EP1344945A2 - Ventilkombination - Google Patents
Ventilkombination Download PDFInfo
- Publication number
- EP1344945A2 EP1344945A2 EP03090044A EP03090044A EP1344945A2 EP 1344945 A2 EP1344945 A2 EP 1344945A2 EP 03090044 A EP03090044 A EP 03090044A EP 03090044 A EP03090044 A EP 03090044A EP 1344945 A2 EP1344945 A2 EP 1344945A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- combination according
- laminar
- bores
- valve combination
- 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
-
- 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
- F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
-
- 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
- F15B2013/008—Throttling member profiles
-
- 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
-
- 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
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
-
- 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
-
- 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
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
-
- 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
- F15B2211/40—Flow control
- F15B2211/46—Control of flow in the return line, i.e. meter-out 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
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
- F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve
-
- 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
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
- F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
-
- 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
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure 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
- F15B2211/60—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
Definitions
- the invention relates to a valve combination for a low-noise and controllable Hydraulic control according to the preamble of claim 1, in particular for low noise Speed control of the flow rate of liquid media of hydraulic drives, e.g. Cylinders and engines - with heavily changing load pressures at the consumers and with strongly changing system pressures, such as. B. in storage systems.
- the valve combination is particularly suitable for ship rudder systems and similar hydraulic systems.
- the invention is based on generally known control valves in which a piston or a slide can be displaced in a cylindrical bore in a housing, inlet and outlet spaces arranged in the housing being connected or interrupted.
- proportional valves are usually combined with a pressure compensator and, if necessary, with a load holding valve.
- a pressure compensator for speed control, proportional valves are usually combined with a pressure compensator and, if necessary, with a load holding valve.
- a load holding valve is known from DE 195 47 687. If, for example, a cylinder is operated with a low load pressure and at the same time with a high system pressure, the excess supply of energy must be reduced in such a way that the flow rate in the proportional control valve remains constant despite the changing differential pressure.
- EP 0 253 322 B1 describes a low-noise proportional valve in which the energy is dissipated in the disc piston of the proportional valve itself.
- Another such valve is known from US 3,880,399.
- the flow rate is highly viscosity-dependent. Since the valve piston adjusts to a position determined by the control current and thus also to fixed flow cross sections, changing flow and system pressure conditions and viscosity changes due to temperature fluctuations inevitably result in different flow rates.
- the object of the invention is to improve the solutions known from the prior art, in which case a valve combination had to be developed which made it possible to use hydraulic drives, such as, for example, cylinders and motors, even with strongly changing load pressures at the consumers and with strongly changing system pressures, for example in Storage systems, controllable and at the same time quiet to operate. It is important to design the energy reduction in such a way that on the one hand the noise-reducing effect is achieved at the point of greatest energy reduction and on the other hand the proportional valve works independently of viscosity. Ultimately, the background for this is the extremely high requirements in submarine construction, with the desire to move almost silently (signature-free) under water, especially since low noise is an essential criterion for a submarine.
- the present valve combination accordingly consists of a pressure compensator, a load-holding valve and a proportional valve, the pistons of which are arranged axially displaceably in bores of one or more housings which contain the inlet and outlet spaces.
- the proportional valve is equipped with a hollow piston, the load holding valve and the pressure compensator for reducing the main part of the excess energy being provided with pistons with laminar disk stacks.
- the connecting sections in the pistons of the pressure compensator and the load holding valve on the outlet side consist of a large number of radial slots and on the inlet side of eccentrically arranged axial channels, the medium entering the inlet chamber through the axial holes in the laminar disc stack and radially exits through the slots in the drain chamber.
- the combination of hollow piston and laminar disc piston according to the invention is achieved that the energy reduction takes place in such a way that on the one hand the noise-reducing Effect of the laminar discs at the point of greatest energy loss - namely in the pressure compensator and in the load holding valve - is achieved and on the other hand, the proportional valve is regulated with a small residual energy reduction can work regardless of the changing viscosity.
- considerable noise minimization is achieved controllability achieved.
- the known from the prior art Proportional valve with disc piston is quiet in itself, but not adjustable. The controllability was achieved with a valve combination, however, the noise reduction was canceled.
- the invention Accordingly, a teaching is presented that has a noise-reducing effect for the various Rule and tax cases enabled.
- valve combination With the valve combination according to the invention the entire range in terms of pressure and viscosity changes covered.
- a significant advantage of the present invention continues to exist in being completely independent of the most varied on the hydraulic drives acting environmental conditions, the other actuators pull, and regardless of the current pressure level in the storage system the hydraulic system (a minimum pressure is required), by equipping the pressure compensator and the load holding valve with laminar disks, the pressure drop between the individual discs and not at Exit occurs, the control and regulation of the drives as quiet as possible.
- the goal of minimizing noise emissions With known solutions, the simultaneously regulated flow can only be used for certain Achieve situations.
- the axial channels of the disks are formed by different bores on different pitch circle diameters and the radial outlet slots are designed with the same or variable width by turning off the disk thickness up to the inner bores.
- the slot width can be generated and / or varied by spacing disks between dislodged disks.
- the radial outlet slots are designed with the same or variable width by milling down to the holes.
- the stack of disks has the same or different slot widths between the disks, depending on the characteristic requirements. The sum of all cross-sections enables a laminar flow of the medium in the stack of laminar discs, the pressure drop not occurring at the transition from the slots to the outlet space, but in the slots between the individual discs.
- the slot width can be generated and / or varied by spacing disks between disks that have not been turned off.
- a piston or slide is created which consists of a large number of joined parts and which can have extremely narrow connecting spaces, but in which the flow flows essentially in a laminar manner.
- the connecting sections of the piston of the proportional valve on the outlet side consist of a large number of differently sized radial bores arranged in several parallel rows on the piston circumference and on the inlet side of at least two central axial bores.
- Pressure compensator, load holding valve and proportional valve are piped together as separate components or combined to form a common control block.
- the control block preferably consists of nodular cast iron or also of other materials, for example of non-magnetic materials.
- the invention described below represents a valve combination - consisting of pressure compensator 1, proportional control slide 2 and load holding valve 3, the aim of which is to operate hydraulic drives - for example cylinders and motors - at the same time in a quiet and controllable manner, and that with strongly changing load pressures at the consumers and at strong changing system pressures such as in storage systems.
- the invention is based on a generally known structure of a controller, as can be seen in FIG. 1.
- the three components of the control system can be piped together as separate components, as shown schematically in FIG. 1a, or else combined to form a common control block, as shown in FIG. 1b.
- the control blocks can be made from the commonly used nodular cast iron as well as from a - magnetic materials for special requirements.
- Figure 2 shows the piston 4 of the pressure compensator 1 or the load-holding valve 3 with laminar disks 6.
- Figure 3 shows a laminar disk 6a in version A.
- Figure 4 shows a laminar disk 6b in version B.
- Figure 5 shows the flow direction of a laminar disk stack 6 made of laminar disks 6a Version A. The arrows indicate the flow of the medium flowing through.
- FIG. 6 shows the proportional valve 2 with a hollow piston 5.
- FIG. 5 shows the direction of flow through the laminar disk stack 6. It is important for the flow that the medium enters the inlet space 7 through the axial bores 8 in the disk stack 6 and exits radially through the gaps 9 into the outlet space 10.
- the example of a laminar disc 6a is shown, in which the axial channels are formed by different bores 8 on different pitch circle diameters, the radial outlet gaps 9 can be designed with variable width by turning off the disc thickness up to the inner bores.
- the gap width can also be generated or varied by spacers between laminar disks that have not been turned.
- 4 shows a disc variant 6b, in which the gaps 9 are produced by milling up to the bores 8.
- the disk stack 6 can also be designed in such a way that different gap widths result between the individual disks.
- the piston of the proportional valve (FIG. 6), on the other hand, is designed as a hollow piston 5, in which the connection between the respective inlet and outlet connections is made via radial bores 5b in the piston and the axial bores 5a and 5a '.
- radial bores 5b in the piston
- 5a ' from P to A or from A to T.
- the bores 5b can have different diameters and are arranged in several parallel rows on the piston circumference to ensure the required flow cross-section.
- the bores result in a smaller wetted surface with turbulent flow, which means that the flow coefficient and thus the flow rate become independent of the oil viscosity and therefore only depend on the pressure difference at the main control piston.
- the pressure difference is determined by the setting of the preload on the spring 11 of the pressure compensator 1. In order to remain quiet in the bores despite the turbulent flow, the pressure difference at the control piston 5 is set correspondingly low at approximately 4 bar.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Valves (AREA)
- Fluid-Driven Valves (AREA)
- Control Of Fluid Pressure (AREA)
- Compressor (AREA)
- Superconductors And Manufacturing Methods Therefor (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Wird z.B. ein Zylinder mit geringem Lastdruck und gleichzeitig mit hohem Systemdruck betrieben, muss das Überangebot an Energie gedrosselt werden und zwar derart, dass die Durchflussmenge im Proportionalsteuerventil trotz wechselndem Differenzdruck konstant bleibt. Das Drosseln des Überangebots an Energie erfolgt an den Steuerkanten der Druckwaage und gegebenenfalls des Lasthalteventils, wobei besonders nachteilig ist, dass sich dabei an diesen Steuerkanten eine erhebliche Geräuschabstrahlung einstellt, umso stärker, je größer die Differenz zwischen Last - und Systemdruck ist.
In der EP 0 253 322 B1 wird ein geräuscharmes Proportionalventil beschrieben, in dem der Energieabbau im Scheibenkolben des Proportionalventils selbst erfolgt. Ein weiteres derartiges Ventil ist aus der US 3 880 399 bekannt. Durch die sich in den Laminarscheibenstapeln einstellende laminare Strömung ist die Durchflussmenge jedoch stark viskositätsabhängig.
Da sich der Ventilkolben in eine vom Ansteuerstrom bestimmte Position und somit auch auf fest vorgegebene Strömungsquerschnitte einstellt, ergeben sich bei sich ändernden System - und Lastdruckverhältnissen und auch bei Viskositätsänderungen durch Temperaturschwankungen zwangsläufig auch unterschiedliche Durchflussmengen. Außerdem wird bei sich ändernden Einsatzfällen ( z.B. Einsatz des Verbrauchers bei abweichendem System - oder Lastdruck ) ein spezieller Kolben erforderlich oder die elektrische Ansteuerung des Proportionalventils muss geändert werden. Wird um die Regelbarkeit zu erreichen diesem Ventil eine Druckwaage in bislang üblicher Ausführung (Figur 7) vorgeschaltet, erfolgt der größte Teil des Energieabbaus unter starker Geräuschentwicklung wiederum in der Druckwaage, während sich die geräuschmindernde Wirkung der Laminarscheiben lediglich auf eine geringe Restdruckdifferenz auswirken kann.
Die vorliegende Ventilkombination besteht demnach aus einer Druckwaage, einem Lasthalteventil und einem Proportionalventil, deren Kolben in Bohrungen eines oder mehrerer Gehäuse, welche die Zu- und Ablaufräume enthalten, axial verschiebbar angeordnet sind. Das Proportionalventil ist erfindungsgemäß mit einem Hohlkolben ausgestattet, wobei das Lasthalteventil und die Druckwaage zum Abbau des Hauptteils des Energieüberschusses mit Kolben mit Laminarscheibenstapeln versehen sind. Besonders wichtig ist dabei, dass die Verbindungsabschnitte in den Kolben bei der Druckwaage und beim Lasthalteventil auf der Ablaufseite aus einer Vielzahl von radialen Schlitzen und auf der Zulaufseite aus außermittig angeordneten axialen Kanälen bestehen, wobei das Medium vom Zulaufraum durch die axialen Bohrungen im Laminarscheibenstapel eintritt und radial durch die Schlitze in den Ablaufraum austritt.
Die Schlitzbreite ist durch Abstandsscheiben zwischen nicht abgedrehten Scheiben erzeugbar und/oder variierbar. Die radialen Austrittsschlitze sind mit gleicher oder variabler Breite durch Ausfräsungen bis zu den Bohrungen gestaltet.
Der Scheibenstapel weist je nach Anforderung an die Charakteristik gleiche oder auch unterschiedliche Schlitzbreiten zwischen den Scheiben auf.
Die Summe aller Querschnitte ermöglicht im Laminarscheibenstapel eine laminare Strömung des Medium, wobei der Druckabfall nicht am Übergang von den Schlitzen zum Austrittsraum, sondern in den Schlitzen zwischen den einzelnen Scheiben erfolgt. In einer anderen Ausführungsform ist die Schlitzbreite durch Abstandsscheiben zwischen nicht abgedrehten Scheiben erzeugbar und/oder variierbar. Auf diese Wiese entsteht ein Kolben oder Schieber, der aus einer Vielzahl zusammengefügter Teile besteht und der äußerst schmale Verbindungsräume besitzen kann, in dem jedoch die Strömung im wesentlichen laminar fließt.
Die Verbindungsabschnitte bestehen beim Kolben des Proportionalventils auf der Ablaufseite aus einer Vielzahl von unterschiedlich großen in mehreren parallelen Reihen am Kolbenumfang angeordneten radialen Bohrungen und auf der Zulaufseite aus mindestens zwei zentrischen axialen Bohrungen.
Druckwaage, Lasthalteventil und Proportionalventil sind als separate Bauteile miteinander verrohrt oder zu einem gemeinsamen Steuerblock zusammengefasst. Der Steuerblock besteht vorzugsweise aus Kugelgraphitguß oder auch aus anderen z.B. aus a- magnetischen Werkstoffen.
- Figur 1:
- Schnittdarstellung der Ventilkombination,
- Figur 1a:
- Ventilkombination in einer Verrohrungsversion,
- Figur 1b:
- Ventilkombination in Blockbauweise,
- Figur 2:
- Kolben der Druckwaage bzw. des Lasthalteventils,
- Figur 3:
- Laminarscheibe in Ausführung A,
- Figur 4:
- Laminarscheibe in Ausführung B,
- Figur 5:
- Durchströmungsrichtung der Laminarscheiben,
- Figur 6:
- Proportionalventil mit Hohlkolben.
- Figur 7:
- Druckwaage in bislang üblicher Ausführung
Die Erfindung geht von einem allgemein bekannten Aufbau einer Steuerung aus, wie aus Figur 1 ersichtlich.
Die drei Bestandteile der Steuerung können als separate Bauteile miteinander verrohrt werden, wie schematisch in Figur 1a dargestellt, oder aber auch zu einem gemeinsamen Steuerblock zusammengefasst werden wie in Figur 1b gezeigt. Die Steuerblöcke können sowohl aus dem üblicherweise verwendeten Kugelgraphitguß als auch bei besonderen Anforderungen aus a - magnetischen Werkstoffen hergestellt werden. Figur 2 zeigt den Kolben 4 der Druckwaage 1 bzw. des Lasthalteventils 3 mit Laminarscheiben 6. Figur 3 zeigt eine Laminarscheibe 6a in Ausführung A. Figur 4 zeigt eine Laminarscheibe 6b in Ausführung B. Figur 5 zeigt die Durchströmungsrichtung eines Laminarscheibenstapels 6 aus Laminarscheiben 6a der Ausführung A. Die Pfeile geben den Strömungsverlauf des durchströmenden Mediums an. Figur 6 zeigt das Proportionalventil 2 mit Hohlkolben 5.
Die Laminarscheibenstapel 6 in der Druckwaage 1 und im Lasthalteventil 3 können verschiedenartig gestaltet und geschichtet sein.
Figur 5 zeigt die Durchströmungsrichtung des Laminarscheibenstapels 6. Wichtig bei der Durchströmung ist, dass das Medium vom Zulaufraum 7 durch die axialen Bohrungen 8 im Scheibenstapel 6 eintritt und radial durch die Spalte 9 in den Ablaufraum 10 austritt.
In Fig. 3 ist das Beispiel einer Laminarscheibe 6a gezeigt, bei der die axialen Kanäle durch unterschiedliche Bohrungen 8 auf verschiedenen Teilkreisdurchmessern gebildet werden, die radialen Austrittsspalte 9 können durch Abdrehen der Scheibendicke bis zu den inneren Bohrungen mit variabler Breite gestaltet werden. Die Spaltbreite kann auch durch Abstandsscheiben zwischen nicht abgedrehten Laminarscheiben erzeugt bzw. variiert werden.
Fig. 4 zeigt eine Scheibenvariante 6b, bei der die Spalte 9 durch Ausfräsungen bis zu den Bohrungen 8 erzeugt werden. Die Scheibenstapel 6 können auch derart gestaltet sein, dass sich unterschiedliche Spaltbreiten zwischen den einzelnen Scheiben ergeben. In jedem Fall ist sichergestellt, dass bei entsprechender Schichtung die Summe aller Querschnitte im Laminarscheibenstapel 6 eine laminare Strömung ermöglicht und dass der Druckabfall in den Spalten zwischen den einzelnen Scheiben erfolgt und nicht am Übergang von den Scheiben in den Ablaufraum 10.
Druckwaage 1 und Lasthalteventil 3 stellen sich in bekannter Weise automatisch auf die augenblickliche Lastdruck - bzw. Systemdrucksituation ein. D.h., im Zusammenwirken der Differenz der auf den beiden Kolbenseiten anstehenden Last - bzw. Systemdrücke und der an der jeweiligen Ventilfeder 11 und 12 eingestellten Vorspannkraft verschieben sich die Kolben 4 selbsttätig in die erforderliche Regelstellung. Somit verbinden - dem erforderlichen Energieabbau entsprechend - mehr oder weniger viele Spalte 9 des Laminarscheibenstapels 6 durch Längsverschiebung der Kolben 4 den Zulaufquerschnitt 7 mit dem Ablaufquerschnitt 10 des Lasthalteventils 3 bzw. der Druckwaage 1.
Der Kolben des Proportionalventils (Fig. 6) dagegen ist als Hohlkolben 5 ausgeführt, bei dem die Verbindung zwischen den jeweiligen Zu - und Ablaufanschlüssen über im Kolben angebrachte radiale Bohrungen 5b und den axialen Bohrungen 5a bzw. 5a' erfolgt. Und zwar je nach Kolbenstellung über 5a von P nach B bzw. von B nach T und über 5a' von P nach A bzw. von A nach T. Die Bohrungen 5b können unterschiedliche Durchmesser aufweisen und sind in mehreren parallelen Reihen am Kolbenumfang angeordnet, um den erforderlichen Strömungsquerschnitt zu gewährleisten. Die Bohrungen ergeben im Gegensatz zu den Laminarscheiben bei gleichem Strömungsquerschnitt eine kleinere benetzte Oberfläche mit turbulenter Strömung, wodurch der Strömungsbeiwert und damit die Durchflussmenge unabhängig von der Ölviskosität wird und somit nur noch von der Druckdifferenz am Hauptsteuerkolben abhängt. Die Druckdifferenz wird von der Einstellung der Vorspannung an der Feder 11 der Druckwaage 1 bestimmt. Um trotz turbulenter Strömung in den Bohrungen geräuscharm zu bleiben, wird die Druckdifferenz am Steuerkolben 5 mit ca. 4 bar entsprechend niedrig eingestellt.
Ein weiterer Vorteil des Einsatzes von Laminarscheiben in Druckwaage und Lasthalteventil besteht darin, dass die Schichtung des Scheibenstapels ( Anzahl, schmale oder breite Spalte mit unterschiedlichen Ausformungen ) noch auf der Baustelle vorgenommen werden kann, um das Gesamtsystem zu optimieren, ohne dass eine mechanische Bearbeitung am Hauptsteuerkolben zu erfolgen hat. Wichtig für die Austauschbarkeit der Scheiben ist lediglich, dass Lage und Durchmesser der axialen Bohrungen übereinstimmen, da es sonst zu Querschnittsverengungen bzw. zu Strömungsumlenkungen kommt.
- 1-
- Druckwaage
- 2-
- Proportionalventil
- 3-
- Lasthalteventil
- 4-
- Scheibenkolben
- 5-
- Hohlkolben
- 5a,5a'-
- axiale Bohrungen im Hohlkolben
- 5b-
- radiale Bohrungen im Hohlkolben
- 6-
- Laminarscheiben bzw. Laminarscheibenstapel
- 6a-
- Laminarscheibe Ausführung A
- 6b-
- Laminarscheibe Ausführung B
- 7-
- Zulaufraum für das Medium
- 8-
- axiale Bohrung in den Laminarscheiben bzw. im Scheibenstapel
- 9-
- Austrittsschlitze
- 10-
- Ablaufraum für das Medium
- 11-
- Ventilfeder der Druckwaage
- 12-
- Ventilfeder des Lasthalteventils
- 13-
- Tankleitung
- 14-
- Druckleitung
- Z-
- Zulaufrichtung des Mediums
- A-
- Ablaufrichtung des Mediums
Claims (12)
- Ventilkombination für eine geräuscharme und regelbare Hydrauliksteuerung, bestehend aus einer Druckwaage, einem Lasthalteventil und einem Proportionalventil, deren Kolben in Bohrungen eines oder mehrerer Gehäuse, welche die Zu- und Ablaufräume enthalten, axial verschiebbar angeordnet sind, dadurch gekennzeichnet, dass das Proportionalventil (2) mit einem Hohlkolben (5) ausgestattet ist und das Lasthalteventil (3) und die Druckwaage (1) zum Abbau des Hauptteils des Energieüberschusses mit Kolben (4) mit Laminarscheibenstapeln (6) versehen sind, wobei die Verbindungsabschnitte in den Kolben bei der Druckwaage (1) und beim Lasthalteventil (2) auf der Ablaufseite aus einer Vielzahl von radialen Schlitzen und auf der Zulaufseite aus außermittig angeordneten axialen Kanälen bestehen.
- Ventilkombination nach Anspruch 1, dadurch gekennzeichnet, dass das Medium in die Kolben von Druckwaage (1) und Lasthalteventil (2) vom Zulaufraum (7) durch die axialen Bohrungen (8) im Laminarscheibenstapel (6) eintritt und radial durch die Schlitze (9) in den Ablaufraum (10) austritt.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass die axialen Kanäle der Laminarscheiben (6) durch unterschiedliche Bohrungen (8) auf verschiedenen Teilkreisdurchmessern gebildet werden und die radialen Austrittsschlitze (9) durch Abdrehen der Scheibendicke bis zu den inneren Bohrungen (8) mit gleicher oder variabler Breite gestaltet sind.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass die Schlitzbreite durch Abstandsscheiben zwischen nicht abgedrehten Scheiben erzeugbar und/oder variierbar ist.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass die radialen Austrittsschlitze (9) mit gleicher oder variabler Breite durch Ausfräsungen bis zu den Bohrungen (8) gestaltet sind.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass der Laminarscheibenstapel (6) gleiche und/oder unterschiedliche Schlitzbreiten zwischen den Scheiben aufweist.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass die Summe aller Querschnitte im Laminarscheibenstapel (6) eine laminare Strömung des Medium ermöglicht, wobei der Druckabfall nicht am Übergang von den Schlitzen zum Austrittsraum, sondern in den Schlitzen zwischen den einzelnen Scheiben erfolgt.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, die Verbindungsabschnitte beim Hohlkolben (5) des Proportionalventils (2) auf der Ablaufseite aus einer Vielzahl von unterschiedlich großen in mehreren parallelen Reihen am Kolbenumfang angeordneten radialen Bohrungen (5b) und auf der Zulaufseite aus mindestens zwei zentrischen axialen Bohrungen (5a,5a') bestehen.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass Druckwaage (1), Lasthalteventil (3)und Proportionalventil (2) als separate Bauteile miteinander verrohrt sind.
- Ventilkombination nach einem der obigen Ansprüche, dadurch gekennzeichnet, dass Druckwaage (1), Lasthalteventil (3) und Proportionalventil (2) zu einem gemeinsamen Steuerblock zusammengefasst sind.
- Ventilkombination nach Anspruch 10, dadurch gekennzeichnet, dass der Steuerblock aus Kugelgraphitguß besteht.
- Ventilkombination nach Anspruch 10, dadurch gekennzeichnet, dass der Steuerblock aus a- magnetischen Werkstoffen besteht.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10211299A DE10211299B4 (de) | 2002-03-14 | 2002-03-14 | Ventilkombination |
DE10211299 | 2002-03-14 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1344945A2 true EP1344945A2 (de) | 2003-09-17 |
EP1344945A3 EP1344945A3 (de) | 2004-06-16 |
EP1344945B1 EP1344945B1 (de) | 2006-10-25 |
Family
ID=27762919
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03090044A Expired - Lifetime EP1344945B1 (de) | 2002-03-14 | 2003-02-20 | Ventilkombination |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1344945B1 (de) |
AT (1) | ATE343727T1 (de) |
DE (2) | DE10211299B4 (de) |
ES (1) | ES2272889T3 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8042451B2 (en) | 2004-11-08 | 2011-10-25 | Kabushiki Kaisha Toyota Jidoshokki | Hydraulic control apparatus |
CN106855070A (zh) * | 2016-12-19 | 2017-06-16 | 武汉船用机械有限责任公司 | 一种比例流量插装阀及其控制方法 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10321914A1 (de) | 2003-05-15 | 2004-12-02 | Bosch Rexroth Ag | Hydraulische Steueranordnung |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3880399A (en) | 1974-04-01 | 1975-04-29 | Fisher Controls Co | Multistage noise reducing flow control valve |
EP0253322B1 (de) | 1986-07-12 | 1990-06-20 | Howaldtswerke-Deutsche Werft Ag | Geräuscharmes Hydraulik-Ventil |
DE19547687A1 (de) | 1995-12-20 | 1997-06-26 | Rexroth Mannesmann Gmbh | Hydraulischer Antrieb, insbesondere für ein Ruder eines Schiffes |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4018245A (en) * | 1975-11-12 | 1977-04-19 | Baumann Hans D | Perforated valve trim and method for producing the same |
DE29716577U1 (de) * | 1997-09-15 | 1997-11-13 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Lasthalteventil |
-
2002
- 2002-03-14 DE DE10211299A patent/DE10211299B4/de not_active Expired - Fee Related
-
2003
- 2003-02-20 ES ES03090044T patent/ES2272889T3/es not_active Expired - Lifetime
- 2003-02-20 EP EP03090044A patent/EP1344945B1/de not_active Expired - Lifetime
- 2003-02-20 DE DE50305457T patent/DE50305457D1/de not_active Expired - Lifetime
- 2003-02-20 AT AT03090044T patent/ATE343727T1/de not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3880399A (en) | 1974-04-01 | 1975-04-29 | Fisher Controls Co | Multistage noise reducing flow control valve |
EP0253322B1 (de) | 1986-07-12 | 1990-06-20 | Howaldtswerke-Deutsche Werft Ag | Geräuscharmes Hydraulik-Ventil |
DE19547687A1 (de) | 1995-12-20 | 1997-06-26 | Rexroth Mannesmann Gmbh | Hydraulischer Antrieb, insbesondere für ein Ruder eines Schiffes |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8042451B2 (en) | 2004-11-08 | 2011-10-25 | Kabushiki Kaisha Toyota Jidoshokki | Hydraulic control apparatus |
CN106855070A (zh) * | 2016-12-19 | 2017-06-16 | 武汉船用机械有限责任公司 | 一种比例流量插装阀及其控制方法 |
CN106855070B (zh) * | 2016-12-19 | 2018-07-31 | 武汉船用机械有限责任公司 | 一种比例流量插装阀及其控制方法 |
Also Published As
Publication number | Publication date |
---|---|
EP1344945B1 (de) | 2006-10-25 |
ES2272889T3 (es) | 2007-05-01 |
EP1344945A3 (de) | 2004-06-16 |
DE10211299B4 (de) | 2005-03-31 |
DE10211299A1 (de) | 2003-10-09 |
DE50305457D1 (de) | 2006-12-07 |
ATE343727T1 (de) | 2006-11-15 |
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