EP1387090B1 - Dispositif à actionnement hydraulique - Google Patents

Dispositif à actionnement hydraulique Download PDF

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Publication number
EP1387090B1
EP1387090B1 EP20030015768 EP03015768A EP1387090B1 EP 1387090 B1 EP1387090 B1 EP 1387090B1 EP 20030015768 EP20030015768 EP 20030015768 EP 03015768 A EP03015768 A EP 03015768A EP 1387090 B1 EP1387090 B1 EP 1387090B1
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EP
European Patent Office
Prior art keywords
pressure
line
pump
hydraulic drive
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20030015768
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German (de)
English (en)
Other versions
EP1387090A3 (fr
EP1387090A2 (fr
Inventor
Michael Bökmann
Norbert Gwozdz
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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Filing date
Publication date
Priority claimed from DE10329067A external-priority patent/DE10329067A1/de
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Priority to EP04029899.4A priority Critical patent/EP1564414B1/fr
Publication of EP1387090A2 publication Critical patent/EP1387090A2/fr
Publication of EP1387090A3 publication Critical patent/EP1387090A3/fr
Application granted granted Critical
Publication of EP1387090B1 publication Critical patent/EP1387090B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0426—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling the number of pumps or parallel valves switched on
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1476—Special return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—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
    • F15B2211/41536—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 being connected to multiple ports of an 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
    • F15B2211/47—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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—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
    • F15B2211/55—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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

Definitions

  • the invention relates to a hydraulic drive for a consumer, in particular for a hydraulic cylinder according to the preamble of patent claim 1.
  • a hydraulic drive for a lifting cylinder known.
  • a bottom-side cylinder space of the lifting cylinder is supplied via a constant pump with variable-speed electric motor with pressure medium from a tank.
  • a piston rod-side annular space of the lifting cylinder is connected to a hydraulic accumulator.
  • the effective in the stroke direction (extension of the cylinder) pressure is thus determined by the constant pump and the effective pressure in the opposite direction by the pressure in the hydraulic accumulator.
  • the direction of rotation is reversed via the control of the fixed displacement pump, so that pressure fluid from the cylinder chamber is flowed into the tank and the cylinder moves in through the pressure in the hydraulic accumulator or annulus and the weight of the load.
  • the fixed displacement pump works as a motor and the electric motor as a generator, so that the power gained can be fed back into the grid.
  • a disadvantage of this solution is that on the one hand the device-technical effort for filling the hydraulic accumulator is relatively high and that on the other hand, the hydraulic accumulator can be charged only in the resting phases, so that the pressure in the hydraulic accumulator during operation of the system fall below a predetermined limit and Thus, the function of the lifting cylinder is no longer guaranteed in the predetermined manner.
  • a disadvantage of this solution is that due to the use of a single-acting cylinder, the retraction movement of the cylinder substantially by the effective Load and speed of the constant-action pump acting as a motor is determined because in the lowering direction - not as in the above-described embodiment - no pressure acts.
  • the invention has the object of developing a hydraulic drive for one of a pumping arrangement and a hydraulic accumulator pressurized with consumers such that the pressure in the hydraulic accumulator can be kept constant with low device complexity.
  • the hydraulic drive has a bypass line via which a pressure line leading from the pumping arrangement to the consumer and a storage line leading from the hydraulic accumulator to the consumer are connected to one another.
  • a flow control valve or a pressure reducing valve is provided, via which pressure medium can flow from the pressure line into the storage line for filling the hydraulic accumulator, so that it is ensured that the hydraulic accumulator can also be charged during the operation of the consumers.
  • the flow control valve may be a - preferably adjustable - throttle or a flow control valve.
  • the consumer is preferably designed as a hydraulic cylinder.
  • the pump assembly is connected via a pressure line to a bottom-side cylinder chamber and the hydraulic accumulator via the storage line to a piston rod side annulus.
  • bypass line via a pressure relief valve with a Tank connected, so that the maximum storage pressure is limited by the value set on the pressure relief valve.
  • a non-return valve opening in the direction of the accumulator line can be provided therein.
  • this bypass line can also be integrated into the piston of the cylinder.
  • the consumer preferably the cylinder is associated with an advantageous embodiment, a displacement sensor, via which the stroke position of the piston is detected and a corresponding control of the pumping arrangement and, if necessary, the throttle device takes place.
  • valve arrangement over which both pumps are connected to the consumer at low consumer pressure and upon reaching a threshold pressure, the pump with the larger displacement is switched to pressureless circulation or the like, so that only the smaller pump effective is.
  • Internal gear pumps are preferably used for the pumps of the pumping arrangement.
  • the hydraulic drive according to the invention can be used particularly advantageously for a bending cylinder of a bending press.
  • the single FIGURE shows a circuit diagram of a hydraulic drive according to the invention for a bending press.
  • a bending press 1 has a double-acting bending cylinder 2, via which a clamped on a machine bed workpiece 4 with the force required for bending can be acted upon.
  • the bending cylinder 2 is a run as an open circuit hydraulic drive with a pumping arrangement 6 and a hydraulic accumulator 8 assigned.
  • pressure medium can be sucked from a tank T and conveyed via a pressure line 10 into a bottom-side cylinder chamber 12 of the bending cylinder 2.
  • the hydraulic accumulator 8 is connected via a storage line 14 with a piston rod side annular space 16 of the bending cylinder 2.
  • the pumping arrangement 6 has a variable-speed drive 18, so that for extending the bending cylinder 2 towards the workpiece 4, pressure medium from the tank T is conveyed via the pump arrangement 6, the pressure line 10 into the cylinder space 12. This effective in the extension direction pressure of the pressure in the hydraulic accumulator 8 corresponding pressure in the annular space 16 counteracts.
  • the direction of rotation of the pumping arrangement 6 is reversed via the variable-speed drive 18, so that pressure medium from the cylinder chamber 12 via the pumping arrangement 6 flows to the tank.
  • the pressure in the hydraulic accumulator 8 then acts in the retraction direction, so that the piston of the bending cylinder 2 is retracted.
  • the pumping arrangement 6 acts as a motor, so that correspondingly the drive 18, for example an asynchronous motor, acts as a generator.
  • the stroke position of the bending cylinder 2 is detected by a displacement sensor 20, so that in response to its signal, the drive of the drive 18 can be carried out.
  • a special feature of the solution according to the invention is that in the embodiment illustrated in the figure, the storage line 14 and the pressure line 10 are connected to each other via a bypass line 22.
  • this bypass line an adjustable throttle device 24 is arranged.
  • the bypass line 22 is further connected via a pressure relief valve 26 to the tank T.
  • the pressure in the hydraulic accumulator 8 is set to a predetermined, relatively low limit.
  • a check valve 28 is provided in the bypass line 22, which opens in the direction of the storage line 14.
  • This check valve 28 prevents pressure fluid from entering the pressure cylinder 10 from the annulus 16 or from the hydraulic accumulator 8 when the bending cylinder 2 retracts and thus the hydraulic accumulator 8 is discharged - in this case, the bending cylinder 2 would stop or slow its return movement.
  • a flow control valve (not shown) may be provided in the bypass line 22, via which the pressure medium volume flow flowing to the storage line 14 is independent of the pressure difference in the pressure line 10 and in the storage line 14.
  • Another alternative solution may be to replace the throttle device 24 and possibly the pressure relief valve 26 by a pressure reducing valve in certain applications.
  • the pressure in the storage line 14 (secondary pressure) is kept constant, the valve increasingly closes with increasing pressure in the storage line and finally compensates only leakage losses in the storage line.
  • the hydraulic accumulator 8 is preceded by a safety valve 56.
  • a pressure medium flow for charging the hydraulic accumulator 8 can be diverted from the pressure line 10 during operation of the bending press, so that it is ensured that it is always charged to the predetermined limit.
  • the pressure relief valve 26 opens upon reaching this limit and thus a small flow of pressure medium via the bypass line 22 to the tank T out, the pump assembly 6 must be operated at a slightly higher speed than is the case with the inventive solutions without bypass line. By this speed increase, a pressure pulsation of the pump is reduced, so that a uniform extension movement of the bending cylinder 2 is ensured.
  • the pumping arrangement 6 consists of two pumps coupled to each other, which are each designed as a constant pump.
  • the left in the figure pump, hereinafter referred to as small pump 30, is designed with a comparatively small displacement, while the other, large pump 32 is designed with a relatively large displacement.
  • Both pumps 30, 32 are coupled together and are driven by the variable speed drive 18.
  • the pressure port of the small pump 30 is connected via a high pressure pump line 34 to the pressure line 10.
  • a pump pressure limiting valve 36 is arranged, that when a maximum pressure in the high-pressure pump line 34 is exceeded, a connection opens to the tank T, so that the pressure delivered by the small pump 30 is limited to this maximum value.
  • From the high-pressure pump line 34 further branches off a Nachsaugtechnisch 38, in which a closing in the direction of the tank T out check valve 40 is arranged.
  • the large pump 32 is connected via a low-pressure pump line 42 and a switching valve 44 to the pressure line 10.
  • this switching valve 44 opens the connection between the low-pressure pump line 42 and the pressure line 10.
  • a control surface of the switching valve 44 acting against the force of a spring 46 is acted upon via a control line 48 with the pressure in the pressure line 10.
  • the switching valve 44 is switched to a switching position in which the low-pressure pump line 42 is connected to the tank T - the large pump 32 is then also connected without pressure circulation.
  • the pressure of the large pump 32 via a further pump pressure relief valve 50 is limited to a maximum value. From the low-pressure pump line 42 branches off a further Nachsaug effet 52 with check valve 54 from.
  • both pumps 30, 32 are driven by the variable-speed drive 18.
  • the switching valve 44 is in its basic position, so that the pressure medium flows of both pumps 30, 32 are added and conveyed via the pressure line 10 into the cylinder chamber 12.
  • the bending cylinder 2 extends at a comparatively high speed and in the cylinder chamber 12, a corresponding pressure builds up.
  • the switching valve 44 is switched to its second switching position, so that the low-pressure pump line 42 is connected to the tank T. From this threshold pressure promotes only the small pump 30 pressure fluid to the bending cylinder 2. That is, to hold the stroke position of the bending cylinder 2 and to build the maximum pressures only the smaller pump 30 is used, so that at such high pressures acting on the return torque is comparatively low and according to the drive 18 can be designed with less torque.
  • bypass line 22 is executed with the associated valve assembly as an independent component. In principle, it is also possible to integrate this Bypassleitugng 22 in the hydraulic cylinder 2. It can the Bypass line 22, for example, pass through the piston, so that by this bypass line with the integrated throttle (24) of the cylinder chamber (12) and the annular space (16) are connected.
  • a hydraulic drive for a consumer preferably for a double-acting cylinder whose pressure chamber is supplied via a pump arrangement with variable-speed drive with pressure medium, while an effective in the opposite direction of the pressure chamber of a hydraulic accumulator is acted upon.
  • pressure medium can be diverted via a bypass line and a flow control valve or a pressure reducing valve of the funded by the pumping arrangement pressure medium flow, so that charging even during operation of the consumer or is possible.
  • the application further discloses a pumping arrangement in which two pumps with different stroke volumes are driven by a common variable-speed drive, wherein at high pressures on the consumer only the pump with a lower displacement is effective, so that the drive can be designed with relatively small torque.

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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 (7)

  1. Entraînement hydraulique pour une charge (2) comprenant deux espaces de pression (12, 16) agissant à l'opposé l'un de l'autre, dont l'un est connecté par le biais d'une conduite de pression (10) à un agencement de pompe (6) de l'entraînement hydraulique, qui présente un entraînement (18) à régime variable, et dont l'autre est connecté par le biais d'une conduite d'accumulateur (14) à un accumulateur hydraulique (8) de l'entraînement hydraulique, et comprenant une conduite de dérivation (22) de l'entraînement hydraulique reliant la conduite de pression (10) à la conduite d'accumulateur (14), caractérisé en ce que dans la conduite de dérivation (22) est disposé(e) un étranglement (24), de préférence réglable, ou une soupape de régulation de flux ou une soupape de réduction de pression.
  2. Utilisation d'un entraînement hydraulique selon la revendication 1, comprenant une charge qui est un cylindre (2) avec un espace de cylindre (12) du côté du fond et un espace annulaire (16) du côté de la tige de piston.
  3. Utilisation d'un entraînement hydraulique selon l'une quelconque des revendications précédentes, dans laquelle une soupape de limitation de pression (26) est disposée dans la conduite de dérivation (22) pour limiter la pression de l'accumulateur.
  4. Utilisation d'un entraînement hydraulique selon l'une quelconque des revendications précédentes, dans laquelle un clapet anti-retour (28) s'ouvrant dans la direction de la conduite d'accumulateur (14) est prévu dans la conduite de dérivation (22).
  5. Utilisation d'un entraînement hydraulique selon l'une quelconque des revendications précédentes, dans laquelle une soupape de sécurité (56) est montée en amont de l'accumulateur hydraulique (8).
  6. Utilisation d'un entraînement hydraulique selon l'une quelconque des revendications précédentes 2 à 5, dans laquelle un capteur de position (20) est associé au cylindre (2).
  7. Entraînement hydraulique selon la revendication 1, dans lequel l'agencement de pompe (6) présente deux pompes à débit constant avec des volumes nominaux différents.
EP20030015768 2002-08-02 2003-07-10 Dispositif à actionnement hydraulique Expired - Lifetime EP1387090B1 (fr)

Priority Applications (1)

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EP04029899.4A EP1564414B1 (fr) 2002-08-02 2003-07-10 Dispositif de commande hydraulique

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DE10235631 2002-08-02
DE10235631 2002-08-02
DE10329067A DE10329067A1 (de) 2002-08-02 2003-06-27 Hydraulischer Antrieb
DE10329067 2003-06-27

Related Child Applications (3)

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EP04029899.4A Division-Into EP1564414B1 (fr) 2002-08-02 2003-07-10 Dispositif de commande hydraulique
EP04029899.4A Division EP1564414B1 (fr) 2002-08-02 2003-07-10 Dispositif de commande hydraulique
EP04029899.4 Division-Into 2004-12-16

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EP1387090A2 EP1387090A2 (fr) 2004-02-04
EP1387090A3 EP1387090A3 (fr) 2005-06-22
EP1387090B1 true EP1387090B1 (fr) 2014-04-30

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DE102005043367B4 (de) * 2005-09-12 2016-09-08 Laeis Gmbh Steuervorrichtung und Steuerverfahren für eine Kolben-Zylinder-Anordnung
IT1391262B1 (it) * 2008-09-23 2011-12-01 Interpump Hydraulics Spa Dispositivo di distribuzione per circuiti idraulici.
TR200906352A2 (tr) * 2009-08-18 2010-12-21 Demi̇rer Teknoloji̇k Si̇stemler Sanayi̇ Ti̇caret Li̇mi̇ted Şi̇rketi̇ Hidrolik abkant preslerde enerji tasarrufu sağlayan bir yapılanma.
TR201008886A2 (tr) 2010-10-27 2011-04-21 Coşkunöz Metal Form Maki̇na Endüstri̇ Ve Ti̇c. A.Ş. Bir servo hidrolik pres
DE102011108285A1 (de) 2010-12-22 2012-06-28 Robert Bosch Gmbh Hydraulischer Antrieb
TR201101488A2 (tr) 2011-02-16 2012-03-21 Ermaksan Maki̇na Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇ Düşük gürültü seviyesine sahip enerji tasarruflu abkant pres
DE102012022871A1 (de) * 2012-11-22 2014-05-22 Hydac System Gmbh Stellvorrichtung
DE102014008114A1 (de) * 2014-06-03 2015-12-03 Liebherr-Aerospace Lindenberg Gmbh Elektrisch betriebene Motor-Pumpeneinheit
CN105673596B (zh) * 2016-04-05 2017-05-10 广东精铟海洋工程股份有限公司 一种具有自动保压功能的双液压控制系统及其试验方法
CN110848181B (zh) * 2019-10-18 2021-04-23 中联重科股份有限公司 液压传动系统和起重机

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AT392674B (de) * 1981-10-01 1991-05-27 Hoerbiger Ventilwerke Ag Einrichtung zum selbsttaetigen rueckstellen eines stellzylinders
DE3330670A1 (de) * 1983-08-25 1985-03-14 J. und H. Büter Maschinenfabrik GmbH, 4472 Haren Doppeltwirkende kolben-zylinder-einheit
DE3524790A1 (de) * 1985-07-11 1987-01-22 Rexroth Mannesmann Gmbh Digitale volumenstromregelung fuer konstantpumpen
DE9407123U1 (de) * 1994-04-29 1994-07-14 Schwarzwaelder Edelputzwerk Gm Vorrichtung zur Geschwindigkeitsregelung hydraulischer Antriebe
DE4439667C2 (de) * 1994-11-07 1998-07-02 Festo Ag & Co Arbeitszylinder
CN1159219A (zh) * 1995-05-16 1997-09-10 特鲁宁格有限公司 具有至少一根液压轴的设备
DE19715157A1 (de) * 1997-04-11 1998-10-15 Rexroth Mannesmann Gmbh Hydraulische Anordnung zur Druckmittelversorgung eines Pressenzylinders, insbesondere einer Kakaopresse
DE19750815B4 (de) * 1997-11-17 2006-09-28 Sms Demag Ag Biegevorrichtung für ein Metallband

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EP1387090A2 (fr) 2004-02-04

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