EP2005006B1 - Vorgesteuerter druckkompensator mit verschiedenen bereichen und steuersystem zu seiner vorsteuerung - Google Patents

Vorgesteuerter druckkompensator mit verschiedenen bereichen und steuersystem zu seiner vorsteuerung Download PDF

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Publication number
EP2005006B1
EP2005006B1 EP07727891A EP07727891A EP2005006B1 EP 2005006 B1 EP2005006 B1 EP 2005006B1 EP 07727891 A EP07727891 A EP 07727891A EP 07727891 A EP07727891 A EP 07727891A EP 2005006 B1 EP2005006 B1 EP 2005006B1
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EP
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Prior art keywords
pressure
control system
line
compensator
valve
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EP07727891A
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English (en)
French (fr)
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EP2005006A1 (de
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Gianluca Ganassi
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Walvoil SpA
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Walvoil SpA
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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • 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
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/50—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the present invention relates to a differential-area pressure compensator and to its control system of the hydraulic, mechanical or electro-hydraulic type.
  • Directional control valves for controlling the fluid flow delivered to actuators regardless of pressure, are widely used in hydraulics.
  • Such valves are commonly known as load sensing directional control valves or load sensing control valves.
  • Flow sharing valves are a subset of these load sensing control valves.
  • Load sensing control valves are of the closed center or open center type.
  • open center load sensing control valves discharge all the flow delivered by the pump, while closed center control valves do not.
  • open center load sensing control valves have a pressure compensator bypass-connected to the delivery line, which discharges the pump-delivered fluid flow not demanded by the actuators; if the overall flow demanded by the actuators does not exceed the flow delivered by the pump, then the pressure compensator discharges the flow not demanded by the actuators at a delivery pressure that is equal to the higher pressure among the served ports, usually named LS pressure, plus a pressure margin depending on the compensator spring, e.g. 14 bar.
  • an open center load sensing control valve wastes a non negligible amount of power, equal to the flow delivered by the pump multiplied by the pressure margin .
  • DE 10 2004 014 113 A1 discloses a device for reducing the pressure margin in the standby state, thereby providing energy savings.
  • the pressure compensator 12 discharges all pump-delivered flow at the pressure of 3 bar, because the pressure on the spring side 13 is the discharge pressure, the pilot valve 17 being open; the pressure compensator 10 is closed because the delivery pressure does not reach 21 bar.
  • the pressure compensator 12 When at least one actuator requires oil, i.e. when the LS pressure is greater than zero, the pressure compensator 12 is in the closed position because the pressure on the spring side 13 is the delivery pressure, the pilot valve 17 being closed; the pressure compensator 10 discharges the flow not demanded by actuators at the pressure of 21 bar plus the LS pressure.
  • a valve bypass-connected to the delivery line in a load sensing control valve, discharges the pump-delivered fluid flow not demanded by the actuators to the low pressure line, at a first (lower) value or a second (higher) value of pressure margin, depending on how the valve is controlled by a hydraulic, mechanical or electrohydraulic control system.
  • the compensator is normally closed; it is biased closed by a spring and by the LS pressure; it is biased open by two pressures respectively exerted on two appropriately determined different areas, one subjected to the delivery pressure and the other to the delivery pressure or the LS pressure depending on the control system.
  • a first object of the present invention is to save energy in the standby state, by decreasing the pressure margin from the operating state to the standby state and increasing the pressure margin in the opposite case.
  • the control system is a three-way two-position hydraulically actuated pilot valve, which is biased on one side by the LS pressure and on the other side by a spring having a pressure rating of about 2 bar and by the discharge pressure: when the LS pressure is zero, the pilot valve transmits the delivery pressure to the compensator area controlled thereby; when the LS pressure is not zero, it transmits the LS pressure.
  • a second object of the present invention is specific for load sensing, flow sharing systems and consists in allowing the operator to select slow or fast operation of the machine, for normal or fine motion of the actuators.
  • control system is a three-way, two-position mechanically or electrically actuated pilot valve which, like the hydraulic pilot valve described above, transmits either the delivery pressure or the LS pressure to the compensator area controlled thereby.
  • a third object of the present invention is specific for load sensing, flow sharing systems and consists in simultaneously fulfilling the first and the second objects.
  • the control system is a three-way, two position hydraulically actuated pilot valve, combined with a three-way two-position mechanically or electrically actuated pilot valve:
  • the hydraulically actuated pilot valve is biased on one side by the LS pressure and on the other side by a spring having a pressure rating of about 2 bar and by the discharge pressure so that, when the LS pressure is zero, it transmits the delivery pressure, and when the LS pressure is not zero, it transmits the LS pressure to the solenoid valve.
  • the mechanically or electrically actuated pilot valve in turn transmits the delivery pressure or the pressure it receives from the hydraulically actuated three-way two-position pilot valve to the compensator area controlled thereby.
  • the compensator is normally closed; it is biased open by the delivery pressure; it is biased closed by a spring and by two pressures respectively exerted on two appropriately determined different areas, one subjected to the LS pressure and the other to the delivery pressure or the LS pressure depending on the control system.
  • control system can be designed to fulfill the first, second, or third objective.
  • Figure 1 shows a hydraulic circuit, including a fixed-displacement pump 1, connected by a high-pressure line P to a load sensing, flow sharing control valve V, which discharges the fluid through a low pressure line T into the tank 2.
  • the load sensing, flow sharing control valve V has an inlet cover F and two elements or sections E1 and E2, each controlling an actuator through the ports A1, B1 and A2, B2.
  • Each element has a spool 4, a local pressure compensator 3 comprising therein a signal selector S, which is mechanically kept open or closed by a piston 5 with a spring M of negligible force.
  • the piston 5 presses against the compensator 3 of the element E at the higher pressure in the control valve V, said compensator 3 and piston 5 thus acting as a check valve, whereas, in the sections at lower pressure, the piston 5 is kept detached from the compensator 3, so that this latter performs its function of pressure compensator.
  • the amount of fluid flowing through an orifice is proportional to the area of the orifice and to the square root of the pressure drop thereacross, assuming the other factors are equal.
  • flow rate is controlled by adjusting the position of the spool, as the effective pressure drop across the flow rate control or metering orifice of each spool is the same for all elements and is equal to pressure margin, regardless of the pressure of loads.
  • Pressure margin is a quasi constant value under flow unsaturated conditions and decreases as saturation occurs.
  • the high pressure line P is connected to the low pressure line T through the differential-area pressure compensator C piloted through the control line 15 by the control system S.
  • the compensator C is a two-way continuous position valve 6, which is biased closed by a spring 7 and by the LS pressure exerted on the surface 8, and is biased open by the pressure P exerted on the surface 9 and the control pressure of line 15 on the surface 10.
  • the valve 6 can be designed in various manners within the functional arrangement as set out above.
  • Figure 5 shows a first embodiment according to the first way of carrying out the differential-area pressure compensator shown in fig. 1 .
  • the control system S is a three-way, two-position pilot valve 11, whose spool is piloted on the surface 13 by the pressure T and is biased by a spring 12 whose force against the area of the control surface corresponds to about 2 bar; on the other surface 14 it is controlled by the LS pressure.
  • the pilot valve 11 normally transmits the pressure P to the surface 10 of the valve 6 through the control line 15, and it transmits the LS pressure when it is switched.
  • the differential-area compensator C piloted by the control system S of Figure 1 sets the pressure margin to a first value from 3 to 7 bar, e.g. 5 bar, if the operator does not actuate any spool, or to a second value from 14 to 25 bar, e.g. 14 bar, if the operator actuates at least one spool, thereby allowing to save energy in the standby state.
  • the LS pressure is zero, as no spool is operated.
  • the pilot valve 11 is in the position depicted in Figure 1 due to the bias of the spring 12, and transmits the pressure P to the surface 10 of the valve 6 through the line 15.
  • the pressure margin p P - p LS is equal to a first value, corresponding to F7 / A8, in this example to 5 bar: therefore, in the standby state, the differential-area compensator C controlled by the control system S of Figure 1 discharges the whole flow delivered by the pump 1 at a pressure of 5 bar.
  • the LS pressure increases and switches the pilot valve 11, whereby the control system S pilots the surface 10 of the valve 6 through the control line 15 with the LS pressure.
  • FIG 2 shows a load sensing, flow sharing control valve V comprising a pilot-operated differential-area pressure compensator C as shown in Figure 1 , in which the control system S is a three-way two-position electrically actuated spool 17.
  • the spool 17 normally transmits the LS pressure through the control line 15 and, in the excited position, it transmits the pressure P.
  • control system S allows to set the pressure margin to two values, e.g. 5 and 14 bar.
  • the flow to the port is proportional to the square root of the pressure margin, assuming the other factors are equal, therefore if the pressure margin decreases, flows to the workports are accordingly reduced, for finer control of the machine.
  • pressure margin control depends on the position of the electrically actuated spool 17, therefore on the operator, who can select normal speed (normal control) or reduced speed (fine control) of the machine actuators.
  • the operating principle is unchanged if the three-way two-position spool 17 is mechanically or electrically controlled.
  • FIG 3 shows a load sensing, flow sharing control valve V comprising a pilot-operated differential-area pressure compensator C as shown in Figures 1 and 2 , and a control system S in the form of a three-way two-position hydraulically actuated pilot valve 18 in combination with a three-way two-position electrically actuated spool 22.
  • the spool of the pilot valve 18 is piloted on the surface 20 by the pressure T and is biased by a spring 19 whose force against the area of the control surface corresponds to about 2 bar; on the other surface 21 it is controlled by the LS pressure.
  • the pilot valve 18 normally transmits the pressure P to the spool 22 through the line 23, and it transmits the LS pressure when it is switched.
  • the spool 22 normally connects the line 23 to the control line 15 and, in the excited position, it transmits the pressure P to the control line 15.
  • the differential-area compensator C When the spool 22 is in the position shown in figure 3 , the differential-area compensator C, controlled by the control system S , sets the pressure margin to a first value, e.g. 5 bar, if the operator does not actuate any spool, or to a second value, e.g. 14 bar, if the operator actuates at least one spool, thereby allowing to save energy in the standby state; when the operator switches the spool 22, the pressure margin is set to the first 5 bar value even in operating conditions, for fine control of the machine actuators.
  • a first value e.g. 5 bar
  • a second value e.g. 14 bar
  • the high pressure line P is connected to the low pressure line T through the differential-area pressure compensator C piloted through the control line 33 by the control system S.
  • the compensator C is a two-way continuous position valve 24, which is biased open by the pressure P exerted on the surface 28, and is biased closed by a spring 25, by the control pressure of 33 exerted on the surface 26 and by the LS pressure on the surface 27.
  • the valve 24 can be designed in various manners within the functional arrangement as set out above.
  • Figure 6 shows an embodiment according to the second way of carrying out the differential-area pressure compensator shown in fig. 4 .
  • the control system S is a three-way, two-position pilot valve 29, whose spool is piloted on the surface 31 by the discharge pressure p T and is biased by a spring 30 whose force against the area of the control surface corresponds to about 2 bar; on the other surface 32 it is piloted by the LS pressure.
  • the pilot valve 29 normally transmits the LS pressure to the surface 26 of the valve 24 through the control line 33, and it transmits the pressure pp when it is switched.
  • the differential-area compensator C controlled by the control system S of Figure 4 sets the pressure margin to a first value from 3 to 7 bar, e.g. 5 bar, if the operator does not actuate any spool, or to a second value from 14 to 25 bar, e.g. 14 bar, if the operator actuates at least one spool, thereby allowing to save energy in the standby state.
  • the LS pressure is zero, as no spool is operated.
  • the pilot valve 29 is in the position depicted in Figure 4 due to the bias of the spring 30, and transmits the LS pressure to the surface 26 of the valve 24 through the line 33.
  • the pressure margin pP - pLS is equal to a first value, corresponding to F25 / A28, in this example to 5 bar, therefore, in the standby state, the differential-area compensator C controlled by the control system S of Figure 4 discharges the whole flow delivered by the pump 1 at a pressure of 5 bar.
  • the LS pressure increases and switches the valve 29, whereby the control system S pilots the surface 26 of the valve 24 through the line 33 with the pressure pP.
  • control systems described above for the compensator according to the first way of carrying out the present invention can be easily used for the compensator of the second way of carrying out the present invention.
  • Figure 5 shows an embodiment according to the first way of carrying out the differential-area pressure compensator shown in Figure 1 .
  • a passage 106 is formed in the body 108 of the inlet cover F, whose section has an area A8 and within which the valve 6 slides between two plugs 115 and 116.
  • Two annular recesses 105 and 103 are provided within the passage 106: the recess 105 receives pressurized fluid through the high pressure P line from the pump 1; the recess 103 is connected to the tank 2 through the low pressure T line.
  • the valve 6 normally closes the connection between the recesses, 105 and 103 because its edge 111 covers the edge 110 of the body 108.
  • the spring 7 operates in the closing direction on the surface 8 of the valve 6 in combination with the LS pressure reigning in the chamber 107, which is delimited by the surface 8, the body 108 and the plug 116.
  • a bore 114 whose section has an area A9, is formed in the valve 6, on the opposite side of the surface 8.
  • a piston 100 sliding within the bore 114, has two surfaces at its ends, the surface 112 on the side of the valve 6, and the surface 101 on the side of the plug 115.
  • the piston 100 delimits a chamber 113 between the surface 112 and the surface 9, in which there is the pressure P, thanks to the holes 109 and 104 in the valve 6.
  • the piston 100 When in the chamber 102 there is the LS pressure, the piston 100 is biased against the plug 115 by the pressure pP in 113, and when in the chamber 102 there is the pressure pP, the piston 100 is in neutral equilibrium. In both cases, the piston 100 exerts no force on the valve 6, whose balanced state is determined by the pressures exerted on the surfaces 8, 9 and 10 and by the spring 7, as explained in the description of Figure 1 .
  • Figure 6 shows an embodiment according to the second way of carrying out the differential-area pressure compensator shown in Figure 4 .
  • a bore 211 is formed in the body 209 of the inlet cover F, whose section has an area A27 and within which the valve 204 slides.
  • Two recesses 205 and 203 are provided within the bore 211: the recess 205 receives pressurized fluid through the high pressure P line from the pump 1; the recess 203 is connected to the tank 2 through the low pressure T line.
  • the valve 204 normally closes the connection between the recess 205 and the recess 203 because its edge 208 covers the edge 207 of the body 209.
  • the spring 25 operates in the closing direction on the surface 27 of the valve 204 in combination with the LS pressure reigning in the chamber 206, which is delimited by the surface 27, the plug 215 and the body 209.
  • a piston 201 slides within the bore 210 and has two surfaces at its ends, the surface 212 on the side of the valve 204, and the surface 28 on the side of the plug 214.
  • the piston 201 delimits a chamber 200 with the surface 28, the body 209 and the plug 214, with the delivery pressure pP therein.
  • the piston 201 When the pressure in the chamber 202 is the LS pressure, the piston 201 is pushed against the valve 204 by the pressure pP in the chamber 200.

Claims (7)

  1. Von einem Kontrollsystem (S) gesteuerter Differenz-Flächen-Druckausgleicher (C), wobei das gesagte Kontrollsystem (S) des hydraulischen, mechanischen oder elektro-hydraulischen Typs ist, in einem gegen eine hydraulische Ladung empfindlichen Kontrollventil (V), enthaltend eine Hochdruckleitung (P), eine Niederdruckleitung (T), und eine Leitung (LS) bei dem LS Druck der höheren Ladung, wobei der gesagte üblicherweise geschlossene und dauerhaft ausrichtende Zwei-Weg-Ausgleicher (C) die Hochdruckleitung (P) mit der Niederdruckleitung (T) verbindet, wobei der gesagte Ausgleicher (C) den von einer Pumpe gelieferten und nicht von den Aktoren geforderten Fluss einer Flüssigkeit zur Niederdruckleitung (T) auslädt, und wobei die Druckgrenze bei der er den von der Pumpe gelieferten und nicht von den Aktoren geforderten Fluss der Flüssigkeit gleich einem ersten Wert von 3 bis 7 bar ist, oder einem zweiten Wert von 14 bis 25 bar ist, in Abhängigkeit davon, wie der gesagte Differenz-Flächen-Ausgleicher (C) von einem Kontrollsystem (S) gesteuert wird, wobei der gesagte Ausgleicher (C) von der Wirkung einer Feder (7) und des LS Druckes auf einer ersten Oberfläche (8) in Richtung eines Schließens beaufschlagt ist und von der Wirkung des Lieferdruckes (P) auf einer zweiten Oberfläche (9) und von dem vom Kontrollsystem (S) auf einer dritten Oberfläche (10) übertragenen Pilotdruck beaufschlagt ist, wobei die Summe der Flächen der letzten zwei Oberflächen (9, 10) gleich der Fläche der ersten ist, und wobei der Pilotdruck des Kontrollsystems (S) gleich dem Lieferdruck (P) oder dem LS Druck ist, dadurch gekennzeichnet, dass das gesagte Kontrollsystem ein 3-Weg- 2-Stellung- Pilotventil (11) ist, gesteuert vom Niederdruck LS, das wenn der LS Druck gleich Null ist, den Lieferdruck der von ihm kontrollierter Oberfläche (10) überträgt, während, wenn der LS Druck ungleich Null ist, den LS Druck überträgt.
  2. Von einem Kontrollsystem (S) gesteuerter Differenz-Flächen-Druckausgleicher (C), wobei das gesagte Kontrollsystem (S) des hydraulischen, mechanischen oder elektro-hydraulischen Typs ist, in einem gegen eine hydraulische Ladung empfindlichen Kontrollventil (V), enthaltend eine Hochdruckleitung (P), eine Niederdruckleitung (T), und eine Leitung (LS) bei dem LS Druck der höheren Ladung, wobei der gesagte üblicherweise geschlossene und dauerhaft ausrichtende Zwei-Weg-Ausgleicher (C) die Hochdruckleitung (P) mit der Niederdruckleitung (T) verbindet, wobei der gesagte Ausgleicher (C) den von einer Pumpe gelieferten und nicht von den Aktoren geforderten Fluss einer Flüssigkeit zur Niederdruckleitung (T) auslädt, und wobei die Druckgrenze bei der er den von der Pumpe gelieferten und nicht von den Aktoren geforderten Fluss der Flüssigkeit gleich einem ersten Wert von 3 bis 7 bar ist, oder einem zweiten Wert von 14 bis 25 bar ist, in Abhängigkeit davon, wie der gesagte Differenz-Flächen-Ausgleicher (C) von einem Kontrollsystem (S) gesteuert wird, wobei der gesagte Ausgleicher (C) von der Wirkung einer Feder (7) und des LS Druckes auf einer ersten Oberfläche (8) in Richtung eines Schließens beaufschlagt ist und von der Wirkung des Lieferdruckes (P) auf einer zweiten Oberfläche (9) und von dem vom Kontrollsystem (S) auf einer dritten Oberfläche (10) übertragenen Pilotdruck beaufschlagt ist, wobei die Summe der Flächen der letzten zwei Oberflächen (9, 10) gleich der Fläche der ersten ist, und wobei der Pilotdruck des Kontrollsystems (S) gleich dem Lieferdruck (P) oder dem LS Druck ist, dadurch gekennzeichnet, dass das gesagte Kontrollsystem ein 3-Weg- 2-Stellung- Pilotspule (17) ist, elektrisch oder mechanisch gesteuert, die den Lieferdruck (P) oder den LS Druck der von ihm gesteuerten Oberfläche überträgt.
  3. Von einem Kontrollsystem (S) gesteuerter Differenz-Flächen-Druckausgleicher (C), wobei das gesagte Kontrollsystem (S) des hydraulischen, mechanischen oder elektro-hydraulischen Typs ist, in einem gegen eine hydraulische Ladung empfindlichen Kontrollventil (V), enthaltend eine Hochdruckleitung (P), eine Niederdruckleitung (T), und eine Leitung (LS) bei dem LS Druck der höheren Ladung, wobei der gesagte üblicherweise geschlossene und dauerhaft ausrichtende Zwei-Weg-Ausgleicher (C) die Hochdruckleitung (P) mit der Niederdruckleitung (T) verbindet, wobei der gesagte Ausgleicher (C) den von einer Pumpe gelieferten und nicht von den Aktoren geforderten Fluss einer Flüssigkeit zur Niederdruckleitung (T) auslädt, und wobei die Druckgrenze bei der er den von der Pumpe gelieferten und nicht von den Aktoren geforderten Fluss der Flüssigkeit gleich einem ersten Wert von 3 bis 7 bar ist, oder einem zweiten Wert von 14 bis 25 bar ist, in Abhängigkeit davon, wie der gesagte Differenz-Flächen-Ausgleicher (C) von einem Kontrollsystem (S) gesteuert wird, wobei der gesagte Ausgleicher (C) von der Wirkung einer Feder (7) und des LS Druckes auf einer ersten Oberfläche (8) in Richtung eines Schließens beaufschlagt ist und von der Wirkung des Lieferdruckes (P) auf einer zweiten Oberfläche (9) und von dem vom Kontrollsystem (S) auf einer dritten Oberfläche (10) übertragenen Pilotdruck beaufschlagt ist, wobei die Summe der Flächen der letzten zwei Oberflächen (9, 10) gleich der Fläche der ersten ist, und wobei der Pilotdruck des Kontrollsystems (S) gleich dem Lieferdruck (P) oder dem LS Druck ist, dadurch gekennzeichnet, dass das gesagte Kontrollsystem ein 3-Weg- 2-Stellung- Pilotventil (18) ist, gesteuert vom LS Druck, in Verbindung mit einer 3-Weg- 2-Stellung-Pilotspule (22), elektrisch oder mechanisch gesteuert, wobei das hydraulische Pilotventil (18) der Spule (22) den Lieferdruck (22) überträgt, wenn der LS Druck gleich Null ist, oder den LS Druck wenn der LS Druck ungleich Null ist, und wobei die Spule (22) jeweils den Lieferdruck (P) oder den Druck überträgt, den es vom 3-Weg 2-Stellung- Ventil (18) empfängt und gesteuert vom LS Druck auf der Oberfläche (10) ist.
  4. Von einem Kontrollsystem (S) gesteuerter Differenz-Flächen-Druckausgleicher (C), wobei das gesagte Kontrollsystem (S) des hydraulischen, mechanischen oder elektro-hydraulischen Typs ist, in einem gegen eine hydraulische Ladung empfindlichen Kontrollventil (V), enthaltend eine Hochdruckleitung (P), eine Niederdruckleitung (T), und eine Leitung (LS) bei dem LS Druck der höheren Ladung, wobei der gesagte üblicherweise geschlossene und dauerhaft ausrichtende Zwei-Weg-Ausgleicher (C) die Hochdruckleitung (P) mit der Niederdruckleitung (T) verbindet, wobei der gesagte Ausgleicher (C) den von einer Pumpe gelieferten und nicht von den Aktoren geforderten Fluss einer Flüssigkeit zur Niederdruckleitung (T) auslädt, und wobei die Druckgrenze bei der er den von der Pumpe gelieferten und nicht von den Aktoren geforderten Fluss der Flüssigkeit gleich einem ersten Wert von 3 bis 7 bar ist, oder einem zweiten Wert von 14 bis 25 bar ist, in Abhängigkeit davon, wie der gesagte Differenz-Flächen-Ausgleicher (C) von einem Kontrollsystem (S) gesteuert wird, wobei der gesagte Ausgleicher (C) von der Wirkung des Lieferdruckes (P) auf einer ersten Oberfläche (28) in Richtung eines Öffnens beaufschlagt ist und von der Wirkung einer Feder (25), des LS Druckes auf einer zweiten Oberfläche (27) und von dem vom Kontrollsystem (S) auf einer dritten Oberfläche (26) übertragenen Steuerung in Richtung eines Schließens beaufschlagt ist, wobei die Summe der Flächen der letzten zwei Oberflächen (27, 26) gleich der Fläche der ersten (28) ist, und wobei der Pilotdruck des Kontrollsystems (S) gleich dem Lieferdruck (P) oder dem LS Druck ist, dadurch gekennzeichnet, dass das gesagte Kontrollsystem ein 3-Weg- 2-Stellung- Pilotventil (29) ist, gesteuert vom LS Druck, in Verbindung mit einer 3-Weg- 2-Stellung-Pilotspule (22), das, wenn der LS Druck gleich Null ist, den LS Druck auf der von ihm gesteuerten Oberfläche überträgt, während wenn der LS Druck ungleich Null ist, den Lieferdruck überträgt.
  5. Von einem Kontrollsystem (S) gesteuerter Differenz-Flächen-Druckausgleicher (C), wobei das gesagte Kontrollsystem (S) des hydraulischen, mechanischen oder elektro-hydraulischen Typs ist, in einem gegen eine hydraulische Ladung empfindlichen Kontrollventil (V), enthaltend eine Hochdruckleitung (P), eine Niederdruckleitung (T), und eine Leitung (LS) bei dem LS Druck der höheren Ladung, wobei der gesagte üblicherweise geschlossene und dauerhaft ausrichtende Zwei-Weg-Ausgleicher (C) die Hochdruckleitung (P) mit der Niederdruckleitung (T) verbindet, wobei der gesagte Ausgleicher (C) den von einer Pumpe gelieferten und nicht von den Aktoren geforderten Fluss einer Flüssigkeit zur Niederdruckleitung (T) auslädt, und wobei die Druckgrenze bei der er den von der Pumpe gelieferten und nicht von den Aktoren geforderten Fluss der Flüssigkeit gleich einem ersten Wert von 3 bis 7 bar ist, oder einem zweiten Wert von 14 bis 25 bar ist, in Abhängigkeit davon, wie der gesagte Differenz-Flächen-Ausgleicher (C) von einem Kontrollsystem (S) gesteuert wird, wobei der gesagte Ausgleicher (C) von der Wirkung des Lieferdruckes (P) auf einer ersten Oberfläche (28) in Richtung eines Öffnens beaufschlagt ist und von der Wirkung einer Feder (25), des LS Druckes auf einer zweiten Oberfläche (27) und von dem vom Kontrollsystem (S) auf einer dritten Oberfläche (26) Steuerung in Richtung eines Schließens beaufschlagt ist, wobei die Summe der Flächen der letzten zwei Oberflächen (27, 26) gleich der Fläche der ersten (28) ist, und wobei der Pilotdruck des Kontrollsystems (S) gleich dem Lieferdruck (P) oder dem LS Druck ist, dadurch gekennzeichnet, dass das gesagte Kontrollsystem ein 3-Weg- 2-Stellung-Pilotventil, elektrisch oder mechanisch gesteuert, das den Lieferdruck (P) oder den LS Druck auf der von ihm gesteuerten Oberfläche (26) überträgt.
  6. Von einem Kontrollsystem (S) gesteuerter Differenz-Flächen-Druckausgleicher (C), wobei das gesagte Kontrollsystem (S) des hydraulischen, mechanischen oder elektro-hydraulischen Typs ist, in einem gegen eine hydraulische Ladung empfindlichen Kontrollventil (V), enthaltend eine Hochdruckleitung (P), eine Niederdruckleitung (T), und eine Leitung (LS) bei dem LS Druck der höheren Ladung, wobei der gesagte üblicherweise geschlossene und dauerhaft ausrichtende Zwei-Weg-Ausgleicher (C) die Hochdruckleitung (P) mit der Niederdruckleitung (T) verbindet, wobei der gesagte Ausgleicher (C) den von einer Pumpe gelieferten und nicht von den Aktoren geforderten Fluss einer Flüssigkeit zur Niederdruckleitung (T) auslädt, und wobei die Druckgrenze bei der er den von der Pumpe gelieferten und nicht von den Aktoren geforderten Fluss der Flüssigkeit gleich einem ersten Wert von 3 bis 7 bar ist, oder einem zweiten Wert von 14 bis 25 bar ist, in Abhängigkeit davon, wie der gesagte Differenz-Flächen-Ausgleicher (C) von einem Kontrollsystem (S) gesteuert wird, wobei der gesagte Ausgleicher (C) von der Wirkung des Lieferdruckes (P) auf einer ersten Oberfläche (28) in Richtung eines Öffnens beaufschlagt ist und von der Wirkung einer Feder (25), des LS Druckes auf einer zweiten Oberfläche (27) und von dem vom Kontrollsystem (S) auf einer dritten Oberfläche (26) Steuerung in Richtung eines Schließens beaufschlagt ist, wobei die Summe der Flächen der letzten zwei Oberflächen (27, 26) gleich der Fläche der ersten (28) ist, und wobei der Pilotdruck des Kontrollsystems (S) gleich dem Lieferdruck (P) oder dem LS Druck ist, dadurch gekennzeichnet, dass das gesagte Kontrollsystem ein 3-Weg- 2-Stellunghydraulisches Pilotventil, vom LS Druck gesteuert, in Verbindung mit einem 3-Weg- 2-Stellung- manuell oder elektrisch gesteuerten Ventil, wobei das hydraulische Pilotventil dem Solenoid-Ventil den LS Druck überträgt wenn der LS Druck gleich Null ist, oder den Lieferdruck (P) wenn der LS Druck ungleich Null ist, und das Solenoid-Ventil jeweils den LS Druck oder den Druck überträgt, den es vom 3-Weg- 2-Stellung- Ventil empfängt, vom LS Druck gesteuert auf der Oberfläche (26).
  7. Ausgleicher (C) nach Anspruch 4 oder 5 oder 6, dadurch gekennzeichnet, dass es aus einem Ventil (204) und einem Kolben (201) besteht, deren Durchmesser grösser als die Spule des Ventils (204) ist;
    - das gesagte Ventil (204) wird von der Feder (25) und von dem LS Druck beaufschlagt, und ist mittels des Pilotdruckes des Kontrollsystems (S) und des Kolbens (201) offen gehalten,
    - der gesagte Kolben (201) wird auf einer Seite von dem Ventil (204) und von dem Pilotdruck des Kontrollsystems gedrückt, und auf der anderen Seite von dem Druck der Hochdruckleitung (P) gedrückt.
EP07727891A 2006-04-12 2007-04-06 Vorgesteuerter druckkompensator mit verschiedenen bereichen und steuersystem zu seiner vorsteuerung Active EP2005006B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000036A ITPR20060036A1 (it) 2006-04-12 2006-04-12 Compensatore di pressione ad aree differenziali pilotato e suo sistema di pilotaggio.
PCT/EP2007/053423 WO2007116035A1 (en) 2006-04-12 2007-04-06 Pilot-operated differential-area pressure compensator and control system for piloting same

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EP2005006A1 EP2005006A1 (de) 2008-12-24
EP2005006B1 true EP2005006B1 (de) 2010-09-29

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CN104047931A (zh) * 2014-06-23 2014-09-17 柳州柳工液压件有限公司 三通压力补偿器总成

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US8375975B2 (en) 2007-06-26 2013-02-19 Walvoil S.P.A. Load sensing directional control valve with an element having priority under saturation conditions
IT1391608B1 (it) * 2008-11-06 2012-01-11 Walvoil Spa Metodo per limitare la potenza massima richiesta dall impianto idraulico di una macchina per movimento terra e distributore operante detto metodo
EP4279750A1 (de) 2021-10-21 2023-11-22 Bucher Hydraulics S.p.A. Einlassabschnitt zur verwendung in einem hydraulischen verteiler

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US3937129A (en) * 1974-10-23 1976-02-10 The Scott & Fetzer Company Load responsive system with area change flow extender
DE3905654C2 (de) * 1989-02-24 1998-10-29 Bosch Gmbh Robert Hydraulische Steuervorrichtung
JP2004019873A (ja) * 2002-06-19 2004-01-22 Toyota Industries Corp 油圧制御装置および該油圧制御装置を備えた産業車両
DE102004014113A1 (de) 2004-03-23 2005-10-20 Sauer Danfoss Aps Nordborg Hydraulische Ventilanordnung
US7182097B2 (en) 2004-08-17 2007-02-27 Walvoil S.P.A. Anti-saturation directional control valve composed of two or more sections with pressure selector compensators

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104047931A (zh) * 2014-06-23 2014-09-17 柳州柳工液压件有限公司 三通压力补偿器总成
CN104047931B (zh) * 2014-06-23 2017-01-04 柳州柳工液压件有限公司 三通压力补偿器总成

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EP2005006A1 (de) 2008-12-24
WO2007116035A1 (en) 2007-10-18
ITPR20060036A1 (it) 2007-10-13
ATE483111T1 (de) 2010-10-15

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