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EP2372167B1 - Vorrichtung zur Steuerung eines Vorsteuerdrucks, insbesondere eines Ausgleichsventils - Google Patents

Vorrichtung zur Steuerung eines Vorsteuerdrucks, insbesondere eines Ausgleichsventils Download PDF

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Publication number
EP2372167B1
EP2372167B1 EP20100425101 EP10425101A EP2372167B1 EP 2372167 B1 EP2372167 B1 EP 2372167B1 EP 20100425101 EP20100425101 EP 20100425101 EP 10425101 A EP10425101 A EP 10425101A EP 2372167 B1 EP2372167 B1 EP 2372167B1
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EP
European Patent Office
Prior art keywords
opening
valve
obturator
piloting
pressure
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.)
Not-in-force
Application number
EP20100425101
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English (en)
French (fr)
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EP2372167A1 (de
Inventor
Andrea Storci
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth Oil Control SpA
Original Assignee
Bosch Rexroth Oil Control SpA
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Publication date
Application filed by Bosch Rexroth Oil Control SpA filed Critical Bosch Rexroth Oil Control SpA
Priority to EP20100425101 priority Critical patent/EP2372167B1/de
Publication of EP2372167A1 publication Critical patent/EP2372167A1/de
Application granted granted Critical
Publication of EP2372167B1 publication Critical patent/EP2372167B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • 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
    • 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
    • F15B2211/50—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
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a device for controlling a piloting pressure, in particular the piloting pressure of a balance valve.
  • the prior art contains hydraulic activating circuits for hydraulic actuators, for example for a cylinder of an arm of a lifting apparatus, in which a first circuit branch connects a hydraulic distributor, in turn associated to a pump, with the chamber of the actuator being associated to the lifting of the load and a second branch connects the distributor with the chamber associated to the descent of the load.
  • the circuit is provided with a balance valve predisposed for controlling the fluid flow along the first branch during the descent stage of the load.
  • a piloting conduit removes a piloting pressure from the second branch which piloting pressure acts by opening the balance valve during the descent stage of the load.
  • chokes have been placed on the piloting conduit. These chokes determine a localised load loss by effect of which the increase in the piloting pressure P PIL commanding the opening of the balance valve is gradual and controlled with respect to the increase in pressure P B in the second branch (i.e. the branch which during the lowering stage of the load is the delivery branch).
  • the curve S approximately represents the progress of the piloting pressure P PIL as a function of the pressure P B in the second branch using a choke.
  • a drawback of the above-cited known solution is the delay in the activation of the cylinder with respect to the operator's command, especially evident when the operating liquid in the hydraulic circuit is very viscous (for example when cold).
  • This delay is due to the presence of the choke and can be schematised in figure 1 by observing that the piloting pressure P PIL reaches value P V of opening of the balance valve (a value predetermined by the calibration of the valve spring) when the delivery pressure P B to the cylinder has already reached a relatively high level P S .
  • P V of opening of the balance valve a value predetermined by the calibration of the valve spring
  • a check valve is located along the piloting conduit, in parallel with the choke.
  • the valve normally open, enables passage of the piloting fluid up to reaching a determined pressure downstream of the valve. On reaching the determined pressure, the valve closes and the piloting fluid flow continues via the choke.
  • the presence of the check valve, located in parallel with the choke enables a rapid increase of the piloting pressure in the first stages of sending the piloting signal to the balance valve. In this way, the lowering of the load begins promptly in response to the lowering command.
  • the above-described solution exhibits however a not entirely satisfactory aspect.
  • the check valve exhibits a certain tendency to closure following pressure peaks or flow peaks along the piloting conduit. As these pressure or flow peaks are rather frequent, so are the closures of the check valve, which undesirably slow down the opening of the balance valve.
  • JP 59016022 An example of prior art device suffering the same drawback above is given in JP 59016022 .
  • the device comprises a coupling part provided between a load and an actuator.
  • the coupling part has a gap acting as a backlash.
  • a changeover valve is provided to a hydraulic driving circuit closer to the actuator, a check valve, pressure reducing valve and relief valve are provided successively in front of the changeover valve, and maximum pressure for operating the actuator is set to the relief valve.
  • the load does not operate on the pressure reducing valve, but enough pressure to operate the actuator is set.
  • the aim of the present invention is to realise a device for control of a piloting pressure of a balance valve which enables reduction of the delay in response of the balance valve or, more in general, of a hydraulically-piloted organ.
  • An advantage of the invention is that is provides a device which enables prompt and progressive activation of the piloted organ.
  • a further advantage of the invention is to considerably reduce the delay in opening of the balance valve in an activating circuit for a hydraulic actuator and to prevent onset of instability and oscillation phenomena of the valve.
  • the hydraulic actuator 9 has a first chamber 10 and a second chamber 11 respectively associated to the raising and lowering of a load 12.
  • the activating circuit comprises a hydraulic distributor 13 in turn connected to a source of operating fluid under pressure, typically a pump.
  • a first branch 14 connects the distributor 13 with the first chamber 10, while a second branch 15 connects the distributor 13 with the second chamber 11.
  • a balance valve 16 is arranged along the first branch 14 to regulate the flow rate of operating fluid which unloads from the first chamber 10 during the descent stage of the load 12.
  • a piloting conduit 17 takes from the second branch 15 a piloting pressure which acts to open the balance valve 16.
  • the balance valve 16 exhibits a first connection which is connected to the first chamber 10 and a second connection connected to the distributor 13.
  • the balance valve has a obturator which is mobile between the open position, in which the first connection is set in communication with the second connection, and a closed position, wherein the first and the second connections are not in communication with one another.
  • the obturator of the balance valve 16 is pushed towards the closed position thereof by means of a spring, while it is pushed towards its open position by the force exerted thereon by the pressure exerted by the piloting fluid removed from the second branch 15.
  • the balance valve comprises a single-acting valve connected in parallel to the obturator for enabling free flow of the piloting fluid from the second to the first connection.
  • the function of the balance valve 16 is to enable, during raising of the load, free flow of the operating liquid to the first chamber 10 of the actuator 9. During the descent of the load, the balance valve 16 controls and limits the flow rate of the operating fluid which unloads from the first chamber 10 towards the distributor 13, such as to slow down the descent of the load.
  • the device of the present invention illustrated in figure 2 , is predisposed to be positioned along the piloting conduit 17. It comprises a choke 8, predisposed to be interposed between a piloting fluid source and an organ 16, in particular the balance valve 16, which is activatable by the piloting fluid.
  • the device further comprises a pressure reducer valve 2, arranged in parallel with the choke 8, which is normally open and is predisposed to close when the piloting fluid pressure reaches a determined level.
  • the reducer valve 2 is provided with an obturator 21 which is mobile between an open position, in which the piloting fluid flow is enabled through the reducer valve 2, and a closed position, in which the piloting fluid flow is not enabled through the reducer valve 2.
  • the obturator 21 is pushed towards the open position thereof by effect of the thrust exerted by an elastic element 25, while it is pushed towards the closed position thereof by effect of the thrust exerted by the piloting fluid pressure on a thrust surface 210 of the obturator 21.
  • the thrust surface 210 is defined by the front section of the obturator 21, i.e. by the area of the circle delimited by the external edge of the obturator 21.
  • the obturator 21 is advantageously conformed and arranged such that the thrust surface 210 is not exposed to the direct flow of the piloting liquid in inlet to the reducer valve 2.
  • the thrust surface 210 is exposed directly only to the piloting fluid pressure downstream of the reducer valve 2.
  • the conformation of the obturator 21 and the arrangement of the thrust surface 210 are such that any peaks of flow rate and/or pressure of the piloting fluid in inlet to the reducer valve 2 do not have the effect of nudging the obturator 21 towards the closed position.
  • the obturator 21 is only subject to the effect of the pressure present downstream of the reducer valve 2, which pressure also acts on the balance valve 16. In this way any peaks of flow rate and/or pressure of the piloting fluid in inlet to the reducer valve 2, as they do not nudge the obturator 21 to closure, do not slow down the flow of the piloting fluid towards the balance valve 16.
  • the obturator 21 is sealedly slidable along a longitudinal axis x internally of a seating 22.
  • the seating 22 exhibits at least an inlet opening 23, predisposed to be connected to the piloting conduit 17, and at least an outlet opening 24 predisposed to be connected to the balance valve 16.
  • the obturator 21 is mobile between at least an open position ( figure 2 ), in which the inlet opening 23 and the outlet opening 24 are in communication and the piloting fluid can flow from the inlet opening to the outlet opening, and at least a closed position ( figure 3 ), in which communication between the inlet opening and the outlet opening is prevented.
  • An elastic element 25, preferably a helical spring possible provided with a calibrating organ 26 is predisposed to push the obturator 21 towards the open position. Differently, the pressure downstream of the outlet opening 24, which unloads on the thrust surface 210, pushes the obturator 21 towards the closed position.
  • the obturator 21 exhibits a communicating conduit 211 arranged longitudinally and parallel to the sliding direction of the obturator 21.
  • the communicating conduit 211 is provided with a first opening 212 and a second opening 213.
  • the second opening 213 is set in communication with the outlet opening 24 of the reducer valve 2.
  • the first opening 212 in the open position of the obturator 21, is in communication with the inlet opening 23 of the reducer valve 2, such that the inlet opening 23 is in communication with the outlet opening 24 via the first opening 212, the communicating conduit 211 and the second opening 213.
  • the first opening 212 In the closed position of the obturator 21, the first opening 212 is not in communication with the inlet opening 23 of the reducer valve 2.
  • the first opening 212 is arranged at an annular groove 214 located on the lateral surface of the obturator 21.
  • the annular groove 214 delimits, in cooperation with the internal wall of the seating 22, an annular chamber into which the first opening 212 opens.
  • the annular chamber In the open position of the obturator 21, the annular chamber at least partly faces the inlet opening 23 of the reducer valve 2, while in the closed position of the obturator 21 the annular chamber is not in communication with the inlet opening 23.
  • the first opening 212 develops perpendicular to the communicating conduit 211, such that the piloting fluid coming from the inlet opening 23 of the reducer valve 2 flows internally of the communicating conduit 211 from a transversal direction with respect to the longitudinal development of the communicating conduit 211. In this way, the dynamic effect due to the flow of the piloting fluid in inlet to the communicating conduit 211 is directed perpendicular to the sliding direction of the obturator 21, and the obturator 21 is therefore not pushed to slide.
  • the inlet opening 23 and the first opening 212 are substantially facing in the same direction.
  • the outlet opening 24 and the second opening 213 are reciprocally aligned.
  • the directions of orientation of the inlet opening and the first opening are in turn perpendicular to the orientation direction of the outlet opening and the second opening.
  • the special conformation of the obturator 21 is such that the obturator 21 does not suffer from any pressure or flow rate peaks on opening the inlet 23 of the reducer valve 2.
  • the displacement of the obturator 21 towards the closed position is determined only by the pressure present at the outlet opening 24 of the reducer valve 2.
  • the reducer valve 2 does not perform undesired and unexpected closures, but closes only when the pressure present at the outlet opening 24 reaches a determined value, in particular a value determined by the force exerted by the elastic element 25.
  • the elastic element 25 or spring is housed in a low-pressure chamber 27.
  • the chamber 27 of the spring 25 is set in communication with the first branch 14 of the circuit connecting the distributor 13 with the first chamber 10 of the actuator 9, which chamber 10 is associated to the raising of the load.
  • this branch is normally at low pressure, and the spring chamber of the reducer valve is also at low pressure.
  • the eventual presence of pressure in the chamber 27 would raise the calibration value of the reducer valve 2, i.e. the pressure required for determining the displacement of the obturator 21 towards the closed position. This might effectively occur by effect of a pressurised oil flow present in the first branch 14 of the circuit during the descent. In this condition the calibration of the reducer valve 2, i.e.
  • the pressure required for displacing the obturator 21 towards the closed position would increase slightly and, consequently, the pressure transmitted to the piloting of the balance valve would also increase, in this way facilitating the opening of the valve.
  • the chamber 27 containing the spring 25 might also be ventilated by air.
  • a single-acting valve 3 can be interposed between the reducer valve 2 and the balance valve 16, which single-acting valve 3 has a function of enabling flow of the fluid only from the reducer valve 2 towards the piloting of the balance valve 16, while reverse flow is prevented. In this way all unexpected back-flow of the piloting fluid in outlet from the piloting of the balance valve 16 is prevented. This unexpected flow might obtain in a case of a pressure drop in the second branch 15 of the circuit, and might lead to an undesired closing of the balance valve 16.
  • the obturator 21 displaces into the closed position and the piloting fluid flow proceeds through the choke 8, such that the piloting pressure P PIL further increases through the choke up to reaching the value P V at which the balance valve 16 opens. Thereafter, on closure of the reducer valve 2, the piloting pressure P PIL increases from value P X to value P V at a smaller inclination with respect to a situation in which the reducer valve 2 is open, as shown by the curve T of figure 1 . This smaller inclination depends on the pressure drop caused by the choke 8.
  • the curve S of figure 1 denotes the progress of the piloting pressure P PIL for a control device comprising only the choke 8 but not the reducer valve 2.
  • the curve S clearly shows how the piloting pressure P PIL reaches the start value P V of the opening of the balance valve 16 when the pressure P B in the second branch 15 is at a decidedly greater value than the curve T. This means that, thanks to the device of the invention, the balance valve 16 opens decidedly before, such that the lowering of the load follows very rapidly on from the operator's descent command.
  • the choke 8 which has the task of stabilising the functioning of the actuator 9 during the descent stage of the load, effectively performs this task even where the passage section is relatively large.
  • the choke 8 of the device of the invention can be decidedly more open with respect to a stabilising choke in a device lacking the reducer valve 2. Consequently it can be seen from figure 1 that the inclination of the curve S, relative to a more accentuated choke, is less than the inclination of the second tract of the curve T, which relates to the choke used in the present device, in which P PIL is greater than P X . This enables the operator to have an even more direct and immediate control of the actuator 9, as the response of the actuator 9 is even more prompt for each positional variation of the distributor 13.
  • the balance valve 16 the obturator of which has been piloted, i.e. pushed, into the open position by the piloting fluid, has to return to the closed position, sending at least a part of the piloting fluid in discharge.
  • the piloting fluid can be discharged only passing through the choke 8, due to the presence of the single-acting valve 3. This might cause an undesired delay in the closure of the obturator of the balance valve 16, and therefore an excessive delay in the halting of the load.
  • the device of the present invention can advantageously be provided with a pressure limiter valve 4 arranged in parallel with the choke 8 and the reducer valve 2.
  • the limiter valve is provided with an obturator which is mobile between an open position, in which the operating fluid flow through the valve is enabled, and a closed position, in which the flow is not enabled.
  • the obturator is pushed towards the closed position by effect of the thrust exerted by an elastic means, while it is pushed towards the open position by the piloting fluid pressure.
  • the limiter valve 4 enables the piloting fluid flow only from the balance valve 16 to the second branch 15, while it prevents the reverse flow, and enables flow only if the piloting fluid pressure rises above a determined value corresponding to the thrust exerted by the elastic means. At least a part of the piloting fluid can be rapidly discharge through the limiter valve 4, such as to enable the obturator of the balance valve 16 to displace rapidly towards the closed position thereof, at least for a considerable part of the run towards the closed position.
  • the device of the invention can be used for controlling the piloting pressure towards any hydraulically-piloted organ, with the aim of having a very rapid start-up of the piloted organ in response to an external command supplied via the piloting pressure supply.
  • the device obviates delays in start-up of the hydraulically-piloted organ while at the same time preventing instability phenomena in the functioning of the piloted organ after start-up.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (11)

  1. Vorrichtung zur Steuerung eines Vorsteuerdrucks, umfassend eine Drossel (8), die ausgelegt ist, um zwischen eine Quelle des Vorsteuerfluids und ein durch das Vorsteuerfluid zu betätigendes Organ (16) gelagert zu werden, wobei ein parallel zur Drossel (8) angeordnetes Ventil (2) normalerweise offen und ausgelegt ist, um zu schließen, wenn der Druck des Vorsteuerfluids einen bestimmten Wert erreicht, wobei das Ventil (2) ein Druckminderventil ist, das mit einem Verschluss (21) versehen ist;
    wobei der Verschluss (21) zwischen einer offenen Stellung, in der ein Vorsteuerfluidfluss durch das Druckminderventil (2) gelassen wird, und einer geschlossenen Stellung, in der der Vorsteuerfluidfluss nicht durch das Druckminderventil (2) gelassen wird, beweglich ist, wobei der Verschluss durch die Wirkung eines Schubs, der von einem elastischen Element (25) ausgeübt wird, in seine offene Stellung gedrückt wird, wobei der Verschluss durch die Wirkung des Schubs, der vom Vorsteuerfluiddruck auf eine Schubfläche (210) des Verschlusses (21) ausgeübt wird, in seine geschlossene Position gedrückt wird; dadurch gekennzeichnet, dass der Verschluss (21) so ausgebildet und angeordnet ist, dass die Schubfläche (210) nicht dem im Einlass zum Druckminderventil (2) befindlichen direkten Fluss des Vorsteuerfluids ausgesetzt ist, wobei die Schubfläche (210) dem Vorsteuerfluiddruck erst nach dem Druckminderventil (2) direkt ausgesetzt ist.
  2. Vorrichtung nach einem der vorangehenden Ansprüche, wobei der Verschluss (21) abschließend entlang einem Sitz (22) verschiebbar ist, der mindestens eine Einlassöffnung (23), die ausgelegt ist, um das Vorsteuerfluid zu empfangen, und mindestens eine Auslassöffnung (24), durch die das Vorsteuerfluid zum Organ (16) geleitet werden kann, aufweist.
  3. Vorrichtung nach Anspruch 2, wobei der Verschluss (21) zwischen mindestens einer offenen Stellung, in der die Einlassöffnung (23) und die Auslassöffnung (24) miteinander in Verbindung stehen und das Vorsteuerfluid von der Einlassöffnung zur Auslassöffnung fließen kann, und mindestens einer geschlossenen Position, in der die Verbindung zwischen der Einlassöffnung und der Auslassöffnung verhindert wird, beweglich ist.
  4. Vorrichtung nach Anspruch 3, wobei der Verschluss (21) eine Verbindungsleitung (211) aufweist, die mit einer ersten Öffnung (212) und einer zweiten Öffnung (213) ausgestattet ist, wobei die zweite Öffnung (213) mit der Auslassöffnung (24) des Druckminderventils (2) in Verbindung steht, wobei die erste Öffnung (212) in der offenen Stellung des Verschlusses (21) mit der Einlassöffnung (23) in Verbindung steht, sodass die Einlassöffnung (23) mit der Auslassöffnung (24) über die erste Öffnung (212), die Verbindungsleitung (211) und die zweite Öffnung (213) in Verbindung steht, wobei in der geschlossenen Position des Verschlusses (21) die erste Öffnung (212) nicht in Verbindung mit der Einlassöffnung (23) steht.
  5. Vorrichtung nach Anspruch 4, wobei die Einlassöffnung (23) und die erste Öffnung (212) im Wesentlichen in eine selbe Richtung zeigen, wobei die Auslassöffnung (24) und die zweite Öffnung (213) aneinander ausgerichtet sind, wobei die Orientierungsrichtung der Einlassöffnung (23) und der ersten Öffnung (212) lotrecht zur Ausrichtungsrichtung der Auslassöffnung (24) und der zweiten Öffnung (213) sind.
  6. Vorrichtung nach Anspruch 5, wobei die erste Öffnung (212) an einem ringförmigen Kanal (214) angeordnet ist, der an der Seitenfläche des Verschlusses (21) ausgebildet ist und gemeinsam mit der Innenwand des Sitzes (22) eine ringförmige Kammer abgrenzt, in der die erste Öffnung (212) mündet, wobei die ringförmige Kammer in der offenen Stellung des Verschlusses (21) zumindest zum Teil der Einlassöffnung (23) gegenüberliegt, wobei die ringförmige Kammer in der Verschlussstellung des Verschlusses (21) nicht mit der Einlassöffnung (23) in Verbindung steht.
  7. Vorrichtung nach einem der vorangehenden Ansprüche, wobei das elastische Element bzw. die Feder (25) in einer Niederdruckkammer (27) aufgenommen ist.
  8. Vorrichtung nach Anspruch 7, wobei die Kammer (27) des elastischen Elements (25) durchlässig für Luft ist.
  9. Vorrichtung nach einem der vorangehenden Ansprüche, umfassend ein nach dem Druckminderventil (2) angeordnetes einfachwirkendes Ventil (3), das ausgelegt ist, um den Fluss des Vorsteuerfluids vom Druckminderventil (2) zum vorzusteuernden Organ (16) zu ermöglichen und einen Rücklauf zu verhindern.
  10. Vorrichtung nach einem der vorangehenden Ansprüche, umfassend ein Druckbegrenzungsventil (4), das parallel zur Drossel (8) und zum Druckminderventil (2) angeordnet ist, das ausgelegt ist, um den vom Organ (16) abzuleitenden Vorsteuerfluidfluss zu ermöglichen und einen Rücklauf zu verhindern.
  11. Antriebskreis für einen hydraulischen Aktuator (9), umfassend einen Hydraulikzylinder; eine erste Abzweigung (14), die ausgelegt ist, den Verteiler (13) mit einer ersten Kammer (10) des hydraulischen Aktuators (9) zu verbinden; eine zweite Abzweigung (15), die ausgelegt ist, den Verteiler (13) mit einer zweiten Kammer (11) des hydraulischen Aktuators (9) zu verbinden, wobei das Organ ein Ausgleichsventil ist, wobei das Ausgleichsventil (16) entlang der ersten Abzweigung (14) angeordnet ist, um das im Auslass von der ersten Kammer (10) befindliche Betriebsfluid während einer Senkungsphase der Ladung (12) zu regulieren; eine Drossel (8), die zwischen der zweiten Abzweigung (15) und dem Ausgleichsventil (16) liegt; dadurch gekennzeichnet, dass er eine Vorrichtung zur Steuerung des Vorsteuerdrucks nach einem der vorangehenden Ansprüche umfasst, die parallel zur Drossel (8) zwischen der zweiten Abzweigung (15) und dem Ausgleichsventil (16) angeordnet ist.
EP20100425101 2010-03-30 2010-03-30 Vorrichtung zur Steuerung eines Vorsteuerdrucks, insbesondere eines Ausgleichsventils Not-in-force EP2372167B1 (de)

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EP20100425101 EP2372167B1 (de) 2010-03-30 2010-03-30 Vorrichtung zur Steuerung eines Vorsteuerdrucks, insbesondere eines Ausgleichsventils

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EP20100425101 EP2372167B1 (de) 2010-03-30 2010-03-30 Vorrichtung zur Steuerung eines Vorsteuerdrucks, insbesondere eines Ausgleichsventils

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EP2372167A1 EP2372167A1 (de) 2011-10-05
EP2372167B1 true EP2372167B1 (de) 2012-11-14

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CN106050784A (zh) * 2016-08-14 2016-10-26 宁波市博尔法液压有限公司 一种平衡阀
CN110360174A (zh) * 2019-06-14 2019-10-22 常德中联重科液压有限公司 平衡阀的阀体、阀杆组件、平衡阀和液压缸伸缩控制回路

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EP2786958B1 (de) * 2013-04-05 2017-06-14 Bosch Rexroth Oil Control S.p.A. Steuerungsvorrichtung zum Ablassen einer Ladung
CN103486105B (zh) * 2013-10-14 2016-02-24 徐州重型机械有限公司 一种先导滑阀的控制装置
CN103982482A (zh) * 2014-05-30 2014-08-13 徐州重型机械有限公司 一种起重机、其伸缩臂控制系统及平衡阀
CN108953713B (zh) * 2018-08-22 2021-09-28 宁波威森搏乐机械制造有限公司 流量型平衡阀
CN108661971B (zh) * 2018-08-22 2020-04-17 玉环信得利阀业股份有限公司 一种负载传感型流量控制平衡阀
CN109099023B (zh) * 2018-09-29 2020-08-21 艾肯（江苏）工业技术有限公司 平衡阀
EP4428376A1 (de) * 2023-03-07 2024-09-11 Valvole Italia S.r.l. Vorrichtung zur steuerung des senkens eines hydraulischen zylinders, insbesondere zur steuerung des senkens eines bedienungsarms

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CN106050784A (zh) * 2016-08-14 2016-10-26 宁波市博尔法液压有限公司 一种平衡阀
CN110360174A (zh) * 2019-06-14 2019-10-22 常德中联重科液压有限公司 平衡阀的阀体、阀杆组件、平衡阀和液压缸伸缩控制回路

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