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WO2007116035A1 - Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter - Google Patents

Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter Download PDF

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Publication number
WO2007116035A1
WO2007116035A1 PCT/EP2007/053423 EP2007053423W WO2007116035A1 WO 2007116035 A1 WO2007116035 A1 WO 2007116035A1 EP 2007053423 W EP2007053423 W EP 2007053423W WO 2007116035 A1 WO2007116035 A1 WO 2007116035A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
control system
compensator
way
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.)
Ceased
Application number
PCT/EP2007/053423
Other languages
English (en)
Inventor
Gianluca Ganassi
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.)
Walvoil SpA
Original Assignee
Walvoil SpA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Walvoil SpA filed Critical Walvoil SpA
Priority to EP07727891A priority Critical patent/EP2005006B1/fr
Priority to AT07727891T priority patent/ATE483111T1/de
Priority to DE602007009509T priority patent/DE602007009509D1/de
Publication of WO2007116035A1 publication Critical patent/WO2007116035A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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

  • TITLE PILOT-OPERATED DIFFERENTIAL-AREA PRESSURE COMPENSATOR AND CONTROL SYSTEM FOR PILOTING SAME
  • the present invention relates to a differential- area pressure compensator and to its control system of the hydraulic , mechanical or electrohydraulic 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 . They behave like any other load sensing control valve when the pump delivers enough flow to meet the demand of the actuators; in addition, when the system is in a flow saturation condition, they distribute the pump-delivered flow to all operating ports proportionally to their demand, without causing any operating actuator to stop.
  • 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.
  • LS pressure higher pressure among the served ports
  • 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 .
  • 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.
  • the object of this invention is to provide a valve, bypass-connected to the delivery line in a load sensing control valve, which 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 pressure compensator operates with differential areas and is controlled by a 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 second 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.
  • 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 third 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 fourth object of the present invention is specific for load sensing, flow sharing systems and consists in simultaneously fulfilling the second and the third 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 pressure compensator operates with differential areas and is controlled by a control system.
  • 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 second, third or fourth objective.
  • Figure 1 is a hydraulic diagram showing a first way of carrying out the differential-area pressure compensator piloted by a control system, in which the control system is a three-way two-position hydraulically actuated pilot valve;
  • Figure 2 is a hydraulic diagram showing a variant of the control system of the pilot-operated differential-area pressure compensator of Figure 1, in which the control system is a three-way two-position electrically actuated pilot valve;
  • Figure 3 is a hydraulic diagram showing a variant of the control system of the pilot-operated differential-area pressure compensator as shown in Figures 1 and 2, in which the control system is a three-way two-position hydraulically actuated valve in combination with a three-way two-position electrically actuated pilot valve;
  • FIG. 4 is a hydraulic diagram showing a second way of carrying out the differential-area pressure compensator piloted by a control system, in which the control system is a three-way two-position hydraulically actuated pilot valve;
  • FIG. 5 shows the preferred embodiment of the differential-area pressure compensator according to the first way of carrying out the present invention shown in Figure 1 ;
  • FIG. 6 shows the preferred embodiment of the differential-area pressure compensator according to the second way of carrying out the present invention shown in Figure 4.
  • 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
  • the load sensing, flow sharing control valve V has an inlet cover F and two elements or sections El and E2 , each controlling an actuator through the ports Al , Bl 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 the preferred embodiment according to the first way of carrying out the present invention 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
  • 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.
  • 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
  • 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.
  • 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 .
  • Figure 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 .
  • 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
  • valve 24 is designed in such a manner that:
  • the valve 24 can be designed in various manners within the functional arrangement as set out above.
  • Figure 6 shows the preferred embodiment according to the second way of carrying out the present invention shown in fig. 4.
  • the control system S is a three-way, two-position pilot valve 29, whose spool is piloted on the surface
  • 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 p P 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 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 the preferred embodiment for the differential-area pressure compensator according to the first way of carrying out the present invention 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
  • 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 the preferred embodiment for the differential-area pressure compensator according to the second way of carrying out the present invention 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 passage 210 In the body 209, opposite to the surface 27, there is a passage 210, of greater diameter than the bore 211, whose section has an area A28.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Control Of Fluid Gearings (AREA)
  • Control Of Transmission Device (AREA)

Abstract

L'invention concerne une vanne de régulation directionnelle à détection de charge hydraulique dans laquelle un compensateur de pression, relié par dérivation à la conduite de distribution, évacue le débit de fluide distribué par la pompe et non exigé par les actionneurs vers la conduite à basse pression, avec une première valeur (inférieure) ou une deuxième valeur (supérieure) de marge de pression, en fonction de la façon dont une de ses zones différentielles est pilotée par un système de commande hydraulique, mécanique ou électro-hydraulique.
PCT/EP2007/053423 2006-04-12 2007-04-06 Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter Ceased WO2007116035A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07727891A EP2005006B1 (fr) 2006-04-12 2007-04-06 Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter
AT07727891T ATE483111T1 (de) 2006-04-12 2007-04-06 Vorgesteuerter druckkompensator mit verschiedenen bereichen und steuersystem zu seiner vorsteuerung
DE602007009509T DE602007009509D1 (de) 2006-04-12 2007-04-06 Vorgesteuerter druckkompensator mit verschiedenen bereichen und steuersystem zu seiner vorsteuerung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPR2006A000036 2006-04-12
IT000036A ITPR20060036A1 (it) 2006-04-12 2006-04-12 Compensatore di pressione ad aree differenziali pilotato e suo sistema di pilotaggio.

Publications (1)

Publication Number Publication Date
WO2007116035A1 true WO2007116035A1 (fr) 2007-10-18

Family

ID=38229093

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/053423 Ceased WO2007116035A1 (fr) 2006-04-12 2007-04-06 Compensateur de pression a zones differentielles et a fonctionnement pilote, et systeme de commande pour le piloter

Country Status (5)

Country Link
EP (1) EP2005006B1 (fr)
AT (1) ATE483111T1 (fr)
DE (1) DE602007009509D1 (fr)
IT (1) ITPR20060036A1 (fr)
WO (1) WO2007116035A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009001377A1 (fr) * 2007-06-26 2008-12-31 Walvoil S.P.A. Soupape de commande directionnelle à détection de charge dont un élément a la priorité dans des conditions de saturation
ITPR20080071A1 (it) * 2008-11-06 2010-05-07 Walvoil Spa Metodo per limitare la potenza massima richiesta dall impianto idraulico di una macchina per movimento terra e distributore operante detto metodo
EP4170188A1 (fr) 2021-10-21 2023-04-26 Bucher Hydraulics S.p.A. Section d'entrée destinée à être utilisée dans un distributeur hydraulique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3937129A (en) * 1974-10-23 1976-02-10 The Scott & Fetzer Company Load responsive system with area change flow extender
DE3905654A1 (de) * 1989-02-24 1990-08-30 Bosch Gmbh Robert Hydraulische steuervorrichtung
EP1375927A2 (fr) * 2002-06-19 2004-01-02 Kabushiki Kaisha Toyota Jidoshokki Dispositif de commande hydraulique et engin à travaux avec un dispositif de commande hydraulique
DE102004014113A1 (de) 2004-03-23 2005-10-20 Sauer Danfoss Aps Nordborg Hydraulische Ventilanordnung
US20060037649A1 (en) 2004-08-17 2006-02-23 Walvoil S.P.A. Anti-saturation directional control valve composed of two or more sections with pressure selector compensators

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3937129A (en) * 1974-10-23 1976-02-10 The Scott & Fetzer Company Load responsive system with area change flow extender
DE3905654A1 (de) * 1989-02-24 1990-08-30 Bosch Gmbh Robert Hydraulische steuervorrichtung
EP1375927A2 (fr) * 2002-06-19 2004-01-02 Kabushiki Kaisha Toyota Jidoshokki Dispositif de commande hydraulique et engin à travaux avec un dispositif de commande hydraulique
DE102004014113A1 (de) 2004-03-23 2005-10-20 Sauer Danfoss Aps Nordborg Hydraulische Ventilanordnung
US20060037649A1 (en) 2004-08-17 2006-02-23 Walvoil S.P.A. Anti-saturation directional control valve composed of two or more sections with pressure selector compensators

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009001377A1 (fr) * 2007-06-26 2008-12-31 Walvoil S.P.A. Soupape de commande directionnelle à détection de charge dont un élément a la priorité dans des conditions de saturation
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
ITPR20080071A1 (it) * 2008-11-06 2010-05-07 Walvoil Spa Metodo per limitare la potenza massima richiesta dall impianto idraulico di una macchina per movimento terra e distributore operante detto metodo
EP2184495A1 (fr) * 2008-11-06 2010-05-12 Walvoil S.p.A. Procédé de limitation de la puissance maximale requise par le système hydraulique d'un engin de terrassement et vanne de contrôle directionnelle permettant de faire fonctionner ce procédé
EP4170188A1 (fr) 2021-10-21 2023-04-26 Bucher Hydraulics S.p.A. Section d'entrée destinée à être utilisée dans un distributeur hydraulique
EP4279750A1 (fr) 2021-10-21 2023-11-22 Bucher Hydraulics S.p.A. Section d'entrée destinée à être utilisée dans un distributeur hydraulique
US11852249B2 (en) 2021-10-21 2023-12-26 Bucher Hydraulics S.P.A Inlet section for use in a hydraulic distributor
US12123502B2 (en) 2021-10-21 2024-10-22 Bucher Hydraulics S.P.A Inlet section for use in a hydraulic distributor

Also Published As

Publication number Publication date
EP2005006A1 (fr) 2008-12-24
EP2005006B1 (fr) 2010-09-29
ATE483111T1 (de) 2010-10-15
DE602007009509D1 (de) 2010-11-11
ITPR20060036A1 (it) 2007-10-13

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