EP2115305B1 - Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique - Google Patents

Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique Download PDF

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Publication number
EP2115305B1
EP2115305B1 EP08758919.8A EP08758919A EP2115305B1 EP 2115305 B1 EP2115305 B1 EP 2115305B1 EP 08758919 A EP08758919 A EP 08758919A EP 2115305 B1 EP2115305 B1 EP 2115305B1
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EP
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Prior art keywords
pressure
pressure chamber
piston
actuating unit
hydraulic
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EP08758919.8A
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German (de)
English (en)
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EP2115305A1 (fr
Inventor
Bert Brahmer
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Voith Patent GmbH
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Voith Patent GmbH
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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
    • F15B11/044—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"
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • 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
    • F15B2211/3144—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single 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
    • F15B2211/40—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
    • F15B2211/405—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
    • F15B2211/415—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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow 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
    • F15B2211/40—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
    • F15B2211/50—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
    • F15B2211/515—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
    • F15B2211/55—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
    • F15B2211/70—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

Definitions

  • the invention relates to a hydraulic drive in particular for machine tools, for example for a press, punching machine, nibbling machine and the like, according to the preamble of claim 1 and a method for controlling the hydraulic drive according to the preamble of claim 12.
  • FIGS. 1 . 2 and 4 refer to previously used arrangements.
  • FIG. 1 shows the basic apparatus structure of a conventional hydraulic drive for a punching machine.
  • Pressure supply device comprises in the in FIG. 1 1, a constant-displacement pump 1.1 for generating an operating pressure and a first pressure-limiting valve 1.2, which can be adjusted to a desired outlet pressure range, are shown.
  • a first hydraulic accumulator 1.3 is connected, by its use, the volume flow in the supply network can be increased in a short time.
  • a first pressure chamber 1.8 in the working cylinder 1.5 of the drive is always connected via the first line B to the pressure source, whereas a second pressure chamber 1.7 can be connected in the working cylinder 1.5 by means of the 3-way valve either with the pressure source or a tank 1.9.
  • the two pressure chambers 1.7, 1.8 are separated from each other by the piston 1.6 of the working cylinder 1.5, wherein the surface on the piston 1.6, which is acted upon by pressure from the first pressure chamber 1.8, due to the one-sided piston rod is smaller than the surface of the piston 1.6, with Pressure from the second pressure chamber 1.7 is acted upon.
  • the extension of the piston 1.6 or connected to this piston rod is effected by connecting the second pressure chamber 1.7 with the pressure source, the maximum extension force is determined by the area ratio of the two mentioned the pressure chambers 1.7, 1.8 limiting and opposing surfaces of the piston 1.6.
  • the piston 1.6 Due to the resistance that opposes the workpiece of the piston movement, the piston 1.6 is first decelerated, and in the second pressure chamber 1.7 is built according to the required cutting force of the necessary pressure. According to the modulus of elasticity of the hydraulic oil in the second pressure chamber 1.7, a spring energy is stored in the oil column in the second pressure chamber 1.7, that is, the oil column is biased, so to speak.
  • FIG. 2 shows the basic apparatus structure of another conventional hydraulic drive similar to that of the FIG. 1 , however with a 4/3-way valve 2.1 instead of the 3-way valve (3/3-way valve) 1.4 from the FIG. 1 , also, this 4/3-way valve 2.1, as the 3-way valve 1.4 from the FIG. 1 , Also be designed as a continuous valve or switching valve. Notwithstanding the in the FIG. 1 However, the first pressure chamber 1.8 is always connected to the pressure source when the second pressure chamber 1.7 is connected to the tank 1.9, and with the pressure source, no constant pressure on the first line B and thus the first pressure chamber 1.8 is exercised the tank 1.9 connected when the second pressure chamber 1.7 is connected to the pressure source.
  • both pressure chambers 1.7, 1.8 are separated from both the pressure source and the tank 1.9, whereas according to the FIG. 1 only the second pressure chamber 1.7 in the middle position of the 3-way valve 1.4 is separated from both the pressure source and the tank 1.9.
  • FIG. 4 shows a path / time graph of the piston 1.6 of the conventional hydraulic drive of Fig.1 ,
  • TOS top of sheet
  • BOS bottom of sheet
  • TDC top dead center
  • the European patent application EP 0 676 547 A1 describes a flow control device and a lowering brake valve with a metering orifice, over which a predetermined pressure difference is maintained and thereby the speed of adjustment of a hydraulic cylinder is to be kept constant. If the pressure difference deviates from its predetermined value, a control piston, which regulates a quantity of hydraulic fluid flowing through, is displaced in a changing manner until the pressure difference across the metering orifice returns to its predetermined value.
  • the EP 0 676 547 A1 a flow control device that responds to an undesirable volume flow of hydraulic medium that has been adjusted due to the process, to bring the flow to the desired value again.
  • the patent DE 196 08 582 B4 describes a hydro-compensator for surge suppression in the return line of a hydraulic system.
  • a check valve and a nozzle connected in parallel is provided in the return or tank line.
  • the closing body of the check valve is pressed by a compression spring against a seat.
  • the force exerted by the compression spring on the closing body corresponds to a certain pressure in the tank line section between a directional control valve and the check valve. Only when this pressure is exceeded, the check valve opens.
  • the nozzle causes the pressure in said tank line section to drop to atmospheric pressure after a certain time.
  • a damper in the tank line is shown, which in turn reacts to changes in the pressure in the tank line.
  • the European patent application EP 1 484 209 A1 describes a hydraulic actuator, in particular for a convertible roof.
  • the actuator comprises a double-acting cylinder and a throttle device which is selectively switched to a throttled and a non-throttled state.
  • the throttle device is kept in the non-throttling state.
  • the speed of the piston is faster than predetermined by the pressurization, resulting in a pressure drop in the cylinder chamber.
  • a control piston detects this pressure loss and, in response, switches the throttle device into the throttled state. As a result, the extension movement of the piston is braked.
  • the invention has for its object to provide a hydraulic drive, in particular for a machine tool, such as punching machine, nibbling machine or a press specify, in which the described disturbing noises and cavitation eliminated or at least reduced.
  • the hydraulic drive which is provided in particular for a press, a punching or nibbling machine, has a double-acting working cylinder, the piston having an effective in the retraction direction first working surface and an effective in the extension direction second working surface.
  • the work surfaces each delimit a pressure chamber.
  • the two work surfaces are in particular the two single working surfaces of the piston, that is, the working cylinder then has exactly two pressure chambers.
  • at least two different pressures can be switched by means of an actuator on one or both working surfaces. In particular, this is an embodiment, as initially described with reference to the FIGS.
  • an adjusting unit is additionally provided in the hydraulic drive, which allows a throttled backflow of hydraulic medium from the first pressure chamber bounded by the first working surface.
  • the drive also has control means, with which before an abrupt acceleration of the piston due to the sudden release of force, the actuator is controlled such that effected by the control unit effected by throttling a hydraulic damping of the movement of the piston.
  • the hydraulic drive according to the invention or the method according to the invention thus prevent the unwanted sudden acceleration of the piston by measures that are already taken as a precaution, that is, the actuator causes a throttling of the return flow of hydraulic fluid from the first pressure chamber before a sudden acceleration of the piston has been used.
  • the Anrieb reacts not advantageous to a pressure drop in the limited by the second working surface second pressure chamber, but switches the actuator so that it causes a throttled back flow of hydraulic medium from the limited of the first working surface first pressure chamber, in response to a pressure increase in the second limited by the second working surface pressure chamber.
  • the adjusting unit can directly effect the throttling of the hydraulic medium flowing out of the first pressure chamber, that is to say have a throttle point - with a constant or adjustable flow cross-section - which is selectively switched into and out of the flow path or permanently in the flow path Flow path is arranged and whose flow cross section is selectively changed between a throttling position and a non or substantially non-throttling position or is variable.
  • the actuator causes the throttling indirectly, that is, it is connected in parallel to a throttle - with a constant or adjustable flow cross-section with respect to the hydraulic medium flow and selectively releases an additional flow cross-section in a bypass line to the throttle or blocks (partially or completely).
  • the outflow of hydraulic medium from the first pressure chamber which can be throttled directly or indirectly by the actuating unit, that is to say the flow due to displacement by the extending piston, takes place, for example, in the direction of the pressure supply, in particular by means of a pump and / or an accumulator, by means of which the first pressure chamber advantageous permanently, in particular as in the FIG. 1 , or optionally, in particular as in the FIG. 2 , connected is.
  • the actuator can basically be designed in any conceivable, suitable manner.
  • the actuator comprises a flow valve (also flow valve or throttle valve), which is arranged in a first line or in a bypass line parallel to this, can flow through the hydraulic medium from the first pressure chamber.
  • the flow control valve is, for example, a control valve, a directional control valve or a throttle point with a constant cross section.
  • a control valve for example, a control valve, a directional control valve or a throttle point with a constant cross section.
  • the actuator is a 2/2-way valve, which - when arranged in said bypass line to a throttle point in the first line - is continuous in a first switching position and locks in a second switching position.
  • a 2/2-way valve directly in said first line, via which hydraulic medium can flow from the first pressure chamber be arranged and have two switching positions, wherein the flow resistance through the 2/2-way valve in the first switching position less than in the second switching position is.
  • the adjusting unit in the first line or parallel to a throttle point in the first line
  • the adjusting unit is designed so that it depends on the ratio of the supply pressure to the pressure p A , the in the second working surface limited second pressure chamber prevails, can be brought into the passage position or blocking position or in non-throttled position or throttle position.
  • the switching of the actuator can also be done in dependence on the ratio of the pressures in the two pressure chambers.
  • a first control surface of the actuating unit with the supply pressure or the pressure from the first pressure chamber can be acted upon, while a second control surface of the actuating unit with the pressure p A in the second pressure chamber can be acted upon, wherein the actuating unit in dependence on the ratio of the on the first pressure applied to the pressure applied to the second control surface in the passage position or blocking position or in unthrottled position or throttle position is brought.
  • the working cylinder is designed as a differential cylinder, that is, only one side of the piston is provided with a piston rod, whereby the piston has two different sized effective surfaces, which are acted upon by the pressure from a respective pressure chamber.
  • the second pressure chamber for extending or retracting the piston is optionally acted upon by means of the actuator with supply pressure or tank pressure, while the first pressure chamber is constantly acted upon by supply pressure.
  • the second pressure chamber can be connected to a low-pressure source, a high-pressure source or a tank, while the first pressure chamber is always connected to the low-pressure source.
  • the first pressure chamber and the second pressure chamber are each selectively connectable to a pressure source or tank and in particular separable from both, wherein in one embodiment with a 4/3-way valve, as shown in the FIG. 2 is shown, the first pressure chamber is always connected to the pressure source when the second pressure chamber is connected to the tank and vice versa.
  • the actuator is, for example, a continuously variable valve, a servo valve with electrical actuation or a linear amplifier or copying valve with mechanical feedback of the position of the piston in the working cylinder.
  • the noise during punching or the like of the workpiece can be significantly attenuated. Furthermore, the risk of cavitation is significantly reduced.
  • the Indian FIG. 3 in principle and schematically shown hydraulic drive according to the invention comprises in the FIGS. 1 and 2 a constant pump 3.1 shown for generating an operating pressure as well as an adjustable pressure to a desired output pressure relief valve 3.2.
  • a hydraulic accumulator 3.3 is connected in the supply network, by means of which the volume flow in the supply network can be increased in a short time.
  • the pressure supply may also have a storage charge at the location of the pressure limiting valve 3.2.
  • a variable displacement pump with controllable pump power could be provided.
  • the operating pressure acts via the first line B on the annular first working surface 3.15 of the piston 3.6 and exerts on the latter acting in the retraction time constant force.
  • the first working surface 3.15 opposite second working surface 3.16 of the piston 3.6 switch to tank so that there is a force acting on the piston resulting force in retraction and thus the piston moves back 3.6.
  • the connection P is connected to the supply pressure of the pressure source via the second pressure chamber 3.7 to the second working surface 3.16, the piston 3.6 extends.
  • the maximum force is known to be defined by the ratio of the second working surface 3.16 to the first working surface 3.15.
  • the maximum extension force can be increased while maintaining a high overall efficiency, for example, by providing an additional supply pressure (high pressure "HD”) which is higher than the primary applied supply pressure (low pressure "ND").
  • This high pressure can be switched on in different ways, for example load-dependent.
  • a high-pressure connection as they are from the documents DE 10 2004 024 126 A1 and EP 1 138 958 B1 is known to be resorted to.
  • a controllable throttle valve or, as in this case, a constant throttle 3.13 is arranged in the first line B.
  • the throttle 3.13 is bypassed by a bypass line 3.14, which opens on both sides of the throttle 3.13 in the first line B.
  • a 2/2-way valve 3.10 is arranged as a proper actuator, with which the flow of the hydraulic medium through the bypass line 3.14 can either be passed or blocked.
  • the 2/2-way valve 3.10 is operated hydraulically in the present case.
  • a first control surface 3.12 of the 2/2-way valve 3.10 is acted upon by the supply pressure p and a second control surface 3.11 of the 2/2-way valve 3.10 with the pressure p A prevailing in the second pressure chamber 3.7 or in the second line A behind the directional control valve 3.4 ,
  • the pressure in the second line A or in the second pressure chamber 3.7 corresponding to the area ratio of the two working surfaces 3.15 and 3.16 always significantly lower than the pressure in the first line B and in the first pressure chamber 3.8 or in the illustrated connection of the control pressure line for the actuator (2/2-way valve 3.10) before the throttle 3.13 as the supply pressure p, which prevails there.
  • the directional control valve 3.4 can be reversed without the risk of the occurrence of a negative pressure in the second line A for reversing the piston movement direction.
  • the pressure in the second pressure chamber 3.7 or in the second line A, to which the control pressure line of the 2/2-way valve 3.10 is connected also drops, so that the 2/2 Directional valve 3.10 is automatically switched to the passage position again.
  • the switching threshold between the throttled position and non-throttled position can be set to any pressure ratio between the pressures in the lines A and B and thus to any working force of the piston.
  • this switching threshold is advantageously set to a value just below the maximum value of the worker in the first pressure stage (ND).
  • a controllable throttle valve may be provided.
  • the throttle 13 can be replaced by a directional control valve, in particular 2/2-way valve, which in the first switching position unthrottled and in the second switching position a has throttled passage.
  • This 2/2-way valve (not shown), corresponding to the 2/2-way valve 3.10 from the FIG. 3 be controlled to allow a throttled backflow of hydraulic medium according to the invention from the limited first of the first working surface 3.15 first pressure chamber 3.8 optionally, always at or before a sudden acceleration of the piston 3.6 due to its sudden power relief.
  • a comparatively unthrottled return flow of hydraulic medium from the first pressure chamber 3.8 or in the first pressure chamber 3.8, the latter at a retraction movement of the piston 3.6 be provided, in particular by automatic switching or holding the 2/2-way valve 3.10 according to FIG. 3 or a 2/2-way valve with throttled passage position instead of the throttle 3.13, if in the second pressure chamber 3.7 and the second line A, a lower pressure than in the first pressure chamber 3.8 or the first line B, or, in the illustrated connection of the control pressure line to the control surface 3.12 of the 2/2-way valve 3.10 (seen from the pressure source) in front of the throttle 3.13 when the pressure in the second pressure chamber 3.7 or in the second line A exceeds the supply pressure p.
  • FIG. 5 relating to the inventive hydraulic drive of FIG. 3 relates, the time course of the path of the piston 3.6 and the prevailing in the second pressure chamber 3.7 pressure p A is shown graphically. Due to the pressure increase in the second pressure chamber 3.7, the 2/2-way valve 3.10 is brought into the blocking position. After breaking the workpiece, the piston 3.6 is accelerated due to the throttling effect only to a relatively low speed 5.4. The pressure gradient 5.1 is compared with Fig. 4 significantly flatter, and the pressure p A remains above the range of cavitation.

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

Claims (16)

  1. Entraînement hydraulique, en particulier pour une presse, une machine de poinçonnage ou de grignotage,
    1.1 avec un vérin de travail (3.5) à double action dont le piston (3.6) présente une première surface de travail (3.15) agissant dans la direction de rentrée et une deuxième surface de travail (3.16) agissant dans la direction de sortie, lesquelles limitent chacune une chambre de pression (3.7, 3.8), dans lequel 1.2 pour faire rentrer le piston (3.6) dans le vérin de travail (3.5) et pour l'en faire sortir, au moins deux pressions différentes peuvent être appliquées sur au moins l'une des surfaces de travail (3.15, 3.16) au moyen d'un actionneur,
    1.3 l'entraînement hydraulique présentant une unité d'actionnement qui permet, alternativement, un reflux étranglé ou un reflux relativement non étranglé de fluide hydraulique hors de la première chambre de pression (3.8) limitée par la première surface de travail (3.15),
    caractérisée en ce que
    1.4 l'entraînement présente des moyens de commande avec lesquels, avant une accélération brusque du piston (3.6) du fait de sa décharge de force soudaine, l'unité d'actionnement peut être commandée de telle sorte qu'il se produise un amortissement hydraulique du mouvement du piston (3.6) par un étranglement renforcé, provoqué directement ou indirectement par l'unité d'actionnement, du reflux auparavant relativement non étranglé de fluide hydraulique hors de la première chambre de pression (3.8),
    1.5 l'unité d'actionnement étant commutée en fonction d'une augmentation de pression dans la deuxième chambre de pression (3.7) limitée par la deuxième surface de travail (3.16) de telle sorte qu'elle provoque le reflux étranglé renforcé de fluide hydraulique hors de la première chambre de pression (3.8) limitée par la première surface de travail (3.15) lors d'une augmentation d'une pression dans la deuxième chambre de pression (3.7).
  2. Entraînement hydraulique selon la revendication 1, caractérisé en ce qu'un étranglement (3.13) est disposé dans une première conduite (B), par laquelle le fluide hydraulique peut sortir de la première chambre de pression (8), et l'unité d'actionnement, en particulier sous la forme d'un distributeur, est prévue dans une conduite de dérivation (3.14) qui est disposée en parallèle à l'étranglement (3.13) pour ouvrir et fermer sélectivement la conduite de dérivation (3.14).
  3. Entraînement hydraulique selon la revendication 1, caractérisé en ce que l'unité d'actionnement comprend une soupape d'étranglement qui est disposée dans une première conduite (B), par laquelle le fluide hydraulique peut sortir de la première chambre de pression (3.8), et qui présente au moins deux positions de commutation dans lesquelles, dans une première position de commutation, l'étranglement du reflux de fluide hydraulique hors de la première chambre de pression (3.8) est obtenu et, dans la deuxième position de commutation, un étranglement relativement faible ou un reflux sensiblement sans étranglement hors de la première chambre de pression (3.8) ou une entrée de fluide hydraulique dans la première chambre de pression (3.8) est obtenu(e).
  4. Entraînement hydraulique selon la revendication 3, caractérisé en ce que l'unité d'actionnement, qui est réalisée en particulier sous la forme d'un distributeur 2/2, est intégrée dans l'entraînement hydraulique de manière à être mise dans sa première position de commutation avec étranglement ou dans sa deuxième position de commutation avec étranglement réduit en fonction du rapport entre la pression d'alimentation d'une source de pression, en particulier d'une pompe (3.1) ou d'un accumulateur hydraulique (3.3), et la pression pA qui règne dans la deuxième chambre de pression (3.7) limitée par la deuxième surface de travail (3.16).
  5. Entraînement hydraulique selon la revendication 2, caractérisé en ce que l'unité d'actionnement est réalisée sous la forme d'un distributeur 2/2 (3.10).
  6. Entraînement hydraulique selon la revendication 2 ou 5, caractérisé en ce que l'unité d'actionnement est intégrée dans l'entraînement de manière à être mise en position de passage ou en position de blocage en fonction du rapport entre la pression d'alimentation d'une source de pression, en particulier d'une pompe (3.1) ou d'un accumulateur hydraulique (3.3), et la pression pA qui règne dans la deuxième chambre de pression (3.7) limitée par la deuxième surface de travail (3.16).
  7. Entraînement hydraulique selon l'une des revendications 2 à 6, caractérisé en ce qu'une première surface de commande (3.12) de l'unité d'actionnement est soumise à la pression de la première chambre de pression (3.8), d'une première conduite (B) raccordée à celle-ci ou à la pression d'alimentation d'une source de pression, en particulier d'une pompe (3.1) ou d'un accumulateur hydraulique (3.3), et une deuxième surface de commande (3.11) de l'unité d'actionnement est soumise à la pression de la deuxième chambre de pression (3.7) ou d'une deuxième conduite (A) raccordée à celle-ci, l'unité d'actionnement étant mise en position d'étranglement ou d'étranglement réduit, respectivement en position de passage ou en position de blocage, en fonction du rapport entre la pression exercée sur la première surface de commande (3.12) et la pression exercée sur la deuxième surface de commande (3.11).
  8. Entraînement hydraulique selon l'une des revendications 1 à 7, caractérisé en ce que le vérin de travail (3.5) est réalisé sous la forme d'un vérin différentiel.
  9. Entraînement hydraulique selon l'une des revendications 1 à 8, caractérisé en ce que pour faire sortir ou rentrer le piston (3.6), la deuxième chambre de pression (3.7) peut être soumise à la pression d'alimentation ou à la pression du réservoir au moyen de l'actionneur, et que la première chambre de pression (3.8), en cas de reflux non étranglé de fluide hydraulique hors de celle-ci, est soumise en permanence à la pression d'alimentation.
  10. Entraînement hydraulique selon l'une des revendications 1 à 8, caractérisé en ce que la deuxième chambre de pression (3.7) peut être reliée à une source de basse pression, une source de haute pression ou un réservoir, et que la première chambre de pression (3.8) est constamment reliée à la source de basse pression.
  11. Entraînement hydraulique selon l'une des revendications 1 à 8, caractérisé en ce que pour faire sortir ou rentrer le piston (3.6), la deuxième chambre de pression (3.7) et la première chambre de pression (3.8) sont soumises alternativement à la pression d'alimentation ou à la pression du réservoir au moyen de l'actionneur.
  12. Procédé de commande d'un entraînement hydraulique avec un vérin de travail (3.5) à double action dont le piston (3.6) présente une première surface de travail (3.15) agissant dans la direction de rentrée et une deuxième surface de travail (3.16) agissant dans la direction de sortie, lesquelles limitent chacune une chambre de pression (3.7, 3.8), dans lequel, pour faire rentrer et sortir le piston (3.6), au moins deux pressions différentes peuvent être appliquées sur au moins une surface de travail (3.15, 3.16) au moyen d'un actionneur,
    caractérisé en ce
    qu'avant une accélération brusque du piston (3.6) du fait de sa décharge de force soudaine, un reflux auparavant relativement non étranglé de fluide hydraulique hors de la première chambre de pression (3.8) limitée par la première surface de travail (3.15) est étranglé de manière renforcée, de sorte que le mouvement de sortie du piston (3.6) est amorti hydrauliquement, l'unité d'actionnement étant commutée en fonction d'une augmentation de pression dans la deuxième chambre de pression (3.7) limitée par la deuxième surface de travail (3.16) de telle sorte qu'elle provoque le reflux étranglé renforcé de fluide hydraulique hors de la première chambre de pression (3.8) limitée par la première surface de travail (3.15) lors d'une augmentation de pression dans la deuxième chambre de pression (3.7).
  13. Procédé selon la revendication 12, caractérisé en ce que l'étranglement renforcé est produit par la fermeture d'une conduite de dérivation (3.14) qui est disposée en parallèle à un étranglement (3.13) dans une première conduite (B), par laquelle le fluide hydraulique peut sortir de la première chambre de pression (3.8), et qui contourne l'étranglement (3.13).
  14. Procédé selon la revendication 13, caractérisé en ce que la fermeture de la conduite de dérivation (3.14) est produite au moyen d'une unité d'actionnement, en particulier sous la forme d'un distributeur 2/2 (3.10), laquelle ou lequel est commuté(e) ou commandé(e) en particulier en fonction du rapport des pressions ou de la différence des pressions entre la pression dans la deuxième chambre de pression (3.7) ou dans une deuxième conduite (A) raccordée à celle-ci et la pression dans la première chambre de pression (3.8), dans une première conduite (B) raccordée à celle-ci ou la pression d'alimentation.
  15. Procédé selon la revendication 12, caractérisé en ce que l'étranglement renforcé est produit par la commande ou la commutation d'une unité d'actionnement qui est disposée dans une première conduite (B), par laquelle du fluide hydraulique est évacué de la première chambre de pression (3.8), et qui est en particulier réalisée sous la forme d'un distributeur 2/2 ayant une première position de commutation avec un étranglement relativement plus fort et une deuxième position de commutation avec un étranglement relativement plus réduit, et l'étranglement renforcé est produit par commutation dans la première position de commutation.
  16. Procédé selon la revendication 15, caractérisé en ce que l'unité d'actionnement est commutée en fonction du rapport des pressions ou de la différence des pressions entre la pression dans la deuxième chambre de pression (3.7) ou dans une deuxième conduite (A) raccordée à celle-ci et la pression dans la première chambre de pression (3.8), dans une première conduite (B) raccordée à celle-ci ou la pression d'alimentation.
EP08758919.8A 2007-06-12 2008-05-31 Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique Active EP2115305B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007027603A DE102007027603A1 (de) 2007-06-12 2007-06-12 Hydraulischer Antrieb, insbesondere für Werkzeugmaschinen, und Verfahren zum Steuern des hydraulischen Antriebs
PCT/EP2008/004349 WO2008151732A1 (fr) 2007-06-12 2008-05-31 Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique

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EP2115305A1 EP2115305A1 (fr) 2009-11-11
EP2115305B1 true EP2115305B1 (fr) 2018-03-21

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DE102007027603A1 (de) 2008-12-18
CN101796307A (zh) 2010-08-04
US20100132349A1 (en) 2010-06-03
US8549983B2 (en) 2013-10-08
CN101796307B (zh) 2014-05-28
EP2115305A1 (fr) 2009-11-11

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