EP2488764B1 - Valve system - Google Patents
Valve system Download PDFInfo
- Publication number
- EP2488764B1 EP2488764B1 EP10768695.8A EP10768695A EP2488764B1 EP 2488764 B1 EP2488764 B1 EP 2488764B1 EP 10768695 A EP10768695 A EP 10768695A EP 2488764 B1 EP2488764 B1 EP 2488764B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- pilot
- pressure medium
- piston
- 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.)
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Links
- 230000006835 compression Effects 0.000 claims description 14
- 238000007906 compression Methods 0.000 claims description 14
- 239000012530 fluid Substances 0.000 claims description 11
- 230000000694 effects Effects 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000004146 energy storage Methods 0.000 description 2
- 230000002706 hydrostatic effect Effects 0.000 description 2
- 230000036316 preload Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
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
- F15B11/02—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
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
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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
- F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
- F15B2211/40—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
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
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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
- F15B2211/50—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
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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
- Y10T137/86582—Pilot-actuated
-
- 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
Definitions
- the invention relates to a valve arrangement for pressure control of a pressure medium from a pressure medium pump to at least a first consumer, with a pilot operated pressure control valve, acted upon by the pressure medium main piston and a pilot piston, wherein a pressure space between a piston rear side of the main piston and the pilot piston can be relieved.
- LS load-sensing pressure from the load tap of the consumer in a pressure chamber after the Pilot piston is present.
- the pump pressure can be essentially compared with the spring preload on the control piston plus the pressure at the load (LS) and at
- the DE 103 22 585 A1 describes, for example, a valve arrangement for pressure control of a pressure medium from a pressure medium pump to a consumer, wherein a main control valve may be hydraulically controlled by a pilot valve.
- a modular valve system with at least one valve housing having at its opposite ends both inside and outside the circumference and inside the housing standardized nominal sizes for attaching further valve components.
- Such valve components may be a valve piston, an energy store, a pilot valve and at least one fluid port for defining the valve assembly formed in the manner of a Einschraubpatrone in an environment.
- the DE 10 2005 059 240 A1 shows and describes a hydrostatic drive system with a variable-stroke pressure medium pump, which supplies a consumer with pressure medium via control valves.
- a variable-stroke pressure medium pump which supplies a consumer with pressure medium via control valves.
- serving as a recirculation pressure compensator is set to a minimum control pressure difference.
- the pressure medium pump is set to a minimum delivery volume, wherein the pressure medium flow coming from the pressure medium pump via the pressure compensator flows with low power losses to a pressure medium container.
- a valve with a pump, a tank and a user port is disclosed.
- a valve piston can be moved in the valve housing and separates the pump connection from the tank connection in a blocking position.
- the fluid flow is between Pump connection and user connection adjustable in the sense of a reduction of the fluid flow by a constant value.
- the hydraulic drive system builds complex and has no minimized pressure losses.
- the DE 689 08 317 T2 describes a pressure control valve, the main valve of a pilot valve, which is arranged in a common valve housing, is piloted.
- the present invention seeks to provide a valve arrangement for pressure control of a pressure medium, which allows a further minimization of the pressure loss when no consumer is connected. This object is achieved with a valve assembly having the features of claim 1 in its entirety.
- a valve arrangement for pressure control of a pressure medium is provided by a pressure medium pump to a consumer, which provides a pilot-operated pressure control valve with a spring-loaded main piston.
- a pilot piston which controls a valve seat for a fluid-carrying connection to a back pressure chamber of the main piston, is part of the pressure control valve.
- the piston-back pressure chamber of the main piston is pressurized by the pump pressure via a first throttle in the main piston, so that the circulating pressure compensator thus formed allows a comparison between the pump pressure and the pressure at the load tap plus the spring preloads of the main control piston and the pilot piston.
- a by the respective set spring voltages higher pressure of the pressure medium pump than the pressure at the load tap of the consumer turns it.
- the invention is further provided to arrange a relief valve for the space between the main piston and pilot piston.
- the relief valve is formed as a valve or poppet valve, wherein a valve element of the relief valve is arranged such that there is no pressure of the Lastabgriffs, which corresponds to an inoperative position of the consumer, a pressure medium flow from the space between the main piston and pilot piston to a pressure medium tank, tank or in the LS line allows.
- the relief valve When operating in non-pressurized circulation, the relief valve is open and the main valve can also be opened. The pilot valve is closed.
- the relief valve according to the invention thus enables a substantial reduction of the pressure losses of the valve assembly in comparison to the known circuits of circulation pressure compensators.
- pressure medium can be discharged from the pressure medium connection of the pressure control valve via a first throttle and via the relief valve to the pressure medium container.
- Pressure medium can be guided to the relief valve via a longitudinal channel between the pressure chamber of the main piston and a further second pressure chamber, which is effetbar by the pilot piston.
- the longitudinal channel has a further, second throttle.
- the second throttle divides the longitudinal channel into two channel sections one.
- a first channel section is in this case assigned to the pressure chamber of the main piston.
- a second channel portion of the longitudinal channel is fluidly associated with the second pressure chamber, which is Wegfahrbar by the pilot piston.
- the second throttle can serve as an attenuator for the relief valve.
- the relief valve is arranged in the housing of the pressure regulating valve.
- the valve element of the relief valve is in this case guided axially movable in a longitudinal bore.
- Via at least one annular recess in the housing of the pressure regulating valve or in the valve element of the relief valve, a fluid-conducting connection to the one or the other channel portion of the longitudinal channel in at least one displacement position of the valve element can be produced.
- the valve element of the relief valve is preferably biased by means of an energy accumulator (compression spring) in the direction of the second pressure chamber, which is passable by the pilot piston.
- the pilot piston of the pilot valve can in this case control a fluid-conducting connection between a load tap LS and a free, the energy storage opposite side of the valve element of the relief valve.
- the valve element of the relief valve blocks a fluid-conducting connection between the pressure chamber of the main piston and the pressure fluid reservoir.
- valve element of the relief valve In the case of a consumer inoperative position, however, and an LS pressure approaching zero, the valve element of the relief valve, on the other hand, is brought under the action of the energy accumulator into a displacement position in which a direct fluid-conducting connection between the pressure chamber of the main piston via the relief valve to the pressure medium container is opened. Pressure fluid flows through the annular recess on the relief valve.
- the annular recess in the housing or in the valve element opens into the second channel section of the longitudinal channel between the pressure control valve and the pilot valve
- the annular recess is connected in a fluid-conducting manner to the second pressure chamber of the pilot piston or of the pressure chamber which can be passed through by the pilot piston.
- the relief valve can be arranged in parallel arrangement to the pressure control valve between a pressure medium pump and the pressure medium container.
- the relief valve may be directly precontrolled, but it may also be advantageous to form the relief valve as an electrically operable 2/2-way valve, which is driven, for example, by a pressure signals of a pressure sensor processing control and / or regulating device.
- In the 1a is a closed, hydraulic circuit of a valve assembly 1, with a constant-pressure medium pump 3 for supplying a consumer 4 with pressure medium 2.
- the consumer 4 is shown as a hydraulic motor with two possible directions of flow.
- the consumer 4 is driven via an electrically operated 4/3-way valve 19.
- This valve control is a 2/2-way valve 20 upstream with pressure limiting function in the open switching position.
- a hydraulic system In the in 1a shown embodiment of a hydraulic system are two consumers 4, each with identical valve control technology connected in parallel, which can be powered by the constant-pressure medium pump 3. At this point, the operation of the thus formed valve control block for the consumer 4 will not be discussed in more detail, since this is known from the prior art ago sufficiently.
- the hydraulic system provides a constant-pressure fluid pump 3 as a cheaper alternative to a variable, but requires control of their flow to operate the consumer 4 with a predetermined speed can. It requires a flow control valve, in particular a pressure control valve, which overall represents a simpler overall solution, which is incidentally more cost-effective than that which results when using a variable displacement pump.
- Fig. 1a is to represent a load-independent constant speed of both consumers 4, a single pressure control valve 5 with a feedforward under consideration of a load tap LS for both consumers 4 is provided.
- the load tap LS is in each case initially separated at each changeover valve 18 for each consumer 4.
- a check valve 22 is in each case connected in the hydraulic circuit before each shuttle valve 18.
- Each check valve 22 has the same set opening pressure and opens in the direction of the pressure control valve 5, in particular in the direction of its load-sensing connection LS.
- the main piston 6 is longitudinally displaceably guided in a bore 29 of the housing 12 in a main valve control section.
- the main piston 6 controls a centrally and axially guided into the housing 12 pressure medium inlet 30.
- a possible fluid-conducting connection to a radially out of the housing 12 guided pressure medium connection 31, which optionally consists of a plurality of radially arranged passage holes in the housing 12 and is connectable to a pressure medium tank 11, from which the pressure medium pump 3 takes pressure fluid for the hydraulic circuit made become.
- the main valve 23 is designed with respect to its effective cross-section such that the entire volume flow of pressure medium 2 can be directed from the constant-pressure medium pump 3 to the pressure medium tank 11.
- a first throttle 13 is arranged in the form of a through hole or bore with a definable diameter in its piston crown. This makes it possible that the pressure on the pump side is reported to the piston rear side 9 of the main piston 6.
- the main piston 6 is formed substantially as a cylindrical sleeve with a piston crown as a fluid separation, so that on the piston rear side 9 a cup-shaped pressure chamber 8 is formed, which serves for centering and receiving the compression spring 24 and the further pressure medium 2 can accommodate.
- a bore 32 with a diameter of about 1/5 of the guided in the valve housing 12 main piston 6 is centrally mounted.
- the bore 32 has a second, second throttle 14 approximately at its axial center.
- the bore 32 is divided into a first channel section 32 'and a second channel section 32 " Fig. 1b, d and f in particular details I, the first channel section 32 'is associated with the pressure chamber 8 of the main valve 23, while the second channel section 32''is associated with a second pressure chamber 35, which is passable by the pilot piston 7.
- the pilot piston 7 in turn is formed as a flat disc with a centering aid 33 in the form of a truncated cone for a compression spring 26.
- the pilot piston 7 is acted upon by the force of the compression spring 26, which is supported with radial play in a bore 34 for the pilot piston 7 and the compression spring 26.
- the piston front side, second pressure chamber 35 is the same pressure chamber as the space 34, in which the compression spring 26 is introduced. So far there is no need for poetry.
- the space 34 of the pilot valve piston 7 opens a, the housing wall of the housing 12 traversing hole 36 for the load tap LS of the consumer 4.
- the Flow pressure of the pilot valve 25 results from the pressure defined by the compression spring 26 plus the pressure at the load tap LS.
- the pilot valve 25 opens and due to the main valve 23 and pressure medium can via the main valve 23 to the pressure fluid container 11th flow away.
- the pressure control valve 5 is additionally the relief valve 10 with a valve element 27 arranged in an axial region A in a longitudinal bore 40 movable between the pilot valve 25 and the main valve 23, in particular is connected in parallel.
- the relief valve 10, which in its integration into the housing 12 in an enlarged view in the Fig.1b, d and f is shown is radially laterally offset from a longitudinal axis 37 of the valve housing 12 and has an approximately same diameter as the bore 32 formed by the load bore above and below the second throttle 14.
- a valve element 27 or a relief valve piston is at an upper stop abutting shown, to which it terminates approximately flush with the end of the bore 34 for receiving the pilot piston 7.
- the relief valve piston is spring-loaded at its opposite end face in the sense of an open position of a smaller energy storage 28, a compression spring, which applies, for example, a flow pressure of 0.5 bar.
- annular recess 41 which is formed as an annular groove 38 in the periphery of the relief valve piston, is provided.
- the valve assembly 1 communicates the ring recess 41 each with the first channel portion 32 'of the bore 32. If now on the load tap side of the pilot valve piston 7 and thus on the side facing away from the compression spring 28 no pressure on the load tap LS more, so takes the relief valve piston in the 1a . 1e and 1f shown position. The annular groove 38 thereby comes into coincidence with an associated opening 39 of the bore 34.
- Pressure medium can thus from the pressure chamber 8 on the piston rear side 9 of the main piston 6 via the bore 32, the opening 39 and communicating with the opening connecting line 42 in the housing 12th are guided over the annular groove 38 to a departure 15 of the relief valve 10.
- the pressure medium 2 then flows without pressure so far, without the pressure medium pump 3 must promote against the set pressure on the pilot valve 25.
- the relief valve piston moves against the spring force of its compression spring 26th in the in Figure 1C and 1 d shown position in which there is no overlap of the opening 39, the connecting line 42 with the annular groove 38.
- the pressure control valve 5 is then in its above-described control operation without being influenced by the relief valve 10th
- the 1E and 1f Again, in a schematic, not to scale longitudinal section one opposite the 1a . 1b . 1c and 1d modified variant of a valve assembly 1, in turn, combined in a housing 12 of the pressure control valve 5 with a so far offset opening 39 that ensures that the outflow of the pressure medium 2 from the pressure chamber 8 takes place in the LS line.
- the opening 39 is associated with the second channel portion 32 " Throttle 14 acts as a damping effect on the entire operation of the valve assembly 1, in particular on the main piston. 6
- Fig.2 and 3 show the interconnection of the three valves 10, 23 and 25 with a pressure medium tap according to the solutions of the 1a and 1c , In this way, the valve arrangement 1 according to the invention can be realized even in a dissolved valve design.
- Fig. 4 and 5 show one to the Figure 3 comparable circuit diagram, wherein the relief valve 10 as a 2/2-way valve 16, but designed for the entire volume flow of the pressure medium pump 3 may be formed.
- the relief valve can be integrated as a rule small constructive valve in an existing pressure control valve. It is advantageous in this respect to arrange the relief valve axially between the pilot valve and the main valve, wherein a valve piston of the relief valve can be inserted from the pilot valve side into a housing of the pressure regulating valve. It can thereby also make the main bore for the relief valve from the same valve side as a throttle between the pressure chamber and the pilot valve.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Description
Die Erfindung betrifft eine Ventilanordnung zur Druckregelung eines Druckmittels von einer Druckmittelpumpe zu zumindest einem ersten Verbraucher, mit einem vorgesteuerten Druckregelventil, mit einem von dem Druckmittel beaufschlagten Hauptkolben und einem Vorsteuerkolben, wobei ein Druckraum zwischen einer Kolbenrückseite des Hauptkolbens und dem Vorsteuerkolben entlastet werden kann.The invention relates to a valve arrangement for pressure control of a pressure medium from a pressure medium pump to at least a first consumer, with a pilot operated pressure control valve, acted upon by the pressure medium main piston and a pilot piston, wherein a pressure space between a piston rear side of the main piston and the pilot piston can be relieved.
Will man die Verfahrgeschwindigkeit eines Hydrozylinders oder die Drehzahl eines Hydromotors unabhängig von der an einem Stromventil herrschenden Druckdifferenz und unabhängig von Temperatur oder Viskosität eines dafür verwendeten Druckmittels und weiter unabhängig von der zu bewegenden Last konstant halten, so kommen regelmäßig sog. Druckregelventile zum Einsatz. Dabei wird der nicht durch das Druckregelventil gelenkte Druckmittelstrom unter relativ großen Leistungs- und Druckverlusten für eine Druckmittelpumpe über ein Druckbegrenzungsventil abgeführt.If you want to keep the travel speed of a hydraulic cylinder or the speed of a hydraulic motor regardless of the prevailing at a flow control valve pressure and regardless of temperature or viscosity of a pressure medium used for this purpose and further independent of the load to be moved, so-called. Pressure control valves are used regularly. In this case, the pressure medium flow which is not directed by the pressure regulating valve is discharged via a pressure limiting valve under relatively large power and pressure losses for a pressure medium pump.
Um solche Leistungsverluste zu minimieren, ist es bekannt, ein als Druckwaage arbeitendes Druckregelventil mit einem Lastabgriff an einem Verbraucher, etwa eines Hydrozylinders derart zu verknüpfen, dass der sog. LS(Load-Sensing)-Druck vom Lastabgriff des Verbrauchers in einem Druckraum nach dem Vorsteuerkolben ansteht. Insbesondere dadurch läßt sich der Pumpendruck im Wesentlichen mit der Federvorspannung am Steuerkolben zuzüglich des Druckes am Verbraucher (LS) vergleichen und beiIn order to minimize such power losses, it is known to link a working as a pressure compensator pressure control valve with a load on a consumer, such as a hydraulic cylinder such that the so-called. LS (load-sensing) pressure from the load tap of the consumer in a pressure chamber after the Pilot piston is present. In particular, the pump pressure can be essentially compared with the spring preload on the control piston plus the pressure at the load (LS) and at
einer Außerbetriebstellung des Verbrauchers das Druckmittel mit weniger Energieverlust als beim Einsatz mit einem Druckbegrenzungsventil abführen. Der Leistungsverlust solcher bekannter vorgesteuerter Druckregelventile mit Druckwaagenfunktion ist jedoch nicht vollständig zu vermeiden.an inoperative position of the consumer dissipate the pressure medium with less energy loss than when used with a pressure relief valve. However, the power loss of such known pilot-operated pressure control valves with pressure compensator function can not be completely avoided.
Die
Die
In der
Das hydraulische Antriebssystem baut komplex und weist keine minimierten Druckverluste auf.The hydraulic drive system builds complex and has no minimized pressure losses.
Die
Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine Ventilanordnung zur Druckregelung eines Druckmittels anzugeben, die eine weitere Minimierung des Druckverlustes, wenn kein Verbraucher geschaltet ist, ermöglicht. Diese Aufgabe wird mit einer Ventilanordnung mit den Merkmalen des Patentanspruches 1 in seiner Gesamtheit gelöst.Based on this prior art, the present invention seeks to provide a valve arrangement for pressure control of a pressure medium, which allows a further minimization of the pressure loss when no consumer is connected. This object is achieved with a valve assembly having the features of
Erfindungsgemäß ist eine Ventilanordnung zur Druckregelung eines Druckmittels von einer Druckmittelpumpe zu einem Verbraucher vorgesehen, die ein vorgesteuertes Druckregelventil mit einem federbelasteten Hauptkolben vorsieht. Ein Vorsteuerkolben, der einen Ventilsitz für eine fluidführende Verbindung an einem rückseitigen Druckraum des Hauptkolbens steuert, ist Bestandteil des Druckregelventils. Der kolbenrückseitige Druckraum des Hauptkolbens ist über eine erste Drossel im Hauptkolben vom Pumpendruck druckbeaufschlagt, so dass die derart gebildete Umlaufdruckwaage einen Vergleich zwischen dem Pumpendruck und dem Druck am Lastabgriff plus der Federvorspannungen des Hauptsteuerkolbens und des Vorsteuerkolbens erlaubt. Ein um die jeweiligen eingestellten Federspannungen höherer Druck der Druckmittelpumpe als der Druck am Lastabgriff des Verbrauchers stellt sich dabei ein. Erfindungsgemäß ist ferner vorgesehen, ein Entlastungsventil für den Raum zwischen Hauptkolben und Vorsteuerkolben anzuordnen.According to the invention a valve arrangement for pressure control of a pressure medium is provided by a pressure medium pump to a consumer, which provides a pilot-operated pressure control valve with a spring-loaded main piston. A pilot piston, which controls a valve seat for a fluid-carrying connection to a back pressure chamber of the main piston, is part of the pressure control valve. The piston-back pressure chamber of the main piston is pressurized by the pump pressure via a first throttle in the main piston, so that the circulating pressure compensator thus formed allows a comparison between the pump pressure and the pressure at the load tap plus the spring preloads of the main control piston and the pilot piston. A by the respective set spring voltages higher pressure of the pressure medium pump than the pressure at the load tap of the consumer turns it. The invention is further provided to arrange a relief valve for the space between the main piston and pilot piston.
Das Entlastungsventil ist als Schieber- oder Sitzventil gebildet, wobei ein Ventilelement des Entlastungsventils derart angeordnet ist, dass es bei keinem Druck des Lastabgriffs, der einer Außerbetriebstellung des Verbrauchers entspricht, einen Druckmittelfluss von dem Raum zwischen Hauptkolben und Vorsteuerkolben an einen Druckmittelbehälter, Tank oder in die LS-Leitung ermöglicht. Beim Betrieb im drucklosen Umlauf ist das Entlastungsventil geöffnet und ebenso kann das Hauptventil geöffnet sein. Das Vorsteuerventil ist dabei geschlossen.The relief valve is formed as a valve or poppet valve, wherein a valve element of the relief valve is arranged such that there is no pressure of the Lastabgriffs, which corresponds to an inoperative position of the consumer, a pressure medium flow from the space between the main piston and pilot piston to a pressure medium tank, tank or in the LS line allows. When operating in non-pressurized circulation, the relief valve is open and the main valve can also be opened. The pilot valve is closed.
Steigt der Druck am Lastabgriff allerdings über einen eingestellten Wert an dem Entlastungsventil an, so schließt das Entlastungsventil den dergestalt gebildeten Bypass und ermöglicht eine Load-Sensing-geregelte Funktion des Druckregelventils gemäß dem bekannten Stand der Technik. Haupt- und Vorsteuerventil sind dabei in Regelposition.However, if the pressure at the load tap increases above a set value at the relief valve, then the relief valve closes the bypass formed in this way and permits a load-sensing-controlled function of the pressure regulating valve according to the known prior art. Main and pilot valve are in control position.
Das erfindungsgemäße Entlastungsventil ermöglicht somit eine wesentliche Reduzierung der Druckverluste der Ventilanordnung im Vergleich zu den bekannten Schaltungen von Umlaufdruckwaagen.The relief valve according to the invention thus enables a substantial reduction of the pressure losses of the valve assembly in comparison to the known circuits of circulation pressure compensators.
In einer Verfahrstellung des Ventilelements des Entlastungsventils kann Druckmittel vom Druckmittelanschluss des Druckregelventils kommend über eine erste Drossel und über das Entlastungsventil zu dem Druckmittelbehälter abgeführt werden. Druckmittel kann hierbei über einen Längskanal zwischen dem Druckraum des Hauptkolbens und einem weiteren zweiten Druckraum, der vom Vorsteuerkolben durchfahrbar ist, an das Entlastungsventil geführt werden. In einem besonders bevorzugten Ausführungsbeispiel der Ventilanordnung weist der Längskanal eine weitere, zweite Drossel auf. Dabei teilt die zweite Drossel den Längskanal in zwei Kanalabschnitte ein. Ein erster Kanalabschnitt ist hierbei dem Druckraum des Hauptkolbens zugeordnet. Ein zweiter Kanalabschnitt des Längskanals ist dem zweiten Druckraum, der vom Vorsteuerkolben durchfahrbar ist, fluidisch zugeordnet. Die zweite Drossel kann als Dämpfungsglied für das Entlastungsventil dienen. In einem besonders bevorzugten Ausführungsbeispiel ist das Entlastungsventil im Gehäuse des Druckregelventils angeordnet. Das Ventilelement des Entlastungsventils ist hierbei axial verfahrbar in einer Längsbohrung geführt. Über mindestens eine Ringausnehmung im Gehäuse des Druckregelventils oder im Ventilelement des Entlastungsventils ist eine fluidführende Verbindung zu dem einen oder anderen Kanalabschnitt des Längskanals in zumindest einer Verfahrstellung des Ventilelements herstellbar.In a displacement position of the valve element of the relief valve, pressure medium can be discharged from the pressure medium connection of the pressure control valve via a first throttle and via the relief valve to the pressure medium container. Pressure medium can be guided to the relief valve via a longitudinal channel between the pressure chamber of the main piston and a further second pressure chamber, which is durchfahrbar by the pilot piston. In a particularly preferred embodiment of the valve arrangement, the longitudinal channel has a further, second throttle. In this case, the second throttle divides the longitudinal channel into two channel sections one. A first channel section is in this case assigned to the pressure chamber of the main piston. A second channel portion of the longitudinal channel is fluidly associated with the second pressure chamber, which is durchfahrbar by the pilot piston. The second throttle can serve as an attenuator for the relief valve. In a particularly preferred embodiment, the relief valve is arranged in the housing of the pressure regulating valve. The valve element of the relief valve is in this case guided axially movable in a longitudinal bore. Via at least one annular recess in the housing of the pressure regulating valve or in the valve element of the relief valve, a fluid-conducting connection to the one or the other channel portion of the longitudinal channel in at least one displacement position of the valve element can be produced.
Das Ventilelement des Entlastungsventils ist bevorzugt mit Hilfe eines Energiespeichers (Druckfeder) in Richtung des zweiten Druckraumes, der von dem Vorsteuerkolben durchfahrbar ist, vorgespannt. Der Vorsteuerkolben des Vorsteuerventils kann hierbei eine fluidführende Verbindung zwischen einem Lastabgriff LS und einer freien, dem Energiespeicher gegenüberliegenden Seite des Ventilelementes des Entlastungsventils ansteuern. Bei Teillast- oder Vollastbetrieb eines mit Hilfe des Druckregelventils geregelten Verbrauchers und einem entsprechenden LS-Druck sperrt das Ventilelement des Entlastungsventils eine fluidführende Verbindung zwischen dem Druckraum des Hauptkolbens und dem Druckmittelbehälter. Bei einer Außerbetriebstellung eines Verbrauchers hingegen und einem gegen Null gehenden LS-Druck wird das Ventilelement des Entlastungsventils hingegen unter Wirkung des Energiespeichers in eine Verfahrposition gebracht, in der eine direkte fluidführende Verbindung zwischen dem Druckraum des Hauptkolbens über das Entlastungsventil zu dem Druckmittelbehälter geöffnet ist. Druckmittel fließt hierbei über die Ringausnehmung an dem Entlastungsventil.The valve element of the relief valve is preferably biased by means of an energy accumulator (compression spring) in the direction of the second pressure chamber, which is passable by the pilot piston. The pilot piston of the pilot valve can in this case control a fluid-conducting connection between a load tap LS and a free, the energy storage opposite side of the valve element of the relief valve. In part-load or full load operation of a regulated by means of the pressure control valve load and a corresponding LS-pressure, the valve element of the relief valve blocks a fluid-conducting connection between the pressure chamber of the main piston and the pressure fluid reservoir. In the case of a consumer inoperative position, however, and an LS pressure approaching zero, the valve element of the relief valve, on the other hand, is brought under the action of the energy accumulator into a displacement position in which a direct fluid-conducting connection between the pressure chamber of the main piston via the relief valve to the pressure medium container is opened. Pressure fluid flows through the annular recess on the relief valve.
Bei einer Ventillösung, bei der die Ringausnehmung im Gehäuse oder im Ventilelement in den zweiten Kanalabschnitt des Längskanals zwischen dem Druckregelventil und dem Vorsteuerventil mündet, ist die Ringausnehmung an dem zweiten Druckraum des Vorsteuerkolbens bzw. des von dem Vorsteuerkolben durchfahrbaren Druckraums fluidführend angebunden.In a valve solution in which the annular recess in the housing or in the valve element opens into the second channel section of the longitudinal channel between the pressure control valve and the pilot valve, the annular recess is connected in a fluid-conducting manner to the second pressure chamber of the pilot piston or of the pressure chamber which can be passed through by the pilot piston.
Anstelle einer integrierten Bauweise von Vorsteuerventil, Hauptventil und Entlastungsventil ist auch eine dezentrale Einzelanordnung der genannten Ventile zu einer erfindungsgemäßen Gesamtventilanordnung möglich. Das Entlastungsventil läßt sich dabei in paralleler Anordnung zu dem Druckregelventil zwischen einer Druckmittelpumpe und dem Druckmittelbehälter anordnen. Das Entlastungsventil kann direkt vorgesteuert sein, es kann aber auch vorteilhaft sein, das Entlastungsventil als elektrisch betätigbares 2/2-Wege-Ventil auszubilden, welches beispielsweise von einer Drucksignale eines Drucksensors verarbeitenden Steuer- und/oder Regelungseinrichtung angesteuert ist.Instead of an integrated design of pilot valve, main valve and relief valve and a decentralized individual arrangement of said valves to a total valve arrangement according to the invention is possible. The relief valve can be arranged in parallel arrangement to the pressure control valve between a pressure medium pump and the pressure medium container. The relief valve may be directly precontrolled, but it may also be advantageous to form the relief valve as an electrically operable 2/2-way valve, which is driven, for example, by a pressure signals of a pressure sensor processing control and / or regulating device.
Nachstehend ist die Erfindung anhand von in der Zeichnung dargestellten Ausführungsbeispielen im Einzelnen erläutert. Dabei zeigen:
- Fig. 1a
- einen schematischen, nicht maßstäblichen Längsschnitt durch eine erfindungsgemäße Ventilanordnung mit einem Entlastungsventil in geöffneter Schaltstellung in einem Druckregelventil mit Anbindung an eine Konstantstrom-Druckmittelpumpe und an zwei Verbraucher;
- Fig.1b
- ein Detail I in
Fig.1a ; - Fig.1c
- einen schematischen, nicht maßstäblichen Längsschnitt durch eine erfindungsgemäße Ventilanordnung mit einem Entlastungsventil in Regelstellung des Hauptventils und des Vorsteuerventils mit geschlossener Schaltstellung des Entlastungsventils;
- Fig.1d
- ein Detail I in
Fig.1c ; - Fig.1e
- ein weiteres Ausführungsbeispiel für ein Druckregelventil nach der Erfindung mit einem Entlastungsventil;
- Fig.1f
- ein Detail I in
Fig.1e ; - Fig.2
- einen hydraulischen Schaltplan für eine weitere Ausführungsform der erfindungsgemäßen Ventilanordnung;
- Fig. 3
- einen weiteren hydraulischen Schaltplan einer weiteren Ausführungsform der Ventilanordnung mit einer Verbindung eines Entlastungsventils nach einer ersten Drossel und vor einer zweiten Drossel zwischen dem Hauptsteuerventil und dem Vorsteuerventil des Druckregvelventils;
- Fig.4 und 5
- weitere Ausführungsbeispiele in der Art eines hydraulischen Schaltplans bezogen auf die erfindungsgemäße Ventilanordnung.
- Fig. 1a
- a schematic, not to scale longitudinal section through a valve assembly according to the invention with a relief valve in the open position in a pressure control valve with connection to a constant flow pressure medium pump and two consumers;
- 1b shows
- a detail I in
1a ; - Figure 1C
- a schematic, not to scale longitudinal section through a valve assembly according to the invention with a relief valve in control position of the main valve and the pilot valve with closed switching position of the relief valve;
- Fig.1d
- a detail I in
Figure 1C ; - 1E
- a further embodiment of a pressure control valve according to the invention with a relief valve;
- Fig.1f
- a detail I in
1E ; - Fig.2
- a hydraulic circuit diagram for a further embodiment of the valve assembly according to the invention;
- Fig. 3
- a further hydraulic circuit diagram of another embodiment of the valve assembly with a connection of a relief valve after a first throttle and before a second throttle between the main control valve and the pilot valve of the Druckregvelventils;
- 4 and 5
- further embodiments in the manner of a hydraulic circuit diagram related to the valve arrangement according to the invention.
In der
In dem in
Wie die
Die Funktionsweise des Druckregelventils 5 entspricht einer vorgesteuerten Umlaufdruckwaage 17, wobei in einem gemeinsamen Gehäuse 12 drei von der Funktion her verschiedene Ventile zusammengefaßt sind. Die grundsätzliche funktionale Verknüpfung der Ventile ist auch in
ein Hauptventil 23mit einem Hauptkolben 6 und einer diesen vorspannenden Druckfeder 24,ein Vorsteuerventil 25mit einem Vorsteuerkolben 7 und diesen vorspannenden Druckfeder 26, und- ein als Kleinstventil gebildetes Entlastungsventil 10
mit einem Ventilelement 27 oder Entlastungsventilkolben und einem diesen in Richtung einer Geschlossen-Position haltenden Energiespeicher 28.
- a
main valve 23 with amain piston 6 and a biasing thiscompression spring 24, - a
pilot valve 25 with apilot piston 7 and this biasingcompression spring 26, and - a
discharge valve 10 formed as a miniature valve with avalve element 27 or relief valve piston and anenergy store 28 which holds this in the direction of a closed position.
In dem patronenartigen, als Einschraubventil ausgebildeten Gehäuse 12 des Druckregelventils 5 ist in einem Hauptventil-Steuerabschnitt der Hauptkolben 6 in einer Bohrung 29 des Gehäuses 12 längsverschiebbar geführt. Der Hauptkolben 6 steuert dabei einen zentral und axial in das Gehäuse 12 geführten Druckmitteleinlass 30 an. Hierbei kann eine mögliche fluidführende Verbindung zu einem radial aus dem Gehäuse 12 geführten Druckmittelanschluss 31, der gegebenenfalls aus mehreren radial angeordneten Durchlassbohrungen in dem Gehäuse 12 besteht und an einen Druckmittelbehälter 11 anschließbar ist, aus der die Druckmittelpumpe 3 Druckmittel für den hydraulischen Kreis entnimmt, hergestellt werden.In the cartridge-like, designed as
Das Hauptventil 23 ist in Bezug auf seinen wirksamen Querschnitt derart ausgelegt, dass der gesamte Volumenstrom an Druckmittel 2 von der Konstant-Druckmittelpumpe 3 zu dem Druckmittelbehälter 11 gelenkt werden kann. In dem Hauptkolben 6 ist in seinem Kolbenboden eine erste Drossel 13 in Form einer Durchgangsöffnung oder -bohrung mit definierbarem Durchmesser angeordnet. Dadurch ist es ermöglicht, dass der pumpenseits anstehende Druck auf die Kolbenrückseite 9 des Hauptkolbens 6 gemeldet ist. Der Hauptkolben 6 ist im Wesentlichen als zylindrische Hülse ausgebildet mit einem Kolbenboden als Fluidtrennung, so dass auf der Kolbenrückseite 9 ein topfförmiger Druckraum 8 gebildet ist, der zur Zentrierung und zur Aufnahme der Druckfeder 24 dient und des weiteren Druckmittel 2 aufnehmen kann. In axialer Richtung des Druckregelventils 5 ist zentral eine Bohrung 32 mit einem Durchmesser von etwa 1/5 des im Ventilgehäuse 12 geführten Hauptkolbens 6 angebracht. Die Bohrung 32 weist in etwa ihrer axialen Mitte eine weitere, zweite Drossel 14 auf. Durch die zweite Drossel 14 ist die Bohrung 32 in einen ersten Kanalabschnitt 32' und einen zweiten Kanalabschnitt 32" aufgeteilt. Wie auch die
Der Vorsteuerkolben 7 wiederum ist als flache Scheibe mit einer Zentrierhilfe 33 in Form eines Kegelstumpfes für eine Druckfeder 26 gebildet. Der Vorsteuerkolben 7 wird mit der Kraft der Druckfeder 26, die sich mit radialem Spiel in einer Bohrung 34 für den Vorsteuerkolben 7 und die Druckfeder 26 abstützt, beaufschlagt. Der kolbenvorderseitige, zweite Druckraum 35 ist der gleiche Druckraum wie der Raum 34, in den die Druckfeder 26 eingebracht ist. Soweit bedarf es keiner Dichtung. In den Raum 34 des Vorsteuerventilkolbens 7 mündet eine, die Gehäusewand des Gehäuses 12 durchquerende Bohrung 36 für den Lastabgriff LS der Verbraucher 4. Der Fließdruck des Vorsteuerventils 25 ergibt sich dabei aus dem von der Druckfeder 26 definierten Druck zuzüglich des Druckes am Lastabgriff LS. Ist der Pumpendruck größer als der Druck aus LS und der von der Druckfeder 26 des Vorsteuerkolbens 7 eingestellte und der von der Feder 24 des Hauptkolbens eingestellten Drucks, so öffnet das Vorsteuerventil 25 und infolge das Hauptventil 23 und Druckmittel kann über das Hauptventil 23 zum Druckmittelbehälter 11 abfließen.The
Wie die
In axialer Nähe zu dem druckfederseitigen Ende des Entlastungsventilkolbens ist eine Ringausnehmung 41, die als eine Ringnut 38 in dem Umfang des Entlastungsventilkolbens gebildet ist, vorgesehen. In dem in den
Die
Die
Die
Das Entlastungsventil kann in der Regel als klein aufbauendes Ventil in ein vorhandenes Druckregelventil integriert sein. Es ist insoweit vorteilhaft, das Entlastungsventil axial zwischen dem Vorsteuerventil und dem Hauptventil anzuordnen, wobei ein Ventilkolben des Entlastungsventils von der Vorsteuerventilseite in ein Gehäuse des Druckregelventils einsetzbar ist. Es lassen sich dadurch auch die Hauptbohrung für das Entlastungsventil von derselben Ventilseite wie eine Drossel zwischen dem Druckraum und dem Vorsteuerventil fertigen. The relief valve can be integrated as a rule small constructive valve in an existing pressure control valve. It is advantageous in this respect to arrange the relief valve axially between the pilot valve and the main valve, wherein a valve piston of the relief valve can be inserted from the pilot valve side into a housing of the pressure regulating valve. It can thereby also make the main bore for the relief valve from the same valve side as a throttle between the pressure chamber and the pilot valve.
Claims (8)
- A valve assembly for pressure control of a pressure medium (2) from a pressure medium pump (3) to at least one first consumer (4), comprising a pilot-operated pressure control valve (5), with a main piston (6) pressurised by the pressure medium (2) and a pilot-operated piston (7), a pressure chamber (8) between a rear side (9) of the main piston (6) and the pilot-operated piston (7) being able to be relieved, characterised in that a relief valve (10) is connected to the pressure chamber (8) such as to convey fluid, which relief valve opens at a pressure medium pressure on a load sensor (LS) which displays on off position of the consumer (4) and returns pressure medium (2) having low pressure into a pressure medium tank (11) or to the pressure medium pump (3), and that the relief valve (10) closes when the pressure of the pressure medium on the load sensor (LS) displays the consumer (4) in the operating position.
- The valve assembly according to Claim 1, characterised in that pressure medium coming from the pressure medium port (30) of the valve assembly (1), conveyed via a first throttle (13) and via the relief valve (10), can be discharged in its travel position to the pressure medium tank (11).
- The valve assembly according to Claim 2, characterised in that there is another, second throttle (14) in a longitudinal channel (32) between the pressure chamber (8) of the main piston (6) and another, second pressure chamber (35) which can be traversed by the pilot-operated piston (7).
- The valve assembly according to Claim 2 or 3, characterised in that the second throttle (14) divides the longitudinal channel (32) into two channel sections, of which the one, first channel section (32') is assigned to the pressure chamber (8) of the main piston (6), and the other, second channel section (32") is assigned to the second pressure chamber (35) which can be traversed by the pilot-operated piston (7).
- The valve assembly according to any of the preceding claims, characterised in that a valve element (27) of the relief valve (10) is conveyed in a longitudinal bore hole (40) of the housing (12) of the pressure control valve (5), a fluid-conveying connection to one channel section (32', 32") or the other in at least one travel position of the valve element (27) being able to be established via at least one annular recess (41) in the housing (12) and/or in the valve element (27).
- The valve assembly according to Claim 5, characterised in that the valve element (27) under the effect of an energy store (compression spring) (28) is preloaded in the direction of the second pressure chamber (35) with the pilot-operated piston (7), and that the pilot-operated piston (7) actuates a fluid-conveying connection between a load sensor (LS) and a free side of the valve element (27), which side is opposite the energy store (28).
- The valve assembly according to Claim 5 or 6, characterised in that the valve element (27), at least when fully exposed to the LS pressure, blocks the fluid-conveying connection between the pressure chamber (8) of the main piston (6) and the pressure medium tank (11) and otherwise clears it.
- The valve assembly according to any of Claims 5 to 7, characterised in that in a valve solution in which the annular recess (41) in the housing (12) or in the valve element (27) discharges into the second channel section (32") of the longitudinal channel (32), the annular recess (41) is connected to the second pressure chamber (35) of the pilot-operated piston (7) such as to convey fluid via a connecting line (42).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009049548A DE102009049548A1 (en) | 2009-10-16 | 2009-10-16 | valve assembly |
PCT/EP2010/006289 WO2011045063A1 (en) | 2009-10-16 | 2010-10-14 | Valve assembly |
Publications (2)
Publication Number | Publication Date |
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EP2488764A1 EP2488764A1 (en) | 2012-08-22 |
EP2488764B1 true EP2488764B1 (en) | 2016-06-08 |
Family
ID=43383531
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP10768695.8A Active EP2488764B1 (en) | 2009-10-16 | 2010-10-14 | Valve system |
Country Status (4)
Country | Link |
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US (1) | US8973609B2 (en) |
EP (1) | EP2488764B1 (en) |
DE (1) | DE102009049548A1 (en) |
WO (1) | WO2011045063A1 (en) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
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DE202011101545U1 (en) * | 2011-06-08 | 2012-09-13 | Robert Bosch Gmbh | Hydraulic Control Block and Proportional Relief Valve and Hydraulic Shift Assembly for Sensitive Hydraulic Control |
GB2501486A (en) * | 2012-04-24 | 2013-10-30 | Jc Bamford Excavators Ltd | Work machine having a hydraulic system comprising variable orifice ratios |
DE102012010522A1 (en) | 2012-05-25 | 2013-11-28 | Hydac Fluidtechnik Gmbh | Valve for valve arrangement |
CN102889253A (en) * | 2012-09-20 | 2013-01-23 | 三一重工股份有限公司 | Hydraulic system and engineering machinery |
EP2757024B1 (en) * | 2013-01-16 | 2015-06-24 | Danfoss Power Solutions Aps | A hydraulic steering control arrangement |
CH708930A1 (en) * | 2013-12-06 | 2015-06-15 | Liebherr Machines Bulle Sa | Pressure relief valve. |
CN105840574B (en) | 2015-01-16 | 2018-04-06 | 徐工集团工程机械股份有限公司 | Load sensing multi-way valve and construction machinery hydraulic system |
US10323762B2 (en) * | 2016-04-21 | 2019-06-18 | Parker-Hannifin Corporation | Three-way pressure control and flow regulator valve |
DE102017200418A1 (en) * | 2017-01-12 | 2018-07-12 | Robert Bosch Gmbh | Valve assembly for dual-circuit summation |
US20190032811A1 (en) * | 2017-07-25 | 2019-01-31 | Pratt & Whitney Canada Corp. | Damped relief valve using double pistons |
CN107355550B (en) * | 2017-08-17 | 2023-06-06 | 广东美的暖通设备有限公司 | Throttle valve |
DE102017008359A1 (en) * | 2017-09-06 | 2019-03-07 | Hydac Fluidtechnik Gmbh | Valve |
DE102021001960A1 (en) * | 2021-04-14 | 2022-10-20 | Hydac Fluidtechnik Gmbh | Valve |
CN113738793B (en) * | 2021-09-09 | 2022-02-22 | 北京裕峻汽车技术研究院有限公司 | Braking system and control method of hydraulic retarder |
DE102022002192A1 (en) | 2022-06-17 | 2023-12-28 | Hydac Fluidtechnik Gmbh | Volume flow supply |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2706483B2 (en) * | 1988-09-28 | 1998-01-28 | 日立建機株式会社 | Pressure control valve |
DE19744337A1 (en) * | 1997-10-07 | 1999-04-08 | Mannesmann Rexroth Ag | Pilot operated pressure relief valve |
DE10039936A1 (en) * | 2000-08-16 | 2002-03-07 | Fluidtech Gmbh | Valve |
US6966329B2 (en) * | 2003-01-27 | 2005-11-22 | Hydraforce, Inc. | Proportional pilot-operated flow control valve |
US7063100B2 (en) * | 2003-03-06 | 2006-06-20 | Hydraforce Inc. | Flow regulator with pressure relief combination valve |
DE10322585B4 (en) * | 2003-05-20 | 2018-12-06 | Hydac Fluidtechnik Gmbh | Valve Modular systems |
DE102005059240A1 (en) * | 2005-12-12 | 2007-06-14 | Linde Ag | Hydrostatic drive system for controlling load of e.g. ground conveyor, has pump with delivery volume adjusting device that is controllable by control device, and circulating device managing connection of feed pipe of pump with container |
DE102010005524A1 (en) * | 2010-01-23 | 2011-07-28 | Robert Bosch GmbH, 70469 | Flow control valve with damping chamber |
-
2009
- 2009-10-16 DE DE102009049548A patent/DE102009049548A1/en not_active Withdrawn
-
2010
- 2010-10-14 EP EP10768695.8A patent/EP2488764B1/en active Active
- 2010-10-14 WO PCT/EP2010/006289 patent/WO2011045063A1/en active Application Filing
- 2010-10-14 US US13/261,264 patent/US8973609B2/en active Active
Non-Patent Citations (1)
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Also Published As
Publication number | Publication date |
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WO2011045063A1 (en) | 2011-04-21 |
US20120199765A1 (en) | 2012-08-09 |
DE102009049548A1 (en) | 2011-04-21 |
US8973609B2 (en) | 2015-03-10 |
EP2488764A1 (en) | 2012-08-22 |
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