EP4211355A1 - Système d'entraînement alimenté par gaz et procédé de fonctionnement - Google Patents

Système d'entraînement alimenté par gaz et procédé de fonctionnement

Info

Publication number
EP4211355A1
EP4211355A1 EP21777205.2A EP21777205A EP4211355A1 EP 4211355 A1 EP4211355 A1 EP 4211355A1 EP 21777205 A EP21777205 A EP 21777205A EP 4211355 A1 EP4211355 A1 EP 4211355A1
Authority
EP
European Patent Office
Prior art keywords
chamber
pressure
control
control valve
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP21777205.2A
Other languages
German (de)
English (en)
Other versions
EP4211355B1 (fr
EP4211355C0 (fr
Inventor
Olivier Georg Reinertz
Katharina Schmitz
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.)
Rheinisch Westlische Technische Hochschuke RWTH
Original Assignee
Rheinisch Westlische Technische Hochschuke RWTH
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 Rheinisch Westlische Technische Hochschuke RWTH filed Critical Rheinisch Westlische Technische Hochschuke RWTH
Publication of EP4211355A1 publication Critical patent/EP4211355A1/fr
Application granted granted Critical
Publication of EP4211355B1 publication Critical patent/EP4211355B1/fr
Publication of EP4211355C0 publication Critical patent/EP4211355C0/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F15B11/02—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
    • F15B11/0413—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed in one direction only, with no control in the reverse direction, e.g. check valve in parallel with a throttle 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
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/064—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with devices for saving the compressible medium
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40592—Assemblies of multiple valves with multiple valves in parallel flow paths
    • 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
    • F15B2211/41509—Flow control characterised by the connections of the flow 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • 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
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • 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
    • F15B2211/51—Pressure control characterised by the positions of the valve element
    • F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/515—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
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member 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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of a differential pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/6653—Pressure 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting 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
    • F15B2211/75—Control of speed of the output member
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
    • F15B2211/8855—Compressible fluids, e.g. specific to pneumatics

Definitions

  • the invention relates to a gas-operated drive system, comprising a drive with a first chamber and a second chamber, which are separated from one another by a movable working element of the drive, in particular by a piston, one chamber of the two chambers forming a chamber driving the working element having a Gas source can be connected and the other chamber of the two chambers to form a chamber counteracting the movement of the working element can be connected at the same time via an exhaust air throttle with a gas sink, in particular by means of a switching valve.
  • the gas escaping through the exhaust air throttle also flows through a check valve opening in the direction of the gas sink.
  • This has the advantage that for a return stroke of the working element, the gas cannot/does not have to flow through the exhaust air throttle, but can be guided past the exhaust air throttle in parallel, possibly through other system components, in particular bypassing the exhaust air throttle.
  • the invention further relates to a method for operating a gas-operated drive system, comprising a drive with a first chamber and a second chamber, which are separated from one another by a movable working element of the drive, in particular by a piston, one chamber of the two chambers being used to form a das Chamber driving the working element is connected to a gas source and the other chamber of the two chambers to form a chamber counteracting the movement of the working element is simultaneously connected to a gas sink via an exhaust air throttle, in particular by means of a switching valve.
  • Drive systems and methods of this type are well known in the prior art.
  • DE 102009 001 150 A1 generally describes the throttling of pneumatic cylinders.
  • Typical drives of such a system are e.g.
  • pressurized gas is introduced into one of the chambers from a pressure source providing gas at a pressure greater than ambient atmospheric pressure, e.g. a compressor, whereby a force moving the working element is exerted on the working element.
  • This chamber thus forms a driving chamber.
  • the movement forces gas out of the other chamber.
  • This chamber from which gas is displaced as the working element moves, forms the opposing chamber.
  • the size of the counteracting force can be influenced by throttling the gas flow from the counteracting chamber in the direction of a gas sink, e.g. simply the environment, by means of an exhaust air throttle.
  • the exhaust air throttle is referred to as such, even if air is not used as the gas, since this term has prevailed in the relevant terminology.
  • the exhaust air throttle is preferably set in such a way, in particular with regard to the pressure drop across the exhaust air throttle, that a so-called supercritical flow of the gas through the exhaust air throttle results.
  • this can usually be achieved if the pressure on the inlet side in front of the exhaust air throttle is at least twice as high is the outlet pressure after the exhaust air restrictor.
  • the pressures stated here and below are absolute pressures.
  • the flow velocity reaches the speed of sound, which has the advantage that the velocity of the working element, e.g. the piston in a pneumatic cylinder, is load-independent in the quasi-stationary state.
  • the invention can also provide subcritical flow in which the speed of sound is not reached.
  • the object of the invention is to develop a system and a method of the type mentioned at the outset in such a way that an energetically more favorable mode of operation of an exhaust air throttled system can be achieved, preferably with the further achievement of a supercritical flow in the exhaust air throttle, in order to obtain a preferred load-independent movement of the working element .
  • the driving chamber is assigned a control valve, through which the driving chamber can be filled with gas from the gas source, the opening cross section of the control valve depending on a prevailing flow direction in front of the exhaust air throttle or dropping above the exhaust air throttle
  • Control pressure is adjustable, in particular with the control valve of the opening cross section can be enlarged when the control pressure falls below a first limit pressure and the opening cross section can be reduced, in particular the control valve can be closed when the control pressure falls below a second limit pressure.
  • the object is achieved in that the driving chamber is/is assigned a control valve, through which the driving chamber is filled with gas from the gas source, the opening cross-section of the control valve depending on a prevailing flow direction in front of the exhaust air throttle or above the exhaust air throttle is adjusted as the control pressure falls, in particular in such a way that the opening cross section is increased with the control valve when the falling control pressure falls below a first limit pressure and the opening cross section is reduced, in particular the control valve is closed when the further falling control pressure falls below a second limit pressure.
  • the invention can preferably provide that when the control pressure is greater than the first limit pressure, the control valve is initially closed, i.e. it only opens when the pressure falls below the first limit pressure and the opening cross section increases as the control pressure continues to fall.
  • control valve when the first limit pressure is present, the control valve is already partially open and does not close completely even if the control pressure increases further.
  • control valve increases the opening cross-section as the control pressure falls and as the control pressure rises reduced.
  • control valve reduces the opening cross section with falling control pressure and increases it with increasing control pressure.
  • the respective change in the opening cross section is dependent on the change in the control pressure and, in particular, also on its sign. This dependency can be linear, but it doesn't have to be. A non-linear dependency between the control pressure change and the opening cross-section change can also be provided.
  • a non-return valve opening in the direction of the driving chamber is preferably located in the gas flow path in series with the control valve.
  • a check valve parallel to the control valve is a check valve blocking in the direction of the driving chamber. The flow of gas into the chamber occurs through the control valve, while a return flow occurs, e.g. during a return stroke of the
  • Working element takes place past the control valve, especially when this is closed by its switching position in the return stroke.
  • the advantage of the invention is that a first limit pressure can be selected which ensures that the exhaust air throttle is operated with a desired differential pressure level across the exhaust air throttle. If the pressure falls below the limit, the control valve opens and more gas can flow into the driving chamber in order to obtain the desired pressure condition. In this way, regulation to the desired pressure level can take place.
  • the drive in particular the cylinder, works against a relatively low external load and consequently a low pressure difference at the working element is sufficient to carry out the task
  • the driving chamber is not fully brought up to the supply pressure of the system, in contrast to conventional exhaust air throttled systems, but only with the air volume filled, which leads to a pressure that is slightly higher than the pressure required to perform the task while maintaining a supercritical flow at the exhaust air throttle.
  • a return stroke of the working element is made possible, for example, in particular after switching by means of a changeover valve, by supplying gas, preferably bypassing the exhaust air throttle, into the previously counteracting and now driving chamber, with the gas escaping during the return stroke from the previously driving and now counteracting chamber closed control valve, for example, through a check valve that opens in the return stroke.
  • the gas inflow can take place in the return stroke, e.g. through a pressure control valve, in particular a pressure reducer, which is fluidically parallel to the exhaust air throttle, e.g. is still in series with a check valve opening in the direction of the chamber.
  • control valve When the third limit pressure in the chamber currently to be filled is exceeded, the control valve is returned to an at least partially open position, so that a new working stroke of the working element can be carried out, in particular by adjusting the desired control pressure in the range of the first limit pressure or in the range between the first and second limit pressure.
  • the invention preferably provides that the first limit pressure is greater and the second limit pressure is less than a pressure that prevails in front of the exhaust air throttle or drops across the exhaust air throttle, which is required for a supercritical gas flow in the exhaust air throttle.
  • This required pressure can be 2 bar, for example amount to absolute pressure.
  • the first limit pressure is 1% to 25% greater than the pressure required for supercritical flow, for example the pressure required may typically be 2 bar.
  • a value of 2.3 bar for the first limit pressure is preferred because of the required control range below the first limit pressure.
  • the second limit pressure is at least 5% to 50% lower than the pressure required for supercritical flow and is preferably 1.5 bar.
  • the third limit pressure is preferably only slightly below the second limit pressure.
  • real valve constructions usually have larger control spans, so that with the aforementioned values a third limit pressure of, for example, 1.3 bar can be realistically and fluid-mechanically easily achieved.
  • all of the stated pressure data for the limit values and the pressure required for the supercritical flow are to be understood with a possible variation of plus/minus 10% of the stated value.
  • One way of controlling the control valve or the valve actuator located therein with regard to the opening cross section can be that the system has an electronic/electrical controller with which the control pressure can be measured, e.g. with a pressure sensor in a gas line section between the counteracting chamber and the exhaust air throttle, and with which an electric valve drive for adjusting the valve actuator in the control valve can be controlled as a function of the measured value of the control pressure.
  • valve drive can be driven to move the valve actuator to increase the opening cross section, in particular to move it in a first direction with falling control pressure when the Control pressure falls below the first limit value and to move the valve actuator to reduce the opening cross section, in particular to move in a second direction opposite to the first, when the further falling control pressure falls below the second limit value, in particular at the end of the stroke of the working element.
  • a preferred embodiment can provide that the movement of the valve actuator is purely gas-driven, so that an additional electronic control can be omitted.
  • a gas line can preferably be provided for this purpose, with which the control valve is fluidly connected to the counteracting chamber, the control pressure acting in the gas line acting on the valve actuator of the control valve.
  • the control pressure acting in the gas line acting on the valve actuator of the control valve.
  • valve actuator to be preloaded with an actuating force, e.g. by means of a spring acting on the valve actuator, by means of which the valve actuator can be displaced as the control pressure falls.
  • the opening cross section of the control valve is increased in a pressure range between the first and second limit pressure with falling control pressure due to the movement of the valve actuator and in a pressure range below the second limit pressure with further falling control pressure due to the movement of the valve actuator the opening cross section of the control valve is reduced until it is preferably completely closed when the third limit pressure is reached.
  • valve actuator in the pressure range between the first and second limit pressure and in the pressure range below the second limit pressure in particular both at the initially effected Enlargement of the opening cross section as well as in the subsequently effected reduction of the opening cross section is moved in the same direction.
  • control valve has a characteristic curve which describes the dependence of the opening cross section and the adjustment path and which has a reversing slope at an adjustment path position between the two extreme possible adjustment path positions.
  • characteristic curve which describes the dependence of the opening cross section and the adjustment path and which has a reversing slope at an adjustment path position between the two extreme possible adjustment path positions.
  • control valve has two control edges in the valve body that interact with the valve actuator or two control edges that are each arranged on separate valve actuators connected in series, in particular in a direction of movement of the valve actuator defined by falling control pressure in a first movement segment through interaction with the first Control edge of the opening cross section can be enlarged and in a following second movement section in the same direction of movement can be reduced by interaction with the second control edge of the opening cross section, in particular until the opening cross section is completely closed.
  • a pressure regulating valve in particular a pressure reducer with a non-return valve, can be connected in parallel with the exhaust air throttle, which is assigned to the counteracting chamber, through which the opposing chamber can be filled with gas, in particular while shutting off the exhaust air throttle.
  • the invention can provide that a switching valve is provided in the line area between the control valve and the drive, and the exhaust air throttle and the drive, with the in one first switching stage, the first chamber can be connected to the control valve and at the same time the second chamber can be connected to the exhaust air throttle and in a second switching stage the second chamber can be connected to the control valve and at the same time the first chamber can be connected to the exhaust air throttle.
  • the system has only one exhaust air throttle and only one control valve, but these interact with a respective chamber by switching both in the working stroke and in the return stroke.
  • the exhaust air throttle is preferably always connected downstream to the pressure sink and the control valve is always acted upon by gas from the pressure source on the inlet side.
  • a pressure regulating valve preferably a pressure reducing valve, parallel to the control valve, with which a minimum pressure of the driving chamber is always guaranteed, bypassing the control valve which is in the closed position at the end of a working stroke. If the direction of movement of the drive is reversed by switching the changeover valve, there is always sufficient pressure in the previously driving chamber, so that decompression of the chamber now counteracting the movement causes a pressure build-up in front of the exhaust air throttle, which is carried out via the control line and the force exerted in this way on the valve actuator in the control valve causes an opening of the control valve, as a result of which a next pressure-controlled working stroke in the opposite direction is made possible.
  • this pressure regulating valve is provided for starting up the drive system from a completely depressurized state.
  • each of the two chambers is assigned an arrangement of an exhaust air throttle and a control valve with a control line connected to the other chamber, with each of the two chambers in a process phase in which the respective chamber acts as a driving chamber , Can be filled with gas through the associated control valve and each of the two chambers in a process phase in which the respective Chamber acts as a counteracting chamber, can be emptied through the associated exhaust air throttle, in particular wherein in both process phases the respective stroke from the working element takes place with the pressure control described via the currently active control valve.
  • one of the arrangements can be connected to the pressure source by means of a switching valve, the other arrangement being connected to the pressure sink at the same time.
  • check valves in each of the two arrangements can be used to ensure that when a respective arrangement is connected to the pressure source, the gas flow takes place via the control valve in the direction of the chamber to be filled and a gas flow via the exhaust air throttle is prevented, and vice versa when connected to the Pressure sink takes place a gas flow via the exhaust air throttle to the pressure sink and a gas flow through the control valve is prevented.
  • a pressure control valve in particular a pressure reducer, is connected in parallel with at least one of the arrangements, preferably with both arrangements, with which the system can be switched from a pressure-relieved state in both chambers to an operating state, in particular by gas filling of one of the both chambers by the pressure control valve and simultaneous pressurization and opening of the control valve associated with the other chamber.
  • the invention can also provide for the integration of an arrangement for the application of minimum pressure for starting up the system from a state without pressure in both chambers directly into the control valve.
  • FIG. 1 shows a first embodiment of the invention with a cylinder-piston unit A as the working element, the piston 3 of which separates two chambers 1 and 2. It is assumed here that the working element A performs a working stroke when the piston rod of the piston 3 extends.
  • a pressure source 4 can be connected to a line L1 and at the same time a pressure sink 6 can be connected to a line L2, or vice versa.
  • the pressure control according to the invention is only carried out during the working stroke, in particular to ensure that the chamber 1 driving the working stroke is only filled with gas via the control valve 8 to such an extent that there is a supercritical flow at the exhaust air throttle 5 .
  • control valve 8 via which the filling of the chamber 1 takes place, is located in the line L1, which leads to the chamber 1 driving in the working stroke.
  • a check valve R1 is arranged parallel to the control valve, which prevents an inflow into the chamber, bypassing the control valve 8, but allows gas to flow out of the chamber 1 on the return stroke, in particular when the control valve 5 is then (as shown here) closed.
  • gas is displaced from chamber 2, which counteracts the movement of piston 3 in the working stroke, to pressure sink 6 via exhaust air throttle 5 and check valve R2, which is in series with it and opens in the direction of pressure sink 6.
  • the invention provides that a gas line 9 as a control line 9 connects the control valve 8 to a line section that lies in the line L2 between the counteracting chamber 2 and the exhaust air throttle 5 .
  • the control pressure acting in this line section acts via the control line 9 on the valve actuator in the control valve 8 and can influence the position of the valve actuator and thus the opening cross section of the control valve 8, namely in accordance with the invention in such a way that with falling Control pressure when the control pressure falls below a first limit pressure, the opening cross-section is increased, so that more gas flows into the driving chamber and when the pressure falls further below a second limit pressure, which is smaller than the first limit pressure Opening cross-section is reduced, preferably completely closed, in particular when a third limit pressure is reached, preferably which is smaller than the second limit pressure.
  • control pressure is kept in the control range around the first limit pressure until it falls below the second limit pressure.
  • This can preferably be selected in such a way that a supercritical flow is achieved in the exhaust air throttle; the first limit pressure is therefore greater than the minimum pressure that is necessary for the supercritical flow.
  • the second limit pressure is preferably lower than this minimum pressure.
  • control valve 8 reduces its opening until it closes, preferably when the third limit pressure is reached or fallen below.
  • a return stroke can be initiated by switching over the switching valve 7 .
  • connecting the pressure source 4 to the line L2 causes the check valve R2 to close and the check valve R3 to open, which is in series with a pressure control valve 12, through which the chamber 2 is filled for the return stroke.
  • the gas then displaced from the chamber 1 can escape unhindered to the pressure sink 6, e.g. to the environment via the open check valve R1.
  • the pressure build-up in chamber 2 also applies force to the valve actuator in control valve 8 via control line 9, so that it opens again, in particular when the third limit pressure is reached or exceeded, and initiates the next working stroke.
  • the pressure conditions required for cyclic working strokes are thus maintained.
  • the system can be started from a rest position by pressurizing chamber 2 .
  • Figure 2 shows an embodiment in which a pressure-controlled movement of the piston 3 takes place both in the working stroke and in the return stroke based on the control pressure in the control line 9.
  • the control valve 8 is provided in the line L1, which in this embodiment is constantly connected to the pressure source 4.
  • the pressure sink 6 is constantly connected to the line L2 with the exhaust air throttle 5.
  • chamber 1 is now selectively connected to the control valve and chamber 2 to the exhaust air throttle via the switching valve, or vice versa.
  • the previously described pressure regulation with the control valve 8 thus always takes place with respect to the currently driving chamber of both chambers 1, 2 and the exhaust air throttling always takes place in the gas that flows out of the currently counteracting chamber.
  • the pressure control valve 12 can be provided in order to achieve a minimum filling of the formerly driving chamber, a pressurization of the control line 9 and an opening of the control valve 8 in an initial pressureless state of both chambers in the switching position shown here with the control valve closed (at the end of the working stroke). .
  • the system is thus put back into its regular operating state and can perform a movement by switching over the switching valve.
  • FIG. 3 shows a further possible embodiment, in which each of the two chambers 1 and 2 is assigned an arrangement AN1 or AN2 consisting of a control valve 8 and an exhaust air throttle 5.
  • the control line 9 of a control valve 8 that is assigned to a specific chamber has a fluid connection to the other chamber in each case.
  • R1 allows flow through the control valve 8 to the chamber, while at the same time R2 blocks flow through the exhaust throttle when the pressure source 4 is connected to the arrangement AN1 or AN2, respectively, and R2 allows flow out of the chamber through the exhaust throttle 5, at the same time R1 blocks a flow through the control valve 8 when the pressure sink 6 is connected to the arrangement AN1 or AN2.
  • the switching valve 7 can alternately connect the pressure source 4 and the pressure sink 6 to an arrangement AN1, AN2. With the same effect as described above, it is achieved that in the working stroke and in the return stroke, or in the case of reversing working strokes, a pressure control takes place which fulfills the desired pressure criterion in the exhaust air throttling, preferably a supercritical flow.
  • the invention can provide for a pressure control valve 11 with a non-return valve to be located parallel to the arrangement AN2, through which the system can be started up initially when both chambers are pressureless, as has also been described above. Furthermore, a pressure control valve can also lie parallel to the arrangement AN1, which is not shown.
  • FIGS. 4a and 4b show a possible embodiment of a control valve 8 with a valve actuator 8a, which has two actuator bodies 8b and 8c connected by a tapered area.
  • a valve actuator 8a can be provided in all possible designs of the valve 8.
  • the valve actuator 8a is pressurized here on the left by the control pressure from the control line 9 and is force-loaded here on the right by a spring 13, which is arranged in a pressure-relieved space. With falling control pressure in the line 9, the valve actuator 8a is thus shifted to the left in relation to this representation.
  • the opening cross section is increased in the action between the valve actuator 8a (its actuator body 8b) and the control edge SK1 and the opening cross section is reduced in the action between the valve actuator 8a (its actuator body 8c) and the control edge SK2.
  • the opening cross-section between ports 4 (to the pressure source) and 1 (to the chamber/to the controlled volume) can thus be adjusted as a function of the control pressure.
  • the limit pressures mentioned can be defined by means of the spring 13, the force of which can be adjustable.
  • Control valve 8 at port 23 is relieved of gas pressure on the right-hand side.
  • the second and third limit pressures can depend on the first and can be determined by the spring and the design of the control valve in terms of the geometry of the control edges.
  • the illustration in FIG. 4a shows a position with the maximum opening cross section, which can be present at a control pressure between the first and second limit pressures or preferably at the second limit pressure.
  • the control valve can preferably close with increasing control pressure when the first limit pressure is exceeded, or initially reduce the opening cross section with increasing control pressure and then close, in particular if there is no residual opening, e.g.
  • Limit pressure according to the invention with falling control pressure increase the opening cross section up to the maximum opening position shown. If the control pressure drops further, the opening cross-section is reduced until it closes at the control edge SK2.
  • FIG. 4b shows an embodiment of the same control valve of FIG. 4a, in a position in which the first limit pressure in the control line 9 can be present.
  • the control valve is closed at the control edge SK1 and would increase the opening cross-section from the closed position with a falling control pressure starting from this position. Starting from this position, the control valve 8 would remain closed with an increasing control pressure.
  • FIG. 5 shows an embodiment in which, compared to FIGS. 4a and 4b, two springs 13a, 13b are arranged coaxially within one another.
  • the spring 13b acts directly on the valve actuator 8a, the spring 13a indirectly via the bearing element 14, which can be displaced up to the stop 15.
  • a first displacement range of the valve actuator 8a is thus defined, in which both springs interact and a second - when the bearing element 14 in Stop is - in which only the spring 13b acts.
  • the limit pressures and the gradients of the opening characteristics of the two control edges as a function of the control pressure can thus be decoupled from one another.
  • the space in which the springs 13a and 1b are arranged is pressure-relieved via connection 23.
  • FIG. 6 shows an embodiment in which the embodiment in FIGS. 4a and 4b has been expanded to include an integrated minimum pressurization for starting from an unpressurized state. As a result, the pressure reducers 11 and 12 shown in the previous FIGS. 2 and 3 and provided for
  • the piston 20 shown on the right serves to return the downstream pressure of the control valve 8 for the application of minimum pressure.
  • a spring 21 acts on the piston 20 , which is acted upon by the pressure regulated by the control valve through the bore 22 , ie in particular the pressure in the driving chamber 1 . Port 1 and 22 are thus preferably directly connected.
  • the spring 21 is prestressed so that the piston 20 only moves to the left when there is sufficient post-pressure from the control valve 8 , ie when the pressure in the driving chamber 1 has a minimum pressure predetermined by the spring 21 .
  • the space in which the springs 13b and 21 are arranged is pressure-relieved via the connection 23.
  • the position of the piston defines the spring preload of the springs 13b and 13c. These define the position of the valve actuator 8a both as a function of the control pressure in line 9 and as a function of its preload and consequently the position of the piston 20.
  • a spring system 21 consisting of cup springs can be used in particular to load the piston 20 .
  • Figure 7 shows a modification of the versions of Figure 5 and Figure 6. Insofar as the functions described there and in Figures 4 are not replaced by the functions described below, these also apply to the version of Figure 7.
  • the piston 20 in this embodiment no longer acts on the valve actuator via a resilient spring 13b, but here rigidly via the piston rod 20a.
  • the interaction of piston 20 and spring 21 is reversed in direction here. Again, the space in which the spring 21 is arranged is pressure-relieved through the port 23.
  • the piston 20 is therefore pressurized from the direction of the inside of the valve with the pressure of the port 1, e.g. via the line 22, which connects the space to the left of the piston 20 connects to port 1 preferably inside the valve.
  • the limit pressures and the gradients of the opening characteristics of the two control edges can be decoupled from one another as a function of the control pressure.
  • this is not done here by the springs 13b and 21 lying one inside the other, but instead by the realization of different opening cross-sections depending on the position in the effect between a control edge, here the control edge SK1 and the valve actuator 8a, in particular in the case of an actuating body, here the actuating body 8b of the valve actuator 8a.
  • This way of influencing the characteristic via different opening cross-sections depending on the position can be carried out according to the invention independently of the other specific constructions shown in the valve 8 .
  • a control body e.g. here the control body 8b
  • the control grooves 8d end in front of the right axial end of the adjusting body 8b.
  • control pressure is applied here preferably via the connection 9, onto the axial end face of the right-hand adjusting body 8b, on which the piston rod 20a also acts.
  • the action takes place against the spring 13c on the other side of the valve actuator 8a, which is arranged in a pressure-relieved space via the connection 23.
  • the movement of the valve actuator 8a is the other way around in the embodiment of FIG. 7 compared to FIGS.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

L'invention concerne un système d'entraînement alimenté par gaz qui comprend un élément d'entraînement (A) avec une première chambre (1) et une deuxième chambre (2), qui sont séparées l'une de l'autre par une pièce de travail mobile (3) de l'élément d'entraînement (A), en particulier par un piston (3), une chambre (1) parmi les deux chambres (1, 2) pouvant être raccordée à une source de gaz (4) pour former une chambre (1) entraînant la pièce de travail (3), et l'autre chambre (2) parmi les deux chambres (1, 2) pouvant être raccordée dans un même temps par l'intermédiaire d'un étrangleur de gaz d'échappement (5) à un puits de gaz (6), en particulier au moyen d'une soupape d'inversion (7), pour former une chambre contrebalançant le mouvement de la pièce de travail (3), une soupape de commande (8) étant attribuée à la chambre d'entraînement (1), la soupape de commande permettant de remplir la chambre d'entraînement (2) de gaz en provenance de la source de gaz (4) ; la section transversale d'ouverture de la soupape de commande (8) pouvant être ajustée en fonction d'une pression de commande prévalant en amont de l'étrangleur de gaz d'échappement (5) dans la direction de circulation ou une pression de commande chutant sur l'étrangleur de gaz d'échappement (5) ; la soupape de commande (8) permettant d'agrandir la section transversale d'ouverture lorsque, à mesure que la pression de commande chute, elle passe au-dessous d'une première pression seuil, et permettant de réduire la section transversale d'ouverture, en particulier la soupape de commande (8) pouvant être fermée, lorsque, à mesure que la pression de commande continue de diminuer, elle passe au-dessous d'une deuxième pression seuil. L'invention concerne également un procédé de fonctionnement d'un système d'entraînement alimenté par gaz.
EP21777205.2A 2020-09-07 2021-09-06 Système d'entraînement alimenté par gaz et procédé de fonctionnement Active EP4211355B1 (fr)

Applications Claiming Priority (2)

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DE102020123331.0A DE102020123331A1 (de) 2020-09-07 2020-09-07 Gasbetriebenes Antriebssystem und Verfahren zum Betrieb
PCT/EP2021/074528 WO2022049298A1 (fr) 2020-09-07 2021-09-06 Système d'entraînement alimenté par gaz et procédé de fonctionnement

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CN116277332B (zh) * 2022-09-09 2024-02-09 广东豪德数控装备股份有限公司 板材齐头装置及其气路系统和控制方法、封边机

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Publication number Priority date Publication date Assignee Title
JPS5028159A (fr) 1973-07-05 1975-03-22
US4175473A (en) * 1976-06-08 1979-11-27 Shoketsu Kinzoku Kogyo Kabushiki Kaisha Fluid circuit
US4192346A (en) 1976-08-25 1980-03-11 Shoketsu Kinzoku Kogyo Kabushiki Kaisha Control valve
JPS54101070A (en) 1978-01-27 1979-08-09 Hitachi Metals Ltd Fluid cylinder control circuit
FR2738040B1 (fr) 1995-08-24 1997-10-17 Charmois Claude Dispositif pour la regulation de la vitesse de l'organe d'actionnement d'un actionneur pneumatique
WO2005045257A1 (fr) * 2003-11-07 2005-05-19 Japan Science And Technology Agency Actionneur utilisant un cylindre a fluides, procede pour commander l'actionneur et dispositifs a etrangleur
DE102004025322A1 (de) * 2004-05-19 2005-12-15 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102004063044B4 (de) * 2004-12-22 2006-12-21 Sauer-Danfoss Aps Hydraulische Steuerung
WO2009133956A1 (fr) 2008-05-02 2009-11-05 国立大学法人筑波大学 Actionneur, procédé de commande d’actionneur et programme de commande d’actionneur
DE102009001150A1 (de) 2009-02-25 2010-09-02 Robert Bosch Gmbh Pneumatik-Drosselrückschlagventil
RU2685167C1 (ru) 2018-09-10 2019-04-16 федеральное государственное бюджетное образовательное учреждение высшего образования "Донской государственный технический университет", (ДГТУ) Адаптивный пневматический привод с обратной пневматической связью

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EP4211355C0 (fr) 2024-07-24
US20230304514A1 (en) 2023-09-28
WO2022049298A1 (fr) 2022-03-10
DE102020123331A1 (de) 2022-03-10
US12000412B2 (en) 2024-06-04
CN116194678A (zh) 2023-05-30

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