device in the preamble of claim 1 specified type.
- a electro-hydraulic control device are the two load-holding valves of the working lines hydraulically releasable check valves, and are the two main-way magnetic seat valves as 3/2-way magnetic seat valves trained, each of which is a working line either from the Shut off pressure source and connects to the return line, or shut off to return and connects to the pressure source.
- the control line system comes with the control pressure supplied from the respective higher working pressure leading working line to the Circulating circuit to apply.
- the one from each of the higher Working pressure leading working line tapped control pressure used to holding the load pressure in the shut off from the pressure source working line load-holding valve to unlock, so that this working line is relieved to return.
- Such electro-hydraulic control devices are preferred for transportable Working devices such as screwdrivers, riveting tools, building displacement devices and the like. Used. In these devices, extremely high Working pressures are built up, for example, up to about 800 bar, with a pressure source that works for the maximum pressure with a relatively small flow rate. Due to the high working pressures and the small flow, poppet valves are essential required that have leak-free shut-off positions. With the hydraulic unlockable check valves, which are used as load holding valves, the occurs Effect that after switching off the control device in at least one working line the working pressure is maintained. Due to the seat valves this remains Pressure for very long periods without noticeable waste exist. This represents a significant In addition, it is sometimes necessary when switched off Control device to solve a connection of the working line, which is, however, at upright working pressure can not be carried out or violent separation is dangerous or pollutes the environment with the hydraulic fluid.
- a multi-way valve for water as the hydraulic medium are in the control circuit 2/2-solenoid valves for pressure control of Control chambers of the four main valves provided. Load-holding seat valves with magnetic actuation absence.
- JP 571 07 486 A multi-way valve without load-holding valves is in the neutral position, a discharge path in control chambers and loose sliding fits open from valve elements to the tank. There is only one working line at a time Relieve pressure.
- both chambers are one Hydraulic consumer secured via electrohydraulic proportional valves while each of a 2/2-solenoid proportional pressure control valve and a 2/2 hydraulic proportional valve consists.
- the invention is based on the object, such an electro-hydraulic control device indicate with reduced operating hazard.
- each load-holding valve has an optional electrical passage to the return line Switchable 2/2-way solenoid seat valve is needed, the working pressure in at least one Work management can not be maintained on a permanent basis, but if necessary very high working pressure can easily be reduced to the return by the load-holding valve is electrically set to passage. This can be done routinely (via the associated control device) after each shutdown of the control device take place, or optionally in the event that a working pressure leading working line must be solved for some reason.
- the training of the Load holding valve as a 2/2-way magnetic seat valve also offers the advantage of a leak-free Shut-off position as long as the working pressure must be maintained.
- the 2/2-way solenoid seat valve for each one working line a separate switching magnet to give, together with the solenoid of the main-way magnetic seat valve the other work management is operable.
- This offers the advantage that when applying the one working line automatically the other working line connected to the return.
- it allows the separate solenoid, the respective 2/2-way solenoid seat valve also independent of the solenoid of the main-way magnetic seat valve, and a pressurized Working line to connect to the return, through an optional Actuation of the solenoid of the 2/2-way solenoid seat valve whose working line to relieve.
- the optional pressure relief of a working line under working pressure is expedient then perform comfortable when after switching off the control device the coming of the pressure source pressure medium through the circulation circuit is derived without pressure. Then there is no at the main path magnetic seat valves significant pressure, if to relieve one or both working lines with a short switching pulse, the respective 2/2-way magnetic seat valve on passage is switched to the return.
- the circulation circuit is suitably by a load-dependent control pressure actuated.
- the control pressure can be direct or indirect the respective working line or from the pressure line via the control line system be tapped.
- the circulation circuit reliably in the position for unpressurized Circulation, it is useful if to the control line system for each Working line a solenoid-confirmed control pressure relief seat valve to the return connected.
- the relief seat valve is closed and leakproof, so that the control pressure is reliably maintained. Will the relief seat valve turned on, the control pressure collapses and goes the circulation circuit in the position for non-pressurized circulation.
- each relief seat valve of the solenoid of the Main way magnetic seat valve with actuated.
- anyone Relief seat valve it would be possible for anyone Relief seat valve to give its own solenoid, which, for special situations, is operable separately from the solenoid of the main path solenoid seat valve.
- the relief seat valve can additionally the task of tapping the control pressure from the respective working line or, alternatively, assigned from the pressure line be.
- the relief seat valve is a 3/2-way magnetic seat valve educated.
- the relief seat valve In the event that the control pressure is tapped directly from the pressure line, can the relief seat valve, however, be a simple 2/2-solenoid seat valve, the only for processing the control pressure amount, i. is relatively compact form.
- the circulation circuit a 2/2-way pressure compensator circulation valve, expediently also in poppet design, between the pressure line and the return line.
- the seat valve design is suitable for high working pressures because of the leak-free shut-off position.
- control pressure medium in the control line system it may be appropriate to the pressure compensator circulation valve a two-way flow regulator assigned, between the pressure line and the control line system is working.
- An electro-hydraulic control device H shown in FIG. 1 is used, for example for directional control of a hydraulic consumer or hydraulic motor, the two working lines A, B is connected (not shown).
- a pressure line 1 is supplied, from which another Pressure line 2 to two main-way magnetic seat valves VA, VB for one working line A, B branches off.
- the two main-way magnetic seat valve VA, VB 3/2-way magnetic seated valves, each by a solenoid MA, MB are operated.
- MB are the consumer lines A, B shut off from the pressure line 2 and at the same time Return lines 3 and a return line 4 connected to a return R.
- Leakage-free return valves 9 in the working lines A, B verhindem but one Backflow.
- a circulation circuit U contained in a loop 5, which is a conventional 2/2-way switching or Control valve with leak-free seat function in the shut-off contains, with derived from the pressure line 1 control pressure in the opening direction and with a Control line system 7 acting control pressure and a control spring in the closing direction is charged.
- the control line system 7 is to the working lines A, B output of the main-way magnetic seat valves VA, VB connected.
- the higher control pressure of each Working line is connected via appropriately switched shuttle valves 8 to the closing side the circulation circuit U brought.
- the control line system 7 is connected via a bypass line 7 'to the return line 4 connected, if the electro-hydraulic control device H only for one Hydro consumer is provided.
- the control line system 7 shown via a Connecting line 7 "connected to another shuttle valve 8 ', the Feed control pressure in the control line system, if the electro-hydraulic control device H is not actuated or the control pressure in the shuttle valve 8 'accordingly is high.
- a branch 10 of the working line B branches a line 11 to a branch 12 of the return line 3 from.
- line 11 is as a load-holding valve LB a 2/2-solenoid seat valve provided by a spring 16 in the shown leak-free Locking position is held.
- the 2/2-solenoid seat valve is solenoid operated, namely either via the solenoid MA of the main-way magnetic seat valve VA, or (indicated by dashed lines) via its own solenoid M, always together can be operated with the solenoid MA.
- the line 14 is also as LA load-holding valve contains a 2/2-solenoid seat valve, which comes from the solenoid MB of the main-way magnetic seat valve VB is actuated (or possibly its own Switching magnet M has).
- the electro-hydraulic control device is switched off. If the pressure source P promotes, the pressure medium via the circulation circuit U in the return directed. If the hydraulic consumer to be acted upon via the working line A, wherein at the same time the pressure medium is pushed out via the working line B to the return line is energized, the solenoid MA is energized (function a) to the main-way magnetic seat valve VA and the load-holding valve LB change. Thereupon the pressure line is 2 connected to the working line A, and will also increase the working pressure in the Working line A fed into the control line system 7. This will make the circulation circuit U brought into the shut-off position shown or held in this. Of the Hydro consumer moves.
- the switching magnet MB is energized (function b), whereby the operation proceeds as explained, but with different flow directions, and with a control pressure in the control line system 7, via the other shuttle valve and the switching shuttle valve 8 in the circulation circuit U is effective.
- the load-holding valves LB, LA are similar to the 2/2 solenoid seat valves of Fig. 1, with the difference, in the shut-off position in both Shut off flow directions leak-tight.
- the conduit parts 11a and 14a lead in each case directly to the return line 4. From the line part 11a branches at a junction 17 a line 18 to a relief solenoid seat valve EA for the control line system 7 from that via a coming from a junction 19 line 20th Also with control pressure from the working line A is supplied.
- the relief solenoid seat valve EA in this embodiment is a 3/2-way magnetic seated valve, which is actuated by the solenoid MA, which also the load-holding valve LB and the Main way magnetic seat valve VA actuated.
- Altemativ could be the relief valve EA (or the load-holding valve LB) have their own switching magnet.
- a conduit 22 branches to one Relief solenoid seat valve EB down, which also serves as a 3/2-way magnetic seat valve formed and the switching magnet MB of the other main-way magnetic seat valve VB is actuated.
- Relief solenoid seat valve EB For tapping the control pressure for the control line system. 7 via the relief solenoid seat valve EB is one at a branch 23 of the working line B branching line 24 connected according to the line 20th
- the switching magnet becomes MA excited (function a), the valves VA, LB and EA substantially simultaneously in changed their other switch positions.
- the pressure line 2 is then with the working line A, while the working line B via the line 11 and the line part 11a is connected to the return manifold 4.
- To reduce the working pressure in working line A is sufficient it to energize the solenoid MB for a short time (function b) to the working pressure via the line 14 and the load-holding valve LA and the line part 14a in to reduce the return line 4.
- the embodiment of the electro-hydraulic control device H in FIG. 3 differs from that of Fig. 2 in that the control pressure for the control line system 7 is tapped directly from the pressure line 2. Lead to this purpose from a branch 25 of the pressure line 2 lines 26 to the relief solenoid seat valves EA and EB. The further function corresponds to that of FIG. 2.
- FIG. 4 differs from that of FIGS. 2 and 3 by another type of tapping the control pressure for the control line system. 7 And here is the control pressure directly to a branch 27 from the pressure line 1 tapped.
- the relief solenoid seat valves EA and EB are simple 2/2-way solenoid seat valves in the control line system 7, which only on the control pressure medium amount need to be interpreted, and only in the flow direction to Shut off return pipe R leak-tight.
- the two relief solenoid seat valves EA and EB are arranged in series in the control line system 7. The function corresponds largely the function explained for FIGS. 2 and 3. To the working pressure from the Working line A after switching off the control device, the switching solenoid MB briefly energized; however, to reduce the working pressure in the work line B briefly the solenoid MA.
- FIG. 5 largely corresponds to that of FIG. 4.
- a two-way flow regulator Z is provided, which determines the amount of the control pressure medium in Control line system 7 finely dosed.
- the two-way current regulator works after the Principle of a pressure balance, the pilot pressures upstream and downstream of a Throttle and a control spring is actuated.
- the further function corresponds to that in FIG. 4 explained.
- FIG. 6 largely corresponds to the embodiments of FIG. 4 and 5.
- the here without control line system is operated with a working line 29 from a branch 28 in the Pressure line 1 via the arranged in series relief solenoid seat valves EA, EB leads to the return R.
- the relief solenoid seat valves EA, EB designed so that they in the pressureless circulation the entire Operate working current from the pressure source.
- the other function corresponds described to Figs. 4 and 5.
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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)
- Forklifts And Lifting Vehicles (AREA)
Abstract
Description
Claims (11)
- Elektrohydraulische Steuervorrichtung (H) zur Richtungssteuerung wenigstens eines Hydromotors, insbesondere für Arbeitsdrücke bis oberhalb ca. 450 bar in einer tragbaren Arbeitsvorrichtung, mit zwei Arbeitsleitungen (A, B) und einer Druckquelle (P), wobei die Arbeitsleitungen (A, B) wahlweise abwechselnd über ein Hauptwege-Magnetsitzventil (VA, VB) mit der Druckquelle (P) verbindbar oder von der Druckquelle (P) absperrbar sind, mit je einem Lasthalteventil (LA, LB) pro Arbeitsleitung (A, B), das in der die Druckquelle (P) mit der jeweils anderen Arbeitsleitung verbindenden Schaltstellung des Hauptwege-Magnetsitzventils aus einer Lasthaltestellung für die jeweils eine Arbeitsleitung auf Durchgang zum Rücklauf (R) schaltbar ist, und mit einer bei von der Druckquelle (P) abgesperrten Arbeitsleitungen (A, B) zwischen der Druckquelle (P) und dem Rücklauf (R) wirksamen Umlaufschaltung (U), dadurch gekennzeichnet, dass jedes Lasthalteventil (LA, LB) zum gewollten Entlasten der zugeordneten Arbeitsleitung (A, B) ein wahlweise elektrisch auf Durchgang zum Rücklauf (R) schaltbares 2/2-Wege-Magnetsitzventil ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Lasthalte-2/2-Wege-Magnetsitzventil für die jeweils eine Arbeitsleitung (A oder B) und das Hauptwege-Magnetsitzventil (VA, VB) der jeweils anderen Arbeitsleitung (B, A) durch einen gemeinsamen Schaltmagneten (MA, MB) betätigt werden.
- Elektrohydraulische Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das 2/2-Wege-Magnetsitzventil für die jeweils eine Arbeitsleitung (A, B) einen eigenen Schaltmagneten (M) aufweist, der gemeinsam mit dem Schaltmagneten (MA) des Hauptwege-Magnetsitzventils (VA, VB) der anderen Arbeitsleitung (B, A) betätigbar ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der eigene Schaltmagnet (M) wahlweise getrennt vom Schaltmagneten (MA, MB) des Hauptwege-Magnetsitzventils (VA, VB) der jeweils anderen Arbeitsleitung (B, A) elektrisch betätigbar ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Umlaufschaltung (U) durch einen wahlweise von jeder Arbeitsleitung (A, B) oder von einer mit der Druckquelle (P) verbundenen Druckleitung (1, 2) direkt oder indirekt über ein Steuerleitungssystem (7) abgegriffenen Steuerdruck beaufschlagbar ist, und dass an das Steuerleitungssystem (7) für jede Arbeitsleitung (A, B) ein magnetbetätigtes Steuerdruck-Entlastungs-Sitzventil (EA, EB) zum Rücklauf (R) angeschlossen ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass das Entlastungs-Sitzventil (EA) entweder mit einem eigenen, zusammen mit dem Schaltmagneten (MA, MB) des Hauptwege-Magnetsitzventils (VA, VB) dieser Arbeitsleitung (A oder B) betätigbaren Magneten oder durch den Schaltmagneten (MA, MB) des Hauptwege-Magnetsitzventils (VA, VB) auf Durchgang schaltbar ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass das Entlastungs-Sitzventil (EA, EB) bei indirektem Abgreifen des Steuerdrucks aus der Arbeitsleitung (A, B) oder aus der Druckleitung (1, 2) ein 3/2-Wege-Magnetsitzventil ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass das Entlastungs-Sitzventil (EA, EB) bei direktem Abgreifen des Steuerdrucks aus der Druckleitung (1, 2) ein 2/2-Wege-Magnetsitzventil ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass die Umlaufschaltung (U) ein 2/2-Wege-Druckwaagen-Umlaufventil zwischen der Druckleitung (1) und dem Rücklauf (R) enthält.
- Elektrohydraulische Steuervorrichtung nach Anspruch 9, dadurch gekennzeichnet, dass im Steuerleitungssystem (7) bei direktem Abgreifen des Steuerdrucks aus der Druckleitung (1) ein dem 2/2-Wege-Druckwaagen-Umlaufventil zugeordneter Zweiwege-Stromregler (Z) vorgesehen ist.
- Elektrohydraulische Steuervorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass in der Umlaufschaltung (U) die beiden jeweils auf den vollen Arbeitsstrom ausgelegten Entlastungs-Sitzventile (EA) in einem Arbeitsstromweg (29) von der Druckleitung (1) zum Rücklauf (R) in Serie geschaltet sind.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202004003749U DE202004003749U1 (de) | 2004-03-10 | 2004-03-10 | Elektrohydraulische Steuervorrichtung |
DE202004003749U | 2004-03-10 |
Publications (2)
Publication Number | Publication Date |
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EP1574720A1 true EP1574720A1 (de) | 2005-09-14 |
EP1574720B1 EP1574720B1 (de) | 2009-03-11 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20040026604 Not-in-force EP1574720B1 (de) | 2004-03-10 | 2004-11-09 | Elektrohydraulische Steuervorrichtung und Verfahren zu ihrer Abschaltung |
Country Status (4)
Country | Link |
---|---|
US (1) | US7320335B2 (de) |
EP (1) | EP1574720B1 (de) |
AT (1) | ATE425370T1 (de) |
DE (2) | DE202004003749U1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2151586A2 (de) * | 2008-08-09 | 2010-02-10 | Volkswagen Aktiengesellschaft | Hydraulikkreislauf |
EP2241762A1 (de) | 2009-04-15 | 2010-10-20 | HAWE Hydraulik SE | Steuervorrichtung |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7849686B2 (en) * | 2007-02-07 | 2010-12-14 | Sauer-Danfoss Aps | Valve assembly and a hydraulic actuator comprising the valve assembly |
EP2392819B1 (de) * | 2010-05-31 | 2013-04-03 | HAWE Hydraulik SE | Vorrichtung zur elektrohydraulischen Drehverstellung der Rotorblätter am Rotor einer Windkraftanlage |
CN103742615B (zh) * | 2013-12-31 | 2016-08-17 | 广船国际有限公司 | 一种重载生产线链条的自动张紧液压装置 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57107486A (en) | 1980-12-25 | 1982-07-03 | Toyooki Kogyo Co Ltd | Fluid control valve |
DE19500748A1 (de) | 1995-01-12 | 1996-07-18 | Danfoss As | Drei- oder Mehr-Wege-Ventil |
EP0965763A1 (de) | 1998-06-17 | 1999-12-22 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Hydraulische Steuervorrichtung |
US6328275B1 (en) | 2000-02-04 | 2001-12-11 | Husco International, Inc. | Bidirectional pilot operated control valve |
US20020162327A1 (en) | 2001-05-02 | 2002-11-07 | Stephenson Dwight B. | Hydraulic circuit with a return line metering valve and method of operation |
EP1338802A2 (de) | 2002-02-26 | 2003-08-27 | Husco International, Inc. | Hydraulische Steuereinrichtung zum Betreiben von zwei parallel angeordneten Aktuatoren |
US6705079B1 (en) | 2002-09-25 | 2004-03-16 | Husco International, Inc. | Apparatus for controlling bounce of hydraulically powered equipment |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2928005A1 (de) * | 1978-07-18 | 1980-02-14 | Diesel Kiki Co | Ferngesteuerte proportionalregelungs- richtungsumschalt-regelventilvorrichtung |
DE3006259A1 (de) * | 1980-02-20 | 1981-08-27 | Wabco Fahrzeugbremsen Gmbh, 3000 Hannover | Wechselventil fuer pneumatisch gesteuerte tueranlgen |
JP3110861B2 (ja) * | 1992-05-19 | 2000-11-20 | カヤバ工業株式会社 | 電磁比例減圧弁 |
DE4340283A1 (de) * | 1993-11-26 | 1995-06-01 | Claas Ohg | Hydraulisches Steuerventil |
US5960695A (en) * | 1997-04-25 | 1999-10-05 | Caterpillar Inc. | System and method for controlling an independent metering valve |
US6457487B1 (en) * | 2001-05-02 | 2002-10-01 | Husco International, Inc. | Hydraulic system with three electrohydraulic valves for controlling fluid flow to a load |
-
2004
- 2004-03-10 DE DE202004003749U patent/DE202004003749U1/de not_active Expired - Lifetime
- 2004-11-09 EP EP20040026604 patent/EP1574720B1/de not_active Not-in-force
- 2004-11-09 DE DE200450009132 patent/DE502004009132D1/de active Active
- 2004-11-09 AT AT04026604T patent/ATE425370T1/de active
-
2005
- 2005-02-18 US US11/062,051 patent/US7320335B2/en not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57107486A (en) | 1980-12-25 | 1982-07-03 | Toyooki Kogyo Co Ltd | Fluid control valve |
DE19500748A1 (de) | 1995-01-12 | 1996-07-18 | Danfoss As | Drei- oder Mehr-Wege-Ventil |
EP0965763A1 (de) | 1998-06-17 | 1999-12-22 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Hydraulische Steuervorrichtung |
US6328275B1 (en) | 2000-02-04 | 2001-12-11 | Husco International, Inc. | Bidirectional pilot operated control valve |
US20020162327A1 (en) | 2001-05-02 | 2002-11-07 | Stephenson Dwight B. | Hydraulic circuit with a return line metering valve and method of operation |
EP1338802A2 (de) | 2002-02-26 | 2003-08-27 | Husco International, Inc. | Hydraulische Steuereinrichtung zum Betreiben von zwei parallel angeordneten Aktuatoren |
US6705079B1 (en) | 2002-09-25 | 2004-03-16 | Husco International, Inc. | Apparatus for controlling bounce of hydraulically powered equipment |
Non-Patent Citations (1)
Title |
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PATENT ABSTRACTS OF JAPAN vol. 0062, no. 01 (M - 163) 13 October 1982 (1982-10-13) * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2151586A2 (de) * | 2008-08-09 | 2010-02-10 | Volkswagen Aktiengesellschaft | Hydraulikkreislauf |
EP2241762A1 (de) | 2009-04-15 | 2010-10-20 | HAWE Hydraulik SE | Steuervorrichtung |
Also Published As
Publication number | Publication date |
---|---|
US7320335B2 (en) | 2008-01-22 |
DE202004003749U1 (de) | 2005-07-28 |
ATE425370T1 (de) | 2009-03-15 |
US20050199295A1 (en) | 2005-09-15 |
EP1574720B1 (de) | 2009-03-11 |
DE502004009132D1 (de) | 2009-04-23 |
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