EP1701042A2 - Commande hydraulique - Google Patents

Commande hydraulique Download PDF

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Publication number
EP1701042A2
EP1701042A2 EP20060101027 EP06101027A EP1701042A2 EP 1701042 A2 EP1701042 A2 EP 1701042A2 EP 20060101027 EP20060101027 EP 20060101027 EP 06101027 A EP06101027 A EP 06101027A EP 1701042 A2 EP1701042 A2 EP 1701042A2
Authority
EP
European Patent Office
Prior art keywords
pressure
control
inlet
arrangement according
orifice
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.)
Granted
Application number
EP20060101027
Other languages
German (de)
English (en)
Other versions
EP1701042B1 (fr
EP1701042A3 (fr
Inventor
Heinrich Lödige
Christoph Keyl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1701042A2 publication Critical patent/EP1701042A2/fr
Publication of EP1701042A3 publication Critical patent/EP1701042A3/fr
Application granted granted Critical
Publication of EP1701042B1 publication Critical patent/EP1701042B1/fr
Not-in-force 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
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30545—In combination with a pressure compensating valve the pressure compensating valve is arranged between output member and 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • 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
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow 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
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure 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
    • F15B2211/57—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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • F15B2211/5753—Pilot pressure control for closing a 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a consumer according to the preamble of patent claim 1.
  • a control arrangement in which a hydraulic consumer, for example a double-acting cylinder for moving a load via a continuously adjustable directional control valve with pressure medium can be supplied.
  • a hydraulic consumer for example a double-acting cylinder for moving a load via a continuously adjustable directional control valve with pressure medium
  • each unlockable check valves are provided, wherein the inlet-side check valve is brought by the pressure downstream of the directional control valve in an open position.
  • the drain-side check valve can be moved by pressing a poppet into an open position, which allows the drainage of the pressure fluid from the consumer to the directional control valve.
  • via the drain-side blocking block is a flow control by feedback of the discharge pressure before determining the course Schieber tenukante the continuously adjustable directional valve on the topping piston of the blocking block.
  • a control arrangement in which a supply control via an upstream of the control valve individual pressure compensator. This is acted upon in the opening direction by the force of a spring and the pressure in the inlet to the consumer.
  • the DE 36 39 174 C2 shows a control arrangement for a single-acting hydraulic consumer, wherein a LS-pressure compensator is connected upstream of a continuously adjustable directional control valve which is acted upon in the closing direction by the force of a spring and by the individual load pressure and in the opening direction by the pressure between the pressure compensator and the directional control valve.
  • the known control arrangement further has a load-compensated unlockable check valve, via which a sequence control can be performed.
  • a hydraulic control arrangement in which upstream of a Zulaufmessblende an LS-pressure compensator is provided, which is acted upon in the opening direction by the force of a spring and the highest pressure downstream of the Zulaufmessbrende and upstream of a drain metering orifice.
  • the LS pressure compensator acts on the pressure upstream of the inlet orifice plate.
  • suction valves can be used. Due to the comparatively low differential pressure between the suction side and the tank pressure during the suction, however, these valves must have a very large cross-section.
  • biasing valves in the pressure fluid outlet.
  • bias valves are associated with a high energy loss, since the inlet pressure, especially at low loads, must be greatly increased.
  • brake valves Another possibility is to use brake valves. However, these also require a comparatively high pressure on the inlet side in order to control the volume flow on the outlet side and thus to avoid an undersupply of the inlet.
  • the invention has for its object to provide a hydraulic control arrangement for controlling a consumer, by which a deficiency can be avoided with little effort and in the pressure medium flow to the consumer and the running of the consumer pressure medium flow rate can be controlled independently of the load.
  • the hydraulic control arrangement according to the invention is designed with an adjustable inlet and an adjustable flow meter, wherein a pressure in the forward flow pressure compensator is acted upon in the opening direction by a constant force and in the closing direction of the lower of the pressures downstream of the inlet orifice and upstream of the drain orifice.
  • a lockable block is provided, which acts as a check valve in the inlet direction and regulates the drainage pressure medium flow rate in the pressure fluid outlet.
  • both the consumer-flowing and the consumer-running pressure medium volume flows can be kept constant independently of the load pressure.
  • the load can be biased by the pressure compensator and the blocking block of the consumer in all operating conditions, so that the above-mentioned undersupply in the pressure medium inlet is safely avoided.
  • the bias of the load can be easily adjusted by adjusting the force acting on the pressure compensator in the opening direction constant force to the system.
  • the solution according to the invention can be realized with very little effort, the additional valve arrangements described above, such as suction valves, Preload valves, lowering brake valves, etc. are not required. Due to the bias of the consumer, air leakage on the suction side can be reliably avoided.
  • a delivery rate of a pump of the hydraulic control assembly is controlled in response to the greater of the pressures downstream of the metering orifice and upstream of the downcomer orifice. This flow rate is regulated so that in the pump line by a certain pressure difference .DELTA.p above the load pressure lying pump pressure is present (LS system).
  • the inlet and outlet orifice plates are preferably formed by a continuously adjustable directional control valve whose working connections are connected to an inlet and a drain line and the pressure connection is connected to a flow line and the tank connection to a return line.
  • the solution according to the invention makes it possible to carry out the feed cross section opened by an inlet control edge greater than the flow cross section opened by a flow control edge or to control the flow cross section later, so that the coordination of the two control edges is simplified due to the lower requirements for the inlet control edge.
  • the speed of the consumer is then always determined by the flow cross-section.
  • the force acting on the pressure compensator constant force is applied in a variant of the invention by acting on a control surface of a pressure compensator piston control pressure.
  • the constant force can also be applied to the pressure compensator piston via a spring or the like.
  • the adjustment of the bias voltage of the consumer can then be easily changed by adjusting the constant pressure. This can also be lowered by suitable circuit to zero, so that the pressure medium can flow from the consumer, without the pressure medium is conveyed to the inlet.
  • a double-acting consumer such as a differential cylinder unlockable blocking blocks are preferably provided both in the inlet and in the process, each having an actuatable by a control pressure topping piston.
  • the structure of the control arrangement is particularly simple if this control pressure corresponds to the constant control pressure which acts on the pressure compensator in the opening direction.
  • the smaller pressure downstream of the inlet orifice and upstream of the drain orifice can be tapped via an inverse shuttle valve.
  • This shows a circuit diagram of a hydraulic control arrangement for controlling a double-acting consumer.
  • control arrangements are used in particular for controlling the consumers of a mobile implement, for example in a forklift or a tractor.
  • the consumer is designed as a differential cylinder 2, which is connectable via a valve assembly 4 with a pressure medium supply 6.
  • the pressure medium supply 6 has in the illustrated embodiment, a constant displacement pump 8, is sucked via the pressure medium from a tank T and conveyed into a pump line 10.
  • a pump line 10 From the pump line 10 branches off a bypass line 12, in which an inlet pressure compensator 14 is arranged, which is acted upon in the opening direction by the pressure in the pump line 10 and in the closing direction of the highest load pressure of all consumers and the force of a spring 16.
  • This highest load pressure is tapped in a known manner via a shuttle valve cascade of all consumers of the system and is connected via a load reporting line 18 to the inlet pressure compensator 14.
  • the pump 8 can be designed as a fixed displacement pump with speed-controlled drive or as a variable displacement pump.
  • the flowing back from the cylinder 2 pressure fluid flows depending on the direction of movement of the cylinder 2 via a return line 20 or a return line 22 back to the tank T.
  • the valve assembly which is designed for example as a valve disc of a mobile control block, has a pressure port P, a LS port LS, two return ports R and two working ports A, B, the latter via working lines 24, 26 with a bottom-side cylinder chamber 28 and a piston rod side annulus 30 are connected.
  • the valve arrangement consists essentially of a pressure compensator, referred to below as individual pressure compensator 32, a continuously adjustable directional valve 34 indicated by dot-dash lines and two unlockable blocking blocks 36, 38.
  • the continuously adjustable directional control valve 34 usually has a directional part predetermining the pressure medium flow direction and a speed part, respectively is formed by an inlet and a drain measuring aperture. In the circuit diagram shown four measuring orifices are shown schematically, but depending on the setting of the directional part only two orifices are effective. D.
  • the measuring orifice provided with the reference numeral 40 acts as a metering orifice
  • the drain orifice plate is provided with the reference numeral 42, which is effective at a pressure medium flow from the working port B to the tank T.
  • the measuring orifices which are furthermore illustrated, then become effective as inlet orifice 44 and as drain orifice 46.
  • the two drain orifices 42, 46 are each arranged in a return channel 48 and 50, which are each connected to one of the return ports R.
  • the directional valve has two working ports A 'and B', which are connected via a supply line 52 and a drain line 54 to the working ports A, B.
  • the structure of the blocking blocks 36, 38 is known per se, so that detailed explanations are unnecessary.
  • These blocking blocks 36, 38 can be adjusted by means of a poppet piston 56 or 58 from a spring-biased basic position, in each case they act as a check valve in a flow position, which allows a return flow of the pressure medium from the cylinder 2.
  • the actuation of the poppet 56, 58 via a constant control pressure p x , which is tapped from a suitable control pressure supply.
  • the blocking block 36, 38 works load-compensated and regulates the pressure in the respectively assigned line, which then acts as a discharge channel independent of the load to a constant value.
  • the blocking block which is in each case in the inlet, then works as a check valve.
  • the individual pressure compensator 32 In a connected to the pressure port P of the valve assembly 4 feed channel 64, the individual pressure compensator 32 is arranged, which is acted upon in the opening direction by the constant control pressure p x and in the closing direction by the force of a pressure compensator spring 66 and a pressure in a message channel 68.
  • This pressure is the lesser of the pressures in the inlet channel 52 and the outlet channel 54, ie, the smaller of the pressures downstream of the inlet metering orifice 40 and upstream of the metering orifice 42 (at a pressure medium flow toward the working port A and from the working port B to the tank T).
  • This pressure is tapped from the inlet channel 52 and from the outlet channel 54 via a respective tapping channel 70, 72, each leading to an input of an inverse shuttle valve 74. Its output is connected to the signaling channel 68.
  • the pressure medium is conveyed by the pump 8 via the working port A in the cylinder chamber 28 and displaced back from the annular space 30 via the working port B to the tank T.
  • the metering orifice 40 acts as an inlet metering orifice and the metering orifice 42 as a drainage metering orifice, the metering orifices 44, 46 are closed.
  • the directional control valve 34 is adjusted so that an inlet control edge of the directional control valve 34 opens the cross section of the inlet orifice 40 and accordingly a flow control edge opens the cross section of the drain orifice 42.
  • the directional control valve 34 is designed so that the opening cross-section of the inlet metering orifice 40 is greater than that of the drain metering orifice.
  • the pressure medium then flows via the pressure compensator 32, the function of which will be explained in more detail below, the up-flow meter orifice 40, the inlet channel 52 and the check block 36 acting as a check valve, via the working port A and the working line 24 into the cylinder chamber 28 Pressure medium displaced from the annular space 30 and flows through the working line 26, the working port B and from the constant control pressure p x opened blocking block 38, the drain passage 54, the open-drain orifice 42, the return passage 50, via the return port R and the return line 22 back to the tank.
  • the pressures in the inlet channel 52 and in the outlet channel 54 are compared via the inverse shuttle valve 74 and the shuttle valve 80.
  • the larger of the two pressures is guided via the shuttle valve 80 as a LS signal to the LS shuttle valve 82 and from there (if no other higher load pressure is present) to an effective in the closing direction control surface of the inlet pressure compensator 14.
  • the smaller of the two pressures is reported via the inverse shuttle valve 74 and the message channel 68 to the individual pressure compensator 32 and compared there with the constant control pressure p x .
  • the pressure balance slide of the individual pressure balance 32 restricts the pressure fluid flow more strongly. If the tapped over the inverse shuttle valve 74 smaller pressure is too low, the flow opening of the individual pressure compensator 32 is extended and performed according to more pressure medium to the inlet orifice 40.
  • the pressure in the inlet channel 52 is greater than the pressure in the outlet channel 54.
  • the inlet pressure compensator 14 Apart from the pressure loss via the check block acting as a check valve 36 in the inlet of this larger pressure is passed as LS signal and the inlet pressure compensator 14 so set that the pressure in the pump line 10 by a predetermined pressure difference Ap over this highest load pressure is.
  • the lower pressure on the discharge side is reported to the individual pressure compensator 32 and is about 0 bar when the directional control valve 34 is not actuated.
  • the individual pressure compensator 32 is then fully opened by the constant control pressure p x .
  • the pressure in the discharge passage 54 initially drops, so that the individual pressure compensator 32 opens slightly and the pressure medium volume flow increases via the inlet metering orifice 40 until the pressure in the discharge passage 54 reaches the regulating pressure of the individual pressure compensator again.
  • the pressure medium volume flow on the inlet side is accordingly regulated so that the pressure in front of the drain measuring orifice 42 remains constant at the regulating pressure of the individual pressure compensator 32.
  • the opening cross section of the drain metering orifice 42 thus determines, in conjunction with the control pressure of the individual pressure compensator 32, the pressure medium volume flow.
  • the cylinder 2 is clamped, wherein this clamping force is adaptable by a suitable choice of the control pressure p x .
  • the pressure in the drainage channel 54 is throttled by the load-compensated locking block 38 from the load pressure in the annular space 30 or in the working line 26 to a constant level in the drainage channel 54 and kept constant.
  • the moving speed of the cylinder is determined even when pulling load through the opening cross-section of the drain metering orifice 42 in conjunction with the control pressure of the load-compensated blocking block 38.
  • a safety function can be realized, since the two locking blocks 36, 38 act as check valves and the individual pressure compensator 32 is controlled.
  • This safety function can be realized for example by a separate switching valve, via which the constant control pressure p x can be switched off.
  • This safety function can also be made possible by suitable design of the control edge of the directional control valve 34.
  • the constant control pressure p x can be varied in order to adapt the pressure gradient across the control edges of the directional control valve 34 and thus the pressure medium volume flow to different operating conditions for a given orifice.
  • a spring can also be mounted on the left side (view according to the single FIGURE), via which a substantially constant force is applied to the pressure compensator piston of the individual pressure compensator 32 becomes. Other means can be used to keep this force constant.
  • a hydraulic control arrangement for controlling a hydraulic consumer with an adjustable inlet and an adjustable drain metering and arranged in a pressure medium flow pressure compensator.
  • the control arrangement further has a releasable locking block, which acts as a check valve in the inlet direction and in the drain direction by means of a control pressure can be unlocked.
  • the pressure compensator is acted upon in the opening direction by a constant force and in the closing direction by the lower of the pressures downstream of the inlet metering orifice and upstream of the outflow metering orifice.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
EP20060101027 2005-03-11 2006-01-30 Commande hydraulique Not-in-force EP1701042B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510011395 DE102005011395A1 (de) 2005-03-11 2005-03-11 Hydraulische Steueranordnung

Publications (3)

Publication Number Publication Date
EP1701042A2 true EP1701042A2 (fr) 2006-09-13
EP1701042A3 EP1701042A3 (fr) 2007-03-14
EP1701042B1 EP1701042B1 (fr) 2008-10-15

Family

ID=36593790

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060101027 Not-in-force EP1701042B1 (fr) 2005-03-11 2006-01-30 Commande hydraulique

Country Status (5)

Country Link
US (1) US7219591B2 (fr)
EP (1) EP1701042B1 (fr)
AT (1) ATE411476T1 (fr)
DE (2) DE102005011395A1 (fr)
DK (1) DK1701042T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014005410A1 (de) * 2014-03-01 2015-09-03 Hydac Filtertechnik Gmbh Ventilvorrichtung

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007014550A1 (de) * 2007-03-27 2008-10-09 Hydac Filtertechnik Gmbh Ventilanordnung
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EP1701042B1 (fr) 2008-10-15
US7219591B2 (en) 2007-05-22
US20060201321A1 (en) 2006-09-14
DK1701042T3 (da) 2009-02-16
DE102005011395A1 (de) 2006-09-14
DE502006001799D1 (de) 2008-11-27
EP1701042A3 (fr) 2007-03-14
ATE411476T1 (de) 2008-10-15

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