EP2176556B1 - Control arrangement and method for controlling at least two hydraulic consumers - Google Patents
Control arrangement and method for controlling at least two hydraulic consumers Download PDFInfo
- Publication number
- EP2176556B1 EP2176556B1 EP08774827A EP08774827A EP2176556B1 EP 2176556 B1 EP2176556 B1 EP 2176556B1 EP 08774827 A EP08774827 A EP 08774827A EP 08774827 A EP08774827 A EP 08774827A EP 2176556 B1 EP2176556 B1 EP 2176556B1
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- EP
- European Patent Office
- Prior art keywords
- pressure
- pump
- consumer
- load
- load pressure
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—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
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6654—Flow rate control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
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 12.
- a common pump Constant pump with bypass pressure compensator or variable displacement
- pressure medium In the pressure medium flow path between the pump and each consumer a metering orifice and a pressure compensator are provided, via which the pressure medium volume flow to the consumer is adjustable.
- the pressure compensator of the metering orifice is always 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 by the pressure to the respective metering orifice and in the closing direction of a control pressure, which usually corresponds to the highest load pressure of all driven consumers.
- a control pressure which usually corresponds to the highest load pressure of all driven consumers.
- the pressure fluid quantities 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.
- the amount of pressure (undersaturation) is insufficiently provided by the variable displacement pump, only the amount of pressure medium flowing into the load of the highest load is reduced.
- DE 103 42 037 A1 is a so-called EFM system (Electronic Flow Matching) described in which the orifices and the pump are electronically or electro-hydraulically adjusted.
- the load pressure of the consumer is detected in each case via arranged in the pressure fluid flow path to the consumer sensors, such as pressure transducer and determined from the signals of the sensors of the load pressure highest consumers.
- the metering orifice assigned to 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 load pressure of all consumers is reported via an LS channel to the pump and then set in dependence on the load pressure, so that the pump pressure is above the highest load pressure by a predetermined pressure difference.
- the load pressure is picked up by the respective consumers via LS lines and reported via a shuttle valve cascade into the LS channel.
- each LS-pressure relief valve is arranged in the LS lines.
- the LS-pressure relief valve associated with the consumer driven to the stop limits the load pressure to a maximum load pressure, so that the pump is adjusted in accordance with this maximum load pressure - accordingly the pump pressure is adjusted to the LS maximum pressure plus the aforementioned pressure difference - the pump is thus adjusted to its maximum - but limited - delivery pressure. Accordingly, this maximum pressure must be throttled in the pressure fluid flow path to the other consumers via the respective individual pressure compensators to the respective load pressure.
- a small pilot oil volume flow to the tank flows via the LS pressure relief valve assigned to the consumer driven to the stop.
- the pump flow is limited or reduced by a so-called pressure cut on a similar principle as described above, in order to avoid power losses.
- the pressure medium volume flow must be throttled to the lower-load consumers on the individual pressure compensators.
- the DE 198 31 595 A1 shows a hydraulic control arrangement with a limitation of the maximum load pressure of a hydraulic consumer.
- the downstream of the metering orifice pressure compensator is acted upon in the closing direction of a higher pressure than the load pressure of the hydraulic load and thereby limits the load pressure to a limit load pressure.
- the pump is only controlled by the load pressure of another hydraulic consumer if this load pressure is higher than the limit load pressure.
- a hydraulic control arrangement with the features of the preamble of patent claim 1 and a method having the features of the preamble of claim 12 are known from WO 02/42648 known.
- the highest load pressure of other actuated hydraulic consumers is reported, so that the flow of pressure to the other consumers not determined by the limit load pressure, possibly well above the highest load pressure of other hydraulic consumers lying pump pressure, but only by one of the highest load pressure of the other hydraulic consumer specific pump pressure is throttled to the load pressure of other consumers.
- the invention has for its object to provide a control arrangement and a method for controlling at least two hydraulic consumers, in which energy losses are minimized in a simple manner when a predetermined load pressure of the load pressure highest consumer is exceeded.
- the device for adjusting the pump is executed when the maximum load pressure is exceeded with a pressure sensor for detecting the flow pressure to the consumer whose output signal is editable via a control unit in a control signal for controlling the associated metering orifice.
- the associated metering orifice is controlled on reaching the maximum load pressure, so that the consumer in question is no longer supplied, so that only the load pressures of the other, lower-load consumers are taken into account in the pump control.
- an adjustable metering orifice is arranged in the pressure medium flow paths to the consumers supplied via a pump with pressure medium in order to set the pressure medium volume flow individually.
- the pump is set in dependence on the highest load pressure of the consumer so that the pressure medium requirement of all controlled consumers is covered.
- the load pressure of the individual consumer is monitored by means of a device and set when exceeding a predetermined maximum load pressure at a consumer, the pump pressure or the pump quantity in dependence on the pressure medium demand of the other, lower-load consumer, so that the throttle losses of these consumers are minimal compared to the solutions described above ,
- the load pressure of the individual consumer is monitored by means of a device and set when exceeding a predetermined maximum load pressure at a consumer, the pump pressure or the pump quantity in dependence on the pressure medium demand of the other, lower-load consumer, so that the throttle losses of these consumers are minimal compared to the solutions described above .
- the metering orifice is assigned an LS or LUDV individual pressure balance, so that a control arrangement operating according to the current regulator principle or the current dividing principle is formed.
- the maximum load pressure of the control arrangement is limited by LS pressure relief valves in the respective load pressure leading LS lines, accordingly, the prescribed maximum load pressure in the range of the maximum LS pressure set by the LS pressure relief valves.
- the device is designed such that the load pressure signal of the loaded with maximum load pressure consumer can not be reported in the LS channel.
- the pump is designed to be electrically or electrohydraulically activatable, it being possible for a quantity signal for adjusting the pumps to be delivered via the device to the pump.
- This quantity signal can be generated, for example, as a function of the signal for adjusting the metering orifice of the highest-load consumer.
- an additional pressure sensor for detecting the pump pressure may be provided.
- the detected load pressures and the pump pressure are then compared with each other and in the case in which this pressure difference is below a predetermined value, issued via the device, a control signal for controlling the metering orifice of the load highest load and for returning the pump.
- the control of the metering orifice can be stepped (black-white) or via a characteristic curve.
- the control of the metering orifice takes place when the load pressure at this highest load has fallen back below the maximum load pressure. It is preferred that the control of the respective metering orifice takes place only when the actual load pressure is a predetermined pressure difference below the maximum load pressure.
- the system is designed in this case with a certain "pressure hysteresis".
- the control arrangement according to the invention can be embodied, for example, as an LS system (current regulator system), as a LUDV system (current divider system), as an EFM system (LS and LUDV) or as an electrohydraulic positive control system (PC).
- LS system current regulator system
- LUDV system current divider system
- EFM system LS and LUDV
- PC electrohydraulic positive control system
- the swing angle of the pump is increased with the control signal for adjusting the metering orifice.
- This single drawing shows a circuit diagram of an electro-hydraulic directional control valve element 1 of a mobile control block, the usual way consists of an input element, a plurality of directional control valve elements (mechanical, hydraulic, electro-hydraulic) and an end member.
- Such mobile control blocks are described for example in the above-mentioned data sheet RD 64276 Bosch Rexroth AG.
- each hydraulic consumer can be assigned a directional control valve element according to the figure described below.
- Such a directional control valve element 1 has a pressure port P, a control oil supply X, a control oil return Y, a LS port LS, a tank port T and two working ports A, B, which are connected for example with a bottom-side cylinder chamber and a piston rod side annular space of a hydraulic cylinder.
- an LS pump is connected to the pressure port P, via which the directional control valve elements 1 of the control block are supplied with pressure medium. The activation of the LS pump is carried out in the manner described above in response to the highest load pressure of all consumers, which is tapped via a shuttle valve cascade on the mobile control block.
- the pressure port P is connected to a pump channel 2 of the directional control valve element 1, from which an inlet channel 4 branches off. This leads to an input terminal of an individual pressure compensator 6, which forms a current regulator together with a proportional metering valve 8 forming a metering orifice.
- the pressure compensator 6 is biased by a pressure compensator spring 10 in its rest position, which is then taken when the connected to the illustrated directional control valve element 1 consumer has no pressure medium demand and the directional control valve 8 is switched to its illustrated basic position.
- the pressure compensator 6 is moved from the illustrated rest position to a control position, wherein the pressure upstream of the directional control valve 8 via a control line 12 in the closing direction and the pressure downstream of the metering orifice formed by the directional control valve 8 together with the pressure compensator spring 10 in the opening direction to the pressure compensator 6 acts.
- the pressure downstream of the metering orifice is tapped via the LS line 14.
- the output of the pressure compensator is connected via a pressure compensator channel 16 to the input port P of the directional control valve 8.
- This also has two working ports A, B and a tank port T, which is connected via a drain channel 18 with a tank port 20 opening into the tank port T.
- the two working ports A, B are connected via a flow channel 22 and a return channel 24 to the working ports A and B of the directional control valve element.
- the tank port T is connected to the LS line 14 and two LS pressure limiting channels 26, 28.
- the LS pressure limiting channel 26 is assigned to the working connection A and the LS pressure limiting duct 28 to the working connection B of the directional control valve element 1.
- the LS pressure control channels 26, 28 each have an LS pressure relief valve 30 and 32 is arranged, via which the maximum, applied to the load terminals A, B load pressure is limited.
- Both LS pressure relief valves 30, 32 are designed to be adjustable, so that different LS maximum pressures in the flow and in the return are adjustable.
- the two outputs of the LS pressure relief valves 30, 32 are connected to a control oil return passage 34 which is connected to the control oil return Y.
- the adjustment of the directional control valve 8 via two pressure reducing valves 36, 38, whose inputs are connected to a Steuerölzu Switzerlandkanal 40.
- the tank ports of the pressure reducing valves 36, 38 are connected to the control oil return passage 34.
- the set by the pressure reducing valve 36, 38 output pressure is passed via a control line 42 and 44 to the effective in the direction of a or b control surfaces of the directional valve piston.
- the control of the two pressure reducing valves 36, 38 via a respective proportional solenoid in response to a control signal of the control unit.
- These control signals for setting a control pressure difference for adjusting the directional control valve 8 can be specified for example by the operator via a joystick to actuate the connected consumer.
- the return passage 24 is connected via a connecting channel with the tank passage 20, but this connecting channel is shut off via a locking screw 46.
- the pressure in the flow channel 22 and in the return channel 24 is detected via a respective pressure sensor 48, 50 and passed on not shown signal lines to a control unit, also not shown, of the mobile working device.
- a further pressure transducer 52 is provided, via which the pump pressure in the pump channel 2 is detected.
- this pressure sensor 52 is not necessarily required. By means of the pressure transducer 52, however, an alternative pressure cut can be realized.
- the flow channel 22 is connected to the tank channel 20 via a bypass channel 54.
- a pressure limiting Nachsaugventil 56 is provided, can be sucked through to avoid cavitations pressure fluid from the tank passage 20 and via which a pressure protection of the flow channel 22 takes place.
- Such a pressure limiting Nachsaugventil 56 can also be used instead of the screw plug 46, so that the return channel 24 is secured and pressure medium can be sucked.
- the valve spool of the directional control valve 8 can be moved from its illustrated basic position to the left in the positions marked a, in which the pressure port P on the controlled metering orifice the working port A and the working port B is connected to the tank port T.
- a section of the pressure medium flow path located downstream of the controlled metering orifice is also connected to the LS line 14, so that this pressure (downstream of the metering orifice) acts on the pressure compensator 6 in the opening direction.
- the LS line 14 is further connected to the LS pressure limiting channel 26 in the positions marked with a, so that the load pressure in the LS line 14 is limited to the value set on the LS pressure limiting valve 30.
- the pressure in the LS line 14 is applied to the input of a shuttle valve 58 whose other input port is connected to a channel 60 connected to another directional control valve element or tank.
- the output of the shuttle valve 58 is connected via an LS channel 62 with the LS terminals of the further directional valve elements of the other consumer or the pump controller, so that the highest load pressure is passed to the pump controller via a shuttle valve cascade.
- This pump controller regulates the pump pressure so that it is always at a predetermined pressure difference, for example, 20 bar above the maximum load pressure.
- the pressure medium flows via the working port A to the consumer and from this via the working port B to the tank T, wherein the pressure medium flow rate constant load pressure independent via the metering orifice and the upstream LS-pressure compensator 6 constant
- the LS pressure compensator keeps the pressure drop across the metering orifice constant.
- the pressure downstream of the metering orifice which is controlled between the input port P and the working port B of the directional control valve element 1, is tapped via the LS line 14 and guided to the control surface of the LS pressure compensator 6 that is effective in the opening direction.
- the LS line 14 is at the positions marked with b with the LS pressure limiting channel 28, so that the maximum load pressure is then limited by the LS pressure limiting valve 32.
- the directional control valve elements 1 of the other consumers are constructed accordingly. It is now assumed that several of these consumers are actuated simultaneously via the respective directional control valve element 1 and that the load pressure of the consumer connected to the directional control valve 1 to the working ports A, B is the highest load pressure of the system. Accordingly, the pump pressure is adjusted by the aforementioned pressure difference (20 bar) above this highest load pressure. It is assumed that the consumer port A is supplied with pressure medium, so that the directional control valve 8 must be adjusted in one of its marked with a positions. Now moves the associated consumer to stop, so the load pressure at the working port A and thus increases in the LS-pressure limiting channel 26 and in the LS line 14 at.
- the load pressure is limited via the LS pressure relief valve 30 to a maximum value that can not be exceeded.
- the load pressure increase is detected in the flow channel 22 and when reaching a predetermined maximum pressure of approximately the set via the LS pressure relief valve maximum load pressure, a control signal to the two pressure reducing valves 36, 38 delivered via the control unit, not shown, so that these close the metering orifice and accordingly the directional control valve 8 is moved back to its illustrated basic position.
- This closing movement of the directional valve 8 can be sudden or in the form of a characteristic curve (ramp) according to a predetermined characteristic.
- a corresponding control with a closing of the maximum load associated with the metering orifice can also take place when an excessive external load occurs.
- the directional control valve becomes 8 again adjusted to its desired position and the associated consumer again supplied with pressure medium.
- the directional control valve 8 Upon actuation of the consumer in the opposite direction, the directional control valve 8 is moved to its positions indicated by b, in which case the pressure is detected by the further pressure sensor 50 and the metering orifice is closed again when the predetermined maximum load pressure is exceeded.
- the control of the pump does not depend on the highest load pressure but electrically via stored in the control unit characteristics of the pump and the proportional solenoid for driving the pressure reducing valves 38, 46.
- the pressure transducer 52 can be used. It is determined via the control unit based on the stored characteristics and in dependence of the detected pressures in the pump channel 2 and in the channels 22, 24 and the settings of the pressure reducing valves, whether the calculated pressure drop across the metering orifice corresponds to the measured pressure drop.
- LS, LUDV, EFM and PC systems work with the pressure sensors 48, 50.
- EFM and PC systems only the piston of the directional control valve 8 then has to be taken back, with EFM and PC systems, the pump quantity has to be adjusted become. If one has an additional sensor 52, one can apply an alternative decision criterion. However, this also works with all systems.
- EFM systems can also be controlled without the pressure transducer 52 in the manner according to the invention. This can be achieved, for example, by using as input of the EFM calculation not the original joystick signal for actuating the consumer but the reduced signal which is given to the pressure reducing valves 36, 38 when the maximum load pressure is reached in order to close the metering orifice. On the basis of this signal is then based on the stored in the control unit pump characteristic and in dependence From the highest load pressure of the parallel loads the pump is driven to minimize the losses.
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Description
Die Erfindung betrifft eine Steueranordnung zur Druckmittelversorgung von zumindest zwei Verbrauchern gemäß dem Oberbegriff des Patentanspruches 1 und ein Verfahren zur Ansteuerung der Verbraucher gemäß dem Oberbegriff des Patentanspruches 12.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
Zur Ansteuerung mehrerer Verbraucher werden Hydrauliksysteme eingesetzt, bei denen die Verbraucher über eine gemeinsame Pumpe (Konstantpumpe mit Bypassdruckwaage oder Verstellpumpe) mit Druckmittel versorgt werden. Im Druckmittelströmungspfad zwischen der Pumpe und jedem Verbraucher sind eine Zumessblende und eine Druckwaage vorgesehen, über die der Druckmittelvolumenstrom zum Verbraucher einstellbar ist. Dabei unterscheidet man nach dem Stromreglerprinzip und nach dem Stromteilerprinzip arbeitende Systeme, bei Letzteren ist die Druckwaage der Zumessblende stets nachgeschaltet. Diese Stromteilersysteme bezeichnet man auch als LUDV-Systeme, die eine Untergruppe der LS-Systeme darstellen. Bei einem LS-System wird die Pumpe in Abhängigkeit vom höchsten Lastdruck der betätigten hydraulischen Verbraucher so eingestellt, dass der Zulaufdruck um eine vorbestimmte Druckdifferenz über dem höchsten Lastdruck liegt.To control several consumers hydraulic systems are used, in which the consumers are supplied via a common pump (constant pump with bypass pressure compensator or variable displacement) with pressure medium. In the pressure medium flow path between the pump and each consumer 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 systems, in the latter, the pressure compensator of the metering orifice is always downstream. These current divider systems are also referred to as LUDV systems, which represent a subgroup of the LS systems. In an LS system, 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.
Bei LUDV-Systemen sind die nachgeschalteten Druckwaagen in Öffnungsrichtung von dem Druck nach der jeweiligen Zumessblende und in Schließrichtung von einem Steuerdruck beaufschlagt, der üblicher Weise dem höchsten Lastdruck aller angesteuerten Verbraucher entspricht. Bei einem derartigen System werden im Fall einer Untersättigung, die den einzelnen hydraulischen Verbrauchern zufließenden Druckmittelmengen unabhängig vom jeweiligen Lastdruck der hydraulischen Verbraucher verhältnisgleich reduziert (lastunabhängige Durchflussverteilung).In LUDV systems, the downstream pressure compensators are acted upon in the opening direction by the pressure to the respective metering orifice and in the closing direction of a control pressure, which usually corresponds to the highest load pressure of all driven consumers. In such a system, in the case of a supersaturation, the pressure fluid quantities flowing to the individual hydraulic consumers are proportionally reduced independently of the respective load pressure of the hydraulic consumers (load-independent flow distribution).
Bei nach dem Stromreglerprinzip arbeitenden Systemen wird die der Zumessblende vor- oder nachgeschaltete Druckwaage in Schließrichtung vom Druck vor der Zumessblende und in Öffnungsrichtung vom Lastdruck stromabwärts der Zumessblende beaufschlagt, so dass man keine lastunabhängige Durchflussverteilung erhält. Bei gleichzeitiger Betätigung mehrerer hydraulischer Verbraucher und nicht ausreichend von der Verstellpumpe gelieferter Druckmenge (Untersättigung) wird nur die dem Lastdruck höchsten Verbraucher zufließende Druckmittelmenge reduziert.In systems operating according to the current regulator principle, 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. When several hydraulic consumers are actuated at the same time and the amount of pressure (undersaturation) is insufficiently provided by the variable displacement pump, only the amount of pressure medium flowing into the load of the highest load is reduced.
Ein derartiges System ist beispielsweise im Datenblatt RD 64 276 der Bosch Rexroth AG (Steuerblock M4-12) beschrieben.Such a system is described, for example, in data sheet RD 64 276 of Bosch Rexroth AG (control block M4-12).
In der
Werden über die vorbeschriebenen Steueranordnungen zwei oder mehrere Verbraucher betätigt, von denen einer auf Anschlag fährt, so bleibt dieser Verbraucher weiterhin betätigt und es wird entsprechend Druckmittel von der Pumpe zum Verbraucher gefördert wird. Der Druck im Vorlauf des auf Anschlag gefahrenen Verbrauchers ist üblicher Weise über ein Druckbegrenzungsventil begrenzt, das eine Druckmittelverbindung zum Tank öffnet, so dass das überschüssige Druckmittel zum Tank gefördert wird.If two or more consumers are actuated via the above-described control arrangements, one of which drives to a stop, this consumer continues to be actuated and corresponding pressure medium is conveyed from the pump to the consumer. The pressure in the flow of the driven to stop consumer is usually limited by a pressure relief valve, which opens a pressure medium connection to the tank, so that the excess pressure medium is conveyed to the tank.
Bei dem vorgenannten Steuerblock M4-12 wird der Lastdruck aller Verbraucher über einen LS-Kanal zur Pumpe gemeldet und diese dann in Abhängigkeit vom Lastdruck eingestellt, so dass der Pumpendruck um eine vorbestimmte Druckdifferenz oberhalb des höchsten Lastdrucks liegt. Der Lastdruck wird von den jeweiligen Verbrauchern über LS-Leitungen abgegriffen und über eine Wechselventilkaskade in den LS-Kanal gemeldet. Beim Steuerblock M4-12 ist in den LS-Leitungen jeweils ein LS-Druckbegrenzungsventil angeordnet. Das dem auf Anschlag gefahrenen Verbraucher zugeordnete LS-Druckbegrenzungsventil begrenzt den Lastdruck dann auf einen Maximallastdruck, so dass entsprechend die Pumpe in Abhängigkeit von diesem maximalen Lastdruck eingestellt wird - demgemäß wird dann der Pumpendruck auf den LS-Maximaldruck plus der vorgenannten Druckdifferenz eingeregelt - die Pumpe wird somit auf ihren maximalen - aber begrenzten - Förderdruck eingestellt. Dementsprechend muss dieser Maximaldruck im Druckmittelströmungspfad zu den anderen Verbrauchern über die jeweiligen Individualdruckwaagen auf den jeweiligen Lastdruck abgedrosselt werden. Über das dem auf Anschlag gefahrenen Verbraucher zugeordnete LS-Druckbegrenzungsventil fließt ein kleiner Steuerölvolumenstrom zum Tank ab.In the aforementioned control block M4-12, the load pressure of all consumers is reported via an LS channel to the pump and then set in dependence on the load pressure, so that the pump pressure is above the highest load pressure by a predetermined pressure difference. The load pressure is picked up by the respective consumers via LS lines and reported via a shuttle valve cascade into the LS channel. In the control block M4-12 each LS-pressure relief valve is arranged in the LS lines. The LS-pressure relief valve associated with the consumer driven to the stop limits the load pressure to a maximum load pressure, so that the pump is adjusted in accordance with this maximum load pressure - accordingly the pump pressure is adjusted to the LS maximum pressure plus the aforementioned pressure difference - the pump is thus adjusted to its maximum - but limited - delivery pressure. Accordingly, this maximum pressure must be throttled in the pressure fluid flow path to the other consumers via the respective individual pressure compensators to the respective load pressure. A small pilot oil volume flow to the tank flows via the LS pressure relief valve assigned to the consumer driven to the stop.
Ein derartiges System sorgt zwar dafür, dass bei Fahren eines Verbrauchers auf Anschlag die Druckmittelmenge reduziert oder begrenzt wird - es entstehen jedoch durch das Abdrosseln des Pumpendrucks im Druckmittelströmungspfad zu den lastniedrigeren Verbrauchern erhebliche Energieverluste.Although such a system ensures that when driving a consumer to stop the amount of pressure medium is reduced or limited - but it caused by the throttling of the pump pressure in the pressure medium flow path to the lower-load consumers considerable energy losses.
Bei den eingangs beschriebenen LUDV-Systemen, die beispielsweise bei Baggern für die Betätigung der Ausrüstung eingesetzt sind, wird der Pumpenförderstrom durch eine so genannte Druckabschneidung nach einem ähnlichen Prinzip wie oben beschrieben begrenzt oder verringert, um Leistungsverluste zu vermeiden. Auch bei den LUDV-Systemen mit Druckabschneidung muss der Druckmittelvolumenstrom zu den lastniedrigeren Verbrauchern an den Individualdruckwaagen abgedrosselt werden.In the LUDV systems described above, which are used, for example, in excavators for the operation of the equipment, the pump flow is limited or reduced by a so-called pressure cut on a similar principle as described above, in order to avoid power losses. Even with the LUDV systems with pressure cut-off, the pressure medium volume flow must be throttled to the lower-load consumers on the individual pressure compensators.
Die
Eine hydraulische Steueranordnung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 und ein Verfahren mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 12 sind aus der
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Steueranordnung und ein Verfahren zur Ansteuerung von zumindest zwei hydraulischen Verbrauchern zu schaffen, bei denen bei Überschreiten eines vorbestimmten Lastdrucks des lastdruckhöchsten Verbrauchers Energieverluste auf einfache Weise minimiert sind.In contrast, the invention has for its object to provide a control arrangement and a method for controlling at least two hydraulic consumers, in which energy losses are minimized in a simple manner when a predetermined load pressure of the load pressure highest consumer is exceeded.
Diese Aufgabe wird hinsichtlich der Steueranordnung durch die Merkmalskombination des Patentanspruches 1 und hinsichtlich des Verfahrens durch die Merkmalskombination des nebengeordneten Patentanspruches 12 gelöst.This object is achieved with respect to the control arrangement by the feature combination of claim 1 and in terms of the method by the feature combination of the
Gemäß der Erfindung ist die Einrichtung zur Verstellung der Pumpe bei Überschreiten des Maximallastdrucks mit einem Drucksensor zum Erfassen des Vorlaufdrucks zum Verbraucher ausgeführt, dessen Ausgangssignal über eine Steuereinheit in ein Stellsignal zur Ansteuerung der zugeordneten Zumessblende bearbeitbar ist.According to the invention, the device for adjusting the pump is executed when the maximum load pressure is exceeded with a pressure sensor for detecting the flow pressure to the consumer whose output signal is editable via a control unit in a control signal for controlling the associated metering orifice.
Dabei wird es bevorzugt, wenn die zugeordnete Zumessblende bei Erreichen des Maximallastdrucks zugesteuert wird, so dass der betreffende Verbraucher nicht mehr versorgt wird, so dass nur noch die Lastdrücke der anderen, lastniedrigeren Verbraucher bei der Pumpenregelung berücksichtigt werden.It is preferred if the associated metering orifice is controlled on reaching the maximum load pressure, so that the consumer in question is no longer supplied, so that only the load pressures of the other, lower-load consumers are taken into account in the pump control.
Erfindungsgemäß ist in den Druckmittelströmungspfaden zu den über eine Pumpe mit Druckmittel versorgten Verbrauchern jeweils eine verstellbare Zumessblende angeordnet, um den Druckmittelvolumenstrom individuell einzustellen. Die Pumpe wird in Abhängigkeit vom höchsten Lastdruck der Verbraucher derart eingestellt, dass der Druckmittelbedarf aller angesteuerten Verbraucher gedeckt ist. Erfindungsgemäß wird über eine Einrichtung der Lastdruck der einzelnen Verbraucher überwacht und bei Überschreiten eines vorbestimmten Maximallastdrucks an einem Verbraucher der Pumpendruck oder die Pumpenmenge in Abhängigkeit vom Druckmittelbedarf der anderen, lastniedrigeren Verbraucher eingestellt, so dass die Drosselverluste an diesen Verbrauchern gegenüber den eingangs beschriebenen Lösungen minimal sind. Bei der erfindungsgemäßen Anordnung wird somit in dem Fall, in dem ein Verbraucher auf Anschlag fährt oder eine sehr hohe äußere Last auftritt, der Energieverlust innerhalb der Schaltung minimiert, da das Druckniveau der Pumpe im Vergleich zu bestehenden Lösungen reduziert ist.According to the invention, in each case an adjustable metering orifice is arranged in the pressure medium flow paths to the consumers supplied via a pump with pressure medium in order to set the pressure medium volume flow individually. The pump is set in dependence on the highest load pressure of the consumer so that the pressure medium requirement of all controlled consumers is covered. According to the invention, the load pressure of the individual consumer is monitored by means of a device and set when exceeding a predetermined maximum load pressure at a consumer, the pump pressure or the pump quantity in dependence on the pressure medium demand of the other, lower-load consumer, so that the throttle losses of these consumers are minimal compared to the solutions described above , Thus, in the case of the arrangement according to the invention, in the case where a consumer strikes or a very high external load occurs, the energy loss within the circuit is minimized since the pressure level of the pump is reduced compared to existing solutions.
Erfindungsgemäß wird es bevorzugt, wenn der Zumessblende eine LS- oder LUDV-Individualdruckwaage zugeordnet ist, so dass ein nach dem Stromreglerprinzip oder dem Stromteilerprinzip arbeitende Steueranordnung gebildet ist.According to the invention, it is preferred if the metering orifice is assigned an LS or LUDV individual pressure balance, so that a control arrangement operating according to the current regulator principle or the current dividing principle is formed.
Bei einem Ausführungsbeispiel der Erfindung ist der maximale Lastdruck der Steueranordnung durch LS-Druckbegrenzungsventile in den jeweiligen Lastdruck führenden LS-Leitungen begrenzt, dementsprechend liegt der vorbeschriebene Maximallastdruck im Bereich des durch die LS-Druckbegrenzungsventile eingestellten maximalen LS-Drucks.In one embodiment of the invention, the maximum load pressure of the control arrangement is limited by LS pressure relief valves in the respective load pressure leading LS lines, accordingly, the prescribed maximum load pressure in the range of the maximum LS pressure set by the LS pressure relief valves.
Dabei ist es vorteilhaft, wenn die Einrichtung derart ausgeführt ist, dass das Lastdrucksignal des mit Maximallastdruck belasteten Verbrauchers nicht in den LS-Kanal gemeldet werden kann.It is advantageous if the device is designed such that the load pressure signal of the loaded with maximum load pressure consumer can not be reported in the LS channel.
Falls die Steueranordnung als EFM-System ausgeführt sein soll, wird die Pumpe elektrisch oder elektrohydraulisch ansteuerbar ausgeführt, wobei über die Einrichtung an die Pumpe ein Mengensignal zum Verstellen der Pumpen abgegeben werden kann.If the control arrangement is to be embodied as an EFM system, the pump is designed to be electrically or electrohydraulically activatable, it being possible for a quantity signal for adjusting the pumps to be delivered via the device to the pump.
Dieses Mengensignal kann beispielsweise in Abhängigkeit von dem Signal zur Verstellung der Zumessblende des lasthöchsten Verbrauchers generiert werden.This quantity signal can be generated, for example, as a function of the signal for adjusting the metering orifice of the highest-load consumer.
Bei derartigen EFM-Systemen kann neben den vorstehenden Drucksensoren zur Erfassung des höchsten Lastdrucks ein zusätzlicher Drucksensor zum Erfassen des Pumpendrucks vorgesehen sein. In einer Vergleichseinrichtung werden dann die erfassten Lastdrücke und der Pumpendruck miteinander verglichen und in dem Fall, in dem diese Druckdifferenz unterhalb eines vorbestimmten Wertes liegt, über die Einrichtung ein Steuersignal zum Zusteuern der Zumessblende des lasthöchsten Verbrauchers und zum Zurückfahren der Pumpe abgegeben.In such EFM systems, in addition to the above pressure sensors for detecting the highest load pressure, an additional pressure sensor for detecting the pump pressure may be provided. In a comparison device, the detected load pressures and the pump pressure are then compared with each other and in the case in which this pressure difference is below a predetermined value, issued via the device, a control signal for controlling the metering orifice of the load highest load and for returning the pump.
Das Zusteuern der Zumessblende kann stufenförmig (schwarz-weiß) oder über eine Kennlinie erfolgen.The control of the metering orifice can be stepped (black-white) or via a characteristic curve.
Das Aufsteuern der Zumessblende erfolgt dann, wenn der Lastdruck an diesem lasthöchsten Verbraucher wieder unter den Maximallastdruck abgesunken ist. Dabei wird es bevorzugt, wenn das Aufsteuern der betreffenden Zumessblende erst dann erfolgt, wenn der tatsächliche Lastdruck um eine vorbestimmte Druckdifferenz unter dem Maximallastdruck liegt. Das System ist in diesem Fall mit einer gewissen "Druckhysterese" ausgeführt.The control of the metering orifice takes place when the load pressure at this highest load has fallen back below the maximum load pressure. It is preferred that the control of the respective metering orifice takes place only when the actual load pressure is a predetermined pressure difference below the maximum load pressure. The system is designed in this case with a certain "pressure hysteresis".
Die erfindungsgemäße Steueranordnung kann beispielsweise als LS-System (Stromreglersystem), als LUDV-System (Stromteilersystem), als EFM-System (LS und LUDV) oder als elektrohydraulisches Positiv-Control-System (PC) ausgeführt sein. Bei diesem System wird der Schwenkwinkel der Pumpe mit dem Steuersignal zum Einstellen der Zumessblende vergrößert.The control arrangement according to the invention can be embodied, for example, as an LS system (current regulator system), as a LUDV system (current divider system), as an EFM system (LS and LUDV) or as an electrohydraulic positive control system (PC). In this system, the swing angle of the pump is increased with the control signal for adjusting the metering orifice.
Im Folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand einer Zeichnung näher erläutert.In the following, a preferred embodiment of the invention will be explained in more detail with reference to a drawing.
Diese einzige Zeichnung zeigt ein Schaltbild eines elektrohydraulischen Wegeventilelementes 1 eines Mobilsteuerblocks, der üblicher Weise aus einem Eingangselement, mehreren Wegeventilelementen (mechanisch, hydraulisch, elektrohydraulisch) und einem Endelement besteht. Derartige Mobilsteuerblöcke sind beispielsweise im eingangs genannten Datenblatt RD 64276 der Bosch Rexroth AG beschrieben. Dabei kann jedem hydraulischen Verbraucher ein Wegeventilelement gemäß der im Folgenden beschriebenen Figur zugeordnet sein.This single drawing shows a circuit diagram of an electro-hydraulic directional control valve element 1 of a mobile control block, the usual way consists of an input element, a plurality of directional control valve elements (mechanical, hydraulic, electro-hydraulic) and an end member. Such mobile control blocks are described for example in the above-mentioned data sheet RD 64276 Bosch Rexroth AG. In this case, each hydraulic consumer can be assigned a directional control valve element according to the figure described below.
Ein derartiges Wegeventilelement 1 hat einen Druckanschluss P, eine Steuerölzuführung X, eine Steuerölrückführung Y, einen LS-Anschluss LS, einen Tankanschluss T sowie zwei Arbeitsanschlüsse A, B, die beispielsweise mit einem bodenseitigen Zylinderraum und einem kolbenstangenseitigen Ringraum eines Hydrozylinders verbunden sind. Bei dem im Folgenden beschriebenen Ausführungsbeispiel ist an den Druckanschluss P eine LS-Pumpe angeschlossen, über die die Wegeventilelemente 1 des Steuerblocks mit Druckmittel versorgt werden. Die Ansteuerung der LS-Pumpe erfolgt in der eingangs beschriebenen Weise in Abhängigkeit vom höchsten Lastdruck aller Verbraucher, wobei dieser über eine Wechselventilkaskade am Mobilsteuerblock abgegriffen wird.Such a directional control valve element 1 has a pressure port P, a control oil supply X, a control oil return Y, a LS port LS, a tank port T and two working ports A, B, which are connected for example with a bottom-side cylinder chamber and a piston rod side annular space of a hydraulic cylinder. In the embodiment described below, an LS pump is connected to the pressure port P, via which the directional control valve elements 1 of the control block are supplied with pressure medium. The activation of the LS pump is carried out in the manner described above in response to the highest load pressure of all consumers, which is tapped via a shuttle valve cascade on the mobile control block.
Der Druckanschluss P ist an einen Pumpenkanal 2 des Wegeventilelementes 1 angeschlossen, von dem ein Zulaufkanal 4 abzweigt. Dieser führt zu einem Eingangsanschluss einer Individualdruckwaage 6, die gemeinsam mit einem eine Zumessblende ausbildenden proportional verstellbaren Wegeventil 8 einen Stromregler bildet. Die Druckwaage 6 ist über eine Druckwaagenfeder 10 in ihre Ruheposition vorgespannt, die dann eingenommen wird, wenn der an das dargestellte Wegeventilelement 1 angeschlossene Verbraucher keinen Druckmittelbedarf hat und das Wegeventil 8 in seine dargestellte Grundposition geschaltet ist. Bei einem Druckmittelbedarf wird die Druckwaage 6 aus der dargestellten Ruheposition in eine Regelposition verschoben, wobei der Druck stromaufwärts des Wegeventils 8 über eine Steuerleitung 12 in Schließrichtung und der Druck stromabwärts der durch das Wegeventil 8 gebildeten Zumessblende gemeinsam mit der Druckwaagenfeder 10 in Öffnungsrichtung auf die Druckwaage 6 wirkt. Der Druck stromabwärts der Zumessblende wird über die LS-Leitung 14 abgegriffen. Der Ausgang der Druckwaage ist über einen Druckwaagenkanal 16 mit dem Eingangsanschluss P des Wegeventils 8 verbunden. Dieses hat des Weiteren zwei Arbeitsanschlüsse A, B und einen Tankanschluss T, der über einen Ablaufkanal 18 mit einem in den Tankanschluss T mündenden Tankkanal 20 verbunden ist. Die beiden Arbeitsanschlüsse A, B sind über einen Vorlaufkanal 22 und einen Rücklaufkanal 24 mit den Arbeitsanschlüssen A bzw. B des Wegeventilelements verbunden.The pressure port P is connected to a
In der dargestellten Grundposition des Wegeventils 8 sind die beiden Arbeitsanschlüsse A, B und der Druckanschluss P abgesperrt, der Tankanschluss T ist mit der LS-Leitung 14 sowie zwei LS-Druckbegrenzungskanälen 26, 28 verbunden. Dabei ist der LS-Druckbegrenzungskanal 26 dem Arbeitsanschluss A und der LS-Druckbegrenzungskanal 28 dem Arbeitsanschluss B des Wegeventilelementes 1 zugeordnet. In den LS-Druckbegrenzungskanälen 26, 28 ist jeweils ein LS-Druckbegrenzungsventil 30 bzw. 32 angeordnet, über die der maximale, an den Verbraucheranschlüssen A, B anliegende Lastdruck begrenzt ist. Beide LS-Druckbegrenzungsventile 30, 32 sind verstellbar ausgeführt, so dass unterschiedliche LS-Maximaldrücke im Vorlauf und im Rücklauf einstellbar sind. Die beiden Ausgänge der LS-Druckbegrenzungsventile 30, 32 sind mit einem Steuerölrückführkanal 34 verbunden, der an die Steuerölrückführung Y angeschlossen ist.In the illustrated basic position of the
Die Verstellung des Wegeventils 8 erfolgt über zwei Druckreduzierventile 36, 38, deren Eingänge an einen Steuerölzuführkanal 40 angeschlossen sind. Die Tankanschlüsse der Druckreduzierventile 36, 38 sind mit dem Steuerölrückführkanal 34 verbunden. Der von dem Druckreduzierventil 36, 38 eingestellte Ausgangsdruck wird über eine Steuerleitung 42 bzw. 44 zu den in Richtung a bzw. b wirksamen Steuerflächen des Wegeventilkolbens geführt. Die Ansteuerung der beiden Druckreduzierventile 36, 38 erfolgt über jeweils einen Proportionalmagneten in Abhängigkeit von einem Stellsignal der Steuereinheit. Diese Stellsignale zum Einstellen einer Steuerdruckdifferenz zur Verstellung des Wegeventils 8 können beispielsweise durch die Bedienperson über einen Joystick vorgegeben werden, um den angeschlossenen Verbraucher zu betätigen.The adjustment of the
Bei dem dargestellten Ausführungsbeispiel ist der Rücklaufkanal 24 über einen Verbindungskanal mit dem Tankkanal 20 verbunden, dieser Verbindungskanal ist jedoch über eine Verschlussschraube 46 abgesperrt.In the illustrated embodiment, the
Der Druck im Vorlaufkanal 22 und im Rücklaufkanal 24 wird über jeweils einen Drucksensor 48, 50 erfasst und über nicht dargestellte Signalleitungen an eine ebenfalls nicht dargestellte Steuereinheit des mobilen Arbeitsgerätes weiter gegeben. Bei dem dargestellten Ausführungsbeispiel ist ein weiterer Druckaufnehmer 52 vorgesehen, über den der Pumpendruck im Pumpenkanal 2 erfasst wird. Dieser Druckaufnehmer 52 ist jedoch nicht notwendiger Weise erforderlich. Mittels des Druckaufnehmers 52 kann jedoch eine alternative Druckabschneidung realisiert werden.The pressure in the
Bei dem Wegeventilelement 1 ist der Vorlaufkanal 22 über einen Bypasskanal 54 mit dem Tankkanal 20 verbunden. Im Bypasskanal 54 ist ein Druckbegrenzungs-Nachsaugventil 56 vorgesehen, über das zur Vermeidung von Kavitationen Druckmittel aus dem Tankkanal 20 nachgesaugt werden kann und über das auch eine Druckabsicherung des Vorlaufkanals 22 erfolgt. Ein derartiges Druckbegrenzungs-Nachsaugventil 56 kann auch anstelle der Verschlussschraube 46 eingesetzt werden, so dass auch der Rücklaufkanal 24 abgesichert ist und Druckmittel nachgesaugt werden kann.In the directional control valve element 1, the
Durch geeignete Einstellung einer Steuerdruckdifferenz über die Druckreduzierventile 36, 38 kann der Ventilschieber des Wegeventils 8 aus seiner dargestellten Grundposition nach links in die mit a gekennzeichneten Positionen verfahren werden, in denen der Druckanschluss P über die aufgesteuerte Zumessblende mit dem Arbeitsanschluss A und der Arbeitsanschluss B mit dem Tankanschluss T verbunden ist. In diesen mit a gekennzeichneten Positionen ist des Weiteren ein stromabwärts der aufgesteuerten Zumessblende gelegener Abschnitt des Druckmittelströmungspfads mit der LS-Leitung 14 verbunden, so dass dieser Druck (stromabwärts der Zumessblende) die Druckwaage 6 in Öffnungsrichtung beaufschlagt. Die LS-Leitung 14 ist des Weiteren in den mit a gekennzeichneten Positionen mit dem LS-Druckbegrenzungskanal 26 verbunden, so dass der Lastdruck in der LS-Leitung 14 auf den am LS-Druckbegrenzungsventil 30 eingestellten Wert begrenzt ist. Der Druck in der LS-Leitung 14 steht am Eingang eines Wechselventils 58 an, dessen anderer Eingangsanschluss an einen mit einem weiteren Wegeventilelements oder mit Tank verbundenen Kanal 60 angeschlossen ist. Der Ausgang des Wechselventils 58 ist über einen LS-Kanal 62 mit den LS-Anschlüssen der weiteren Wegeventilelemente der sonstigen Verbraucher bzw. dem Pumpenregler verbunden, so dass über eine Wechselventilkaskade der höchste Lastdruck zum Pumpenregler geführt ist. Dieser Pumpenregler regelt den Pumpendruck so ein, dass er stets um eine vorbestimmte Druckdifferenz, beispielsweise um 20 bar oberhalb des maximalen Lastdrucks liegt.By appropriate adjustment of a control pressure difference across the
Bei einem vorbeschriebenen Verschieben des Wegeventilelementes 1 in die mit a gekennzeichnete Position strömt das Druckmittel über den Arbeitsanschluss A zum Verbraucher und von diesem über den Arbeitsanschluss B zum Tank T ab, wobei der Druckmittelvolumenstrom lastdruckunabhängig über die Zumessblende und die vorgeschaltete LS-Druckwaage 6 konstant gehalten wird, wobei die LS-Druckwaage in ihrer Regelposition den Druckabfall über der Zumessblende konstant hält.In a prescribed displacement of the directional control valve element 1 in the position indicated by a, the pressure medium flows via the working port A to the consumer and from this via the working port B to the tank T, wherein the pressure medium flow rate constant load pressure independent via the metering orifice and the upstream LS-
Bei Verstellen des Wegeventilelementes 1 in seine mit b gekennzeichnete Position wird entsprechend der Druckanschluss P mit dem Arbeitsanschluss B und der Arbeitsanschluss A mit dem Tankanschluss T verbunden, so dass praktisch der als Vorlaufkanal 22 bezeichnete Kanal der Rücklaufkanal wird und der mit Rücklaufkanal 24 bezeichnete Kanal der Vorlaufkanal ist, da das Druckmittel über den Arbeitsanschluss B des Wegeventilelementes 1 zum Verbraucher strömt und von diesem über den Arbeitsanschluss A zum Tankanschluss T abströmt.When adjusting the directional control valve element 1 in its position marked b is correspondingly connected to the pressure port P to the working port B and the working port A to the tank port T, so that practically referred to as the
Wie bei den vorbeschriebenen Positionen a wird der Druck stromabwärts der zwischen dem Eingangsanschluss P und dem Arbeitsanschluss B des Wegeventilelementes 1 aufgesteuerte Zumessblende über die LS-Leitung 14 abgegriffen und zu der in Öffnungsrichtung wirksamen Steuerfläche der LS-Druckwaage 6 geführt. Die LS-Leitung 14 ist bei den mit b gekennzeichneten Positionen mit dem LS-Druckbegrenzungskanal 28 verbunden, so dass der maximale Lastdruck dann durch das LS-Druckbegrenzungsventil 32 begrenzt ist.As in the above-described positions a, the pressure downstream of the metering orifice, which is controlled between the input port P and the working port B of the directional control valve element 1, is tapped via the
Die Wegeventilelemente 1 der anderen Verbraucher sind entsprechend aufgebaut. Es sei nun angenommen, dass mehrere dieser Verbraucher über das jeweilige Wegeventilelement 1 gleichzeitig betätigt werden und dass der Lastdruck des am Wegeventil 1 an die Arbeitsanschlüsse A, B angeschlossenen Verbrauchers der höchste Lastdruck des Systems ist. Entsprechend wird der Pumpendruck um die vorgenannte Druckdifferenz (20 bar) oberhalb dieses höchsten Lastdrucks eingestellt. Es sei angenommen, dass der Verbraucheranschluss A mit Druckmittel versorgt wird, so dass das Wegeventil 8 in eine seiner mit a gekennzeichneten Positionen verstellt werden muss. Fährt nun der zugeordnete Verbraucher auf Anschlag, so steigt der Lastdruck am Arbeitsanschluss A und damit auch im LS-Druckbegrenzungskanal 26 und in der LS-Leitung 14 an. Der Lastdruck ist jedoch über das LS-Druckbegrenzungsventil 30 auf einen Maximalwert begrenzt, der nicht überschritten werden kann. Über den Druckaufnehmer 48 wird der Lastdruckanstieg im Vorlaufkanal 22 erfasst und bei Erreichen eines vorbestimmten Maximaldrucks der in etwa dem über das LS-Druckbegrenzungsventil eingestellten maximalen Lastdruck entspricht, wird über die nicht dargestellte Steuereinheit ein Steuersignal an die beiden Druckreduzierventile 36, 38 abgegeben, so dass diese die Zumessblende schließen und entsprechend das Wegeventil 8 in seine dargestellte Grundposition zurückgefahren wird. Diese Schließbewegung des Wegeventils 8 kann sprungartig oder aber in Form einer Kennlinie (Rampe) nach einer vorgegebenen Charakteristik erfolgen. Bei vollständig geschlossener Zumessblende sinkt auch der in die LS-Leitung 14 gemeldete Lastdruck ab, so dass die Pumpenregelung nach Zusteuern des Wegeventils 8 in Abhängigkeit von den lastniedrigeren, parallelen Verbrauchern erfolgt. Der höchste Lastdruck dieser parallelen, lastniedrigeren Verbraucher wird dann zum Pumpenregler gemeldet und die Pumpe auf einen entsprechend niedrigeren Wert eingestellt, so dass die D-rosselverluste an den lastniedrigeren Verbrauchern wesentlich geringer als beim eingangs beschriebenen Stand der Technik ist.The directional control valve elements 1 of the other consumers are constructed accordingly. It is now assumed that several of these consumers are actuated simultaneously via the respective directional control valve element 1 and that the load pressure of the consumer connected to the directional control valve 1 to the working ports A, B is the highest load pressure of the system. Accordingly, the pump pressure is adjusted by the aforementioned pressure difference (20 bar) above this highest load pressure. It is assumed that the consumer port A is supplied with pressure medium, so that the
Eine entsprechende Steuerung mit einem Schließen der dem lasthöchsten Verbraucher zugeordneten Zumessblende kann auch bei Auftreten einer übermäßigen äußeren Last erfolgen.A corresponding control with a closing of the maximum load associated with the metering orifice can also take place when an excessive external load occurs.
Falls der Lastdruck an dem vormals lasthöchsten Verbraucher wieder unterhalb den am Steuergerät eingegebenen maximalen Lastdruck abfällt, wird das Wegeventil 8 wieder in seine Sollposition verstellt und der zugeordnete Verbraucher wieder mit Druckmittel versorgt.If the load pressure on the previously highest-load consumer again falls below the maximum load pressure entered on the control unit, the directional control valve becomes 8 again adjusted to its desired position and the associated consumer again supplied with pressure medium.
Bei einer Betätigung des Verbrauchers in der Gegenrichtung wird das Wegeventil 8 in seine mit b gekennzeichneten Positionen verstellt, wobei dann der Druck über den weiteren Druckaufnehmer 50 erfasst und bei Überschreiten des vorbestimmten Maximallastdrucks die Zumessblende wieder zugesteuert.Upon actuation of the consumer in the opposite direction, the
Bei einem EFM-System erfolgt die Ansteuerung der Pumpe nicht in Abhängigkeit vom höchsten Lastdruck sondern elektrisch über in der Steuereinheit abgelegte Kennlinien der Pumpe und der Proportionalmagnete zum Ansteuern der Druckreduzierventile 38, 46. Bei derartigen EFM-Systemen kann der Druckaufnehmer 52 eingesetzt werden. Dabei wird über die Steuereinheit anhand der abgelegten Kennlinien und in Abhängigkeit der erfassten Drücke im Pumpenkanal 2 und in den Kanälen 22, 24 und der Einstellungen der Druckreduzierventile ermittelt, ob der rechnerische Druckabfall über der Zumessblende dem gemessenen Druckabfall entspricht. Falls dieser Druckabfall zu gering ist und der Pumpendruck in etwa dem Lastdruck entspricht, ist dies ein zuverlässiges Indiz dafür, dass der Verbraucher entweder auf Anschlag gefahren ist oder dass die Last zu hoch ist - in diesem Fall wird dann die Zumessblende in der vorbeschriebenen Weise zugesteuert und die Pumpenmenge elektronisch in Abhängigkeit vom Druckmittelbedarf der lastniedrigeren Verbraucher abgesenkt. D.h. die vorbeschriebene Steuerung lässt sich sowohl elektrisch als elektrohydraulisch realisieren.In an EFM system, the control of the pump does not depend on the highest load pressure but electrically via stored in the control unit characteristics of the pump and the proportional solenoid for driving the
Grundsätzlich funktionieren LS-, LUDV-, EFM- und PC- Systeme mit den Drucksensoren 48, 50. Bei LS- und LUDV- Systemen muss dann nur der Kolben des Wegeventils 8 zurückgenommen werden, bei EFM- und PC- Systemen zusätzlich die Pumpenmenge angepasst werden. Wenn man einen zusätzlichen Sensor 52 hat, kann man ein alternatives Entscheidungskriterium anwenden. Dies geht allerdings auch wieder mit allen Systemen.In principle, LS, LUDV, EFM and PC systems work with the
EFM-Systeme lassen sich jedoch auch ohne den Druckaufnehmer 52 in der erfindungsgemäßen Weise regeln. Dies kann beispielsweise dadurch erreicht werden, dass als Eingang der EFM-Berechnung nicht das ursprüngliche Joysticksignal zum Betätigen des Verbrauchers sondern das reduzierte Signal verwendet wird, das beim Erreichen des vorbeschriebenen Maximallastdrucks an die Druckreduzierventile 36, 38 gegeben wird, um die Zumessblende zu schließen. Auf der Basis dieses Signals wird dann anhand der in der Steuereinheit abgelegten Pumpenkennlinie und in Abhängigkeit vom höchsten Lastdruck der parallelen Verbraucher die Pumpe angesteuert, um die Verluste zu minimieren.However, EFM systems can also be controlled without the
Offenbart sind eine Steueranordnung und ein Verfahren zum Ansteuern zumindest zweier hydraulischer Verbraucher, wobei bei Überschreiten eines vorbestimmten maximalen Lastdrucks eines der Verbraucher, die Pumpe in Abhängigkeit vom Druckmittelbedarf der anderen, lastniedrigeren Verbraucher angesteuert wird.Disclosed are a control arrangement and a method for controlling at least two hydraulic consumers, wherein when a predetermined maximum load pressure of one of the consumers, the pump is driven in response to the pressure medium requirement of the other, lower-load consumer.
Claims (13)
- Control arrangement for controlling at least two hydraulic consumers which can be supplied with pressure medium via a pump, there being arranged in the pressure-medium flow path to each of the consumers an electrically or electrohydraulically adjustable metering diaphragm (8), via which the pressure-medium volume flow to the consumer can be set, and there being a device, via which, when a maximum load pressure is reached in the forward flow (22, 24) of a consumer, the pump pressure or pump rate can be set as a function of the pressure-medium demand of the consumer or of the other consumers, characterized in that the device has a pressure transducer (48, 50) for detecting the forward-flow pressure, the output signal from which can be processed via a control unit into an actuating signal for controlling the assigned metering diaphragm (8).
- Control arrangement according to Patent Claim 1, the metering diaphragm (8) being closable when the maximum load pressure is reached.
- Control arrangement according to Patent Claim 2, the closing taking place according to a predetermined characteristic curve.
- Control arrangement according to one of the preceding patent claims, the load pressure of the consumers being picked off by means of an LS line (14; 26, 28) and being communicated to an LS duct (62), and the pump pressure of the pump being capable of being set as a function of the load pressure in the LS duct (62).
- Control arrangement according to one of the preceding patent claims, the metering diaphragm being assigned an LS or LUDV individual pressure balance (6).
- Control arrangement according to one of the preceding patent claims, an LS pressure-limiting valve (30, 32) being arranged in the LS line (14; 26, 28).
- Control arrangement according to one of the preceding patent claims, the device being designed in such a way that the load-pressure signal from the consumer with the highest load pressure is not taken into account in the control of the pump.
- Control arrangement according to one of the preceding patent claims, the pump being controlled electrically or electrohydraulically, and a rate signal being capable of being transmitted to the pump via the control unit for the purpose of lowering the pump pressure.
- Control arrangement according to Patent Claim 8, the rate signal being capable of being generated as a function of the signal for adjusting the metering diaphragm (8).
- Control arrangement according to Patent Claims 5 and 8 or 9, with a pressure transducer (52) for detecting the pump pressure and with a comparator device for comparing the load pressure in the forward flow (22, 24) and the pump pressure, and with a device for transmitting a control signal for closing the metering diaphragm (8) of the consumer with the highest load and for returning the pump when the pressure difference between the pump pressure and load pressure is below a predetermined value.
- Control arrangement according to one of the preceding patent claims, this being designed as an LS or LUDV system or as an EFM or positive-control system.
- Method for controlling a plurality of hydraulic consumers, to each of which an electrically or electrohydraulically adjustable metering diaphragm (8) for setting the pressure-medium volume flow is assigned, the highest load pressure of the consumers being detected and being used for setting the pump, and, when a maximum load pressure of a consumer is overshot, the pump control taking place as a function of the load pressure of the consumer or of the other consumers, characterized in that, when the maximum load pressure is overshot, the metering diaphragm of the consumer with the highest load pressure is closed.
- Method according to Patent Claim 12, the opening of the metering diaphragm (8) taking place when the load pressure of the consumer has fallen below the maximum load pressure by the amount of a specific pressure difference.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007035971A DE102007035971A1 (en) | 2007-08-01 | 2007-08-01 | Control arrangement and method for controlling at least two hydraulic consumers |
PCT/EP2008/058760 WO2009015999A1 (en) | 2007-08-01 | 2008-07-07 | Control arrangement and method for controlling at least two hydraulic consumers |
Publications (2)
Publication Number | Publication Date |
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EP2176556A1 EP2176556A1 (en) | 2010-04-21 |
EP2176556B1 true EP2176556B1 (en) | 2012-09-12 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP08774827A Not-in-force EP2176556B1 (en) | 2007-08-01 | 2008-07-07 | Control arrangement and method for controlling at least two hydraulic consumers |
Country Status (7)
Country | Link |
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US (1) | US8429909B2 (en) |
EP (1) | EP2176556B1 (en) |
JP (1) | JP5074591B2 (en) |
KR (1) | KR20100040900A (en) |
CN (1) | CN101765717A (en) |
DE (1) | DE102007035971A1 (en) |
WO (1) | WO2009015999A1 (en) |
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JP5553614B2 (en) * | 2007-02-21 | 2014-07-16 | シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | Hydraulic system |
DE102012216252A1 (en) * | 2012-09-13 | 2014-03-13 | Robert Bosch Gmbh | Hydraulic control arrangement for hydraulic drive of mini excavator, has input in front of metering orifice in fluid communication with another input at back of pressure chamber, and output connected to load signaling line |
DK3020983T3 (en) * | 2014-11-14 | 2020-08-10 | Danfoss Power Solutions Aps | Input module for a valve group |
JP7253478B2 (en) * | 2019-09-25 | 2023-04-06 | 日立建機株式会社 | working machine |
DE102019216771A1 (en) * | 2019-10-30 | 2021-05-06 | Robert Bosch Gmbh | Hydraulic control arrangement for supplying pressure medium to at least two hydraulic consumers |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JP3228931B2 (en) * | 1992-02-18 | 2001-11-12 | 日立建機株式会社 | Hydraulic drive |
DE19831595B4 (en) * | 1998-07-14 | 2007-02-01 | Bosch Rexroth Aktiengesellschaft | Hydraulic circuit |
DE10058032A1 (en) | 2000-11-23 | 2002-05-29 | Mannesmann Rexroth Ag | Hydraulic control arrangement |
DE10342037A1 (en) | 2003-09-11 | 2005-04-07 | Bosch Rexroth Ag | Control arrangement and method for pressure medium supply of at least two hydraulic consumers |
-
2007
- 2007-08-01 DE DE102007035971A patent/DE102007035971A1/en not_active Withdrawn
-
2008
- 2008-07-07 US US12/669,988 patent/US8429909B2/en not_active Expired - Fee Related
- 2008-07-07 EP EP08774827A patent/EP2176556B1/en not_active Not-in-force
- 2008-07-07 KR KR1020107002321A patent/KR20100040900A/en not_active Application Discontinuation
- 2008-07-07 CN CN200880101126A patent/CN101765717A/en active Pending
- 2008-07-07 JP JP2010518594A patent/JP5074591B2/en not_active Expired - Fee Related
- 2008-07-07 WO PCT/EP2008/058760 patent/WO2009015999A1/en active Application Filing
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Publication number | Publication date |
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DE102007035971A1 (en) | 2009-02-05 |
US20100192562A1 (en) | 2010-08-05 |
KR20100040900A (en) | 2010-04-21 |
JP2010534816A (en) | 2010-11-11 |
JP5074591B2 (en) | 2012-11-14 |
CN101765717A (en) | 2010-06-30 |
EP2176556A1 (en) | 2010-04-21 |
US8429909B2 (en) | 2013-04-30 |
WO2009015999A1 (en) | 2009-02-05 |
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