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EP1564414B1 - Hydraulic drive - Google Patents

Hydraulic drive Download PDF

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Publication number
EP1564414B1
EP1564414B1 EP04029899.4A EP04029899A EP1564414B1 EP 1564414 B1 EP1564414 B1 EP 1564414B1 EP 04029899 A EP04029899 A EP 04029899A EP 1564414 B1 EP1564414 B1 EP 1564414B1
Authority
EP
European Patent Office
Prior art keywords
pressure
line
pump
hydraulic
consumer
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
EP04029899.4A
Other languages
German (de)
French (fr)
Other versions
EP1564414A1 (en
Inventor
Michael Bökmann
Norbert Gwozdz
Manfred Mitze
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
MAE Maschinen und Apparatebau Goetzen GmbH
Original Assignee
Bosch Rexroth AG
MAE Maschinen und Apparatebau Goetzen 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 Bosch Rexroth AG, MAE Maschinen und Apparatebau Goetzen GmbH filed Critical Bosch Rexroth AG
Priority claimed from EP20030015768 external-priority patent/EP1387090B1/en
Publication of EP1564414A1 publication Critical patent/EP1564414A1/en
Application granted granted Critical
Publication of EP1564414B1 publication Critical patent/EP1564414B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • 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
    • 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
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and 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
    • F15B2211/20576—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 problem with the known hydraulic drives is that for a quick extension of the cylinder, a comparatively large pump is required. When pressure build-up in the hydraulic cylinder, a large restoring torque is generated at this large pump, so that the variable-speed drive must be designed so that it can muster the appropriate torque.
  • Such strong electric motors are very expensive and require a considerable volume of construction. Furthermore, the losses in such strong electric motors are relatively large, so that one endeavors to use the smallest possible engines.
  • 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 in a compact low-cost construction, a fast extension movement is possible.
  • valve arrangement over which both pumps are connected to the consumer at low consumer pressure and when 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 can be acted upon with the force required for bending.
  • 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 pump assembly 6 is reversed via the variable-speed drive 18, so that pressure fluid flows from the cylinder chamber 12 via the pumping arrangement 6 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.
  • the storage line 14 and the pressure line 10 are connected to one another via a bypass line 22.
  • a bypass line 22 In 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 In the bypass line 22 is still still still a check valve 28 is provided, 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.
  • the throttle device 24 is formed in the bypass line 22 as a flow control valve (not shown) 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.
  • the hydraulic accumulator 8 is preceded by a safety valve 30.
  • 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 low pressure medium flow over the Bypass line 22 is formed toward the tank T out, the pump assembly 6 must be operated at a slightly higher speed than is the case with the 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 pump assembly 6 consists of two coupled pumps, which are each designed as a constant pump.
  • the left in the figure pump, hereinafter referred to as small pump 31, is designed with a comparatively small displacement, while the other, large pump 32 is designed with a comparatively large displacement.
  • Both pumps 31, 32 are coupled together and are driven by the variable speed drive 18.
  • the pressure port of the small pump 31 is connected via a high-pressure pump line 34 to the pressure line 10.
  • a pump pressure limiting valve 36 is arranged that opens a connection to the tank T out when a maximum pressure in the high-pressure pump line 34 is exceeded, so that the pressure supplied by the small pump 31 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 in its spring-biased home position, the connection between the low-pressure pump line 42 and the pressure line 10. A counter to the force of a spring 46 acting control surface of the switching valve 44 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. Similar to the small pump 31, the pressure of the large pump 32 is limited to a maximum value via another pump pressure limiting valve 50. From the low-pressure pump line 42 branches off a further Nachsaug effet 52 with check valve 54 from.
  • both pumps 31, 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 31, 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 31 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 with the associated valve arrangement designed as an independent component.
  • this bypass line 22 in the hydraulic cylinder 2.
  • 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.
  • the pumping arrangement has two pumps with different stroke volumes, which are driven by the 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)

Description

Die Erfindung betrifft einen hydraulischen Antrieb für einen Verbraucher, insbesondere für einen Hydrozylinder gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic drive for a consumer, in particular for a hydraulic cylinder according to the preamble of patent claim 1.

Aus der US 6,379,119 ist ein hydraulischer Antrieb für einen Hubzylinder bekannt. Ein bodenseitiger Zylinderraum des Hubzylinders wird über eine konstante Pumpe mit drehzahlvariablem Elektromotor mit Druckmittel aus einem Tank versorgt. Ein kolbenstangenseitiger Ringraum der Hubzylinders ist mit einem Hydrospeicher verbunden. Der in Hubrichtung (Ausfahren des Zylinders) wirksame Druck wird somit durch die Konstantpumpe und der in Gegenrichtung wirksame Druck durch den Druck im Hydrospeicher bestimmt. Zum Einfahren des Hydrozylinders wird über die Steuerung der Konstantpumpe die Drehrichtung umgekehrt, so dass Druckmittel aus dem Zylinderraum in den Tank strömt wird und der Zylinder durch den Druck im Hydrospeicher bzw. Ringraum und die Gewichtskraft der Last einfährt.From the US 6,379,119 is 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. To retract the hydraulic cylinder, 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.

Bei Umkehr der Drehzahl arbeitet somit die Konstantpumpe als Motor und der Elektromotor als Generator, so dass die gewonnene Leistung ins Netz zurückgespeist werden kann.When reversing the speed thus 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.

Das Befüllen des Hydrospeichers erfolgt über ein Schaltventil, das im normalen Betrieb des Hubzylinders in einer Sperrstellung ist und in einer Ruhephase des oder der an die Konstantpumpe angeschlossenen Verbraucher in eine Durchgangsstellung gebracht wird, so dass der Hydrospeicher über die Konstantpumpe aufgeladen werden kann.The filling of the hydraulic accumulator via a switching valve, which is in a blocking position during normal operation of the lifting cylinder and is brought in a resting phase of or connected to the fixed displacement pump consumers in a passage position, so that the Hydraulic accumulator can be charged via the constant pump.

In der DE 196 31 804 A1 ist ein hydraulischer Antrieb für einen Hubzylinder eines Aufzugs offenbart, der als Plungerzylinder ausgeführt ist. Zum Anheben einer Last wird der Zylinderraum über eine Konstantpumpe mit Druckmittel beaufschlagt, die von einem drehzahlvariablen Antrieb angetrieben ist. Um eine Druckpulsation bei niedriger Drehzahl der Pumpe und eine Verbesserung der Pumpenschmierung zu ermöglichen, ist eine sich zwischen dem Druckanschluß der Pumpe und dem Hydrozylinder erstreckende Druckleitung über eine verstellbare Drossel mit dem Tank verbunden. Über diese Drossel wird bei geringen Drehzahlen ein Druckmittelstrom zum Tank abgezweigt, so dass die Pumpe mit höherer Drehzahl laufen muß, als dies ohne geöffnete Drossel der Fall wäre. Durch diese Erhöhung der Drehzahl ist eine gleichmäßig Druckmittelversorgung des Verbrauchers und Schmierung der Konstantpumpe gewährleistet. Zum Absenken der Last wird die Drehrichtung der Konstantpumpe umgekehrt, so dass diese als Motor und der angeschlossene Elektromotor als Generator arbeitet.In the DE 196 31 804 A1 discloses a hydraulic drive for a lift cylinder of an elevator, which is designed as a plunger cylinder. To lift a load, the cylinder chamber is acted upon by a constant pump with pressure medium, which is driven by a variable-speed drive. In order to allow a pressure pulsation at low speed of the pump and an improvement of the pump lubrication, a pressure line extending between the pressure port of the pump and the hydraulic cylinder is connected via an adjustable throttle with the tank. About this throttle, a flow of pressure medium is diverted to the tank at low speeds, so that the pump must run at a higher speed than would be the case without the throttle open. This increase in the speed ensures uniform pressure medium supply to the consumer and lubrication of the constant pump. To lower the load, the direction of rotation of the constant pump is reversed so that it works as a motor and the connected electric motor as a generator.

Ein Problem bei den bekannten hydraulischen Antrieben besteht darin, dass zum schnellen Ausfahren des Zylinders eine vergleichsweise große Pumpe erforderlich ist. Bei Druckaufbau im Hydrozylinder wird an dieser großen Pumpe ein großes Rückstellmoment erzeugt, so dass der drehzahlvariable Antrieb so ausgelegt werden muß, dass er das entsprechende Drehmoment aufbringen kann. Derartige starke Elektromotoren sind sehr teuer und beanspruchen ein erhebliches Bauvolumen. Desweiteren sind die Verluste bei derart starken Elektromotoren relativ groß, so dass man bestrebt ist, möglichst kleine Motoren einzusetzen.A problem with the known hydraulic drives is that for a quick extension of the cylinder, a comparatively large pump is required. When pressure build-up in the hydraulic cylinder, a large restoring torque is generated at this large pump, so that the variable-speed drive must be designed so that it can muster the appropriate torque. Such strong electric motors are very expensive and require a considerable volume of construction. Furthermore, the losses in such strong electric motors are relatively large, so that one endeavors to use the smallest possible engines.

Der Erfindung liegt die Aufgabe zugrunde, einen hydraulischen Antrieb für einen von einer Pumpanordnung und einem Hydrospeicher mit Druck beaufschlagten Verbraucher derart weiterzubilden, dass bei kompakter billiger Bauweise eine schnelle Ausfahrbewegung ermöglicht ist.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 in a compact low-cost construction, a fast extension movement is possible.

Diese Aufgabe wird durch einen hydraulischen Antrieb mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by a hydraulic drive having the features of patent claim 1.

Um diesen gegensätzlichen Anforderungen (schnelle Ausfahrbewegung - starker Elektromotor, große Pumpe; kompakte, billige Bauweise und geringe Verlustleistung - kleiner Motor) zu genügen, wird bei dem erfindungsgemäßen hydraulischen Antrieb eine Pumpanordnung verwendet werden, die zwei miteinander gekoppelte Pumpen mit unterschiedlichen Hubvolumina hat.To meet these conflicting requirements (fast extension movement - strong electric motor, large pump, compact, inexpensive construction and low power loss - small motor), in the hydraulic drive according to the invention, a pumping arrangement will be used which has two coupled pumps with different stroke volumes.

Im Hochdruckbereich wirkt nur die kleinere Pumpe, so dass die Verluste verringert und ein vergleichsweise kleiner drehzahlvariabler Antrieb einsetzbar ist. Zum schnellen Ausfahren und zum Druckaufbau wirken beide Pumpen parallel.In the high pressure range, only the smaller pump acts, so that the losses are reduced and a comparatively small variable-speed drive can be used. For fast extension and pressure build-up, both pumps work in parallel.

Dies wird bei einer vorteilhaften Variante durch eine Ventilanordnung erreicht, über die bei geringem Verbraucherdruck beide Pumpen mit den Verbraucher verbunden sind und bei Erreichen eines Schwelldruckes die Pumpe mit dem größeren Hubvolumen auf drucklosen Umlauf oder dergleichen geschaltet wird, so dass nur noch die kleinere Pumpe wirksam ist.This is achieved in an advantageous variant by a valve arrangement over which both pumps are connected to the consumer at low consumer pressure and when 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.

Die Verwendung von Pumpanordnungen mit zwei unterschiedlich großen Pumpen ist per se bereits aus der DE 35 24 790 A1 und der DE 197 15 157 A1 bekannt. Bei der erstgenannten Lösung ist die kleinere Pumpe jedoch alleine zur Versorgung eines Hochdruckverbrauchers vorgesehen, während beide Pumpen gemeinsam einen anderen, mit geringerem Druck arbeitenden Verbraucher versorgen. Bei der in der DE 197 15 157 A1 offenbarten Lösung ist eine der Pumpen eine Verstellpumpe, so dass ein entsprechend hoher vorrichtungstechnischer Aufwand erforderlich ist. Keine der beiden vorgenannten Lösungen offenbart die Verwendung von zwei unterschiedlich großen Konstantpumpen in Verbindung mit einem drehzahlvariablen Antrieb.The use of pump assemblies with two pumps of different sizes is already out of the box per se DE 35 24 790 A1 and the DE 197 15 157 A1 known. In the former solution, however, the smaller pump is provided alone to supply a high-pressure consumer, while both pumps together supply another, working with lower pressure consumer. When in the DE 197 15 157 A1 disclosed solution, one of the pumps is a variable, so that a correspondingly high device complexity is required. Neither of the two aforementioned solutions discloses the use of two different sized constant displacement pumps in conjunction with a variable speed drive.

Für die Pumpen der Pumpanordnung werden vorzugsweise Innenzahnradpumpen verwendet.Internal gear pumps are preferably used for the pumps of the pumping arrangement.

Der erfindungsgemäße hydraulische Antrieb läßt sich besonders vorteilhaft für einen Biegezylinder einer Biegepresse einsetzen.The hydraulic drive according to the invention can be used particularly advantageously for a bending cylinder of a bending press.

Ein bevorzugtes Ausführungsbeispiel der Erfindung wird im folgenden anhand schematischer Zeichnungen näher erläutert.A preferred embodiment of the invention will be explained in more detail below with reference to schematic drawings.

Die einzige Figur zeigt ein Schaltschema eines erfindungsgemäßen hydraulischen Antriebs für eine Biegepresse.The single FIGURE shows a circuit diagram of a hydraulic drive according to the invention for a bending press.

Eine Biegepresse 1 hat einen doppeltwirkend ausgeführten Biegezylinder 2, über den ein auf einem Maschinenbett aufgespanntes Werkstück 4 mit der zum Biegen erforderlichen Kraft beaufschlagbar ist. Dem Biegezylinder 2 ist ein als offener Kreislauf ausgeführter hydraulischer Antrieb mit einer Pumpanordnung 6 und einem Hydrospeicher 8 zugeordnet. Mittels der Pumpanordnung 6 kann Druckmittel aus einem Tank T angesaugt und über eine Druckleitung 10 in einen bodenseitigen Zylinderraum 12 des Biegezylinders 2 gefördert werden. Der Hydrospeicher 8 ist über eine Speicherleitung 14 mit einem kolbenstangenseitigen Ringraum 16 des Biegezylinders 2 verbunden. Die Pumpanordnung 6 hat einen drehzahlvariablen Antrieb 18, so dass zum Ausfahren des Biegezylinders 2 zum Werkstück 4 hin Druckmittel aus dem Tank T über die Pumpanordnung 6, die Druckleitung 10 in den Zylinderraum 12 gefördert wird. Diesem in Ausfahrrichtung wirksamen Druck wirkt der dem Druck im Hydrospeicher 8 entsprechende Druck im Ringraum 16 entgegen. Zum Einfahren des Biegezylinders 2 wird die Drehrichtung der Pumpanordnung 6 über den drehzahlvariablen Antrieb 18 umgekehrt, so dass Druckmittel aus dem Zylinderraum 12 über die Pumpanordnung 6 zum Tank abströmt. Der Druck im Hydrospeicher 8 wirkt dann in Einfahrrichtung, so dass der Kolben des Biegezylinders 2 eingefahren wird. Bei diesem Einfahren wirkt die Pumpanordnung 6 als Motor, so dass entsprechend der Antrieb 18, beispielsweise ein Asynchronmotor, als Generator wirkt.A bending press 1 has a double-acting bending cylinder 2, via which a clamped on a machine bed workpiece 4 can be acted upon with the force required for bending. The bending cylinder 2 is a run as an open circuit hydraulic drive with a pumping arrangement 6 and a hydraulic accumulator 8 assigned. By means of the pumping arrangement 6, 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. For retracting the bending cylinder 2, the direction of rotation of the pump assembly 6 is reversed via the variable-speed drive 18, so that pressure fluid flows from the cylinder chamber 12 via the pumping arrangement 6 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. During this retraction, the pumping arrangement 6 acts as a motor, so that correspondingly the drive 18, for example an asynchronous motor, acts as a generator.

Die Hubposition des Biegezylinders 2 wird über einen Wegmesssensor 20 erfaßt, so dass in Abhängigkeit von dessen Signal die Ansteuerung des Antriebs 18 erfolgen kann.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.

Die vorbeschriebenen Bauelemente sind im Prinzip auch bei den Lösungen vorhanden, die in der Beschreibungseinleitung beschrieben sind. Erfindungsgemäß sind die Speicherleitung 14 und die Druckleitung 10 über eine Bypassleitung 22 miteinander verbunden. In dieser Bypassleitung ist eine verstellbare Drosseleinrichtung 24 angeordnet. Die Bypassleitung 22 ist desweiteren über ein Druckbegrenzungsventil 26 mit dem Tank T verbunden. Über das Druckbegrenzungsventil 26 wird der Druck im Hydrospeicher 8 auf einen vorbestimmten, vergleichsweise geringen Grenzwert eingestellt. In der Bypassleitung 22 ist desweiteren noch ein Rückschlagventil 28 vorgesehen, das in Richtung zur Speicherleitung 14 öffnet. Dieses Rückschlagventil 28 verhindert, dass beim Einfahren des Biegezylinders 2 Druckmittel vom Ringraum 16 bzw. vom Hydrospeicher 8 in die Druckleitung 10 einströmt und somit der Hydrospeicher 8 entladen wird - in diesem Fall würde der Biegezylinder 2 stehen bleiben bzw. dessen Rückstellbewegung verlangsamt. Erfindungsgemäß ist die Drosseleinrichtung 24 in der der Bypassleitung 22 als ein Stromregelventil (nicht gezeigt) gebildet, über das der der Speicherleitung 14 zufließende Druckmittelvolumenstrom unabhängig von der Druckdifferenz in der Druckleitung 10 und in der Speicherleitung 14 ist.The above-described components are in principle also present in the solutions described in the introduction to the description. According to the invention, the storage line 14 and the pressure line 10 are connected to one another via a bypass line 22. In 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. About the pressure relief valve 26, the pressure in the hydraulic accumulator 8 is set to a predetermined, relatively low limit. In the bypass line 22 is still still a check valve 28 is provided, 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. According to the invention, the throttle device 24 is formed in the bypass line 22 as a flow control valve (not shown) 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.

Eine Alternativlösung ist erfindungsgemäß, die Drosseleinrichtung 24 und ggf. das Druckbegrenzungsventil 26 durch ein Druckminderventil zu ersetzen. Durch dieses Ventil wird der Druck in der Speicherleitung 14 (Sekundärdruck) konstant gehalten, wobei das Ventil bei steigendem Druck in der Speicherleitung zunehmend schließt und schließlich nur noch Leckageverluste in der Speicherleitung ausgleicht.An alternative solution is according to the invention, to replace the throttle device 24 and possibly the pressure relief valve 26 by a pressure reducing valve. By this valve, 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.

Bei dem dargestellten Ausführungsbeispiel ist dem Hydrospeicher 8 ein Sicherheitsventil 30 vorgeschaltet. Durch geeignete Einstellung des Öffnungsquerschnitts der Drosseleinrichtung 24 kann auch im Betrieb der Biegepresse ein Druckmittelstrom zum Aufladen des Hydrospeichers 8 von der Druckleitung 10 abgezweigt werden, so dass sichergestellt ist, dass dieser stets auf den vorbestimmten Grenzwert aufgeladen ist. Da das Druckbegrenzungsventil 26 bei Erreichen dieses Grenzwerts öffnet und somit ein geringer Druckmittelstrom über die Bypassleitung 22 zum Tank T hin entsteht, muß die Pumpanordnung 6 mit etwas höherer Drehzahl betrieben werden, als dies bei den Lösungen ohne Bypassleitung der Fall ist. Durch diese Drehzahlerhöhung wird eine Druckpulsation der Pumpe verringert, so dass eine gleichmäßige Ausfahrbewegung des Biegezylinders 2 gewährleistet ist.In the illustrated embodiment, the hydraulic accumulator 8 is preceded by a safety valve 30. By suitable adjustment of the opening cross section of the throttle device 24, 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. Since the pressure relief valve 26 opens upon reaching this limit and thus a low pressure medium flow over the Bypass line 22 is formed toward the tank T out, the pump assembly 6 must be operated at a slightly higher speed than is the case with the 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.

Eine Besonderheit des in der Figur dargestellten hydraulischen Antrieb besteht darin, dass die Pumpanordnung 6 erfindungsgemäß aus zwei miteinander gekoppelten Pumpen besteht, die jeweils als Konstantpumpe ausgeführt sind. Die in der Figur linke Pumpe, im folgenden kleine Pumpe 31 genannt, ist mit einem vergleichsweise geringen Hubvolumen ausgeführt, während die andere, große Pumpe 32 mit einem vergleichsweise großem Hubvolumen ausgeführt ist. Beide Pumpen 31, 32 sind miteinander gekoppelt und werden von dem drehzahlvariablen Antrieb 18 angetrieben. Der Druckanschluß der kleinen Pumpe 31 ist über eine Hochdruckpumpenleitung 34 mit der Druckleitung 10 verbunden. In dieser Hochdruckpumpenleitung 34 ist ein Pumpen-Druckbegrenzungsventil 36 angeordnet, dass bei Überschreiten eines Maximaldrucks in der Hochdruckpumpenleitung 34 eine Verbindung zum Tank T hin aufsteuert, so dass der von der kleinen Pumpe 31 gelieferte Druck auf diesen Maximalwert begrenzt ist. Von der Hochdruckpumpenleitung 34 zweigt desweiteren eine Nachsaugleitung 38 ab, in der eine in Richtung zum Tank T hin schliessende Rückschlagventil 40 angeordnet ist.A special feature of the hydraulic drive shown in the figure is that the pump assembly 6 according to the invention consists of two coupled pumps, which are each designed as a constant pump. The left in the figure pump, hereinafter referred to as small pump 31, is designed with a comparatively small displacement, while the other, large pump 32 is designed with a comparatively large displacement. Both pumps 31, 32 are coupled together and are driven by the variable speed drive 18. The pressure port of the small pump 31 is connected via a high-pressure pump line 34 to the pressure line 10. In this high-pressure pump line 34, a pump pressure limiting valve 36 is arranged that opens a connection to the tank T out when a maximum pressure in the high-pressure pump line 34 is exceeded, so that the pressure supplied by the small pump 31 is limited to this maximum value. From the high-pressure pump line 34 further branches off a Nachsaugleitung 38, in which a closing in the direction of the tank T out check valve 40 is arranged.

Die große Pumpe 32 ist über eine Niederdruckpumpenleitung 42 und ein Schaltventil 44 mit der Druckleitung 10 verbunden. Dieses Schaltventil 44 öffnet in seiner federvorgespannten Grundposition die Verbindung zwischen der Niederdruckpumpenleitung 42 und der Druckleitung 10. Eine entgegen der Kraft einer Feder 46 wirkende Steuerfläche des Schaltventils 44 wird über eine Steuerleitung 48 mit dem Druck in der Druckleitung 10 beaufschlagt. Bei Ansteigen des Drucks in der Druckleitung 10 auf einen vorbestimmten Schwellwert, wird das Schaltventil 44 in eine Schaltposition umgeschaltet, in der die Niederdruckpumpenleitung 42 mit dem Tank T verbunden ist - die große Pumpe 32 ist dann auch drucklosen Umlauf geschaltet. Ähnlich wie bei der kleinen Pumpe 31 wird der Druck der großen Pumpe 32 über ein weiteres Pumpen-Druckbegrenzungsventil 50 auf einen Maximalwert begrenzt. Von der Niederdruckpumpenleitung 42 zweigt eine weitere Nachsaugleitung 52 mit Rückschlagventil 54 ab.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 in its spring-biased home position, the connection between the low-pressure pump line 42 and the pressure line 10. A counter to the force of a spring 46 acting control surface of the switching valve 44 is acted upon via a control line 48 with the pressure in the pressure line 10. When the pressure in the pressure line 10 rises to a predetermined threshold, 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. Similar to the small pump 31, the pressure of the large pump 32 is limited to a maximum value via another pump pressure limiting valve 50. From the low-pressure pump line 42 branches off a further Nachsaugleitung 52 with check valve 54 from.

Zu Beginn der Ausfahrbewegung des Biegezylinders 2 werden beide Pumpen 31, 32 vom drehzahlvariablen Antrieb 18 angetrieben. Das Schaltventil 44 befindet sich in seiner Grundposition, so dass die Druckmittelströme beider Pumpen 31, 32 addiert und über die Druckleitung 10 in den Zylinderraum 12 gefördert werden. Der Biegezylinder 2 fährt mit vergleichweise hoher Geschwindigkeit aus und im Zylinderraum 12 baut sich ein entsprechender Druck auf. Bei Erreichen des Schwelldrucks in der Druckleitung 10 wird das Schaltventil 44 in seine zweite Schaltposition umgeschaltet, so dass die Niederdruckpumpenleitung 42 mit dem Tank T verbunden ist. Ab diesem Schwelldruck fördert nur noch die kleine Pumpe 31 Druckmittel zum Biegezylinder 2. D.h., zum Halten der Hubposition des Biegezylinders 2 und zum Aufbau der Maximaldrücke wird lediglich die kleinere Pumpe 30 verwendet, so dass das bei derart hohen Drücken, auf die Pumpe wirkende Rückstellmoment vergleichsweise gering ist und entsprechend der Antrieb 18 mit geringerem Drehmoment ausgelegt werden kann.At the beginning of the extension movement of the bending cylinder 2, both pumps 31, 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 31, 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. Upon reaching the threshold pressure in the pressure line 10, 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 31 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.

Beim vorbeschriebenen Ausführungsbeispiel ist die Bypassleitung 22 mit der dazugehörigen Ventilanordnung als eigenständiges Bauelement ausgeführt. Prinzipiell ist es auch möglich diese Bypassleitung 22 in den Hydrozylinder 2 zu integrieren. Dabei kann die Bypassleitung 22 beispielsweise den Kolben durchsetzen, so dass durch diese Bypassleitung mit der integrierten Drossel (24) der Zylinderraum (12) und der Ringraum (16) verbunden sind.In the above-described embodiment, the bypass line 22 with the associated valve arrangement designed as an independent component. In principle, it is also possible to integrate this bypass line 22 in the hydraulic cylinder 2. In this case, 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.

Offenbart ist ein hydraulischer Antrieb für einen Verbraucher, vorzugsweise für einen doppeltwirkenden Zylinder, dessen einer Druckraum über eine Pumpanordnung mit drehzahlvariablen Antrieb mit Druckmittel versorgbar ist, während ein in Gegenrichtung wirksamer Druckraum mit dem Druck eines Hydrospeichers beaufschlagt ist. Die Pumpanordnung hat zwei Pumpen mit unterschiedlichen Hubvolumina, die von dem gemeinsamen drehzahlvariablen Antrieb angetrieben werden, wobei bei hohen Drücken am Verbraucher nur noch die Pumpe mit geringerem Hubvolumen wirksam ist, so dass der Antrieb mit vergleichsweise kleinem Drehmoment ausgelegt werden kann.Disclosed is 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. The pumping arrangement has two pumps with different stroke volumes, which are driven by the 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.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Biegepressebending press
22
Biegezylinderbending cylinders
44
Werkstückworkpiece
66
Pumpanordnungpump assembly
88th
Hydrospeicherhydraulic accumulator
1010
Druckleitungpressure line
1212
Zylinderraumcylinder space
1414
Speicherleitungstorage line
1616
Ringraumannulus
1818
Antriebdrive
2020
WegmesssensorDisplacement
2222
Bypassleitungbypass line
2424
Drosseleinrichtungthrottling device
2626
DruckbegrenzungsventilPressure relief valve
2828
Rückschlagventilcheck valve
3030
Sicherheitsventilsafety valve
3131
kleine Pumpesmall pump
3232
große Pumpebig pump
3434
HochdruckpumpenleitungHigh-pressure pump line
3636
Pumpen-DruckbegrenzungsventilPump pressure relief valve
3838
Nachsaugleitungsubsequent suction
4040
Rückschlagventilcheck valve
4242
NiederdruckpumpenleitungLow-pressure pump line
4444
Schaltventilswitching valve
4646
Federfeather
4848
Steuerleitungcontrol line
5050
weiteres Pumpen-Druckbegrenzungsventilanother pump pressure relief valve
5252
weitere Nachsaugleitungfurther suction line
5454
Rückschlagventilcheck valve

Claims (4)

  1. Hydraulic drive for a consumer (2) having two pressure spaces (12, 16) which act in opposite directions, wherein the drive comprises a pump arrangement (6) having a variable-speed drive (18) and a pressure line (10) connected to the pump arrangement (6), wherein the pressure line (10) is configured to supply the first pressure space (12) with a pressurizing agent, wherein the hydraulic drive comprises a hydraulic accumulator (8) and an accumulator line (14) connected to the hydraulic accumulator (8), wherein the accumulator line (14) is configured to supply the second pressure space (12) with a pressurizing agent, wherein the pump arrangement (6) has two fixed displacement pumps (31, 32) with different stroke volumes which can also be operated as hydraulic motor, which are driven by the common variable-speed drive (18), and wherein the hydraulic drive comprises a bypass line (22) that connects the pressure line (10) to the accumulator line (14), wherein a flow-control valve (24) or pressure reducing valve is arranged in the bypass line (22).
  2. Hydraulic drive according to patent claim 1, having a valve assembly (44) via which both fixed displacement pumps (31, 32) are connected to the consumer (2) at low consumer pressure, wherein only the fixed displacement pump (31) with the smaller stroke volume is connected to the consumer (2) when a threshold pressure is reached at the consumer (2).
  3. Hydraulic drive according to patent claim 1 or 2, wherein the fixed displacement pumps (31, 32) are internal gear pumps.
  4. Hydraulic drive according to one of patent claims 2 to 3, wherein the consumer is a bending cylinder (2) of a bending press (1).
EP04029899.4A 2002-08-02 2003-07-10 Hydraulic drive Expired - Lifetime EP1564414B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10235631 2002-08-02
DE10235631 2002-08-02
DE10329067 2003-06-27
DE10329067A DE10329067A1 (en) 2002-08-02 2003-06-27 Hydraulic drive
EP20030015768 EP1387090B1 (en) 2002-08-02 2003-07-10 Hydraulic drive

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP03015768.9 Division 2003-07-10
EP20030015768 Division EP1387090B1 (en) 2002-08-02 2003-07-10 Hydraulic drive
EP20030015768 Division-Into EP1387090B1 (en) 2002-08-02 2003-07-10 Hydraulic drive

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EP1564414A1 EP1564414A1 (en) 2005-08-17
EP1564414B1 true EP1564414B1 (en) 2017-06-14

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EP04029899.4A Expired - Lifetime EP1564414B1 (en) 2002-08-02 2003-07-10 Hydraulic drive

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DE (1) DE10329067A1 (en)
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DE102005043367B4 (en) 2005-09-12 2016-09-08 Laeis Gmbh Control device and control method for a piston-cylinder arrangement
DE102008039011B4 (en) 2008-08-21 2020-01-16 MAE Maschinen- u. Apparatebau Götzen GmbH Hydraulic drive arrangement without accumulator and method for hydraulically driving a consumer without accumulator
DE102009058408A1 (en) 2009-07-09 2011-01-13 Robert Bosch Gmbh Electrohydraulic control
DE102009052531A1 (en) 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh machine press
DE102011011750A1 (en) 2011-02-18 2012-08-23 MAE Maschinen- u. Apparatebau Götzen GmbH Accumulator-free hydraulic drive arrangement for and with a consumer, in particular for presses, and method for operating such an accumulatorless hydraulic drive assembly
DE102011015903B4 (en) 2011-04-01 2021-12-16 Robert Bosch Gmbh Pump arrangement
DE102013000725B4 (en) 2013-01-17 2024-02-08 Robert Bosch Gmbh Electro-hydraulic control
CN111425469B (en) * 2020-03-30 2022-07-26 安徽东海机床制造有限公司 Bent plate follow-up material supporting hydraulic system and control method thereof
CN115255097A (en) * 2022-08-16 2022-11-01 曼弗莱德智能制造(江苏)有限公司 Energy-saving hydraulic press for stamping die and energy-saving method

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US6379119B1 (en) * 1995-05-16 2002-04-30 Globemag L-P Hybrid electric and hydraulic actuation system

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DE3217527C2 (en) * 1982-05-10 1986-07-24 Mannesmann Rexroth GmbH, 8770 Lohr Control device for a hydraulic double-acting working cylinder
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US4961316A (en) * 1987-10-28 1990-10-09 Bt Industries Aktiebolag Controlled electric pump drive for hydraulic lifting arrangement with gas spring in motor
US6379119B1 (en) * 1995-05-16 2002-04-30 Globemag L-P Hybrid electric and hydraulic actuation system

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EP1564414A1 (en) 2005-08-17
DE10329067A1 (en) 2004-02-12
ES2640347T3 (en) 2017-11-02

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