EP3112697B1 - Hydrostatische systeme mit wechselventilkörper zur kompensation der differentiellen durchflussrate von einzelstabaktuatoren - Google Patents

Hydrostatische systeme mit wechselventilkörper zur kompensation der differentiellen durchflussrate von einzelstabaktuatoren Download PDF

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Publication number
EP3112697B1
EP3112697B1 EP15174803.5A EP15174803A EP3112697B1 EP 3112697 B1 EP3112697 B1 EP 3112697B1 EP 15174803 A EP15174803 A EP 15174803A EP 3112697 B1 EP3112697 B1 EP 3112697B1
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EP
European Patent Office
Prior art keywords
rod
side chamber
hydraulic
actuator
port
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EP15174803.5A
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English (en)
French (fr)
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EP3112697A1 (de
Inventor
Hakan ÇALI KAN
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DEMIRER TEKNOLOJIK SISTEMLER SANAYI VE TICARET Ltd SIRKETI
Demirer Teknolojik Sistemler Sanayi ve Ticaret LS
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DEMIRER TEKNOLOJIK SISTEMLER SANAYI VE TICARET Ltd SIRKETI
Demirer Teknolojik Sistemler Sanayi ve Ticaret LS
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Priority to EP15174803.5A priority Critical patent/EP3112697B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/027—Check 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/3052—Shuttle 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the present invention relates to closed circuit hydrostatic systems, in which the movement of a single-rod hydraulic actuator is controlled by means of regulating the flow rate of a single pump.
  • the invention particularly relates to an improvement provided in the shuttle valve spool structure in a closed circuit hydrostatic system, where the movement of a single-rod actuator is controlled by regulating the flow rate of a single pump, in order to solve the instability problem encountered while compensating the unequal flow rate, at two ports of the actuator, that occurs due to the asymmetric structure of the actuator.
  • the most common hydrostatic circuit solution wherein a single-rod hydraulic actuator motion is controlled by a single pump is provided by Rahmfeld and Ivantsynova [1].
  • This circuit solution is shown in Figure 5 .
  • the amount of flow rate going to the actuator (1) is determined by a variable displacement pump (2) that is able to operate in 4 quadrants.
  • the secondary pump (M) which is shown to have a tandem connection is merely used for pressurizing the hydraulic accumulator (3), instead of controlling the flow rate going to the actuator (1), and therefore called as charge pump.
  • the hydraulic accumulator (3) fed by a charge pump and maintained at a certain pressure level via a pressure relief valve is used for compensating the differential flow rate formed in the closed circuit system.
  • the differential flow rate formed during actuator (1) movement is compensated through pilot operated check valves (N) found between the hydraulic accumulator (3) and the hydrostatic circuit. Besides these components, the system pressure is limited by a conventional method, wherein two pressure relief valves (O) are connected between the actuator chambers and the accumulator line.
  • the application with publication no US20090120278A1 relates to an electro-hydrostatic actuator with 4-port, double-displacement pump
  • the application with publication no WO2009102740A3 relates to a flow control system for hydraulic machines
  • the application with publication no US8033107B2 relates to a hydrostatic drive embodiment with volumetric flow compensation
  • the application with publication no JPS58102806 (A ) relates to a closed oil pressure circuit for actuator movement
  • the application with publication no US20110209471A1 relates to an embodiment about the velocity control of an unbalanced hydraulic actuator exposed to excessive central load conditions.
  • valve he uses is a closed center one, when the pressure difference between the actuator chambers is less than the shuttle valve cracking pressure, both of the actuator chambers are closed to the accumulator line, and thus an operating region similar to the use of pilot operated check valve ( Figure 8-b ) is formed.
  • the valve spool can not stay in the central position in this critical load pressure region, and would be partially opened in order to compensate the deficient flow rate formed during the retraction, and thus the system would bu unstable.
  • a closed center shuttle valve instead of using a closed center shuttle valve, use of a shuttle valve having a certain orifice opening at the central position is proposed. It is disclosed that the proposed partial orifice opening should be determined such that all of the differential flow rate to be formed at the maximum retracting velocity of the actuator would be met through the two orifices of the centrally positioned valve spool. In this way, instability problems could be solved by a physical technique without using extra valve, sensor, or control components.
  • a closed circuit hydrostatic system according to the preamble of claim 1 is known from document WO2013/112109 A1 .
  • the present invention relates to shuttle valve orifice openings, which meet the above said requirements, eliminate all of the drawbacks and bring about some additional advantages.
  • the primary purpose of the invention is to change the spool structure found in the shuttle valve of a hydrostatic circuit comprising interconnected single-rod hydraulic actuator, pump, hydraulic accumulator, and shuttle valve components, in order to solve the problems of instability and dead pump speed in hydraulic systems.
  • Another purpose of the invention is to provide a solution in hydraulic units comprising single-rod hydraulic actuator that wouldn't cause dead pump speed in the operating region defined as critical load region.
  • Another purpose of the invention is to eliminate the instability problem of the prior art by means of using a valve spool comprising a valve spool underlap (negative spool overlap) such that a certain flow rate passage would be provided between the accumulator line and the actuator rod-side chamber line, and a valve spool overlap such that flow rate passage would be avoided between the accumulator line and the actuator cap-side chamber line, in the center position of the shuttle valve.
  • Another purpose is to eliminate the problem of instability up to a certain velocity [ ⁇ cr ] while the hydraulic actuator is retacting in the region defined as critical load region, by means of the valve spool embodiment operating between the valve spool underlap (negative spool overlap) and the valve spool overlap.
  • Another purpose of the invention is to send the excess flow rate to be formed during the retraction of the hydraulic actuator to the hydraulic accumulator through the valve spool underlap found between port B and port C of the shuttle valve.
  • Another purpose of the invention is to create a valve spool overlap between port A and port C, and in this way, eliminate the unnecessary flow rate between port A and port B, so that the maximum flow rate [ q V
  • xs 0 ] that can be provided to the system through the shuttle valve would be improved compared to the prior art solution, and thus higher critical velocities would be obtained.
  • Another purpose of the invention is to prevent unnecessary energy losses in the critical load region by means of using only one check valve in the system (would be used between the accumulator line and the rod-side chamber line, and wouldn't be used between the accumulator line and the cap-side chamber line).
  • the present invention relates to a closed circuit hydrostatic system according to claim 1.
  • the present invention relates to closed circuit hydrostatic systems, wherein the movement of a single-rod hydraulic actuator (1) is controlled by means of regulating the flow rate of a single pump (2).
  • the improvement of the invention is an embodiment, which solves the problem of instability encountered during compensation of the differential flow rate that occurs as a result of asymmetric hydraulic actuator (1) structure in closed circuit hydrostatic systems, wherein the single-rod actuator (1) movement is controlled via the flow rate of a single pump (2), by means of changing the shuttle valve spool (4.2) structure.
  • valve spool underlap (4.8) and valve spool overlap (4.7) are formed on the shuttle valve spool (4.2) for the central position of the shuttle valve (4), that results with closed and partially open orifice forms between A-C and B-C conduits respectively.
  • FIG. 1 shows the schematic view of the closed circuit hydrostatic system embodiment of the present invention.
  • Single-rod actuator (1) is used in said hydrostatic system.
  • Main components of the hydrostatic system consist of:
  • the control of the position, speed, or force of the hydraulic actuator (1) is made by means of controlling the flow rate entering into/leaving from the single-rod hydraulic actuator (1) in the hydraulic unit.
  • the two ports of the hydraulic actuator (1) found at the cap-side (1.4) and rod-side (1.5) are directly connected to the inlet and outlet ports of the hydraulic pump (2).
  • the direction of the pump flow rates and the positions of the pump (2) pressure/suction ports can vary according to the velocity of the hydraulic actuator (1) and the load applied. Pump flow rate, and thus the hydraulic actuator (1) movement can be controlled by means of changing the pump (2) speed or displacement.
  • the pump (2) that performs flow rate control has the characteristic of operating in all 4 quadrants of the pressure-flow rate plane.
  • the hydraulic unit comprises: a cap-side chamber line (A) providing direct connection between the pump (2) and the cap-side chamber (1.4), a rod-side chamber line (B) providing direct connection between the pump (2) and the rod-side chamber (1.5), and an accumulator line (C) providing connection between the shuttle valve (4) and the hydraulic accumulator (3).
  • a line from the 3-way shuttle valve (4) is connected to the cap-side chamber line (A), while another line is connected to the rod-side chamber line (B).
  • the hydraulic unit also comprises auxiliary components such as pressure relief valve (5) restricting the pressures of the cap-side chamber (1.4) and the rod-side chamber (1.5) found in the hydraulic actuator (1), a check valve (6) providing unidirectional flow from the hydraulic accumulator (3) line to the rod-side chamber (1.5) of the actuator (1) in order to prevent cavitation formation, and an accumulator charge circuit (7) maintaining the hydraulic accumulator (3) at a certain pressure level.
  • auxiliary components such as pressure relief valve (5) restricting the pressures of the cap-side chamber (1.4) and the rod-side chamber (1.5) found in the hydraulic actuator (1), a check valve (6) providing unidirectional flow from the hydraulic accumulator (3) line to the rod-side chamber (1.5) of the actuator (1) in order to prevent cavitation formation, and an accumulator charge circuit (7) maintaining the hydraulic accumulator (3) at a certain pressure level.
  • FIG. 2 shows a side profile view of a preferred embodiment of the shuttle valve (4) having an asymmetric partial opening at a central position.
  • the shuttle valve (4) mainly consists of an outer body (4.1) and a cylindrically-shaped valve spool (4.2) embedded in said body (4.1).
  • the valve spool (4.2) positioned centrally on the shuttle valve (4) determines the structure of the orifice opening.
  • One end of the cylindrical valve spool (4.2) is connected to the valve centering spring (4.3).
  • Said valve centering spring (4.3) is the factor determining the cracking pressure of the shuttle valve (4) and thus the size of the critical load region, by means of maintaining the valve spool (4.2) at a central position.
  • the shuttle valve (4) is a 3-way, 3-position internal pilot operated valve. With this regard, three ports (4.4, 4.5, 4.6) are found on the shuttle valve (4) body (4.1). Among these ports:
  • the improvement of the invention is found at a central position on the shuttle valve (4) spool (4.2) as a valve spool underlap (4.8) between Port B (4.5) and Port C (4.6), and a valve spool overlap (4.7) between Port A (4.4) and Port C (4.6).
  • the valve spool underlap (4.8) enables flow between the hydraulic accumulator line (C) connected to the hydraulic accumulator (3) and the rod-side chamber line (B) connected to the rod-side chamber (1.5) of the hydraulic actuator (1), while the shuttle valve (4) is in central position.
  • the valve spool overlap (4.7) prevents flow between the hydraulic accumulator line (C) connected to the hydraulic accumulator (3) and the cap-side chamber line (A) connected to the cap-side chamber (1.4) of the hydraulic actuator (1), while the shuttle valve (4) is in central position.
  • valve spool underlap (4.8) found between Port B (4.5) and Port C (4.6) at the region defined as critical load region, when the hydraulic actuator (1) is retracted, the differential flow rate formed in the system is sent to the hydraulic accumulator (3) through the hydraulic accumulator line (C). In this way, the shuttle valve (4) stays at the central position up to a certain velocity, and a stable operating region is obtained at the critical load region (F).
  • valve spool overlap (4.7) found between Port A (4.4) and Port C (4.6) flow rate passage is prevented between Port A (4.4) and Port C (4.6) and unnecessary flow rate is not formed between Port A (4.4) and Port B (4.5).
  • critical velocity is increased with regard to the shuttle valves having partially open A-C and B-C orifice structures at the central position [5].
  • movement of a single-rod hydraulic actuator (1) is controlled by means of regulating the flow rate of a two-port pump (2), in which the two ports are directly connected to the actuator.
  • the pump (2) used in the system can generate flow rate in both directions and both of its ports can be pressurized.
  • This component defined as pump (2) in hydraulic systems can also act as a hydraulic motor.
  • This component called as a pump (2) in the circuit and can operate in all four quadrants of the pressure-flow rate plane can preferably be a variable displacement pump or a variable speed constant displacement pump or a displacement and speed controlled hydraulic pump/motor.
  • the requirement for the hydrostatic system of the invention is to be able to regulate/adjust the output flow rate of the component defined as pump (2), instead of its physical structure.
  • the closed area found in front of the piston (1.1) of the hydraulic actuator (1) forms the cap-side chamber (1.4); while the closed area found at the rear part and including the piston rod (1.2) forms the rod-side chamber (1.5). Since the cap-side surface (1.6) of the piston (1.1) facing the cap-side chamber (1.4) and the rod-side surface (1.7) facing the rod-side chamber (1.5) have different areas, during the movement of the piston-rod (1.1, 1.2) assembly of the hydraulic actuator (1), unequal flow rates are formed at the inlet-outlet ports of the hydraulic actuator (1).
  • differential flow rate The difference between the flow rates entering and leaving the hydraulic actuator (1) at any moment is called as differential flow rate.
  • the differential flow rate is directly determined by the rod cross sectional area (1.8) of the actuator rod (1.2).
  • the differential flow rate formed by the hydraulic actuator (1) causes formation of deficient or excessive flow rate in the hydrostatic system having closed circuit structure. Therefore, a hydraulic accumulator (3) is used in order to eliminate differential flow rate and pump leakage etc. losses. Systems (7) having different hydraulic circuit structures can be used in order to charge or maintain the pressure level of said hydraulic accumulator (3).
  • bidirectional flow rate passage between the closed circuit hydraulic system and the hydraulic accumulator (3) is provided through the 3-way, 3-position, and internal pilot operated shuttle valve (4).
  • the position of the shuttle valve (4), and thus which one of the actuator chambers (1.4 or 1.5) that the hydraulic accumulator (3) would be connected is determined by the pressures of the actuator chambers (1.4 and 1.5), which are connected to the pilot lines of the shuttle valve (4). Pressures of the actuator chambers (1.4 and 1.5) are restricted in the hydraulic system by using pressure relief valve (5). Check valve (6) is used to prevent possible risk of cavitation.
  • ( q v ) is the total amount of flow rate passing through the shuttle valve
  • ( ⁇ ) is the ratio of the rod-side surface area (1.7) to the cap-side surface area (1.6)
  • (A) is the cap-side surface area (1.6)
  • ( ⁇ ) is the velocity of the actuator piston cylinder assembly (piston (1.1) and piston shaft (1.2)).
  • q V 1 ⁇ ⁇ A v
  • the velocity (v) of the hydraulic actuator (1) determines the direction of the flow rate passing through the shuttle valve (4).
  • forward movement ( v >0) deficient flow rate necessity occurs, and this deficiency is met for the system by the hydraulic accumulator (3).
  • backward movement ( v >0) excess flow rate is formed and it is sent to the hydraulic accumulator (3).
  • the hydrostatic system has 3 different circuit embodiments according to the position of the shuttle valve (4).
  • the position of the shuttle valve (4) is determined by the pressures of the actuator chambers (1.4 and 1.5), and therefore by the external force ( f L ) acting on the hydraulic actuator (1).
  • the accumulator line (C) is connected via the shuttle valve (4) to the actuator (1) cap-side chamber line (A) in the f L ⁇ (- ⁇ , f L 1 ) operating region found at the left hand side in Figure 3 , and to the rod-side chamber line (B) of the actuator (1) in the f L ⁇ ( f L 2 , ⁇ ) operating region found at the right hand side.
  • Shuttle valve (4) is in fully open position in these two regions, and the valve spool (4.2) position is saturated at its end position.
  • the shuttle valve (4) In the intermediate region defined by f L ⁇ ( f L 1, f L 2 ), the shuttle valve (4) is either centered or partially opened. This region is defined as critical load region (F).
  • the location of the critical load region (F) is determined by the hydraulic accumulator (3) pressure; while its size is determined by the cracking pressure of the shuttle valve (4) used.
  • the valve spool (4.2) can remain in the center position up to a certain actuator velocity
  • the differential flow rate [ ⁇ q] formed at the critical velocity [ ⁇ cr ] of the actuator (1) corresponds to the amount of maximum flow rate [ q V
  • x s 0 ] that can pass through the shuttle valve (4) when it is in center position [q V
  • valve body (4.1) which comprises a valve spool overlap (4.7) between Port A (4.4) and Port C (4.6), and a valve spool underlap (negative spool overlap) (4.8) between Port B (4.5) and Port C (4.6), when the valve spool (4.2) is in center position.
  • the valve spool (4.2) operates between said positive valve spool underlap (4.7) and valve spool overlap (4.8). In this way, in the region that is defined as critical load region (F), the problem of instability would be eliminated up to a certain velocity [ ⁇ cr ] when the actuator (1) is retracted.
  • shuttle valve (4) shown in Figure 2 is preferably chosen as cartridge type, it is also possible to apply the improvements of the present invention to shuttle valves of different types and geometric structures.
  • the centering spring (4.3) used for maintaining the valve spool (4.2) at the center position can be connected in another way or the valve spool underlap (4.8) and valve spool overlap (4.7) formed on the valve body via Port A (4.4), Port B (4.5), and Port C (4.6) within the scope of the invention can have a different geometric structure.

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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 (2)

  1. Geschlossener Kreislauf-Hydrostatiksystem, umfassend einen Einstangenhydraulikaktor (1) mit einem Zylinder (1.3), einem Kolben (1.1), einer Kolbenstange (1.2), einer kappenseitigen Kammer (1.4) und einer stangenseitigen Kammer (1.5);
    eine strömungsgeschwindigkeitsgeregelte Pumpe (2) mit zwei Anschlüssen, die eine Strömung in zwei Richtungen erzeugen kann;
    einen Hydraulikspeicher (3) und
    ein intern pilotfluidbetriebenes 3-Wege-3-Positionen-Wechselventil (4),
    wobei die kappenseitige Kammer (1.4) des Einstangenhydraulikaktors (1) einen Anschluss aufweist, der direkt mit einem der Anschlüsse der Pumpe (2) durch eine kappenseitige Kammerfluidleitung (A) verbunden ist,
    die stangenseitige Kammer (1.5) des Einstangenhydraulikaktors (1) einen Anschluss aufweist, der direkt mit dem anderen Anschluss der Pumpe (2) durch eine stangenseitige Kammerfluidleitung (B) verbunden ist,
    die strömungsgeschwindigkeitsgeregelte Pumpe (2), welche die Strömungsgeschwindigkeit regelt, zu dem Einstangenhydraulikaktor (1) strömt, der Hydraulikspeicher (3) zum Kompensieren der Differenzströmungsgeschwindigkeit verwendet wird, die in dem geschlossenen Kreislauf aufgrund einer Hydraulikaktor- (1) -Bewegung gebildet wird, und das Wechselventil (4) eine bidirektionale Strömung zwischen dem geschlossenen Kreislauf und dem Hydraulikspeicher (3) bereitstellt und einen Körper (4.1), einen Wechselventilschieber (4.2), der mit einer Ventilzentrierungsfeder (4.3) von seinem einen Ende am Innenteil des Körpers (4.1) verbunden ist, umfasst, wobei das Wechselventil (4) ferner umfasst:
    • Anschluss A (4.4), der mit der kappenseitigen Kammer (1.4) durch die kappenseitige Kammerfluidleitung (A) und den Anschluss der kappenseitigen Kammer (1.4), der sich am Zylinder (1.3) des Hydraulikaktors (1) befindet, fluidisch verbunden ist,
    • Anschluss B (4.5), der mit der stangenseitigen Kammer (1.5) durch die stangenseitige Kammerfluidleitung (B) und den Anschluss der stangenseitigen Kammer (1.5), der sich am Zylinder (1.3) des Hydraulikaktors (1) befindet, fluidisch verbunden ist, und
    • Anschluss C (4.6), der mit dem Hydraulikspeicher (3) durch eine Fluidleitung des Hydraulikspeichers (C), die sich an dem intern pilotbetriebenen 3-Wege-3-Positionen-Wechselventil- (4) -Körper (4.1) befindet, fluidisch verbunden ist, und
    gekennzeichnet durch, mit dem Betrieb des geschlossenen Hydrostatiksystems, um das Instabilitätsproblem zu verhindern, das während der Kompensation der Differenzströmungsgeschwindigkeit anzutreffen ist, die infolge der asymmetrischen
    • eine Ventilschieberüberdeckung (4.7), die sich zwischen dem Anschluss A (4.4), der mit der kappenseitigen Kammer (1.4) des Hydraulikaktors (1) verbunden ist, und dem Anschluss C (4.6), der mit dem Hydraulikspeicher (3) verbunden ist, befindet; und Verhindern der Strömung zwischen der Hydraulikspeicherleitung (C), die mit dem Hydraulikspeicher (3) verbunden ist, und der kappenseitigen Kammerleitung (A), die mit der kappenseitigen Kammer (1.4) des Hydraulikaktors (1) verbunden ist, und
    • eine Ventilschieberunterdeckung (4.8), die sich zwischen dem Anschluss B (4.5), der mit der stangenseitigen Kammer (1.5) des Hydraulikaktors (1) verbunden ist, und dem Anschluss C (4.6), der mit dem Hydraulikspeicher (3) verbunden ist, befindet; und Ermöglichen von Strömung zwischen der Hydraulikspeicherleitung (C), die mit dem Hydraulikspeicher (3) verbunden ist, und der stangenseitigen Kammerleitung (B), die mit der stangenseitigen Kammer (1.5) des Hydraulikaktors (1) verbunden ist, die am Wechselventilschieber (4.2) in der Mittelposition des Wechselventils (4) gebildet sind, was entsprechend in geschlossenen und teilweise offenen Öffnungsformen zwischen den Leitungen A-C und B-C resultiert.
  2. Geschlossener Kreislauf-Hydrostatiksystem nach Anspruch 1, ferner umfassend ein Rückschlagventil (6), das zwischen der Speicherleitung (C) und der stangenseitigen Aktorkammerleitung (B) in der Hydraulikeinheit positioniert ist, wo das Wechselventil (4) verwendet wird, und das Ermöglichen von unidirektionaler Strömung von der Hydraulikspeicher-(3) -Leitung zur stangenseitigen Kammer (1.5) des Aktors (1).
EP15174803.5A 2015-07-01 2015-07-01 Hydrostatische systeme mit wechselventilkörper zur kompensation der differentiellen durchflussrate von einzelstabaktuatoren Not-in-force EP3112697B1 (de)

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CN110552928A (zh) * 2019-09-24 2019-12-10 江苏徐工工程机械研究院有限公司 一种集成阀及浮动液压系统
CN113719248B (zh) * 2021-06-24 2024-04-30 江苏徐工工程机械研究院有限公司 一种夹钳同步控制系统、夹钳装置及钻机
CN113431816B (zh) * 2021-07-14 2022-04-15 长沙航空职业技术学院 对称不均等的负叠合比例阀控非对称缸系统的控制方法

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JPS58102806A (ja) 1981-12-15 1983-06-18 Hitachi Constr Mach Co Ltd アクチユエ−タ駆動油圧閉回路
US5329767A (en) 1993-01-21 1994-07-19 The University Of British Columbia Hydraulic circuit flow control
CN101341342B (zh) 2006-06-02 2011-05-18 布鲁宁赫斯海诺马帝克有限公司 具有容积流量补偿的静液压驱动机构
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KR101617609B1 (ko) 2008-02-12 2016-05-18 파커-한니핀 코포레이션 유압 작업 기계용 흐름 관리 시스템
WO2010028100A1 (en) 2008-09-03 2010-03-11 Parker Hannifin Corporation Velocity control of unbalanced hydraulic actuator subjected to over-center load conditions
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