WO2014166935A2 - Presse hydraulique - Google Patents

Presse hydraulique Download PDF

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Publication number
WO2014166935A2
WO2014166935A2 PCT/EP2014/057023 EP2014057023W WO2014166935A2 WO 2014166935 A2 WO2014166935 A2 WO 2014166935A2 EP 2014057023 W EP2014057023 W EP 2014057023W WO 2014166935 A2 WO2014166935 A2 WO 2014166935A2
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
displacer unit
machine
press
coupled
Prior art date
Application number
PCT/EP2014/057023
Other languages
German (de)
English (en)
Other versions
WO2014166935A3 (fr
Inventor
Benedetto Silvani
Heiko Schwannauer
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2014166935A2 publication Critical patent/WO2014166935A2/fr
Publication of WO2014166935A3 publication Critical patent/WO2014166935A3/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • F15B2211/20546—Type of pump variable 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • 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
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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
    • F15B2211/6656—Closed loop control, i.e. control using feedback
    • 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
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to a hydraulic press according to the preamble of
  • Conventional hydraulic presses have two hydrostatic displacement units, which are fluidly connected via an inlet and a return. To generate a pressing force is one of the displacement units with a prime mover,
  • a generic hydraulic press shows the patent CH 681 872 A5.
  • a displacer unit is driven by an electric motor, wherein a flywheel is arranged on a drive shaft of the electric motor.
  • Press ram coupled displacer unit is disclosed as a hydraulic cylinder but also as a hydraulic motor.
  • the press has a control device with a control valve.
  • this can be the pressure medium volume flow from one to the other
  • Displacer unit throttled and limited. On the other hand, over that
  • Control valve the pressure medium of the two working chambers of the hydraulic cylinder to invert the direction of movement of the press ram are inverted.
  • Control means a significant proportion of hydraulic energy is lost and it must be recooled while warming pressure medium. This represents a considerable energy and device technical effort.
  • the invention is based on the object to provide a hydraulic press with increased energy efficiency. This object is achieved by a hydraulic press with the features of
  • a hydraulic press has two hydrostatic displacement units, which are fluidly connected to one another via a first inlet and a first return, in particular connected.
  • To generate a pressing force is one of the two displacement units with a prime mover and the other of the two displacement units with a
  • the invention is a
  • Displacement volume of at least one displacer unit in particular for
  • Adjustment of the pressing force and / or a stroke speed of the plunger adjustable.
  • Controlling the pressurizing agent of the other displacer unit by means of the one displacer unit with pressure loss via a throttle device can be the
  • Displacement volume are controlled pressure loss.
  • the press has a lower power loss and works more energy efficient.
  • Cooling unit for the re-cooling is smaller interpretable.
  • the press according to the invention has the advantage that it has an approximately 35 to 75% higher part yield while increasing service life and a full press force is already available from a stroke rate of one.
  • Press ram is driven to generate the pressing force electromechanically via a servo motor, according to the invention more dynamic time courses of the pressing force and the Press speed can be realized. This is due to the fact that the one displacement unit has a higher Verstelldynamik than the servo motor, since the adjustment of the
  • Displacement volume involved components compared with a to be accelerated or braked rotor of the servomotor, have a significantly lower inertia.
  • the thus more precisely controlled time course positively influences a quality of the component to be pressed.
  • pressure holding of the press ram with minimal drive power can be achieved.
  • this work can only by permanent, high
  • Power consumption can be made from the power grid.
  • the drive according to the invention has a cost advantage.
  • the other displacer unit is preferably coupled via a mechanical coupling mechanism or linkage with the press ram, in particular coupled.
  • Displacement volume is formed. The adjustment of one between the
  • Displacement units flowing pressure medium volume flow then takes place only on the first displacer unit.
  • the other displacer unit may also have an adjustable displacement volume, whereby an even higher Verstelldynamik can be achieved.
  • Displacement volume to be configured, whereby a dynamics of the adjustment of the force and speed of the press ram can be increased.
  • the other displacer unit can be coupled to an electric motor via a drive shaft, in particular coupled.
  • the electric motor preferably has an electronic position and / or speed and / or torque control in Depending on the corresponding set values of the press ram. Preferably, it is designed as a high-pole, slow-running torque servo motor.
  • the one displacer unit has a first hydrostatic hydraulic machine and a second hydrostatic hydraulic machine which can be coupled to the first via a drive shaft, in particular coupled. At least the first of the two hydraulic machines has an adjustable displacement volume. Each of the hydraulic machines has a group of hydrostatic work spaces. About the two hydraulic machines, the other displacement unit with a particularly large
  • Pressure medium volume flow are applied without the need for a particularly large, extra to be designed and to be built hydraulic machine must be provided.
  • the coupling described allows the use of two standard hydraulic machines, which investment, manufacturing, storage and maintenance costs of the press can be reduced.
  • the one displacer unit can deviate from it but also have more than two coupled hydraulic machines.
  • both hydraulic machines of a displacer unit fluidly connected in parallel with the first inlet and the first return, in particular connected.
  • the other displacer unit is device technology particularly simple
  • the other displacer unit has a first
  • Both first hydraulic machines and, via a second inlet and a second return, both first hydraulic machines can be fluidly connected to one another, in particular connected, via the first inlet and the first return.
  • the second hydraulic machine of the one displacer unit has an adjustable displacement volume. In this way, each hydraulic machine of the other displacer unit from its associated hydraulic machine of the one
  • Displacer unit are acted upon via the corresponding supply and return with an individual pressure medium flow. This allows a very differentiated and fine control of the press ram.
  • the displacement volumes of the two hydraulic machines of a displacer unit are independently adjustable. One of the displacement volumes can be independent of the other zero.
  • displacement volumes of the two hydraulic machines of a displacer unit are independently adjustable. One of the displacement volumes can be independent of the other zero.
  • Displacement volume of the first hydraulic machine is greater than that of the second.
  • Hydromachine of the other displacer unit can be assigned the rapid traverse of the press ram with great travel and low pressing force.
  • the press proves to be particularly dynamic and flexibly controllable if, in a further development, the displacement volume of the one displacer unit is adjustable such that a conveying direction of the one displacer unit can be reversed given the same direction of rotation of the drive machine. This reversibility of the press ram and a pendulum stroke are possible. It is advantageous that no switching valves for a reversal of the conveying direction and thus the movement or direction of rotation of the other displacer unit are necessary.
  • Displacer unit or at least one of their hydraulic machines, designed as a single or Doppelaxialkolbenmaschine with a both sides of a neutral position pivotable, in particular fürschwenkbaren, swash plate.
  • the neutral position is characterized in that supported on the swash plate working piston or cylinder working the axial piston machine perform no working stroke and thus no promotion of the pressure medium.
  • each of the displacer units may be configured as a peripheral machine or may comprise one or more hydraulic machines designed as peripheral machines.
  • Hydromachines of the types mentioned are proven and robust standard hydraulic components that can be controlled via equally proven control / regulating devices and methods. Through them a stable operation of the press and a low maintenance are given.
  • the drive machine via at least one electric motor, in particular a three-phase motor with frequency converter is formed.
  • the prime mover can also be modular, that is to say be formed by more than one electric motor.
  • the one displacer unit can be coupled to the drive machine via a flywheel, in particular coupled.
  • a flywheel in particular coupled.
  • the prime mover can thereby be designed smaller and / or operated with less cooling.
  • the flywheel in combination with the one displacement unit also offers a proven solution of hydromechanical
  • Displacer unit goes from motor to pump operation and drives the one displacer unit. This in turn drives the flywheel, which recovers energy.
  • the press has at least one hydraulic cylinder on which a die cushion of the press can be supported, in particular supported.
  • a pressure chamber of the hydraulic cylinder with another hydraulic machine in pressure medium connection can be brought, which in a first
  • Variant can be coupled via a further drive shaft with the drive machine or in a second variant with an electric machine.
  • the recovery for the first variant by a hydromechanical drive support the prime mover and for the second variant hydromechanical / electromechanical carried out by a conversion of press work into electrical energy.
  • the electrical energy in a network for other use or, if the drive machine is designed as an electric machine, the prime mover can be fed.
  • the hydraulic press can be configured in such a way that a try-out operation is enabled by means of a handwheel.
  • the above-described control unit preferably has a memory unit in which a control method with a desired profile of the ram speed is stored.
  • control unit also has a processor unit in which the
  • Control method is executable, wherein the desired profile can be traced by a corresponding control of an adjustment of the one or both displacement units.
  • the other displacer unit can be designed as a double-acting differential cylinder as an alternative to the aforementioned design of the peripheral or piston machine.
  • the first and / or second hydraulic machine preferably each has a group of hydrostatic working spaces, each of which can be fluidly connected in alternation with the inlet and return associated with the hydraulic machine.
  • the one and / or the other displacer unit has two hydraulic machines, then these can be arranged together in a housing of the corresponding displacer unit, or each hydraulic machine has its own housing.
  • FIG. 1 shows a hydraulic circuit diagram of a first embodiment of a hydraulic press
  • FIG. 2 shows a hydraulic circuit diagram of a second embodiment of a hydraulic press
  • FIG. 3 shows a hydraulic circuit diagram of a third embodiment of a hydraulic press
  • Figure 4 is a hydraulic circuit diagram of a fourth embodiment of a hydraulic press.
  • FIG. 5 is a hydraulic circuit diagram of a fifth embodiment of a hydraulic press.
  • a hydraulic press 1 has a displacer unit 2 and another displacer unit 4.
  • the displacer units 2, 4 are arranged in a closed hydraulic circuit via a first inlet 6 and a first return 8, both being designed as pressure medium lines.
  • the one displacement unit 2 is rotatably connected via a drive shaft 10 with a flywheel 12, or coupled.
  • the flywheel 12 is coupled via a further drive shaft 14 with a driving machine attached to a machine carrier 16, which is configured as an electric motor 18.
  • the other displacer unit 4 is coupled via a drive shaft 20 with a press ram 22. This has to convert the rotational movement of the drive shaft in one
  • Pressure medium connection can be brought.
  • the valve 24 is via a spring in one
  • valve 24 can thus fulfill an emergency function by hydraulic short-circuiting of the first inlet 6 with the first return 8 in the event of a power failure.
  • Both the first inlet 6 and the first return 8 are with a
  • Displacement volume designed. It is as a simple axial piston machine in
  • the electric motor 18 is energized and drives via the drive shaft 14, the flywheel 12 and the drive shaft 10 to a displacer unit 2. This promotes pumping pressure medium from the first return 8 in the first inlet 6, whereby in the closed hydraulic circuit the other
  • Displacer unit 4 drives the drive shaft 20 in engine operation. This drives via a press shaft, not shown, and the connecting rod to the press ram 22, so that it executes a stroke. There is a requirement to achieve a desired quality of the component to be pressed, a desired profile of the pressing force and the speed of the
  • Displacer unit 2 and thus low pressure loss.
  • exemplary embodiments 2 to 5 described below only the differences from the first exemplary embodiment will be discussed in greater detail. Otherwise, they correspond to the first embodiment. In this case, components or components which are formed over the embodiments of the same time, provided with the same reference numerals.
  • a press 101 has an electric motor 130, which is coupled to the other displacer unit 4 via a drive shaft (not shown).
  • the electric motor 130 is designed as a torque servo motor.
  • Advantage of this embodiment is that for different gaits of the press either the other displacer unit 4th or the electric motor 130 or both contribute together to the plunger movement.
  • the electric motor 130 is small, or poorly performing and takes over the function of a rapid traverse, wherein the press ram 22 is moved with little force but high speed towards the die cushion.
  • the electric motor 18 and the one displacer unit 2 are activated either in such a way that the other displacer unit 4 has a velocity profile of the
  • Electric motor 130 moves without resistance with, or the other displacer unit 4 is decoupled from the drive shaft 20 so that they do not have to entrain the electric motor 130. If the rapid traverse over into a force passage in which the component is pressed off at a lower speed but with a high pressing force, this assumes the other
  • a displacer unit 202 and another displacer unit 204 each having two with each other via a drive shaft (not shown) coupled hydraulic machines.
  • the displacement units 202, 204 are thus configured as double machines.
  • the one displacer unit 202 has a first hydraulic machine 232 and a second one
  • the other displacer unit 204 has a first hydraulic machine 236 and a second hydraulic machine 238 coupled to it via a drive shaft (not shown). Both are each, as is the other displacer unit 4 of the preceding ones
  • Embodiments designed as an axial piston machine with a constant displacement volume The first two hydraulic machines 232, 236 are fluidly connected to one another via the first inlet 6 and the first return 8.
  • the two second hydraulic machines 234 and 238 are fluidically connected to one another via a second inlet 207 and a second return 209.
  • the second inlet 207 and the second return 209 are in each case via an already described Nachsaug Wegtschventil 26 with a tank or other Pressure medium reservoir for the purpose of Druckstoffnachsaugung connectable.
  • the second inlet 207 can be connected to the second return 209 via an already described 2/2-way seat valve 24.
  • Displacement unit 204 and the first return 8 the above-described power passage and the second hydraulic machine 234 of the one displacer unit 202, the second inlet 207, the second hydraulic machine 238 of the other displacer unit 204 and the second return 209, the above rapid traverse can be provided. Accordingly, the second hydraulic machine 238 is of smaller displacement than the first one
  • Hydromachine 236 configured.
  • Displacer unit 4 a particularly large displacement volume. Nevertheless, in order to achieve a sufficient ram speed, one must with the
  • a correspondingly large, simple displacer unit can be designed and constructed which satisfies the pressure medium requirement
  • two or more smaller hydraulic machines can be coupled and fluidically connected in parallel to the first inlet 6 and the first return 8.
  • the latter solution was chosen for the fourth embodiment according to FIG.
  • a press 301 therefore has a displacer unit 202 with the first one instead of the displacer unit 2 according to FIG.
  • Embodiment according to Figure 3 are now both hydraulic machines 232, 234 fluidly connected to the first inlet 6 and the first return 8, so that analogous to the first embodiment shown in Figure 1, only a closed hydraulic circuit is formed.
  • the other displacer unit 4 via both hydraulic machines 232, 234 beautschbar with pressure medium.
  • the advantage here is that existing, proven Standard hydraulic machines are modularly interconnected. That way are
  • FIG. 4 also shows a
  • the die cushion 340 has a hydraulic cylinder 342 designed as a double-acting differential cylinder, in which a piston 344 with a one-sided piston rod 346 is displaceably arranged.
  • An annular space 348 bounded by the piston 344 and the piston rod 346 is fluidically connected to a hydrostatic pressure medium reservoir 350. About this can be carried out a pre-acceleration of the component to be pressed to reduce force peaks when hitting the press ram.
  • a pressure chamber 352 is further limited, which has a
  • Pressure medium line 354 is fluidly connected to another hydraulic machine 356.
  • This is also designed as an axial piston machine in swash plate design with swiveling swash plate and has a swivel angle sensor 28. It is connected in an open hydraulic circuit with a tank T.
  • Electric motor 18 coupled.
  • the electric motor 18 can drive the hydraulic machine 356 via the drive shaft 358, so that pressure medium is conveyed into the pressure chamber 352 and the piston 344 can be pushed back into its starting position before a press stroke.
  • a direction reversal of the pressure medium volume flow in the pressure line 354 takes place simply by pivoting through the swash plate of the hydraulic machine 356.
  • the first three exemplary embodiments shown can also be expanded by the components for energy recovery shown in FIG. 4.
  • the fifth and final embodiment of a press 401 according to Figure 5 corresponds to the embodiment of FIG 4. except for the embodiment of the energy recovery. Unlike this, the energy recovery takes place in the fifth embodiment not alone on a hydromechanical, but in addition to a
  • the press 401 according to FIG. 5 has a modified electric motor 418. This is connected to an electric machine 460 via an electrical line 462.
  • the electric machine 460 is coupled via a drive shaft arrangement 464 to a hydraulic machine 468, which has a pressure medium connection to the pressure space 352 and to its other
  • Pressure medium connection is connected to a tank T.
  • the hydraulic machine 468 is configured as a swashplate-type axial piston machine with swiveling-through swashplate and has a swivel-angle sensor 28 for measuring a swivel angle. Fluidically parallel to the hydraulic machine 468 is in a pressure medium line 470 a
  • the energy recovery is carried out according to the fifth embodiment such that on the piston 344 depressed by the press ram 22 pressure medium from the pressure chamber 352 is displaced and, if the valve 472 is not fully open and the hydraulic machine 472 has a swing angle not equal to zero over the
  • Hydromaschine 468 the displaced pressure medium from the high pressure to the tank pressure is relaxed.
  • the hydraulic machine 468 drives the electric machine 460 via the drive shaft arrangement 464, which can deliver electrical power to the drive machine 418 via the electrical line 462 in generator operation.
  • Press ram 22 and the other displacer unit 4; 204 is about 1: 5. It follows, that the other displacer unit 4; 204 must run at about 100 to 150 rev / min. For this purpose, it is designed as a so-called slow runner.
  • the one displacer unit 2; 202 should be operated at a higher speed, about 1500 to 2000 U / min, on the one hand to achieve high efficiency and on the other hand with a comparatively low mass of the flywheel 12 to provide a sufficiently high kinetic energy.
  • a hydraulic press with two displacement units, one of which is coupled to a prime mover and the other with a press ram.
  • At least one displacer unit has an adjustable displacement volume.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)

Abstract

Presse hydraulique pourvue de deux unités de refoulement dont la première peut être couplée à une machine d'entraînement et dont la seconde peut être couplée à un coulisseau de la presse. Au moins la première unité de refoulement comporte un volume de refoulement réglable.
PCT/EP2014/057023 2013-04-08 2014-04-08 Presse hydraulique WO2014166935A2 (fr)

Applications Claiming Priority (2)

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DE102013005876.7 2013-04-08
DE102013005876.7A DE102013005876A1 (de) 2013-04-08 2013-04-08 Hydraulische Presse

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WO2014166935A2 true WO2014166935A2 (fr) 2014-10-16
WO2014166935A3 WO2014166935A3 (fr) 2014-12-04

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2774750A1 (fr) 2013-03-08 2014-09-10 Omera S.r.l. Presse pour l'usinage de composants, en particulier des composants métalliques.

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DE102018107245A1 (de) * 2018-03-27 2019-10-02 Moog Gmbh Pressenantrieb mit Energierückgewinnung
IT201900010191A1 (it) * 2019-06-26 2020-12-26 Salvagnini Italia Spa Macchina per lavorare lamiere metalliche
PL3860778T3 (pl) * 2018-10-01 2023-03-06 Salvagnini Italia S.P.A. Maszyna do obróbki blachy
IT201800009060A1 (it) * 2018-10-01 2020-04-01 Salvagnini Italia Spa Sistema di azionamento idraulico per un apparato di punzonatura
DE102022204211A1 (de) * 2022-04-29 2023-11-02 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Betreiben eines hydraulischen Systems mit mindestens einem hydraulisch betätigbaren Steller

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DE3313473A1 (de) * 1983-03-17 1984-09-20 SMS Hasenclever Maschinenfabrik GmbH, 4000 Düsseldorf Spindelpresse
JPS6282142U (fr) * 1985-11-13 1987-05-26
JPH01309797A (ja) * 1988-06-08 1989-12-14 Komatsu Ltd プレスのスライド駆動装置
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JPH0988906A (ja) * 1995-09-25 1997-03-31 Daiichi Denki Kk 弾み車を有する液圧駆動装置
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JPH1158091A (ja) * 1997-08-26 1999-03-02 Aida Eng Ltd サーボモータ駆動プレス機械
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CH681872A5 (en) 1990-11-01 1993-06-15 Bruderer Maschinenfabrik Ag E Mechanism for powering working stroke of hydraulic press - has flywheel mounted on motor shaft and toggle link mechanism for distributing thrust and reducing peak demand on motor throughout cycle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2774750A1 (fr) 2013-03-08 2014-09-10 Omera S.r.l. Presse pour l'usinage de composants, en particulier des composants métalliques.

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DE102013005876A1 (de) 2014-10-09

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