EP2115305A1 - 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

Info

Publication number
EP2115305A1
EP2115305A1 EP08758919A EP08758919A EP2115305A1 EP 2115305 A1 EP2115305 A1 EP 2115305A1 EP 08758919 A EP08758919 A EP 08758919A EP 08758919 A EP08758919 A EP 08758919A EP 2115305 A1 EP2115305 A1 EP 2115305A1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure chamber
piston
hydraulic
hydraulic drive
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
EP08758919A
Other languages
German (de)
English (en)
Other versions
EP2115305B1 (fr
Inventor
Bert Brahmer
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.)
Voith Patent GmbH
Original Assignee
Voith Patent GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP2115305A1 publication Critical patent/EP2115305A1/fr
Application granted granted Critical
Publication of EP2115305B1 publication Critical patent/EP2115305B1/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
    • F15B11/044—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

  • Hydraulic drive in particular for machine tools, and method for
  • 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.
  • Hydraulic drives for machine tools are known in the art.
  • Figures 1, 2 and 4 relate to previously used arrangements.
  • FIG. 1 shows the basic construction of a conventional hydraulic drive for a punching machine.
  • a pressure supply device comprises in the usual manner shown in FIG. 1
  • Embodiment a constant-displacement pump 1.1 for generating an operating pressure as well as an adjustable to a desired output pressure range first pressure relief valve 1.2.
  • 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.
  • Interruption time coincides with the increased as a result of the so-called cutting stroke extension speed of the piston 1.6, it comes in the second line A to suppress, which in turn lead to disturbing noises and cavitation at the control edges or the housing of the 3-way valve 1.4.
  • FIG. 2 shows the basic construction of a further conventional hydraulic drive similar to that of FIG. 1, however with a 4/3-way valve 2.1 instead of the 3-way valve (3/3-way valve) 1.4 from Figure 1. Also, this 4/3-way valve 2.1, as the 3-way valve 1.4 of Figure 1, also as a continuous valve or switching valve be executed. Notwithstanding the embodiment shown in Figure 1, however, no constant pressure on the first line B and thus the first pressure chamber 1.8 is exercised with the pressure source, but the first pressure chamber 1.8 is always connected to the pressure source when the second pressure chamber 1.7 with the Tank 1.9 is connected, and connected to the tank 1.9, when the second pressure chamber 1.7 is connected to the pressure source. In the middle position of the 4/3-way valve 2.1 are both pressure chambers 1.7, 1.8 from both the pressure source and the tank
  • FIG. 2 The embodiment shown in FIG. 2 is based on the same problems as were presented for the embodiment according to FIG.
  • FIG. 4 shows a path / time graph of the piston 1.6 of the conventional hydraulic drive of FIG.
  • TOS top of sheet
  • BOS bottom of sheet
  • the piston is at top dead center TDC.
  • the equilibrium pressure po prevails.
  • the piston 1.6 is extended with the pre-stroke speed 4.3, the pressure is slightly greater than the equilibrium pressure.
  • EP 0 676 547 A1 describes a
  • Volume control device and a lowering brake valve with a metering orifice over which a predetermined pressure difference is maintained and thereby the speed of the 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.
  • EP 0 676 547 A1 discloses a flow control device that responds to an undesirable volume flow of hydraulic medium that has been adjusted as a result of the process in order to bring the volume flow back to the desired value.
  • the patent DE 196 08 582 B4 describes a hydro-compensator for pressure surge smoothing 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.
  • European patent application EP 1 484209 A1 describes a hydraulic actuating device, 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 object of the invention is achieved by a hydraulic drive having the features of claim 1 and a method having the features of claim 12.
  • Advantageous embodiments of the invention are defined in the dependent claims.
  • 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.
  • 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 it (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 figure 1, or optionally, in particular as in the figure 2, is connected.
  • 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
  • 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 setting unit in the first line or parallel to a throttle point in the first line
  • the setting unit is designed so that it depends on the ratio of the supply pressure to the pressure PA, 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 actuator with the supply pressure or the pressure from the first pressure chamber can be acted upon, while a second control surface of the actuator with the pressure PA in the second pressure chamber can be acted upon, wherein the actuating unit in dependence of the ratio of the first Control applied pressure applied to the pressure exerted on the second control surface in the passage position or blocking position or in unthrottled position or throttle position.
  • 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 the retraction or retraction of 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 Figure 2, 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.
  • Figure 1 shows the basic apparatus design of a hydraulic drive according to the prior art
  • Figure 2 shows the basic apparatus structure of another conventional hydraulic drive
  • Figure 3 shows the basic apparatus structure of a hydraulic drive according to the invention
  • Figure 4 is a path / time graph of the piston of the conventional hydraulic drive of Figure 1; and FIG. 5 shows a path / time graph of the piston of the hydraulic drive according to the invention from FIG. 3.
  • the hydraulic drive according to the invention shown schematically and schematically in FIG. 3 comprises according to the embodiments shown in FIGS. 1 and 2 a constant displacement pump 3.1 for generating an operating pressure and a pressure limiting valve 3.2 adjustable to a desired outlet pressure range.
  • 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 on the annular first via the first line B.
  • Working surface 3.15 of the piston 3.6 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 is known from the documents DE 10 2004 024 126 A1 and EP 1 138 958 B1.
  • a controllable throttle valve or, as present, 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.
  • Piston extension speed is reduced.
  • 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 unged rosselten and in the second switching position a has throttled passage.
  • This 2/2-way valve (not shown) can be controlled in accordance with the 2/2-way valve 3.10 of Figure 3, according to the invention a throttled backflow of hydraulic medium from the limited of the first working surface 3.15 first pressure chamber 3.8 optional, 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 into the first pressure chamber 3.8, the latter during a retraction movement of the piston 3.6 be provided, in particular by automatic switching or holding the 2/2
  • FIG. 5 which relates to the hydraulic drive according to the invention of FIG. 3, the time profile of the travel of the piston 3.6 and of the pressure p A prevailing in the second pressure chamber 3.7 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 due to the throttling effect only to a relatively small

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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)

Abstract

L'invention concerne un entraînement hydraulique, en particulier pour une presse, une machine d'estampage ou de poinçonnage, avec un cylindre de travail (3, 5) à double action dont le piston (3.1) présente une première surface de travail (3.15) agissant dans la direction d'enfoncement et une deuxième surface de travail (3.16) agissant dans la direction de sortie, lesquelles délimitent un espace de pression. Pour faire entrer et sortir le piston dans et hors du cylindre de travail, on peut appliquer sur au moins l'une des surfaces de travail au moins deux pressions différentes par le biais d'un actionneur (3.4). L'entraînement hydraulique présente une unité de commande (3.10) qui permet, de manière sélective, un reflux étranglé de fluide hydraulique hors du premier espace de pression (3.8) limité par la première surface de travail. L'invention est caractérisée en ce que l'entraînement présente des moyens de commande (3.11, 3.12) avec lesquels, avant une accélération par saccade du piston du fait de la décharge de force soudaine, l'unité de commande peut être commandée de telle sorte que l'on obtienne un amortissement hydraulique du mouvement du piston par un étranglement du reflux de fluide hydraulique hors du premier espace de pression, provoqué directement ou indirectement par l'unité de commande.
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

Publications (2)

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

Family

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Application Number Title Priority Date Filing Date
EP08758919.8A Active EP2115305B1 (fr) 2007-06-12 2008-05-31 Entraînement hydraulique, en particulier pour machines-outils, et procédé pour commander l'entraînement hydraulique

Country Status (5)

Country Link
US (1) US8549983B2 (fr)
EP (1) EP2115305B1 (fr)
CN (1) CN101796307B (fr)
DE (1) DE102007027603A1 (fr)
WO (1) WO2008151732A1 (fr)

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DE102009048483B4 (de) * 2009-09-29 2012-08-16 Voith Patent Gmbh Schnittschlagdämpfung
CN102287570B (zh) * 2011-06-22 2012-10-03 北京北大先锋科技有限公司 一种提高气动阀门开关速度的方法
DE102012104125A1 (de) * 2012-05-10 2013-11-14 Dieffenbacher GmbH Maschinen- und Anlagenbau Verfahren zum Betreiben einer hydraulischen Presse und eine hydraulische Presse
EP2711560B1 (fr) * 2012-09-21 2019-06-12 HAWE Hydraulik SE Entraînement hydraulique pour un outil pouvant être actionné hydrauliquement
DE102012021544B4 (de) * 2012-10-29 2014-07-10 Terex Cranes Germany Gmbh Teleskopiereinheit mit Zusatzfunktion
CN102979769B (zh) * 2012-12-05 2015-08-05 中联重科股份有限公司 液压缸的伸缩控制回路
JP6250515B2 (ja) 2014-10-07 2017-12-20 日立建機株式会社 建設機械の油圧制御装置
ES2839075T3 (es) 2015-07-06 2021-07-05 Feintool Int Holding Ag Procedimiento y dispositivo para reducir el impacto de corte en una prensa de corte de precisión
US10914322B1 (en) 2016-05-19 2021-02-09 Steven H. Marquardt Energy saving accumulator circuit
US11015624B2 (en) 2016-05-19 2021-05-25 Steven H. Marquardt Methods and devices for conserving energy in fluid power production
US10550863B1 (en) 2016-05-19 2020-02-04 Steven H. Marquardt Direct link circuit
DK179219B1 (en) * 2016-05-26 2018-02-12 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland Fuel or lubrication pump for a large two-stroke compression-ignited internal combustion engine
CN110630574A (zh) * 2019-09-03 2019-12-31 广州通达汽车电气股份有限公司 减速装置、气缸系统及其控制方法
US11391302B2 (en) * 2020-03-16 2022-07-19 Woodward, Inc. Automatic air bleeding system for hydraulics
DE102021101539A1 (de) * 2021-01-25 2022-07-28 Langenstein & Schemann Gmbh Hydraulische Umformmaschine zum Pressen von Werkstücken, insbesondere Schmiedehammer, und Verfahren zum Betreiben einer hydraulischen Umformmaschine, insbesondere eines Schmiedehammers
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Also Published As

Publication number Publication date
WO2008151732A1 (fr) 2008-12-18
EP2115305B1 (fr) 2018-03-21
CN101796307B (zh) 2014-05-28
US20100132349A1 (en) 2010-06-03
US8549983B2 (en) 2013-10-08
CN101796307A (zh) 2010-08-04
DE102007027603A1 (de) 2008-12-18

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