EP4540529A1 - Alimentation en flux volumique - Google Patents

Alimentation en flux volumique

Info

Publication number
EP4540529A1
EP4540529A1 EP23723834.0A EP23723834A EP4540529A1 EP 4540529 A1 EP4540529 A1 EP 4540529A1 EP 23723834 A EP23723834 A EP 23723834A EP 4540529 A1 EP4540529 A1 EP 4540529A1
Authority
EP
European Patent Office
Prior art keywords
pressure
volume flow
control
supply
variable
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.)
Pending
Application number
EP23723834.0A
Other languages
German (de)
English (en)
Inventor
Peter Bruck
Tobias DOHMEN
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP4540529A1 publication Critical patent/EP4540529A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—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
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/275—Control of the prime mover, e.g. hydraulic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • 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
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6656—Closed loop control, i.e. control using feedback
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the invention relates to a volume flow supply, in particular for closed center LS systems, with a pressure supply device and a pressure compensator as components of a supply system for supplying fluid to a hydraulic consumer that can be connected thereto.
  • a valve arrangement is known for pressure control of a pressure medium from a pressure medium pump to at least a first consumer, with a pilot-controlled pressure control valve, with a main piston acted upon by the pressure medium and a pilot control piston, with a pressure chamber between a piston back of the main piston and the Pilot piston can be relieved, with a relief valve being fluidly connected to the pressure chamber, which opens at a pressure medium pressure at the load tap LS, which represents an inoperative position of the consumer and returns pressure medium at low pressure into a pressure medium container or to the pressure medium pump and the relief valve closes , if the pressure medium pressure at the load tap LS represents the consumer being put into operation.
  • valve arrangement for regulating the pressure of a pressure medium is created, which further minimizes the pressure loss if no Consumer is switched, enables. In this way, a significant reduction in the pressure losses of the valve arrangement is achieved compared to known circuits with circulating pressure compensators.
  • a control device in particular for the hydraulic control of components of mobile work machines, consisting of at least one pressure supply and one tank or return connection as well as two useful connections and control and / or regulating valves connected between the individual connections and with two control lines which can control at least one of the control and/or regulating valves, with a modular function block being connected to at least one of the control lines.
  • a suitable design of the modular functional block a large number of other designs of the control devices can be conceptually revised and in this way the functional reliability can also be regularly increased.
  • the pressure supply device for supplying the hydraulic consumer provides demand-oriented volume flow
  • the pressure compensator is formed from a circulating pressure compensator, which removes any excess volume flow from the supply flow and with a control that by controlling the pressure supply device
  • Excess volume flow is reduced to a minimum, creating a structurally simple, cost-effective, robust and demand-oriented volume flow supply for hydraulic systems, such as closed-center ES systems.
  • Such a demand-oriented volume flow supply promotes in the case of On the one hand, oversupply affects system stability; on the other hand, the associated excess volume flow causes hydraulic losses, which must be avoided.
  • the pressure compensator or circulating pressure compensator used in each case can be integrated into a main control block with the aperture or measuring orifice preferably used in each case.
  • the pressure supply device has a variable-speed hydraulic pump which is driven by a variable-speed motor which is controlled by the control system.
  • the losses resulting from the excess volume flow can be reduced to the minimum required for system stability through demand-oriented control.
  • the control has a controller with a predeterminable reference variable, preferably in the form of a PID controller, the controlled variable of which is formed by output values of a sensor, which is designed as a pressure sensor and detects pressure values on the outlet side of the circulating pressure compensator and/or designed as a position sensor, the travel position of the valve slide of the circulating pressure compensator is recorded.
  • a measuring orifice is arranged downstream of the circulating pressure compensator, through which the fluid flows to the tank or return connection and thus to a storage tank.
  • the pressure difference across the measuring orifice can be recorded with a pressure sensor, with the signal from the pressure sensor serving as a controlled variable or actual value for the closed control loop.
  • the speed is controlled by the regulation
  • the hydraulic pump is then regulated in such a way that, ideally, the controlled variable corresponds to the reference variable or the target value.
  • a constant Ap is regulated via the measuring orifice, so that a continuous excess volume flow flows via the circulating pressure compensator within the control range (n ⁇ n max) of the hydraulic pump.
  • the system is therefore in oversupply and works at a stable operating point.
  • the losses resulting from the excess volume flow can be reduced to the minimum required for system stability by the demand-oriented control system.
  • the supply system designed for this purpose only requires a single pressure sensor and the pressure recorded in front of the measuring orifice is independent of the load or the load pressure/pump pressure.
  • Another advantage is the comparatively low pressure level of the measuring orifice, compared to the load-dependent pressures, so that the pressure range to be detected by the sensor is smaller and the resolution of the pressure range is therefore higher. Since the sensor accuracy can be reduced, this results in a cost advantage.
  • the measuring orifice has a damping effect and the measured variable is independent of the load on the hydraulic consumer. This has a positive effect on the signal quality of the sensor and improves the control quality. If necessary, the smoothing of the signal can be dispensed with, which in turn improves the response.
  • the circulation pressure compensator can be made smaller because only a small excess volume flow has to be dissipated in regular operation.
  • the circulating pressure compensator It is also possible to alternatively or additionally equip the circulating pressure compensator with a measuring system with which the slide position of the circulating pressure compensator is recorded.
  • the signal from the slider position serves as a controlled variable (actual value) for the closed control loop.
  • the control then regulates the speed of the hydraulic pump in such a way that, ideally, the controlled variable in turn corresponds to the reference variable (setpoint value).
  • a constant slide position is regulated, which corresponds to a desired excess volume flow via the circulating pressure compensator at a nominal pressure to be defined.
  • the system is therefore in oversupply and works at a stable operating point.
  • the other advantages as shown for the pressure sensor solution also arise here.
  • a constant slide position is regulated that corresponds to the desired pressure difference Apis.
  • the slide position corresponds to the opening point of the circulating pressure compensator. This makes it possible to detect early on when the circulating pressure compensator “goes into control”.
  • the excess volume flow is load-dependent at a constant slide position and is therefore greater at higher load pressures than at lower ones.
  • Possibilities to reduce or avoid this effect include providing a large fine control range for the circulating pressure compensator or additionally or alternatively using the pressure sensor solution for further compensation within the control system.
  • bypass line connected in parallel to the measuring orifice mentioned, which particularly preferably has at least one spring-loaded check valve which opens in the direction of a tank or return line.
  • the pressure difference across the measuring orifice can be limited, particularly in the case of high excess volume flows, for example in standby mode.
  • standby operation occurs when no consumer is activated and the hydraulic pump delivers a volume flow Qmin due to a minimum speed.
  • the opening pressure of the check valve in the bypass must be above the reference value. In standby mode, this is with the circulating pressure and contributes to energy-efficient operation of the pressure supply device.
  • limiting the pressure protects the pressure sensor against overload pressure.
  • At least one further measuring orifice is connected parallel to the one measuring orifice and preferably in front of the check valve when viewed in the flow direction, the free cross section of the further measuring orifice preferably being larger than that of the one orifice.
  • the opening pressure of the bypass check valve for one measuring orifice and the other measuring orifice is then above the bypass check valve for one measuring orifice.
  • the aforementioned fine control range expands the detection range of the sensors used.
  • further system interventions are conceivable, e.g. that a valve or several valves are switched via the measuring orifices above a certain pressure (electrically or hydraulic-mechanically).
  • the invention also relates to a method for carrying out a demand-oriented volume flow supply, in particular for closed center LS systems, using the supply device shown above.
  • a demand-oriented volume flow supply in particular for closed center LS systems, using the supply device shown above.
  • Figure 1 shows an embodiment of a volumetric flow supply
  • Figure 1 shows a volumetric flow supply in the form of a hydraulic circuit diagram, in particular for so-called closed-center LS systems, one of which is designated as a whole by 10 in Figure 1.
  • a system 10 is also referred to as LS-MCV (Main Control Valve).
  • the volume flow supply has a pressure supply device designated as a whole by 12 and a so-called circulating pressure compensator 14 as a pressure compensator.
  • the pressure supply device 12 and the pressure compensator 14 are components of a supply system, designated as a whole by 16, for supplying fluid to a hydraulic consumer that can be connected to it, designated as a whole by 18.
  • the hydraulic consumer 18 has two hydraulic motors 20 with two possible current directions.
  • the respective hydraulic motor 20 is obviously controlled via an electrically actuated 4/3 proportional directional control valve 22.
  • the shuttle valve 24 shown between the assignable hydraulic motor 20 and the proportional valve 22 the higher pressure in the supply to the hydraulic motor 20 is reported into an LS (load sensing) line 26 and there is a 2/2-way valve in this line 28 connected to its control line 29.
  • the respective valve 28 In the open switching position shown, the respective valve 28 has a pressure-limiting function 74 and to this extent the respective valve 28 provides a fluid-carrying connection between a pressure supply line P and an inlet of the respective one Valve 22.
  • the other input of the valve 22 is connected to the tank or return line T, which leads to a storage tank 30, which can also consist of several tank components.
  • the opposite outputs of the respective proportional valve 22 are directed to the control sides of the associated hydraulic motor 20.
  • a check valve 36 is connected in the direction of a central load sensing (LS) line 34, which opens in the direction of the central LS line 34 and in the opposite direction Direction is held in its closed position.
  • LS central load sensing
  • the pressure supply device 12 for supplying the hydraulic consumer 18 provides it with a demand-oriented volume flow in that the circulation pressure compensator 14 removes any excess volume flow from the supply flow, which is made available by the pressure supply device 12 in the pressure supply line P. Furthermore, there is a control system designated as a whole by 28, which helps to reduce the excess volume flow to a minimum by controlling the pressure supply device 12 mentioned.
  • the controller 42 is connected to a motor control 48, for example in the form of a frequency converter, which specifies the required speed for the electric motor M as a manipulated variable and thus sets the hydraulic pump 40 with its respective delivery quantity in a speed-controlled manner, which it collects from the storage tank 30 and feeds it into the pressure supply line P.
  • a motor control 48 for example in the form of a frequency converter, which specifies the required speed for the electric motor M as a manipulated variable and thus sets the hydraulic pump 40 with its respective delivery quantity in a speed-controlled manner, which it collects from the storage tank 30 and feeds it into the pressure supply line P.
  • the control variable 46 mentioned is formed by output values from a pressure sensor 50.
  • This pressure sensor 50 detects pressure values on the outlet side 52 of the circulating pressure compensator 14, for which purpose the pressure sensor 50 is connected to a branch point 54, which leads to the storage tank 30 via a further tank or return line 56.
  • the circulation pressure compensator 14 is connected on the input side to the pressure supply line P via a further branch point 58, which is arranged directly at the outlet of the hydraulic pump 40.
  • the circulation pressure compensator 14 is designed in a slide design as a directly controlled, spring-loaded throttle valve, the valve slide 60 of which on one side together with an energy storage, such as a compression spring 62, an LS pressure from the consumer 18 and on the other side a control pressure via a control line 64 is exposed, which corresponds to the output or supply pressure of the pressure supply device 12, i.e. the respective output pressure of the hydraulic pump 40.
  • the addressed LS pressure is transferred via an LS control line 66 from the central LS line 34 to one control side of the circulating pressure carriage 14 forwarded.
  • Such circulation pressure compensators 14 in a slide design can be directly controlled as shown and with an integrated pressure relief function, for example designed as a screw-in valve, and can be obtained from the owner of the property rights, for example under the order number DWM12121 ZD.
  • the relevant pressure compensators 14 are infinitely variable and closed in the normal position as shown in Figure 1.
  • the task of such a pressure compensator 14 is to keep a set volume flow constant, regardless of pressure fluctuations.
  • As a control valve in combination With the compression spring 62 it keeps the pressure drop across the integrated measuring throttle and thus the connection to the consumer 18 at the same level as required. With the same measuring throttle area, the volume flow remains the same.
  • the pressure compensator 14 also opens to the storage tank 30 via the internal measuring throttle. In this way, such a circulating pressure compensator 14 can be used, for example when lifting variable loads or for Drive a hydraulic motor 20 with the same speed.
  • a pilot-controlled pressure compensator can alternatively be used when implementing the circuit solution according to FIG. 1, which will be explained in more detail below.
  • a measuring aperture 68 On the drain side 52 of the circulating scale 14 shown, there is a measuring aperture 68, which is connected in the direction of the storage tank 30 behind the branch point 54 into the tank or return line 56.
  • a spring-loaded check valve 72 is connected parallel to the measuring orifice 68 in a branch line 70 and opens in the direction of the storage tank 30.
  • a further measuring orifice 74 with a larger cross-section than the first measuring orifice 68 is connected in the branch line 70 parallel to the first measuring orifice 68 and in front of the check valve 72 in the flow direction.
  • the further measuring orifice 74 can also be arranged behind the check valve 72.
  • a resulting excess volume flow is removed from the system 10 via the circulating pressure compensator 14 in such a way that the circulating pressure compensator 14 is followed by a measuring orifice 68, via which the Fluid flows to the storage tank 30.
  • the pressure difference across this measuring orifice 68 is detected with the pressure sensor 50 and the signal from this pressure sensor 50 serves as a controlled variable (actual value) 46 for the closed control loop as the control 38.
  • This control 38 regulates the speed of the hydraulic pump 40 in such a way that that ideally the controlled variable 46 as the actual value corresponds to the reference variable 44 as the target value. Accordingly, with the control presented here according to FIG.
  • a constant Ap is regulated via the one measuring orifice 68, so that within the control range, in which the current speed is in any case smaller than the maximum speed of the hydraulic pump 40, a continuous excess volume flow over the Circulating pressure compensator 14 flows.
  • the supply system is therefore in oversupply and operates at a stable operating point, whereby at the same time the excess volume flow required for system stability is reduced to a required minimum, so that hydraulic losses within the supply are avoided. In this way, a compromise is created between system stability and loss avoidance.
  • the second measuring aperture 74 By using the second measuring aperture 74, the free cross section of which is preferably larger than that of the first measuring aperture 68, a fine control range can be realized and the detection range of the sensor system can be expanded by means of the pressure sensor 50.
  • volume flow can be provided as required, so that the excess volume flow via the circulation pressure compensator 14, and the associated losses, are reduced to a required minimum. Accordingly, an excess volume flow is discharged from the system via the circulating pressure compensator 14 in such a way that at least one measuring orifice 68 is arranged downstream of the circulating pressure compensator 14, via which the fluid flows to the tank 30.
  • the signal from the pressure sensor 50 serves as a controlled variable (actual value) for a closed control loop.
  • the control regulates the speed of the unit in such a way that, ideally, the controlled variable corresponds to the reference variable (setpoint value).
  • a constant Ap is regulated via the measuring orifice 68, which must not be equated with APLS, so that within the control range (n ⁇ n max, unit) a continuous excess volume flow flows via the circulating pressure compensator 14.
  • the system is therefore in oversupply and works at a stable operating point.
  • the system only requires one pressure sensor 50, whereas so-called eLS systems generally require at least two load-dependent sensor values, once in the form of a pump pressure and once in the form of an LS pressure. Furthermore, the detected pressure in front of the measuring orifice 68 is independent of the load or the load pressure/pump pressure. Another advantage is the comparatively low pressure level of the measuring orifice 68 (probably less than 10 bar, depending on the orifice design), compared to the load-dependent pressures with pressure ranges up to 250/350 bar, so that the pressure range of the sensor is smaller and thus the resolution of the pressure range is higher. Accordingly, the sensor accuracy can be reduced, which brings with it a cost advantage.
  • the respective measuring aperture 68 has a damping effect and the measured variable is independent of the load.
  • the circulation pressure compensator 14 can be dimensioned smaller, since only a small excess volume flow has to be dissipated in regular operation.
  • a bypass valve I/return valve I 72 with an upstream further measuring orifice 74 is arranged parallel to the measuring orifice 68 in order to ensure that there is a high excess volume flow, e.g. B. to limit the pressure difference via the measuring orifice 68 in standby mode.
  • standby mode no consumer is activated and the unit delivers a volume flow Qmin, unit due to a minimum speed.
  • the opening pressure of the check valve 72 in the bypass must be above the reference value.
  • the circulating pressure is limited and contributes to energy-efficient operation of the unit.
  • limiting the pressure protects the sensor 50 against overload pressure.
  • Figures 2 and 3 show the volume flow V over the pressure p at the measuring orifice 68 as a controlled variable for the solution according to Figure 1 in diagram form.
  • the opening pressure “bypass of the measuring orifice 68 via check valve 72” is represented by a.
  • the fine control range is marked with b and the excess volume flow is marked with c.
  • the kink point KS 1 after leaving the fine control range b is characteristic.
  • FIG. 3 there is a further second bend point KS 2 in the event that, as shown in the solution according to FIG. 1, a bypass with a further measuring orifice 74 is present next to the first measuring orifice 68.
  • a fine control range b as in Figure 1 is achieved and the further measuring orifice 74 is only flowed through when the opening pressure of the bypass check valve 72 is exceeded.
  • the fine control range b is only achieved by arranging a further aperture or measuring orifice 74, which is preferably larger than the first measuring orifice 68, in front of or behind the bypass valve or check valve 72 of the measuring orifice 68.
  • the measuring orifice 74 is only flowed through when the opening pressure of the bypass valve or check valve 72 is exceeded and, as already explained in Figure 3, this point can be recognized by the kink KS 2 in the volume flow-pressure diagram. Once the kink point KS 2 has been reached, the pressure p above the measuring orifice 68 does not increase any further; only the volume flow V continues to increase. In any case, the detection range of the sensor system, in particular using a pressure sensor 50, is expanded by the fine control range b mentioned.
  • valves or several valves are switched via the measuring orifices 68, 74 above a certain predeterminable pressure, be it electrically or hydraulically-mechanically.
  • the circulating pressure compensator 14 now has a position measuring system, in particular in the form of a displacement sensor 76, with which the position of the valve slide 60 in each control position of the circulating pressure compensator 14 is detected.
  • the signal of the slide position now serves as a controlled variable 46 and represents the respective actual value for the closed control loop in the form of the control 38.
  • This type of control 38 regulates the speed of the hydraulic pump 40 in such a way that, ideally, the controlled variable 46 as the actual value in turn corresponds to the reference variable 44 as the setpoint. Accordingly, a constant slide position is regulated with the control 38 presented here according to FIG of loss volume.
  • the excess volume flow is load-dependent at a constant slide position and accordingly the excess volume flow is greater at higher load pressures than at lower ones.
  • Possibilities for reducing or completely avoiding this effect include providing a large fine control range for the circulating pressure compensator 14 or additionally using the pressure sensor 50 for compensation within the control system 38.
  • the valve slide 60 preferably has a positive overlap within the circulating pressure compensator 14 with an adjusted spring preload/spring stiffness of the compression spring 62.
  • the additional measuring orifices 68 and 74 shown in FIG. 1 as well as the check valve 72 in a bypass line have been omitted and the further tank or return line 56 as a branch opens directly into the storage tank 30 for fluid on the output side.
  • a pressure relief valve 80 is additionally arranged such that the volume flow discharged via the pressure relief valve 80 flows to the tank 30 via the downstream measuring orifice 68 or measuring orifices 68, 74.
  • the pressure relief valve 80 opens mechanically when the set pressure value is exceeded;
  • an electrical solution can also be implemented.
  • a demand-oriented volume flow supply with additional pressure cut-off is possible, without an additional pressure sensor or pressure switch to record the pump Z system pressure, use it in the system or superimpose an additional pressure regulator for pressure cut-off on the demand-oriented control.
  • the function of a pressure cut-off is as follows: The delivery volume flow of the respective unit is limited or reduced when a set pressure, equal to the setting value of the pressure relief valve 80, is reached in order to avoid increased power loss in the system.
  • the pressure relief valve 80 is connected in parallel to the pressure compensator 14 and is fluidly connected to the pressure supply line of the hydraulic pump 40 as well as to the two measuring orifices 68 and 74. Furthermore, in the bypass to the second measuring orifice 74 with a check valve 72, an additional check valve 82 is present, which leads to the tank 30 opens. With the circuit diagram solution according to FIG. 5, a volume flow-pressure diagram as shown in FIG. 3 can be achieved.
  • the additional measuring orifice 74 with check valve 72 can be dispensed with to the extent of the volume flows and pressures to be controlled.
  • a target speed is passed on as an input variable to the motor control 48, which is formed, for example, from a conventional frequency converter.
  • the engine control 48 specifies the respective speed for the engine M as a manipulated variable and this time a variable pump with hydraulic-mechanical control is used as the hydraulic pump 40, which is controlled by a pressure difference across the measuring orifice 68, which is returned hydraulically to the variable pump.
  • the relevant pressure difference is picked up in front of the measuring orifice 68 and the check valve 82.
  • the further measuring aperture 74 with the check valve 72 is not necessary with this solution. Otherwise, the advantageous configurations as described above can be achieved with the solution according to the circuit diagram representation according to FIG.
  • the pressure sensor 50 or other sensor technology can be omitted.
  • a variable-speed unit with speed control is used.
  • the speed control of the unit takes place parallel to the control of the hydraulic pump 40 in the form of a variable displacement pump.
  • the speed control uses the manipulated variable of the variable pump control, which is proportional to the adjustment angle, as the controlled variable (actual value) for a closed control loop.
  • the control regulates the speed of the unit in such a way that, ideally, the controlled variable corresponds to a reference variable (setpoint value).
  • the prerequisite is a variable pump with electrical adjustment, which works in particular electrically-proportionally.
  • the controller 42 ' is preferably a PID controller that receives a reference variable on the input side and a controlled variable that comes from the pressure sensor 50 on the output side. To control the variable displacement pump, the controller 42' then outputs, for example, a current as a manipulated variable, which is proportional to the adjustment angle of the relevant hydraulic pump 40.
  • the manipulated variable of the controller 42' is supplied as a controlled variable to the controller 42 for the motor control 38.
  • a unit with a double pump is now used, with both pumps 40, 40 'feeding into the same system and at least one of the two pumps is connected via a return Impact valve 84 separated from the system.
  • a changeover valve 86 is additionally arranged in front of the check valve 84, which blocks in the direction of the changeover valve 86.
  • the pressure difference across the measuring orifice 68 or the measuring orifices 68, 74 is additionally fed back to the changeover valve 86 as a hydraulic signal.
  • the changeover valve 86 has a control characteristic as shown in more detail in FIG. 11.
  • the upper setting value e which can be specified mechanically or electrically, it connects one of the two pumps 40, 40 'to a further, third pressure level, which is below the system pressure; Ideally, this pressure level corresponds to the tank pressure in tank 30. Only when the pressure falls below a further pressure value than the lower setting value f does the changeover valve 86 switch back and cancel the connection towards the third pressure level (tank pressure). Accordingly, the changeover valve 86, as shown in FIG. 11, has a hysteresis g with respect to the opening and closing pressure.
  • the speed control of the drive M for both hydraulic pumps 40, 40 ' takes place in parallel.
  • the embodiment according to FIG. 10 can also be changed in such a way that the control 38 for the motor M is omitted and the drive or motor M is operated at a fixed target speed (not shown).
  • a controller 42' is used for this purpose, which receives the (pressure) condition switching on h as well as the further (pressure) condition switching off i as an input variable. Furthermore, a (speed) switch-off condition j can be specified as an input condition. Further input variables come from the output side of the pressure sensor 50 and the manipulated variable (speed) on the output side of the frequency converter 48 is passed on to the controller 42 'as a further input variable.
  • the changeover valve 86 according to FIG. 12 is an electrically actuated changeover valve (can also be implemented with normally open valves), with a volume flow-pressure diagram as shown in FIG. 11 being realized, with a hysteresis behavior g as shown.
  • the changeover valve 86 can be designed in very different ways and in the present case is formed from an electromagnetically actuated 2/2-way switching valve, which is connected to the tank 30 on the output side. What all variants have in common, however, is that when the pressure value falls below h, the switching valve 86 is in a position in which there is no connection to a pressure level below the system pressure (pressure of the further pump stage). If another pressure value i is exceeded, however, the switching valve 86 establishes a connection to another pressure level that is below the system pressure; ideally corresponds to the tank pressure. Furthermore, although this is not absolutely necessary, this process can also be coupled to another condition, for example to a speed condition j. The speed control for the drive M takes place in parallel or the unit M can be operated again at a constant speed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne une alimentation en flux volumique, en particulier pour des systèmes LS à centre fermé (10), comprenant un dispositif d'alimentation en pression (12) et un équilibre de pression en tant que composants d'un système d'alimentation pour fournir un fluide à une charge (18) qui peut être reliée hydrauliquement au système d'alimentation. L'invention est caractérisée en ce que le dispositif d'alimentation en pression (12) fournit un flux volumique lorsque cela est nécessaire pour alimenter la charge hydraulique (18) en ce que l'équilibre de pression est constitué d'un équilibre de pression de circulation (14) qui évacue un éventuel flux volumique excédentaire hors du flux d'alimentation. L'alimentation en flux volumique comprend également un dispositif de commande (38) qui réduit le flux volumique excédentaire à un minimum par actionnement du dispositif d'alimentation en pression (12).
EP23723834.0A 2022-06-17 2023-04-26 Alimentation en flux volumique Pending EP4540529A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022002192.7A DE102022002192A1 (de) 2022-06-17 2022-06-17 Volumenstromversorgung
PCT/EP2023/060998 WO2023241843A1 (fr) 2022-06-17 2023-04-26 Alimentation en flux volumique

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EP4540529A1 true EP4540529A1 (fr) 2025-04-23

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EP (1) EP4540529A1 (fr)
CN (1) CN223398985U (fr)
DE (1) DE102022002192A1 (fr)
WO (1) WO2023241843A1 (fr)

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DE102024001405A1 (de) * 2024-04-30 2025-10-30 Hydac Mobilhydraulik Gmbh Versorgungsvorrichtung
DE102024208787A1 (de) 2024-09-16 2026-03-19 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Steuerung eines hydraulischen Antriebssystems und hydraulisches Antriebssystem

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Publication number Priority date Publication date Assignee Title
US4523431A (en) * 1984-02-16 1985-06-18 Caterpillar Tractor Co. Load responsive system
DE102009034212A1 (de) 2009-07-22 2011-02-03 Linde Material Handling Gmbh Hydraulisches Antriebssystem
DE102009049548A1 (de) 2009-10-16 2011-04-21 Hydac Fluidtechnik Gmbh Ventilanordnung
DE102012110978B4 (de) 2012-11-15 2024-02-15 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Antriebssystem
DE102013017093A1 (de) 2013-10-15 2015-04-16 Hydac Filtertechnik Gmbh Steuervorrichtung
DE102020215437B3 (de) 2020-12-07 2022-05-19 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Betreiben einer drehzahlvariablen elektrohydraulischen Pumpe
EP4305248A1 (fr) * 2021-06-30 2024-01-17 Parker-Hannifin Corporation Unité de puissance électro-hydraulique à débit de sortie variable

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US20250369458A1 (en) 2025-12-04
CN223398985U (zh) 2025-09-30
WO2023241843A1 (fr) 2023-12-21

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