EP0502411A2 - Système hydraulique pour commander un vérin entraîné par une charge - Google Patents

Système hydraulique pour commander un vérin entraîné par une charge Download PDF

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Publication number
EP0502411A2
EP0502411A2 EP92103245A EP92103245A EP0502411A2 EP 0502411 A2 EP0502411 A2 EP 0502411A2 EP 92103245 A EP92103245 A EP 92103245A EP 92103245 A EP92103245 A EP 92103245A EP 0502411 A2 EP0502411 A2 EP 0502411A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
consumer
magnet
pilot
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.)
Withdrawn
Application number
EP92103245A
Other languages
German (de)
English (en)
Other versions
EP0502411A3 (en
Inventor
Günter Winkels
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP0502411A2 publication Critical patent/EP0502411A2/fr
Publication of EP0502411A3 publication Critical patent/EP0502411A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • F15B2211/21—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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/505—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
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—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
    • F15B2211/70—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
    • F15B2211/7052—Single-acting output members

Definitions

  • the invention relates to a hydraulic system for controlling a force moving a consumer with a pilot-controlled main valve and with a pilot valve controlled by a magnet, the main valve being switchable by means of the pilot valve into a position supplying a pressure medium to the consumer and a pressure medium discharging from it.
  • Hydraulic systems for controlling the position or the contact pressure of a consumer are widely known and z. B. used to control the distance of a device from the ground.
  • pressure cylinders can be supplied to lifting cylinders via a main valve if it comes from a blocking position is switched into a through position.
  • the changeover takes place via a pilot valve which is operated remotely and, when actuated accordingly, reduces a pilot pressure behind the main valve, so that this is pushed into the open position by means of a pressure applied to the other side of the main valve.
  • the same control is carried out with a second main valve and a second pilot valve if pressure medium is to flow out of the lifting cylinders to a storage container.
  • the object on which the invention is based is seen in designing a hydraulic system for controlling a force which moves a consumer, in particular for controlling its contact force, with a pilot-controlled main valve and with a pilot valve controlled by a magnet such that with only one main and one pilot valve a preselectable pressure is automatically applied to the consumer during a control.
  • the pilot valve is opened and thus reduces pressure behind the main valve as soon as a pressure present at the pilot valve exceeds the force acting on the other side of the pilot valve, ie the counteracting force.
  • This other force could be built up by means of a spring, a magnet or some other pressure.
  • Such an increase in pressure occurs when the consumer z. B. moved with a device due to the nature of the ground away from the ground and no longer on this lies on.
  • the opening of the main valve then causes the pressure medium to flow out of the consumer, so that the device can lower itself until the pilot-controlled pressure is reached again at the consumer.
  • the pressure at which the pilot valve responds and the main valve is actuated can be varied. Such changeability is useful if the operating conditions of the device worn by the consumer change and an adjustment is necessary or desired.
  • the response pressure in the pilot valve can act in a simple manner if it works against the force of a spring, since this is constant and can be calculated.
  • a proportional pressure relief valve with a pilot control and a magnet with changeable application voltage and reverse characteristic is already known [BOSCH - For hydraulics - Product information - HP / VEK 2-BEY 013/5 De, En, Fr (3.90)]; however, it is not known to use such a valve to control the contact pressure or the position of a consumer.
  • the main valve is designed so that the amount of pressure medium flowing through it can be adjusted, the lowering speed of the consumer can be changed so that when the pilot valve responds, the consumer can be moved at a variable speed until a certain support pressure is reached.
  • a hydraulic system 10 contains a reservoir 12, a pump 14, a valve 16, a main valve 18, a pilot valve 20 and a consumer 22.
  • Such a hydraulic system 10 is used to control the lifting and / or lowering of an object engaging the consumer 22, or generally to control its position and, if it is placed on a floor, to control its contact force.
  • the object can be an implement, that is attached to a vehicle, or a header on a harvester, a shovel on a loader or excavator, or a grapple on a forestry machine.
  • numerous other application examples are conceivable.
  • Pressure medium is stored in the reservoir 12 in the form of liquid, in particular oil, which can be pressurized by the pump 14.
  • the pump 14 is designed as a continuously pumping constant current pump which is driven by a motor, not shown.
  • a suction line 24 extends between the pump 14 and the reservoir 12.
  • the delivery rate of the pump 14 is assumed to be 18 l / min.
  • the valve 16 is designed as a two-position valve with three connections, which supplies pressure medium coming from the pump 14 in a position -a to the reservoir 12 and in a position -b- to the consumer 22.
  • a spring 26 and, on the other hand, a magnet 28 are provided for adjusting the valve 16. In a normal switching position, the spring 26 presses the valve 16 into its position -a-. Since the valve 16 is designed as a so-called black-and-white valve, it can only assume one of the positions mentioned, but not an intermediate position.
  • a pressure line 30 extends between the pump 14 and the valve 16
  • a line 32 extends between the valve 16 and the reservoir
  • a line 34 extends from the valve 16 to the consumer 22.
  • a branch 36 leads from the pressure line 30 to a conventional pressure relief valve 38, which opens at a set maximum permissible pressure and allows pressure medium to flow into the reservoir 12.
  • the maximum allowable pressure is above the normal operating pressure of the consumer 22nd
  • a spring-loaded check valve 40 is provided in line 34, which can open in the direction of consumer 22.
  • the main valve 18 is designed as a two-position valve with two connections and is connected on the inlet side to a line 42 and on the outlet side to a line 44. While line 42 establishes a connection between line 34 leading to consumer 22 and main valve 18, line 44 leads to reservoir 12. Position -c- interrupts the flow from the two possible positions -c- and -d- through the main valve 18 and thus the connection between the line 34 and the storage container 12, and the other position -d- provides a connection between the lines 42 and 44, the volume flow flowing through being variably throttled, as will be explained later. It is assumed for the exemplary embodiment that the maximum flow rate is 35 l / min.
  • the main valve 18 is on one side, i.e.. H. with a view of Figure 1 right, acted upon by a spring 46.
  • a pilot line 48 opens on the same side as the spring 46, and on the opposite side the main valve 18 is acted upon by a pressure present in a pilot line 50.
  • the pilot line 50 is connected to the line 42 and is therefore always subject to the pressure at the consumer 22.
  • the pilot valve 20 is connected to a further line 52, which branches off from the line 34 and leads to the reservoir 12. One after the other are on the line 52 a filter 54, a throttle 56, an orifice 58 and the pilot valve 20 are provided.
  • the pilot line 48 branches off between the throttle 56 and the orifice 58 to the main valve 18.
  • a third pilot line 60 is connected on the one hand between the orifice 58 and the pilot valve 20 to the line 52 and on the other hand to one side of the pilot valve 20.
  • a leakage oil line 62 is connected at one end to the pilot valve 20 and at the other end between the pilot valve 20 and the reservoir 12 to the line 52.
  • the pilot valve 20 is acted upon on one side by a spring 64, which counteracts the pressure present in the pilot line 60.
  • the pressure prevailing at the consumer 22 is always present in the pilot line 60, possibly noticeably reduced as a result of flow losses in the throttle 56 and the orifice 58.
  • a magnet 66 acts on the side opposite the spring 64 and together with the pressure in the pilot line 60 to the pilot valve 20.
  • the magnet 66 is advantageously designed as a proportional magnet; in any case, it is a magnet 66 with a known constant hysteresis.
  • the pilot valve 20 In the idle state, the pilot valve 20 is pushed by the spring 64 into a blocking position, in which the connection between the line 34 and the reservoir 12 via the line 52 is interrupted.
  • the magnet 66 In the idle state, the magnet 66 is not actuated, and the pressure present in the pilot line 60 with the associated surface is not sufficient to overcome the force of the spring 64. To compress the spring 64, the magnet 66 must also always be effective.
  • the magnet 66 In order to get from the blocking position -e- into a through position -f-, the magnet 66 must also be activated.
  • the magnet 66 is an electromagnet with an inverted one Characteristic curve as can be seen from FIG. 2.
  • the magnitude of the voltage / current that can be applied to it is variable and is specified by means of a potentiometer 68 via a switch 74. Depending on the size of the applied voltage or the applied current, the force with which the magnet 66 counteracts the spring 64 and thus allows pressure medium to flow out of the line 34 is greater or less.
  • the potentiometer 68 is located on a harvesting machine on a driver platform and can be adjusted from there. The control is selected so that the pilot valve 20 opens completely when the magnet 66 is at full voltage / current.
  • the consumer 22 is designed as a single-acting, linearly movable hydraulic motor, the piston of which can lift a load.
  • a pressure accumulator 70 is connected to the line 34, the input into the pressure accumulator 70 being able to be changed by means of a throttle 72 in order to make the hydraulic system 10 more rigid or more flexible.
  • Figure 1 shows the hydraulic system 10 in its idle state, in which the magnets 28 and 66 are de-energized.
  • the spring 16 pushes the valve 16 into its circulating position -a-, by means of the spring 46 the main valve 18 into its blocking position -c- and by means of the spring 64 the pilot valve 20 into its blocking position -e-; the pressure medium delivered by the pump 14 thus flows via the valve 16 directly into the reservoir 12 without moving the consumer 22.
  • the magnet 28 is in turn activated and thus the valve 16 is pushed into its through position -b-.
  • the magnet 66 is activated so that the force applied by it, together with the force resulting from the pressure in the pilot line 60, stands opposite the spring 64, projects beyond it and shifts the pilot valve 20 into its opening -f-position.
  • This control means that the consumer 22 is always moved by the load acting on it into a position in which the load only acts on it with a predetermined force. For example, a cutting mechanism of a combine harvester should be lowered by means of the consumer 22 until it rests on the ground with a certain force.
  • the position control it is first necessary to establish a relationship between the support pressure of the consumer 22 or the device attached to it, which builds up in the line 34, and the voltage on the magnet 66.
  • the consumer 22 is completely retracted in order to reduce the pressure in the line 34 as much as possible.
  • the magnets 28 and 66 are energized by means of a further switch, not shown, so that the valve 16 assumes its through position and conveys pressure medium to the consumer 22.
  • the switch 74 is closed so that voltage is applied to the magnet 66, which should, however, be the highest possible voltage / current at the start of the adjustment process.
  • the consumer 22 In order for the position control process to take effect, the consumer 22 must extend a certain amount, i.e. H. the load will be lifted.
  • the potentiometer 68 In order to activate the pressure-proportional position control, the potentiometer 68 is connected to the magnet 66 by closing the switch 74 and this is energized with a certain voltage, which generates the preset force directed against the spring 64. The pilot valve 20 is therefore biased.
  • the magnet 28 is energized so that the valve 16 allows pressure medium to flow into the line 34.
  • the application of a voltage to the magnets 28, 66 takes place for a time of, for. B. 5-6 seconds; this period can also be maintained by means of a timer in the form of a relay or the like. If the pressure at the consumer 22 is too high, the consumer 22 lowers in accordance with the previous statements regarding the adjustment process.
  • the pilot valve 20 opens the connection to the storage container 12
  • the pressure in the pilot line 48 decreases and the pressure in the pilot line 50 shifts the main valve 18 into its through position -d-, in which pressure medium can flow out of the consumer 22 into the reservoir 12.
  • the pressure medium can flow off until the pressure increase in the lines 34, 52 is reduced and the spring 64 manages to close the passage through the pilot valve 20, which causes the pilot pressure on the right side of the main valve 18 to rise and this increases also closes. This means that the consumer 22 lowers the load until it z. B. is supported on the floor. It can be clearly seen that by changing the voltage on the magnet 66, the time or pressure point at which the pilot valve 20 opens and initiates the control process can be changed.
  • the switch 74 is opened so that no voltage can be applied to the magnet 66 via the potentiometer 68.
  • the maximum flow rate through the main valve 18 can be changed manually, for which purpose, for example, an adjusting screw 76 can be used, as shown in FIG. 3. So the maximum flow rate of 35 l / min to z. B. 30 l / min can be reduced. This has the consequence that during a lowering process with unchanged Inflow of pressure medium from the pump 14 at 18 l / min can only flow from the consumer 22 at 12 l / min; the lowering speed slows down.
  • an electrically adjustable adjusting device could also be used.
  • a valve block 78 is shown in FIG. 3, which contains in particular the magnets 28 and 66, the valve 16, the main valve 18, the pilot valve 20 and the adjusting screw 76.
  • the previously used reference numerals are entered in the valve block 78 at the relevant points.
  • a detailed explanation is not necessary since the connections and the function are the same, with the exception that the valve 16 is not pilot-controlled directly by means of the magnet 28, but rather. However, this is already known from TM-1352, pages 270-20-5 and 270-20-7 to 270-20 9, Mar-86, by JOHN DEERE, so that no explanation is required here either.
  • the set screw 76 is screwed into a housing 82 so that it can move longitudinally and acts at one end on the spring 46, which presses a slide 84 of the main valve 18 against a seat 86. The further the set screw 76 is moved towards the spring 46 and preloads it accordingly, the less the slide 84 can with a comparable pressure dodge, so that the passage cross-section can be changed.
  • pilot valve 20 Since the pilot valve 20 operates under full voltage / current as a so-called black-white valve or open-close valve and thus does not allow any intermediate positions, it is also excellently suitable for any manual control that may be desired.
  • the hydraulic system according to the invention is particularly suitable for controlling the contact pressure of the consumer, but also for controlling its position.
EP19920103245 1991-03-04 1992-02-26 Hydraulic system for controlling a loaddriven actuator Withdrawn EP0502411A3 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4106845A DE4106845A1 (de) 1991-03-04 1991-03-04 Hydrauliksystem zur steuerung einer einen verbraucher bewegenden kraft
DE4106845 1991-03-04

Publications (2)

Publication Number Publication Date
EP0502411A2 true EP0502411A2 (fr) 1992-09-09
EP0502411A3 EP0502411A3 (en) 1993-02-03

Family

ID=6426425

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920103245 Withdrawn EP0502411A3 (en) 1991-03-04 1992-02-26 Hydraulic system for controlling a loaddriven actuator

Country Status (3)

Country Link
US (1) US5355773A (fr)
EP (1) EP0502411A3 (fr)
DE (1) DE4106845A1 (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
US5359836A (en) * 1993-02-01 1994-11-01 Control Concepts, Inc. Agricultural harvester with closed loop header control
WO2014139613A1 (fr) * 2013-03-09 2014-09-18 Hydac Filtertechnik Gmbh Dispositif de filtration

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DE4235111A1 (de) * 1992-10-17 1994-04-21 Bayerische Motoren Werke Ag Ventilanordnung für Pneumatikleitungen
DE4416194A1 (de) * 1994-05-06 1995-11-09 Rexroth Mannesmann Gmbh Regelsystem für einen hydraulisch betätigten Verbraucher eines Nutzfahrzeugs
AU8002298A (en) * 1997-08-25 1999-03-04 Millers Mechanical (Nz) Limited Improvements in control systems
AT408208B (de) * 2000-02-22 2001-09-25 Hoerbiger Hydraulik Anordnung zur hydraulischen betätigung eines bewegten teils an fahrzeugen, insbesondere eines verdecks, eines heckdeckels, einer abdeckklappe oder dgl.
EP1275854A1 (fr) * 2001-07-09 2003-01-15 Herion Systemtechnik GmbH Méthode et dispositif hydraulique de commande pour la protection contre les surcharges d'une presse mécanique actionnée par une combinaison embrayage-frein
DE20208577U1 (de) * 2002-06-03 2003-12-11 Hawe Hydraulik Gmbh & Co. Kg Elektrohydraulische Hubsteuervorrichtung für Flurförerfahrzeuge
DE10227966A1 (de) * 2002-06-22 2004-01-08 Deere & Company, Moline Hydraulische Steueranordnung für eine mobile Arbeitsmaschine
DE10261225B4 (de) * 2002-12-20 2006-11-16 Dorma Gmbh + Co. Kg Elektrohydraulischer Servotürantrieb zum Antrieb einer Tür, eines Fensters oder dergleichen
DE102004039848A1 (de) * 2004-08-17 2006-03-09 Jungheinrich Ag Fluidschaltung und Flurförderzeug mit Fluidschaltung
US7647753B2 (en) * 2006-12-30 2010-01-19 Headsight, Inc. Header height control system and method
JP5801618B2 (ja) * 2011-06-21 2015-10-28 カヤバ工業株式会社 ブームスプレーヤ及びブーム制振装置
EP2835540B1 (fr) * 2013-08-08 2016-04-27 HAWE Hydraulik SE Entraînement hydraulique
JP7210553B2 (ja) * 2018-04-09 2023-01-23 イーグル工業株式会社 流体圧回路
EP4098810A4 (fr) * 2020-06-22 2024-03-06 Hitachi Construction Mach Co Engin de chantier

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US3597907A (en) * 1965-02-15 1971-08-10 Love Co J E Header elevational control system for crop-harvesting machine
DE1937346A1 (de) * 1967-12-28 1971-02-04 Bosch Gmbh Robert Hydraulische Hubeinrichtung an Maehdreschern
DE2024328A1 (fr) * 1969-05-19 1970-12-17
US4276811A (en) * 1972-11-08 1981-07-07 Control Concepts, Inc. Closed center programmed valve system with load sense
US4276810A (en) * 1972-11-08 1981-07-07 Control Concepts, Inc. Programmed valve system used for positioning control
US4401009A (en) * 1972-11-08 1983-08-30 Control Concepts, Inc. Closed center programmed valve system with load sense
US4622803A (en) * 1984-06-28 1986-11-18 J. I. Case Company Header flotation
US4873817A (en) * 1988-08-01 1989-10-17 United Technologies Automotive, Inc. Electrically controlled pressure relief valve system and method

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US5359836A (en) * 1993-02-01 1994-11-01 Control Concepts, Inc. Agricultural harvester with closed loop header control
US5463854A (en) * 1993-02-01 1995-11-07 Control Concepts, Inc. Agricultural harvester with closed loop ground tracking control
WO2014139613A1 (fr) * 2013-03-09 2014-09-18 Hydac Filtertechnik Gmbh Dispositif de filtration
US10066652B2 (en) 2013-03-09 2018-09-04 Hydac Filtertechnik Gmbh Filter device

Also Published As

Publication number Publication date
EP0502411A3 (en) 1993-02-03
DE4106845A1 (de) 1992-09-24
DE4106845C2 (fr) 1993-03-04
US5355773A (en) 1994-10-18

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