EP0935714B1 - Ventilanordnung mit druckwaage - Google Patents
Ventilanordnung mit druckwaage Download PDFInfo
- Publication number
- EP0935714B1 EP0935714B1 EP97945768A EP97945768A EP0935714B1 EP 0935714 B1 EP0935714 B1 EP 0935714B1 EP 97945768 A EP97945768 A EP 97945768A EP 97945768 A EP97945768 A EP 97945768A EP 0935714 B1 EP0935714 B1 EP 0935714B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- piston
- control
- spool
- 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.)
- Revoked
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
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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
- F15B11/02—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
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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
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
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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
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
-
- 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
-
- 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
- F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
-
- 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
- F15B2211/35—Directional control combined with flow control
-
- 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
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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
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/86702—With internal flow passage
-
- 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
Definitions
- the invention relates to a valve arrangement for Pressure and volume flow adapted supply at least a consumer according to the preamble of the claim 1.
- Double-acting cylinders are often used Front linkages used by agricultural tractors.
- the rear linkage have so far been in most cases single-acting cylinders, due to the versatile uses of modern tractors however, one is increasingly concerned about this, including the Rear linkage with double-acting cylinders.
- Peripheral devices such as packers, Couple plows, cultivators, rollers etc. to a tractor and press.
- valve arrangements In mobile hydraulics, the valve arrangements are endeavored run as compact as possible, so that this often in panel construction or as a compact or monoblock be carried out.
- the Valve plate or compact block the required Connections, such as pump connection, control connection, Work connection, tank connection and the one for admission the control elements of the valve assembly required Housing bores formed.
- load-sensing systems are used by which a load pressure independent Flow current and thus a sensitive speed control of the consumer is reached.
- the pressure difference across the directional control valve is kept constant, by placing individual pressure scales in the consumer connections are switched, the system pressure, i.e. the pressure of the highest load in the system on the respective Reduce consumer pressure.
- DE 36 34 728 C2 describes a valve arrangement for load-independent control of several double-acting hydraulic Consumer revealed at the orifice performed by fine control grooves of the directional spool valve is and downstream of this orifice plate an individual pressure compensator received in a valve housing bore is, via which the hydraulic fluid depending on the control of the Directional valve spool a first or a second work connection is feedable.
- the individual pressure compensator has a piston that moves in the opening direction with the pressure the orifice plate and in the closing direction by a spring and a control pressure is applied.
- a disadvantage of this embodiment is that in the Housing of the valve assembly has a mounting hole for the Pistons of the individual pressure compensator and corresponding line systems to supply the control pressure to the Piston back must be designed so that a considerable manufacturing effort for the creation the valve body is required.
- Another disadvantage is that when using another individual pressure compensator possibly the valve housing bore must be changed so that there is a need different valve housing types are available put.
- DE-OS 36 05 312 discloses a valve arrangement, where the directional valve spool as a hollow spool is carried out from both end sections Blind holes for receiving one piston each an individual pressure compensator are provided.
- the orifice plate of the directional valve is through a jacket bore of the Directional valve spool and through an annulus of the valve housing formed, which is connected to the pump connection is. Through this jacket hole, the hydraulic fluid can after control of the directional spool in one of the Blind holes enter so that the corresponding Piston of the individual pressure compensator against a spring preload postponed and the corresponding work connection is driven to the consumer, in this case a double-acting hydraulic cylinder, with hydraulic fluid to supply.
- the invention is based on the object a valve arrangement for pressure and volume flow to create customized care through which at minimal device-related effort a safe control a consumer is guaranteed.
- the piston of the individual pressure compensator to lead into a hollow slide valve with a jacket bore is provided, on the one hand by the axial displacement of the pressure compensator piston openable and on the other hand, depending on the position of the directional valve spool (Hollow slide) a connection to a first or a produces a second working connection, the device-related Effort compared to the one described above Solutions can be reduced considerably because neither its own mounting hole for the individual pressure compensator Corresponding devices in the valve housing to hold a second pressure compensating piston must be provided in the directional valve spool.
- the invention thus makes it possible Valve housing extremely compact, all essential Control and connecting lines in the Directional valve spool or in the piston of the individual pressure compensator are formed while pump connection, tank connection, Control connection etc. provided in the valve housing become.
- the latter can thus remain essentially unchanged with a variety of different valve arrangements used during the individual adjustments relatively simple by varying the directional spool and the pressure compensator piston can be carried out are.
- the end faces of the directional valve spool with the control pressure be, for example, the individual load pressure of the Consumer, one derived from it, for example artificially increased pressure or the highest system load pressure can be, so that it is ensured that on both directional control sides the same control pressure prevails.
- a separate control line for controlling the individual pressure compensator piston can be saved by using the control pressure applied to the control sides of the directional valve spool through a control passage to the spring side of the Pressure compensator piston is guided.
- the pressure compensator piston with a connecting hole be carried out at a predetermined axial displacement of the pressure compensator piston the pressure compensator piston spring chamber with the piston front is connectable, so that the individual load pressure also the back (spring chamber) of the pressure compensator piston. Due to the tax passage in the This individual load pressure becomes the main valve spool also passed on to the control sides of the directional valve spool, so that it is ensured that the control pressure corresponds to the highest system load pressure in each case.
- the pressure compensator piston fulfills the function of a Shuttle valve, as used in conventional solutions to transmit the highest load pressure in the system.
- the axial movement in the closing direction is particularly easy simply limit by using the pressure compensator piston a radial collar is provided, which corresponds to a trained shoulder of the valve slide bore in Plant can be brought.
- This shoulder can be used at the same time Open the connection hole can be used, so that the shoulder has a double function.
- a particularly versatile valve arrangement has two directional spool, each of which is a hollow spool with an individual pressure compensator piston inside is executed so that only in the valve housing nor the work connections, the tank connection, the Working connection, the corresponding channels and the connecting channels to apply the control pressure to the Hollow slide end faces must be trained.
- the supply line to the consumer can be leak oil-free by providing an electrically unlockable check valve shut off, only in the valve housing the screw-in section for the check valve must be provided.
- Fig. 1 is a starting example of an inventive Valve arrangement 1 shown in plate construction, wherein in a valve plate 2, a pump connection P, a Tank connection T and a control connection LS are executed. Furthermore, two are electrical in the valve plate actuated, continuously adjustable directional valves 4, 6 added, via which the pump connection P and the Tank connection T optionally with work connections A1, B1, A2 or B2 is connectable. These are work connections for example via work lines not shown with the two cylinder chambers of a double-acting hydraulic cylinder connected to a hoist.
- Each directional control valve 4, 6 are an individual pressure compensator 16 and 18 and a measuring aperture 19 assigned, via which the System pressure, i.e. the contact at the pump connection P. Pressure on the respective individual consumer pressure (Load pressure) is throttled.
- the directional valve 6 has a valve spool 12, which in a valve bore 14 of the valve plate 2 axially displaceable is led.
- valve spool 12 The axial displacement of the valve spool 12 takes place via abutting electromagnets 15 arranged on both sides, 17, the plunger 21, 23 on the two front or Control sides 20, 22 of the valve spool 12 act.
- On this end face 20, 22 is a spring plate 24, 26 is supported, on each of which in turn a compression spring 28, 30 attacks the inner bore of a Screw-in section of the electromagnets 15 and 17 supported are.
- valve slide 12 In the initial position specified by the spring preload the valve slide 12 are the spring plate 24, 26 with a radial flange on one shoulder the valve bore 14.
- the valve spool 12 is designed with a blind hole Axial bore 32 provided in the in Fig. 2nd left end 22 of the valve spool 12 opens. There this end face (22) is designed as an annular end face is, the associated plunger 23 acts on a stop disc 34 on a shoulder of the axial bore 32 is present, and for example via a lock washer (not shown) in the axial direction in the axial bore 32 is set.
- the valve bore is with annular spaces 35, 36, 38, 40, 42, 44, 46 and 48, the annular spaces 35 and 48 connected to the connection LS via a load reporting channel 50 are.
- Fig. 1 are about Load reporting channels 50 and a dash-dotted connection channel 51 and the associated annular spaces 35 and 48 (Fig. 2) all end faces 20, 22 of the valve slide 12 connected to each other, so that a uniform Control pressure is present.
- the remaining ring bridge between the two ring spaces 36, 38 is designed as an aperture bore 52 which together with a valve spool section 54 Form orifice 19.
- the valve spool portion 54 is provided with fine control notches 56 so that the cross-section of the metering orifice by appropriate energization of the electromagnets 15, 17 is continuously adjustable. Via the orifice plate 52, 54 thus becomes the hydraulic fluid volume flow supplied to the consumer set so that, for example the extension speed of a hoist adjustable is.
- the jacket of the valve spool 12 In the area of the annular space 38 is the jacket of the valve spool 12 with an inlet bore 57 (Bore star) provided, which opens into the axial bore 32.
- the two annular spaces 40 and 46 are via a tank channel 58 connected to the tank connection T.
- the two annular spaces 42 lying between the annular spaces 46 and 40, 44 are via connecting channels 60 and 62 with the Work ports A1 and B1 connected.
- the connections B1 and B2 are double connections with two parallel connection bores 64 executed.
- Each of the annular spaces 36 to 48 is a corresponding one Assigned to the annular groove on the outer circumference of the valve slide 12, 2 for the sake of clarity Have received reference numerals. About these ring grooves by moving the valve spool 12 a connection between the adjacent channels, i.e. between Working connection and tank connection or pump connection getting produced. In the corner areas of the Annuli 36ff. there are notches or adjustments, an optimal opening of the respective connections allows.
- a pressure compensator piston 66 is located in the axial bore 32 added, the in its basic position shown Sheath bore star 64 closes.
- the pressure compensator piston hereinafter referred to as piston 66, has at its in Fig. 2 left end portion of a radial collar 68 on the a control spring 70 engages the stop washer 34 is supported. In the starting position shown the piston 66 via the control spring 70 with its radial collar 68 biased against a shoulder of the axial bore 32.
- the piston 66 also has a connecting bore, the one from a longitudinal bore 72 and one intersecting radial throttle bore 74 is formed.
- the Longitudinal bore 72 is designed as a blind hole and opens into the right end of the piston in Fig. 2 66.
- the radial throttle bore 74 has a smaller one Cross section as the longitudinal bore and serves as a damping throttle.
- the stop plate 34 and the spring plate 26 are provided with a control passage (not shown) over the pressure in the spring chamber of the compression spring 28 also on the Spring space for the control spring 70 is transmitted so that the piston 66 by the action of the control spring 70 and by the control pressure acting on the control connection LS its stop position (Fig. 2) is pressed.
- connection A1 with hydraulic fluid supplied and the connection B1 with the tank T are connected, the electromagnet 15 is energized, so that the plunger 21 depending on the current makes a stroke to the left.
- This stroke is directly on the control slide 12 transferred so that the aperture bore 52 through the 2 to the left moving valve spool section 54 is controlled.
- the hydraulic fluid can then from the pump connection P in the annulus 38 flow and from there through the inlet bore 57 in reach the interior of the axial bore 32.
- the fluid flowing back from the consumer comes from Working connection B1 via the connecting channel 62 and the assigned annular groove of the valve spool 12 in the annular space 40 and from there into the tank channel 58 and then to Tank connection T.
- control orifice with the radial bore star 64 and the piston 66 Through the pressure compensator (control orifice with the radial bore star 64 and the piston 66) the prevailing system pressure, i.e. the pressure in the axial bore 32 on the Throttled load pressure of the connected consumer, so that the pressure drop across the orifice (orifice bore 52, valve spool section 54) remains constant and thus a volume flow independent of load pressure is guaranteed. Since the control spring 70 has a very low spring rate, corresponds to the pressure upstream of the piston 66 in first approximation about the load pressure at the working connection A1 (B1)
- piston 66 In the event that the system pressure (load pressure) is greater than that prevailing in the spring space for the control spring 70 Control pressure, piston 66 is moved to the left as far as until the radial throttle bore 74 from the as a stop for the radial collar 68 acting axial bore shoulder is opened so that the higher pressure upstream of the piston 66 also on the spring side of the Piston 66 and thus also in the spring chamber of the compression spring 28 is transmitted.
- the piston 66 acts in this way practical as a shuttle valve that ensures is that the highest load pressure in each case in the load reporting channels 50, 51 and thus on the control connection LS.
- A1 is in the working connection a check valve 8 is provided.
- This check valve was published in parallel application 196 ... (11MA7196) described by the applicant, so that in terms of construction Details are referred to this application, the Disclosure to the present application is to be counted.
- check valve 8 shown in FIG. 1 is a check valve with pre-opening, the pre-opening cone 78 directly with the anchor of a Electromagnet is connected. By energizing this The check valve 8 can be electromagneted unlock so that the main cone 76 when flowing from the consumer to the work connection A1 from its valve seat lifts off and thus a backflow to Tank T enables.
- the check valve 8 is with a Radial connection 80 can be pivoted about the longitudinal valve axis provided an extremely flexible adaptation to the connection conditions the valve assembly 1 allowed.
- the Check valve 10 (connection A1) has the same structure.
- FIG. 3 is a schematic of the essential Elements of the valve arrangement shown in FIG. 1.
- valve groups are in the valve plate 2, each consisting of the continuously adjustable directional valves 4, 6 and the pressure compensators 16 assigned to them, 18 trained.
- the directional valve spools are each by the two compression springs 28, 30 and the control pressure (Load signaling pressure) in the load signaling channel 50 in their basic position biased.
- the control pressure Load signaling pressure
- the inlet pressure of the pressure compensator 16 (pressure after the orifice of the directional valve 4) is on the right control side of the pressure compensator 16 in FIG. 3, while on the left side of the control the load signal pressure is applied.
- This causes the piston 66 to the left (Fig. 2) pushed so that the control panel (Sheath bore star 64, piston 66) opened and that Hydraulic fluid via the directional valve 4 to the work connection A1 is headed.
- valve spool 12 Hydraulic fluid bypassing the pressure compensator from Consumers via connection B1 and directional valve 4 to Tank connection T directed. If the The pressure at the inlet of the pressure compensator 16 becomes the piston 66 pushed further to the left until the connecting hole (72, 74) opened and the inlet pressure of the pressure compensator is fed into the load reporting channel 50, so that this pressure now acts as a control pressure.
- In 3 are the check valves for simplicity 8, 10 omitted.
- the invention Solution is characterized by a very simple and compact structure, in particular the overall length is reduced to a minimum as an essential Part of the pressure compensator and the load pressure reporting line can be integrated into the hollow slide.
- a valve arrangement for pressure and volume flow is disclosed adapted supply of at least one consumer, which is continuously adjustable via two work connections
- Directional control valve can be supplied with hydraulic fluid or can be connected to a tank.
- the two work connections the valve arrangement is a common pressure compensator assigned, the piston in an axial bore of the Directional valve spool is guided axially, so that optionally with suitable control of the directional valve one of the two working connections with the pump connection is connectable.
- On both ends of the directional valve spool and on the spring side of the pressure compensator piston each acts a control pressure that, for example, the highest system load pressure, the individual load pressure or corresponds to a pressure derived therefrom.
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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)
- Multiple-Way Valves (AREA)
- Forklifts And Lifting Vehicles (AREA)
Abstract
Description
Claims (10)
- Ventilanordnung zur Druck- und Volumenstrom angepaßten Versorgung zumindest eines Verbrauchers, der über zwei Arbeitsanschlüsse (A1, B1, A2, B2) eines stetig verstellbaren Wegeventils (4, 6) mit Hydraulikfluid versorgbar oder mit einem Tank T verbindbar ist, wobei dem Wegeventil (4, 6) eine Druckwaage (16, 18) zugeordnet ist, deren Kolben (66) in Öffnungsrichtung durch den Druck stromabwärts einer durch das Wegeventil (4, 6) ausgebildeten Meßblende (19) und in Schließrichtung durch eine Steuerfeder (70) und einen Steuerdruck beaufschlagt ist,
dadurch gekennzeichnet, daß ein Ventilschieber (12) des Wegeventils (4, 6) ein Hohlschieber ist, in dem der Kolben (66) der Druckwaage (16, 18) geführt ist, durch dessen Axialbewegung eine Mantelbohrung (64) des Ventilschiebers (12) derart aufsteuerbar ist, daß je nach Ventilschieberstellung wahlweise eine Verbindung zu einem der beiden Arbeitsanschlüsse (A1, B1, A2, B2) durch die Mantelborung (64) herstellbar ist. - Ventilanordnung nach Patentanspruch 1, dadurch gekennzeichnet, daß beide Steuerseiten des Ventilschiebers (12) mit dem Steuerdruck beaufschlagt sind.
- Ventilanordnung nach Patentanspruch 1 oder 2, dadurch gekennzeichnet, daß der Kolben (66) eine Verbindungsbohrung (72, 74) hat, über die bei einer vorbestimmten Axialverschiebung des Kolbens (66) die Kolbenstirnseite mit dem Kolbenfederraum verbindbar ist.
- Ventilanordnung nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß die Meßblende (19) durch eine Blendenbohrung (52) und einen Kolbenabschnitt (54) am Außenumfang des Ventilschiebers (12) gebildet ist und stromabwärts der Meßblende (19) eine in eine Axialbohrung (32) des Ventilschiebers mündende Eingangsbohrung (57) ausgebildet ist, über die die Stirnseite des Kolbens (66) mit Hydraulikdruck beaufschlagbar ist.
- Ventilanordnung nach Patentanspruch 3 oder 4, dadurch gekennzeichnet, daß der Kolben (66) mit einem Radialbund (68) gegen eine Schulter der Axialbohrung (32) vorgespannt ist, wobei die Schulter als Steuerkante zum Aufsteuern der Verbindungsbohrung (72, 74) wirkt.
- Ventilanordnung nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß die zur Federseite des Kolbens (66) benachbarte Ventilschieber-Stirnseite (22, 34, 26) mit einem Steuerdurchlaß versehen ist, über den der Steuerdruck an dieser Ventilschieber-Stirnseite (22) zur Kolbenfederseite führbar ist.
- Ventilanordnung nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß der Steuerdruck ein individueller Lastdruck des Verbrauchers ist.
- Ventilanordnung nach einem der vorhergehenden Patentansprüche mit zwei elektrisch betätigten Wegeventilen (4,6), denen jeweils eine Druckwaage (16, 18) zugeordnet ist, wobei im Ventilgehäuse (2) ein gemeinsamer Pumpenanschluß P, ein gemeinsamer Tankanschluß T und ein gemeinsamer Steuerdruckanschluß LS ausgebildet sind, sowie jedem Wegeventil (4, 6) zumindest zwei Arbeitsanschlüsse (A1, B1, A2, B2) zugeordnet sind und die Stirnseiten der Wegeventilschieber (12) mit dem gleichen Steuerdruck beaufschlagt sind.
- Ventilanordnung nach Patentanspruch 8, dadurch gekennzeichnet, daß der Steuerdruck der höchste Lastdruck ist.
- Ventilanordnung nach Patentanspruch 8 oder 9, dadurch gekennzeichnet, daß in dem Ausgangsanschluß (A1, B1) ein elektrisch betätigbares Rückschlag-Einbauventil (8, 10) eingeschraubt ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19646445 | 1996-11-11 | ||
DE19646445A DE19646445A1 (de) | 1996-11-11 | 1996-11-11 | Ventilanordnung |
PCT/DE1997/002425 WO1998021485A1 (de) | 1996-11-11 | 1997-10-20 | Ventilanordnung mit druckwaage |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0935714A1 EP0935714A1 (de) | 1999-08-18 |
EP0935714B1 true EP0935714B1 (de) | 2003-01-08 |
Family
ID=7811247
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97945768A Revoked EP0935714B1 (de) | 1996-11-11 | 1997-10-20 | Ventilanordnung mit druckwaage |
Country Status (6)
Country | Link |
---|---|
US (1) | US6192928B1 (de) |
EP (1) | EP0935714B1 (de) |
JP (1) | JP2001504198A (de) |
DE (2) | DE19646445A1 (de) |
PL (1) | PL333275A1 (de) |
WO (1) | WO1998021485A1 (de) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19948390B4 (de) * | 1999-10-07 | 2008-11-06 | Bosch Rexroth Aktiengesellschaft | Ventilanordnung |
EP1370773B1 (de) * | 2001-03-21 | 2005-06-22 | Bucher Hydraulics GmbH | Wegeventil |
US6990999B2 (en) * | 2003-05-05 | 2006-01-31 | Kjp Investments Llc | Digitally controlled modular valve system |
US7182097B2 (en) * | 2004-08-17 | 2007-02-27 | Walvoil S.P.A. | Anti-saturation directional control valve composed of two or more sections with pressure selector compensators |
KR100680841B1 (ko) * | 2005-12-06 | 2007-02-08 | 현대자동차주식회사 | 자동 변속기 유압 제어시스템의 매뉴얼 밸브 |
DE102007054134A1 (de) * | 2007-11-14 | 2009-05-20 | Hydac Filtertechnik Gmbh | Hydraulische Ventilvorrichtung |
US8333218B2 (en) * | 2010-01-27 | 2012-12-18 | Mac Valves, Inc. | Proportional pressure controller |
US10024445B2 (en) | 2014-06-25 | 2018-07-17 | Parker-Hannifin Corporation | Reverse flow check valve in hydraulic valve with series circuit |
EP3128216B1 (de) * | 2015-08-07 | 2019-03-13 | Claverham Limited | Hydraulikventil |
CN106122141B (zh) * | 2016-05-31 | 2018-04-03 | 上海人豪液压技术有限公司 | 采用模块化可配组插装阀rhcv组合的电液控制终端 |
DE102018001303A1 (de) * | 2018-02-20 | 2019-08-22 | Hydac Fluidtechnik Gmbh | Ventilvorrichtung |
DE102021001960A1 (de) | 2021-04-14 | 2022-10-20 | Hydac Fluidtechnik Gmbh | Ventil |
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US2888943A (en) | 1957-09-25 | 1959-06-02 | American Brake Shoe Co | Control valve having constant volume output features |
US3744518A (en) | 1971-12-13 | 1973-07-10 | Parker Hannifin Corp | Directional control valve |
US3910311A (en) * | 1974-08-26 | 1975-10-07 | Koehring Co | Pressure compensated control valve |
US3985153A (en) * | 1974-08-28 | 1976-10-12 | Tomco, Inc. | Pressure compensating valve spool assembly for a hydraulic control valve |
US4187877A (en) * | 1975-01-13 | 1980-02-12 | Commercial Shearing Inc. | Compensated work port fluid valves |
DE2647140A1 (de) * | 1976-10-19 | 1978-04-20 | Linde Ag | Ventil mit einem laengsschieber |
DE2649775A1 (de) * | 1976-10-29 | 1978-05-03 | Linde Ag | Ventil mit einem laengsschieber |
US4117862A (en) * | 1977-02-07 | 1978-10-03 | Tomco, Inc. | Pressure compensated control valve |
DE2831697A1 (de) * | 1978-07-19 | 1980-01-31 | Friedrich Freimuth | Bruchgesichertes hydraulisch entsperrbares rueckschlagventil |
US4290447A (en) * | 1979-10-05 | 1981-09-22 | Dynex/Rivett Inc. | Electrohydraulic proportional valve |
DE3115114A1 (de) * | 1980-04-14 | 1982-04-01 | Linde Ag, 6200 Wiesbaden | Schieberventil |
US4388946A (en) * | 1981-04-20 | 1983-06-21 | Linde Aktiengesellschaft | Valves |
CS231935B1 (en) * | 1982-12-31 | 1984-12-14 | Augustin Leiter | Distributor with controlled load independent flow |
US4617798A (en) * | 1983-04-13 | 1986-10-21 | Linde Aktiengesellschaft | Hydrostatic drive systems |
US4631923A (en) * | 1983-10-21 | 1986-12-30 | Devron Engineering Limited | Solenoid operated check valve |
US4520841A (en) * | 1983-12-27 | 1985-06-04 | Glen Brand | Four-way valve |
DE3446945C2 (de) * | 1984-12-21 | 1994-12-22 | Rexroth Mannesmann Gmbh | Wegeventil mit eingebautem vorgesteuerten Stromregelventil |
US4719753A (en) | 1985-02-22 | 1988-01-19 | Linde Aktiengesellschaft | Slide valve for load sensing control in a hydraulic system |
DE3605312A1 (de) * | 1985-02-22 | 1986-08-28 | Linde Ag, 6200 Wiesbaden | Schieberventil |
US4738279A (en) * | 1985-12-17 | 1988-04-19 | Linde Aktiengesellschaft | Multiway valves with load feedback |
US4723475A (en) * | 1986-09-29 | 1988-02-09 | Deere & Company | Fully metered compensation steering system |
DE3634728A1 (de) * | 1986-10-11 | 1988-04-21 | Rexroth Mannesmann Gmbh | Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher |
DE3918926A1 (de) * | 1989-06-09 | 1991-02-14 | Heilmeier & Weinlein | Stromregelventil |
DE4234037C2 (de) * | 1992-10-09 | 2001-03-22 | Mannesmann Rexroth Ag | Ventilanordnung, insbesondere für mobile Arbeitsgeräte |
DE4446142B4 (de) * | 1994-12-23 | 2004-08-19 | Robert Bosch Gmbh | Längsschieberventil mit hydraulischer Antriebsverstärkung |
DE19646425A1 (de) | 1996-11-11 | 1998-05-14 | Rexroth Mannesmann Gmbh | Ventilanordnung |
-
1996
- 1996-11-11 DE DE19646445A patent/DE19646445A1/de not_active Withdrawn
-
1997
- 1997-10-20 JP JP52201898A patent/JP2001504198A/ja active Pending
- 1997-10-20 WO PCT/DE1997/002425 patent/WO1998021485A1/de not_active Application Discontinuation
- 1997-10-20 DE DE59709115T patent/DE59709115D1/de not_active Revoked
- 1997-10-20 PL PL97333275A patent/PL333275A1/xx unknown
- 1997-10-20 EP EP97945768A patent/EP0935714B1/de not_active Revoked
- 1997-10-20 US US09/297,831 patent/US6192928B1/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
WO1998021485A1 (de) | 1998-05-22 |
US6192928B1 (en) | 2001-02-27 |
JP2001504198A (ja) | 2001-03-27 |
EP0935714A1 (de) | 1999-08-18 |
DE59709115D1 (de) | 2003-02-13 |
DE19646445A1 (de) | 1998-05-14 |
PL333275A1 (en) | 1999-11-22 |
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