EP0515608B1 - Hydrauliksystem - Google Patents

Hydrauliksystem Download PDF

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Publication number
EP0515608B1
EP0515608B1 EP92900271A EP92900271A EP0515608B1 EP 0515608 B1 EP0515608 B1 EP 0515608B1 EP 92900271 A EP92900271 A EP 92900271A EP 92900271 A EP92900271 A EP 92900271A EP 0515608 B1 EP0515608 B1 EP 0515608B1
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EP
European Patent Office
Prior art keywords
pump
pressure difference
pressure
hydraulic system
measured
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.)
Expired - Lifetime
Application number
EP92900271A
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German (de)
English (en)
French (fr)
Other versions
EP0515608A1 (de
Inventor
Otwin Eich
Franz-Peter Salz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
Barmag Barmer Maschinenfabrik AG
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Filing date
Publication date
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Publication of EP0515608A1 publication Critical patent/EP0515608A1/de
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • 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
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—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
    • 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
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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

Definitions

  • the invention relates to a hydraulic system according to the preamble of the claim.
  • This hydraulic system is known from WO-A-9002882.
  • the position of the control valves is always readjusted when there is a deviation between the pressure difference between the load pressure and the pump pressure and the specified pressure difference.
  • the regulation provided there thus serves to regulate the pressure difference from the load pressure and the pump pressure as precisely as possible to the predetermined pressure difference, as a result of which the control circuit must constantly readjust the positions of the control valves.
  • a control valve is notified on the one hand of the pressure at the pump and on the other hand of the highest load pressure. If the pump can no longer deliver the volume flow required by the control valves and the associated consumers, the pressure difference between the pressure of the pump and the highest load pressure is reduced. The control valve consequently reduces the supply to the control pressure transmitter, by means of which the valves assigned to the consumers are actuated. This limits the flow of the valves. However, this limitation only becomes effective if there is already an excessive demand. If this limitation comes into effect, the consumers can no longer be controlled by means of their control valves.
  • the object of the invention is to design the hydraulic system so that it is not susceptible to vibration and that any weighting and adaptation of the individual consumer flows to the operating parameters of the pump is also possible.
  • the solution results from the characterizing part of claim 1.
  • the solution has the advantage that it does not affect the response range of the setpoint generator. Therefore, the individual consumers remain controllable even when the consumption is high, while in the known system the speed of the individual consumers can no longer be controlled if the maximum predetermined pump current is exceeded.
  • the control signals of the valves are reduced.
  • the reduction of consumer currents can take place proportionally. However, a reduction according to priorities is also possible if, for. B. an individual consumer should not reduce his speed in contrast to the others.
  • control circuit which is the subject of this invention, intervenes only in exceptional cases, namely when the pumpable pump flow is not sufficient for the consumer flows set on the respective valves, which add up to the current production volume. In this case, the current flow rate is reduced by reducing the respective consumer flows supplied.
  • valves which are assigned to the consumers. Basically, it can be assumed that these valves are adjusted electromagnetically or hydraulically from the outside, that is, by hand or by external input parameters. According to this invention, however, an adjustment signal for reducing the actuation of the valve piston by multiplication is superimposed on these input signals (setpoint signals) when it is determined in the hydraulic system by measuring the pressure difference that the pumpable pump current has been exceeded.
  • the maximum pump current does not necessarily correspond to the maximum pump current that can be pumped. Rather, a lower limit, e.g. B. 80% of the maximum conveyable pump flow. This ensures that the hydraulic system does not fall out of its control range due to an absolute overload of the pump. The same applies to the specified minimum pressure difference.
  • the adaptation of the consumer flows to the specified pump flow that can be conveyed when the minimum limit value of the pressure difference is exceeded is basically achieved by reducing the sum of the consumer flows to the specified limit value. In the simplest case, this can be done by reducing all consumer flows by the same percentage. However, it is also possible to weight the control signals, by means of which the consumer currents are reduced, differently for each consumer. This allows individual consumers to be given priority over other consumers. It can e.g. B. ensure that such consumers for security reasons always have to be loaded with a certain consumer current, e.g. B. hydraulic brakes have priority over other consumers. This will be discussed later.
  • the particular importance of the invention according to claim 1 is that the adaptation of the consumer currents to a predetermined limit value (maximum pump current) by monitoring the minimum pressure difference to be observed only functions when the predetermined limit value is reached. So several control loops are superimposed.
  • An internal control circuit uses the pressure difference Delta P between the pump pressure and the highest load pressure as a measured variable, the specified minimum pressure difference as a control variable and the control position of the control pump as a control variable.
  • the superimposed outer control loop uses the currently measured pressure difference minus the minimum pressure difference in order to reduce the consumer flows and increase the pressure difference again in the event of a deficiency (consumption exceeds the maximum pump current) and the resulting drop below the limit value of the pressure difference (minimum pressure difference).
  • This has the advantage that a desired weighting of the delivery rate, the delivery torque and the delivery pressure of the control pump can be predetermined when the valve position is adapted to the maximum pump flow.
  • the delivery capacity or the torque of the pump which is currently determined from the respective control position of the pump and the delivery pressure of the pump by multiplication, is compared with a target torque, and the output signal obtained from the difference is compared selectable function is superimposed, for example in such a way that the position and adjustability of the valves assigned to the individual consumers is influenced only when a predetermined drive torque is exceeded, but not below this limit value.
  • the position and adjustability of the valves assigned to the individual consumers can be influenced when a certain pressure is exceeded by superimposing the delivery pressure after a certain function, but not below this pressure or only with a certain percentage.
  • the maximum external load is also taken into account when influencing the valves assigned to the consumers, in particular directional valves.
  • the influencing of the pump current supplied to each consumer and the total of the consumers takes place, for. B. electrically or hydraulically in that the entered setpoints of the valves assigned to the individual consumers are influenced as a function of the pressure difference between the highest consumer pressure and the pump pressure of the control pump.
  • a setpoint processing is expedient.
  • the setpoints are the manually or automatically specified control signals for the valves assigned to the consumers. These externally entered setpoints can be fed to the system via attenuators (ramps). This specifies the rates of change at which the consumer currents can change if the setpoints entered change suddenly. It is thereby achieved that the adjustment speed of the pump or pressure differential balance is sufficient in any case to follow the change in the consumer flows over time. There can therefore be no shortage of consumers for a short time. Furthermore, the consumer flows requested by the entered target values can be roughly adapted to the maximum flow rate that can be supplied by the pump.
  • those entered from outside Setpoints are brought into dependence on the sum of the entered setpoints and, in addition, on the specified pump flow that can be pumped or the minimum pressure difference.
  • this leads to a weighting of the individual consumers and ensures that B. for safety reasons - important consumers always have an adequate oil flow.
  • the setpoints are reduced in advance if the specified pump flow that can be conveyed is expected to be exceeded on the basis of the input setpoint signals.
  • control pump 1 can be adjusted hydraulically by means of a control valve 2.
  • the control valve 2 is controlled by a magnet via an amplifier 3 and has a feedback 4 to the control position of the control pump 1.
  • the individual consumers 5 ', 5 ⁇ , 5 ′′′ are controlled by directional valves 6', 6 ⁇ , 6 ′′′, which are actuated by electromagnets a1-a3, b1-b3.
  • Each directional control valve 6 ', 6 ⁇ , 6 ′′′ is preceded by a pressure control valve 7', 7 ⁇ , 7 ′′′.
  • Each of the pressure control valves 7 ', 7 ⁇ , 7 ′′′ is acted on the one hand with the pressure in front of the directional control valve 6', 6 ⁇ , 6 ′′′ and on the other hand with the consumer pressure behind the directional control valve 6 ', 6 ⁇ , 6 ′′′.
  • each Pressure control valves 7 ', 7 ⁇ , 7 ′′′ resulting pump pressure and the highest consumer pressure detected via a shuttle valve chain 8 is given to a differential encoder 9 together.
  • Its output signal represents the pressure drop Delta P between the pump 1 and the highest consumer pressure.
  • This pressure difference is given, together with its differentiation (differentiating element 12), on the one hand, to a delta-p controller 10, which controls the control valve 2 via the amplifier 3 already mentioned.
  • the two signals are given via a weighting block 13 to comparison blocks 14 ', 14 ⁇ , 14 ′′′, which are each assigned to the individual actuators 16', 16 ⁇ , 16 ′′′ of the directional control valves 6 ', 6 ⁇ , 6 ′′′.
  • the comparison blocks 14 ', 14 ⁇ , 14 ′′′ have a second input, to which a desired setpoint from setpoint generator 15', 15 ⁇ , 15 ′′′ can be specified.
  • the comparison blocks 14 ', 14 ⁇ , 14 ′′′ influence the actuators 16', 16 ⁇ , 16 ′′′ in such a way that the adjustment of the valves 6 ', 6 ⁇ , 6 ′′′ is adapted and reduced such that the maximum Pump 1 flow rate cannot be exceeded.
  • torque can also be superimposed, in that the pump pressure and, on the other hand, the already mentioned pressure drop are recorded in a multiplier 17 and the output signal of this multiplier 17 is fed to the weighting module 13 via a comparator 18.
  • FIG. 2 is a functional diagram in which the control unit 21 is shown with the functional modules contained therein.
  • the pressure difference delta P is input to a module 23 in the control unit 21.
  • a limit value Delta P min is specified for module 23. This limit value can be specified constantly if only the input of the pressure difference is connected to the control unit 21. If the pump pressure P is also connected, further processing of the value Delta P follows, which will be discussed later.
  • the measured or further processed pressure difference and the limit value Delta Pmin are weighted.
  • the output signal of the block 23 is given to the weighting block 13.
  • the pressure difference signal Delta P continues to be applied to the Delta P controller 10.
  • the setpoint value of the pressure difference is also given to the delta-P controller 10.
  • the output signal of the delta-P controller 10 leads via amplifier 3 to the control valve 2 shown in FIG. 1, by means of which the control position of the pump 1 is adjusted.
  • the solenoid of the control valve 2 is acted upon by the output current of the amplifier 3. This results in an adjustment of the control valve 2 in the sense that the two sides of the control piston are equally loaded and the control pump 1 is adjusted in the sense of a reduction in the flow rate (pump flow, pump flow) (adjustment piston moves to the left).
  • the output signal of the delta-P controller 10 is applied to the multiplication module 17 at the same time as the pump pressure P tapped via the pressure converter 11.
  • the output signal of the multiplication module 17 represents the current torque M of the pump 1, since the input signal to the amplifier 3 represents the current delivery quantity of the pump 1.
  • This output signal is related in block 18 (comparator) to a maximum possible limit value of the torque.
  • the output signal of the comparator 18 is given to the weighting module 13.
  • the output signal from 1 is reduced according to a time-dependent, continuous function until the torque M of the pump 1 has decreased so far that the equilibrium is established by feedback of the setpoints (which will be discussed later).
  • the output signal of the function block 26 is a multiplication block 24 together with the pressure difference Delta P abandoned.
  • the pressure difference and the output signal, which has been obtained from the torque comparison, are multiplied in the multiplication module 24.
  • the output signal of this multiplication module 24 represents the measured but further processed pressure difference and is given to the weighting module 23 already mentioned and described.
  • the output signal of the function block 26 is thus used to process the pressure difference in the multiplication block 24, as has already been indicated.
  • the weighting module 23 is supplied with a constantly reduced delta P signal. Therefore, the output signal of the weighting module 23 will also decrease continuously and, in the function module 25, the output signal A will be reduced if the overload P P / Delta P min continues.
  • a permanently entered limit value of the pump pressure P max is related to the currently measured pump pressure P.
  • the module 13 also contains a function module 29 which is controlled by the output signal of the comparator 28 and additionally by a limit value which represents the maximum target value S max .
  • These entered variables are processed in the function block 29 in such a way that the function block 29 gives an output signal B which is equal to one as long as the measured pump pressure P is less than the limit value P max of the pressure and which is equal to the limit value S max of the desired values when the measured pump pressure P exceeds the limit value P max of the pump pressure.
  • the weighting block 13 with its two output signals A of the function block 25 and B of the function block 29 then controls comparison elements 14 ', 14 ⁇ , 14 ′′′, each one of the valves 6', 6 ⁇ , 6 ′′′ for the individual Consumers 5 ', 5 ⁇ , 5 ′′′ are assigned.
  • Each of these comparison elements 14 is given a different setpoint S1, S2, S3 via the setpoint generator 15 ', 15 ⁇ , 15 15.
  • these output signals A and B are superimposed on the entered target values.
  • the outputs then go via the actuators 16 ', 16 ⁇ , 16 ′′′ to the respective magnets a1, b1; a2, b2; a3, b3 of the respective valves 6 ', 6 ⁇ , 6 ′′′.
  • the volume flow supplied to the individual consumer 5 ', 5 ⁇ , 5 ′′′ can be reduced to such an extent that the total amount that can be pumped by the pump 1 is not exceeded.
  • the comparison elements 14 - as shown in FIG. 2 - are divided into a multiplication module 31 ', 31 ⁇ , 31 ′′′ and a limitation module 32', 32 ⁇ , 32 ′′′.
  • the output signal A of the function block 25 and the setpoint value S1, S2, S3 are given to the multiplication block.
  • the setpoints S1, S2, S3 are reduced accordingly.
  • the output signal of the multiplication module 31 is given to the limiting module 32 together with the output signal B of the function module 29, which establishes the relationship to the measured pump pressure P.
  • the output signal of the limiting module becomes 32 limited to the entered limit value Smax of the setpoint.
  • a further evaluation of the limit value Smax can be carried out in the sense that either there is no limit at all or the limit value S max is reduced or increased.
  • individual consumers 5 ', 5 ⁇ , 5 ′′′ priorities can be granted.
  • Other consumers can be shut down or treated subordinately if the setpoint specifications S1, S2, S3 would lead to the limit value of the pump current being exceeded.
  • a setpoint generator 33 can be arranged upstream of the control unit 21.
  • the setpoint generator 33 has a first component 34 for each input setpoint S1, S2, S3, which is referred to below as ramp 34.
  • This ramp means that an abruptly entered setpoint only changes over time. This has the effect that the signal processing and adaptation of the hydraulic system can follow in time even when the setpoint input is erratic and there is no temporary undersupply of the consumers 5 ', 5 ⁇ , 5 ′′′.
  • the output signals of the ramps 34 are then multiplied in multiplication modules 35 by input limit values G1 to G3. These limit values represent a certain percentage of the limit value of the pump delivery flow.
  • the signal e2 is given to a function block 37 together with a signal e1.
  • the signal e1 represents the maximum predetermined pump delivery flow in a form that is comparable to the signal e2.
  • the output signal A is equal to 1 as long as the predetermined limit value of the pump delivery flow e1 is greater than the set and weighted sum e2 of the setpoints S1, S2, S3.
  • the output signal A is equal to the quotient of the limit value el and the weighted sum e2 if the weighted sum e2 is greater than the limit value e1.
  • the output signal A of the function block 37 is now given to the multiplication blocks 38 ', 38 ⁇ , 38 ′′′.
  • the respective setpoint S1, S2, S3 is multiplied after it has preferably first been passed over the ramps 34 ′, 34 ⁇ , 34 ′′′.
  • the output signal of the multiplication modules 38 represents the respective setpoint given to the comparison module 14.
  • This setpoint processing ensures that the setpoint values S1, S2, S3 do not lead to a consumption which does not contribute to the predetermined limit value of the pump delivery flow e1 far exceeds. However, this is only a rough precaution.
  • the inventive superimposition of the adaptation of the consumer flows to the measured pump flow ensures that each consumer 5 ', 5 ⁇ , 5 ′′′ remains functional in the frame assigned to it.
  • the particular importance of the invention lies in the fact that on the one hand the pump torque M is corrected, but that a torque control can be superimposed on this torque control by simultaneously also detecting the speed of the pump 1 or its delivery rate.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP92900271A 1990-12-15 1991-12-13 Hydrauliksystem Expired - Lifetime EP0515608B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4040176 1990-12-15
DE4040176 1990-12-15
DE4124793 1991-07-26
DE4124793 1991-07-26
PCT/DE1991/000967 WO1992010684A1 (de) 1990-12-15 1991-12-13 Hydrauliksystem

Publications (2)

Publication Number Publication Date
EP0515608A1 EP0515608A1 (de) 1992-12-02
EP0515608B1 true EP0515608B1 (de) 1995-03-29

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Family Applications (1)

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EP92900271A Expired - Lifetime EP0515608B1 (de) 1990-12-15 1991-12-13 Hydrauliksystem

Country Status (6)

Country Link
US (1) US5297381A (ja)
EP (1) EP0515608B1 (ja)
JP (1) JPH05504819A (ja)
DE (1) DE59105057D1 (ja)
DK (1) DK0515608T3 (ja)
WO (1) WO1992010684A1 (ja)

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* Cited by examiner, † Cited by third party
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DE4219787C1 (de) * 1992-06-17 1994-01-05 Jungheinrich Ag Fahrzeug mit batterie-elektrischem Fahr-Antrieb, insbesondere Hublader
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DK0515608T3 (da) 1995-06-12
EP0515608A1 (de) 1992-12-02
WO1992010684A1 (de) 1992-06-25
JPH05504819A (ja) 1993-07-22
DE59105057D1 (de) 1995-05-04
US5297381A (en) 1994-03-29

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