WO2008131990A1 - Dispositif et procédé de régulation de plusieurs points de distribution - Google Patents

Dispositif et procédé de régulation de plusieurs points de distribution Download PDF

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Publication number
WO2008131990A1
WO2008131990A1 PCT/EP2008/053100 EP2008053100W WO2008131990A1 WO 2008131990 A1 WO2008131990 A1 WO 2008131990A1 EP 2008053100 W EP2008053100 W EP 2008053100W WO 2008131990 A1 WO2008131990 A1 WO 2008131990A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
consumers
metering orifice
pump
control arrangement
Prior art date
Application number
PCT/EP2008/053100
Other languages
German (de)
English (en)
Inventor
Horst Hesse
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2008131990A1 publication Critical patent/WO2008131990A1/fr

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
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • 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
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram
    • 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
    • F15B2211/20546—Type of pump variable 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
    • F15B2211/40—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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of 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
    • F15B2211/705—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 control arrangement for pressure medium supply of at least two consumers according to the preamble of claim 1 and a method for controlling the consumer according to the preamble of claim. 7
  • Hydraulic systems are used to control several consumers, in which the consumers are supplied with pressure medium via a common pump (fixed displacement pump with bypass pressure balance or variable displacement pump).
  • a metering orifice and a pressure compensator are provided, via which the pressure medium volume flow to the consumer is adjustable.
  • a distinction is made according to the current regulator principle and according to the current divider principle operating LS systems in which the pressure compensator of the metering orifice is always connected downstream.
  • These current divider systems are also referred to as LUDV systems, which represent a subgroup of the LS systems.
  • the pump is adjusted in response to the highest load pressure of the actuated hydraulic consumers so that the inlet pressure is a predetermined pressure difference above the highest load pressure.
  • the downstream pressure compensators are acted upon in the opening direction of the pressure to the respective metering orifice and in the closing direction of a control pressure, the usual manner corresponds to the highest load pressure of all driven consumers.
  • the amounts of pressure fluid flowing to the individual hydraulic consumers are proportionally reduced independently of the respective load pressure of the hydraulic consumers (load-independent flow distribution).
  • the pressure compensator upstream or downstream of the metering orifice is acted upon in the closing direction by the pressure before the metering orifice and in the opening direction by the load pressure downstream of the metering orifice, so that no load-independent flow distribution is obtained.
  • DE 103 42 037 A1 discloses a generic control arrangement in which the metering orifices are adjusted electronically or electrohydraulically.
  • the load pressure of the consumer is detected via sensors arranged in the pressure medium flow path to the consumer, for example pressure sensors, and the load-pressure-highest consumers are determined from the signals from the sensors.
  • sensors arranged in the pressure medium flow path to the consumer for example pressure sensors
  • the load-pressure-highest consumers are determined from the signals from the sensors.
  • the metering orifice associated with this consumer is then completely opened, so that the pressure loss over this metering orifice and thus also the pressure loss in the entire system are minimized.
  • the control of the pump takes place in the known solution electrically via the control unit and not - as in the so-called. LS systems - depending on the highest load pressure.
  • the invention has for its object to provide a control arrangement and a method for controlling at least two consumers, in which the energy or pressure loss is reduced by simple means.
  • the control arrangement according to the invention can be constructed according to the current regulator or current divider principle described above.
  • the individual pressure compensator associated with the load-pressure-highest consumer is completely open, so that the pressure compensator piston is in its end position.
  • individual pressure compensator is determined and then issued according to a signal to the control unit to completely pride excusen the associated metering orifice to minimize the pressure loss.
  • the determination of the end position of pressure compensators can be carried out with extremely little effort, since the required transducers are constructed much simpler than the pressure transducer of the known system.
  • the system is designed as a current regulator system, with the consumer upstream or downstream dual pressure balance in the closing direction of the pressure upstream and in the opening direction of the pressure downstream of the associated metering orifice are acted upon.
  • an electromechanical limit switch is preferably used, which is switched on reaching the end position of the individual pressure compensator and emits a corresponding signal to the control unit.
  • the pump of the control arrangement is preferably designed as an electrically or electrohydraulically adjustable variable displacement pump.
  • Such systems can be used particularly effectively in control arrangements for mobile machines, in which the individual functions are actuated by hydraulic cylinders.
  • the adjustment of the metering orifices is preferably carried out electrically or electrohydraulically by means of a joystick or a similar adjusting device.
  • FIG. 1 shows a circuit diagram of a control arrangement according to the invention for supplying pressure medium to two consumers
  • Figure 2 is a schematic representation of a variant of an applicable in the control arrangement of Figure 1 flow regulator consisting of a metering orifice and an upstream individual pressure compensator.
  • FIG. 1 shows a greatly simplified circuit diagram of a control arrangement 1 for supplying pressure medium to two consumers 2, 4.
  • the control arrangement is designed as an EFM system (electronic flow management), whereby the valve elements and a pump 8 influence the pressure medium flow electrically or be controlled electro-hydraulically via a control unit 6.
  • the pressure medium supply of the two consumers 2, 4 via the pump 8, which is designed as a variable displacement pump in the illustrated embodiment, the pivot angle is electrically adjustable via a proportional solenoid 10.
  • NATURALLY lent instead of this EP adjustment by means of a proportional solenoid and a conventional pump regulator can be used, which adjusts the adjustment angle depending on the highest load pressure of all consumers hydraulically / mechanically or electrically.
  • the pressure connection of the pump 8 is connected to a pump line 12, which branches into two feed lines 14, 16 leading to a respective consumer 2, 4.
  • a flow control valve with a proportionally adjustable inlet orifice 18, 20 and in each case a downstream individual pressure compensator 22, 24 is arranged in each case via a feed line 26, 28 with a bottom-side cylinder chamber 30, 32, the consumer 2, 4 designed as a hydraulic cylinder.
  • these hydraulic cylinders are extendable by pressure medium supply, wherein the respective annular space is always connected to a tank.
  • the retraction of the hydraulic cylinder is effected by pressure medium connection of the two bottom-side cylinder chambers 30, 32 with a tank, wherein the pressure medium flow direction and the pressure medium volume flow in the flow determining opening cross-section via a proportional valve is adjustable, in which the respective metering orifice 18, 20 is integrated.
  • the structure of such control arrangements is well known, so that further embodiments are unnecessary.
  • the setting of the opening cross section of the two orifices 18, 20 takes place in the illustrated embodiment electrically via proportional solenoids 34, 36 which are electrically controlled via the control unit 6.
  • the variable displacement pump 8 may be configured with a pressure sensor for detecting the pump pressure, a speed sensor for detecting the pump speed, and a swing angle sensor for detecting the pump swing angle.
  • the characteristics of the variable displacement 2 and the two proportionally adjustable metering orifices 18, 20 are stored so that with the help of all or some of the aforementioned sensors and characteristics extremely precise flow control via the pump 8 is made possible.
  • the two individual pressure compensators 22, 24 are each acted upon in the opening direction by the pressure downstream of the associated metering orifice 18, 36. This pressure is tapped in the illustrated embodiment in each case via a control line 38, 40. In the opening direction further acts a spring, which is not shown in Figure 1. In the closing direction acts on the pressure compensator piston 22, 24, the pressure upstream of the respective metering orifice 18, 20. This is about a to the Inividualruckwaagen 22, 24 out branching control channel 42 from the pump line 12 or the two supply lines 14, 16 tapped.
  • the metering orifices 18, 20 together with the associated individual pressure compensators 22, 24 form a flow regulator, via which the pressure medium volume flow to the associated consumer 2, 4 can be kept constant independent of the load pressure.
  • the position of a pressure compensator piston is detected via sensors 44, 46 and a signal is sent to the control unit 6 when one of the pressure compensator pistons has reached its end position and thus the corresponding pressure compensator is completely opened.
  • control signals are generated by the operator via one or more joysticks, which are processed via the control unit 6 to control signals for controlling the variable displacement pump 8 and the two orifices 18, 20.
  • the variable displacement pump 8 must provide a certain pressure medium volume flow which corresponds to the sum of the setpoint volume flows set via the joystick 48.
  • the variable displacement pump 8 must thus be adjusted in dependence on the setting of the joystick 48 to a pivot angle at which this sum volume flow is delivered.
  • the corresponding adjustment of the variable displacement pump 8 can be carried out in a simple manner as a function of the setpoint value by detecting the current pump pressure, the current pump speed and the set pivoting angle via the pump characteristic curve.
  • volumetric flow errors due to volumetric losses of the variable displacement pump 8 can be compensated because the operator immediately readjusted via the joystick 48, if the consumers 2, 4 are not operated at the desired speed.
  • the highest load pressure then adjusts accordingly to the most heavily loaded consumer and the pressure difference to the lower load consumers is throttled away by the current control of the individual pressure compensators 22, 24.
  • the load pressure highest consumer associated with individual pressure compensator 24 is in its end position (fully open). This end position is via the transducer 44, 46 detected and reported to the control unit 6, so that this is the associated metering orifice 20 completely controlled - the pressure loss across the orifice 18, 20 is thus minimal.
  • the control unit 6 is connected via the signal lines shown in Figure 1 with the proportional magnet 10, 34, 36 and with the two transducers 44, 46, furthermore, a signal line for adjusting the pump speed is shown - since these signal lines are self-explanatory in FIG no reference numbers are shown.
  • FIG. 2 shows an exemplary embodiment of an alternative use in a control arrangement according to FIG. 1 current regulator, in which the pressure compensator of the metering orifice is connected downstream.
  • the same reference numerals as in FIG. 1 are used for components corresponding to each other.
  • the pressure medium volume flow conveyed by the pump 8 flows via the supply line 14 to the inlet of the individual pressure compensator 22, whose pressure compensator piston 50 is biased via a pressure compensator spring 52 into its illustrated opening position, in which a pressure medium connection of the inflow line 14 to one at the outlet connection of the individual pressure compensator 22 connected pressure balance channel 54 is opened via an annular groove 56 of the pressure compensator piston 50.
  • the control channel 42 branches off from the pressure compensator channel 54, so that the pressure upstream of the metering orifice 18 is tapped off and reported to a control chamber 58.
  • the current regulator according to Figure 1 with downstream individual pressure compensator 22, 24 works in the same way.
  • the end position of the pressure compensator piston 50 ie the position in which the opening cross section of the individual pressure compensator 22 is completely opened (view according to FIG. 2), is detected via a mechanical limit switch 44.
  • the limit switch 44 is switched and delivered a corresponding control signal to the control unit 6, so that the associated metering orifice 18 completely auf Kunststofft so that the pressure drop across the metering orifice 18 is equal to 0 or minimal.
  • a control arrangement and a method for supplying pressure medium from at least two consumers which can be supplied by a pump with pressure medium.
  • Each of the consumers are associated with a metering orifice and an individual pressure balance, via which the pressure medium volume flow to the respective consumer is adjustable.
  • an end position of the individual pressure compensator associated with the load pressure-highest consumer is detected, and when the end position is reached, the associated metering orifice is completely opened to minimize the pressure loss.

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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)

Abstract

La présente invention concerne un dispositif et un procédé d'alimentation en encre d'impression à partir de plusieurs points de distributions alimentés en encre d'impression par une pompe. Chaque point de distribution est desservi par un diaphragme doseur et un régulateur individuel de pression permettant de régler le débit d'encre arrivant à chaque point de distribution. Le procédé de l'invention consiste donc à détecter un état final du régulateur individuel de pression desservant le point de distribution dont la pression de charge est la plus élevée, et lorsqu'on arrive à cet état final, à commander au diaphragme doseur une minimisation complète de la perte de pression.
PCT/EP2008/053100 2007-04-26 2008-03-14 Dispositif et procédé de régulation de plusieurs points de distribution WO2008131990A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007019787.1 2007-04-26
DE200710019787 DE102007019787A1 (de) 2007-04-26 2007-04-26 Steueranordnung und Verfahren zur Ansteuerung von zumindest zwei Verbrauchern

Publications (1)

Publication Number Publication Date
WO2008131990A1 true WO2008131990A1 (fr) 2008-11-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/053100 WO2008131990A1 (fr) 2007-04-26 2008-03-14 Dispositif et procédé de régulation de plusieurs points de distribution

Country Status (2)

Country Link
DE (1) DE102007019787A1 (fr)
WO (1) WO2008131990A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105041748A (zh) * 2014-04-29 2015-11-11 罗伯特·博世有限公司 用于多个执行机构的液压的控制装置
CN113775591A (zh) * 2021-11-11 2021-12-10 太原理工大学 可短路阀后压力冗余补偿流量控制系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011106307A1 (de) * 2011-07-01 2013-01-03 Robert Bosch Gmbh Steueranordnung und Verfahren zum Ansteuern von mehreren hydraulischen Verbrauchern

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62194002A (ja) * 1986-02-19 1987-08-26 Seirei Ind Co Ltd 正逆切換油圧回路におけるアクチユエ−タのシヨツク緩和装置
EP0587902A1 (fr) * 1992-02-18 1994-03-23 Hitachi Construction Machinery Co., Ltd. Systeme de commande hydraulique
US5452579A (en) * 1991-07-04 1995-09-26 Danfoss A/S Hydraulic system with pump and load
DE10108536A1 (de) * 2001-02-22 2002-04-04 Rexroth Mecman Stockholm Ab Pneumatikventil mit Mitteln zur elektrischen Erfassung der Endposition eines innenliegenden Schaltelements
DE10342037A1 (de) 2003-09-11 2005-04-07 Bosch Rexroth Ag Steueranordnung und Verfahren zur Druckmittelversorgung von zumindest zwei hydraulischen Verbrauchern

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62194002A (ja) * 1986-02-19 1987-08-26 Seirei Ind Co Ltd 正逆切換油圧回路におけるアクチユエ−タのシヨツク緩和装置
US5452579A (en) * 1991-07-04 1995-09-26 Danfoss A/S Hydraulic system with pump and load
EP0587902A1 (fr) * 1992-02-18 1994-03-23 Hitachi Construction Machinery Co., Ltd. Systeme de commande hydraulique
DE10108536A1 (de) * 2001-02-22 2002-04-04 Rexroth Mecman Stockholm Ab Pneumatikventil mit Mitteln zur elektrischen Erfassung der Endposition eines innenliegenden Schaltelements
DE10342037A1 (de) 2003-09-11 2005-04-07 Bosch Rexroth Ag Steueranordnung und Verfahren zur Druckmittelversorgung von zumindest zwei hydraulischen Verbrauchern

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105041748A (zh) * 2014-04-29 2015-11-11 罗伯特·博世有限公司 用于多个执行机构的液压的控制装置
CN113775591A (zh) * 2021-11-11 2021-12-10 太原理工大学 可短路阀后压力冗余补偿流量控制系统
CN113775591B (zh) * 2021-11-11 2022-01-04 太原理工大学 可短路阀后压力冗余补偿流量控制系统

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