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EP2722165B1 - Circuit hydraulique pour un axe hydraulique et axe hydraulique - Google Patents

Circuit hydraulique pour un axe hydraulique et axe hydraulique Download PDF

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Publication number
EP2722165B1
EP2722165B1 EP13005039.6A EP13005039A EP2722165B1 EP 2722165 B1 EP2722165 B1 EP 2722165B1 EP 13005039 A EP13005039 A EP 13005039A EP 2722165 B1 EP2722165 B1 EP 2722165B1
Authority
EP
European Patent Office
Prior art keywords
valve
hydraulic
pressure
hydraulic machine
control
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.)
Active
Application number
EP13005039.6A
Other languages
German (de)
English (en)
Other versions
EP2722165A2 (fr
EP2722165A3 (fr
Inventor
Gottfried Hendrix
Stefan Schmidt
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.)
Robert Bosch GmbH
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
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Publication of EP2722165A2 publication Critical patent/EP2722165A2/fr
Publication of EP2722165A3 publication Critical patent/EP2722165A3/fr
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Publication of EP2722165B1 publication Critical patent/EP2722165B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump
    • 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
    • F15B2211/20561—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
    • F15B2211/27—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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • 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
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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
    • F15B2211/7055—Linear output members having more than two chambers
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators

Definitions

  • the invention relates to a hydraulic circuit for a hydraulic axle and a hydraulic axle.
  • a hydraulic axis is understood to mean a hydraulic actuator, e.g. a hydraulic cylinder, and the hydraulic or electro-hydraulic control arrangement or circuit that controls the actuator with fluid.
  • Such hydraulic axes are compact, powerful and high-performance drives. These can be used in a variety of industrial automation applications, e.g. in presses, plastic machines, bending machines, etc.
  • such drives are designed to implement at least two movement sequences, namely a fast transfer movement - hereinafter referred to as rapid traverse or rapid stroke - and a force-applying working movement - hereinafter referred to as power traverse, working stroke or pressing traverse.
  • a well-known hydraulic axle shows the application DE 10 2009 043 034 of the applicant.
  • a main cylinder In a pre-tensioned hydraulic system, a main cylinder, a rapid traverse cylinder and a reversible hydraulic machine are connected to one another.
  • the connection of the components can be changed via valves so that one of several hydromechanical transmission ratios predetermined by piston areas, for example, is selected. This allows the rapid strokes or working strokes mentioned to be carried out efficiently.
  • the EP 1 580 437 A1 discloses a hydraulic circuit for a multi-surface cylinder, in which a pressure control valve controls a supply of a pressure medium to a multi-surface cylinder depending on a pressure difference between two supply lines that can be connected to chambers of the multi-surface cylinder.
  • the pressure control valve controls a pressure-controlled valve with three switching positions that are configured to connect/disconnect the supply lines to/from the chambers.
  • the two chambers that are also defined by a piston rod of the multi-surface cylinder are directly connected in a communicating manner.
  • WO 2007/083517 A1 also discloses a hydraulic circuit for a multi-surface cylinder, wherein several valves are configured to connect/disconnect the supply lines to/from the chambers.
  • the FR 2 764 008 A1 discloses an electrohydrostatic servo drive having a multi-surface cylinder with three chambers, a first partial circuit and a second partial circuit.
  • the second partial circuit comprises a pressure accumulator and a supply device and a regulating means for regulating a pressure, and it acts on the third chamber.
  • the first partial circuit has a bidirectional rotary machine which generates a differential pressure between the other two chambers in order to move a piston rod.
  • the first partial circuit is supplied with pressure from the third chamber.
  • the CA 2 279 435 A1 discloses a linear actuator with a bidirectional pump, a hydraulic circuit and a multi-surface cylinder, wherein a piston-side chamber is supplied with pressure medium from a bottom end via a transfer tube, a piston rod-internal chamber and a piston-internal line.
  • the WO 2011/079333 A2 discloses a drive device for a bending press, with a closed hydraulic system having a hydraulic pump with a controllable drive motor, at least one control valve and at least one hydraulic linear actuator.
  • the invention is based on the object of creating a hydraulic circuit for a hydraulic axle, which leads to a hydraulic axle with a relatively simple device.
  • a further object of the invention is to create a hydraulic axle with a simple device.
  • a hydraulic circuit for a multi-surface cylinder.
  • a piston of the multi-surface cylinder has two retraction surfaces and an extension surface, each of which delimits a pressure chamber.
  • the pressure chambers are supplied with and released with pressure medium via a reversible, in particular variable-speed, in particular pivotable hydraulic machine and via control valves. These are provided for switching between a rapid traverse and a power traverse of the multi-surface cylinder.
  • the control valves switch a first retraction surface and the extension surface into regeneration, i.e. the surfaces or their pressure chambers are essentially pressure-balanced.
  • the regeneration of the retraction surface and the extension surface is possible in both directions of travel of the piston of the multi-surface cylinder.
  • both retraction surfaces or the pressure chambers can be connected together via the control valves.
  • This solution has the advantage that the piston of the multi-surface cylinder can be easily extended and retracted in rapid motion.
  • pressure medium can be released from the pressure chamber of the second retraction surface via the hydraulic machine and the control valves and fed to the pressure chamber of the extension surface, whereby pressure medium displaced from the pressure chamber of the first retraction surface by the regeneration is also fed to the pressure chamber of the extension surface.
  • the pressure chamber of the second retraction surface is supplied with pressure medium, while pressure medium is released from the pressure chamber of the extension surface, whereby pressure medium released by the regeneration is fed to the pressure chamber of the first retraction surface.
  • pressure medium can advantageously be released from both pressure chambers of the retraction surfaces via the control valves via the hydraulic machine and fed to the pressure chamber of the
  • the control valves can release pressure medium from the pressure chamber of the extension surface via the hydraulic machine and supply it to the pressure chambers of the retraction surfaces.
  • the circuit according to the invention thus makes it possible to move the piston of the multi-surface cylinder in both directions of movement at a high speed and a low force or at a low speed and a high force.
  • the control valves can be used to shut off the pressure chamber of the extension surface from a high-pressure side of the hydraulic machine, at least in the power mode when the piston is extended, in order to maintain a force of the multi-surface cylinder, which makes further energy supply via the hydraulic machine unnecessary.
  • a first pump connection of the hydraulic machine can be connected to a compensating reservoir via a first storage valve and a second pump connection of the hydraulic machine can be connected to a compensating reservoir via a second storage valve.
  • a first control valve is provided as control valves in the pressure medium flow path between the hydraulic machine and the pressure chamber of the first retraction surface and a second control valve is provided fluidically in series with the first control valve between the latter and the pressure chamber of the extension surface.
  • a shut-off valve is provided in addition to the control valves. This is provided in the pressure medium flow path between the hydraulic machine and the pressure chamber of the extension surface. When the shut-off valve is closed, pressure medium can advantageously not be released from the pressure chamber of the extension surface when the second control valve is closed at the same time, whereby a pressure can essentially be maintained on the extension surface without the use of the hydraulic machine.
  • a switching valve is provided in the pressure medium flow path between the hydraulic machine and the second return surface.
  • the switching valve together with the control valves, can prevent a pressure medium release from the pressure chambers of the return surfaces. If all valves except the second control valve closed, the pressure chambers of the retraction surfaces and the extension surface can be fluidically shut off from the hydraulic machine. This means that by locking the pressure medium in the pressure chambers, preferably without leakage, the piston can be held in any position without the need to supply pressure medium via the hydraulic machine.
  • the shut-off can take place, for example, after a desired pressing pressure has been reached.
  • the hydraulic axis is stiffened by the shut-off.
  • the compensating accumulator for example a hydraulic accumulator with a preload
  • This is connected via the first accumulator valve to a pressure medium flow path between the hydraulic machine and the first control valve and via the second accumulator valve to a pressure medium flow path between the hydraulic machine and the shut-off valve.
  • the preload for the compensating accumulator can be, for example, approximately 1, approximately 2, approximately 3 or approximately 5 bar.
  • the compensation reservoir can be used to compensate for difference quantities and/or compression volumes.
  • a fluid displacement quantity of the pressure chamber of the extension surface minus a fluid displacement quantity of the pressure chamber of the second retraction surface can correspond to at least 70, 80, 90, 95 or 99% of a fluid intake quantity of the pressure chamber of the first retraction surface.
  • the compensation reservoir can then be provided to provide the difference quantity.
  • the fluid displacement quantity of the pressure chamber of the extension surface minus the fluid displacement quantity of the pressure chamber of the second retraction surface corresponds to at least 101, 110, 115, 120 or 130% of the fluid intake quantity of the pressure chamber of the first retraction surface, whereby the compensation reservoir is provided to absorb the difference quantity.
  • the difference quantity can also be zero.
  • the hydraulic machine can be charged by the accumulator valves by closing the control valves, the shut-off valve and the switching valve, so that the charging of the accumulator takes place without affecting the multi-surface cylinder. If, for example, the switching valve and the control valves are open and the shut-off valve is closed, the hydraulic machine can, when a storage valve is open, transfer pressure medium from the accumulator to the pressure chambers of the retraction surfaces and the extension surface, whereby the multi-surface cylinder is preloaded, which leads to a fixed position of its piston. Preloading of the multi-surface cylinder can thus take place without the supply of external pressure medium.
  • the compensation accumulator can also be used advantageously when the multi-surface cylinder is decompressed, in which pressure medium is pumped from the pressure chambers of the retraction surfaces or the extension surface to be decompressed via the hydraulic machine.
  • a check valve is provided that closes fluidically parallel to each storage valve towards the equalizing reservoir.
  • the check valves can then serve as suction valves.
  • the check valves mean that it is no longer necessary to open one of the storage valves when preloading the multi-surface cylinder.
  • a control valve is provided. This can be used to connect the pressure chamber of the first retraction surface to the first compensating reservoir and the pressure chamber of the extension surface to a further second compensating reservoir. Furthermore, the control valve can be used to connect the pressure chamber of the first retraction surface to the pressure chamber of the second compensating reservoir and the pressure chamber of the extension surface to the first compensating reservoir.
  • the second compensating reservoir can also be a hydraulic accumulator with a preload, for example.
  • the control valve can be used to finely position the piston of the multi-surface cylinder, whereby the hydraulic machine can be inactive.
  • the second compensating reservoir can be fluidically connected to the hydraulic machine via a further storage valve, in particular for charging.
  • the second compensating reservoir is preferably connected in the pressure medium flow path between the shut-off valve and the hydraulic machine via its storage valve.
  • the control valve can, for example, be a pulse width modulated control valve, which in particular has no leakage.
  • the switching valve is arranged fluidically parallel to the first control valve.
  • At least one pressure relief valve is provided to prevent overpressure in the hydraulic circuit. It is conceivable to protect the pressure chambers of the multi-surface cylinder using one or more pressure relief valves.
  • the speed and/or a displacement volume can advantageously be adjusted, which in turn allows the extension and retraction speed of the piston of the multi-surface cylinder to be adjusted.
  • the hydraulic machine is advantageously driven by a drive unit in the form of an electric servo motor.
  • control valves, the shut-off valve, the switching valve and the storage valves are designed as directional seat valves.
  • the hydraulic axle is designed as a structural unit.
  • the structural unit of the hydraulic axle has in particular the hydraulic circuit according to the invention, the multi-surface cylinder that can be controlled via the circuit and a control block that has the valves - in particular the control valves, the shut-off valve, the switching valve and the storage valves.
  • the structural unit of the hydraulic axle also has the hydraulic machine and a drive unit, which can in particular be the electric servo motor.
  • the structural unit can be provided with the compensation volumes.
  • the hydraulic axis By designing the hydraulic axis as a structural unit, it is extremely compact and can be used flexibly in a wide variety of installation positions. By arranging the hydraulic machine and the drive unit in the structural unit, it is not necessary to provide the structural unit with external energy other than electrical energy.
  • the hydraulic axis can be designed as a structural unit with a closed hydraulic circuit, which can then be hermetically sealed from its environment.
  • At least two cylinder connections for the multi-surface cylinder are designed as connection surfaces or bores on the control block. This means that no pipes are required for these two cylinder connections.
  • the Multi-surface cylinders can then be flanged directly to the control block, which increases the compactness of the hydraulic axis.
  • the compensating accumulators can be mounted directly on the control block to increase the compactness of the hydraulic axis.
  • control block serves as the machine housing for the hydraulic machine. This can thus be recessed into the control block, whereby an installation space for the hydraulic machine in the control block can be used as a leakage oil collector.
  • a fluidic connection of the hydraulic machine in the control block is made simply, preferably via pipe nipples or pipe plug-in nipples.
  • a displacement sensor for detecting a piston position of the piston of the multi-surface cylinder is provided for controlling the multi-surface cylinder, which is, for example, integrated into the cylinder. It would also be conceivable to arrange the displacement sensor outside the multi-surface cylinder. To control the pressures in the multi-surface cylinder, pressure sensors can be provided to measure these pressures.
  • the hydraulic axis 1 according to the invention is shown.
  • This has a multi-surface cylinder 2, which is used in particular for hydraulic presses.
  • a hydraulic circuit 6 is used to adjust a piston 4 of the multi-surface cylinder 2.
  • This is arranged in a control block 8 and forms a structural unit together with the multi-surface cylinder 2 and a drive unit 10 in the form of an electric servo motor.
  • the drive unit 10 is connected to a hydraulic machine 14 via a drive shaft 12.
  • the hydraulic machine 14 is used in the hydraulic axis 1 as a hydraulic pump that can be pivoted, which means that its delivery volume can be adjusted.
  • the hydraulic machine 14 is advantageously designed within the control block 8, in that the latter forms a pump housing for the hydraulic machine 14.
  • An installation space in the control block 8 for the hydraulic machine 14 then serves as a leakage oil collector. Pipe nipples are provided in the installation space of the control block 8 to easily connect the hydraulic machine 14.
  • the hydraulic machine 14 is reversible and can be driven by the drive unit 10 in both directions of rotation.
  • the drive unit 10 is designed in such a way that it can drive the hydraulic machine 14 at an adjustable speed. With the hydraulic machine 14, a first, second and third pressure chamber 16, 18 and 20 of the multi-surface cylinder 2 can be supplied with pressure medium and pressure medium can be released from the pressure chambers 16, 18 and 20 via the hydraulic machine 14.
  • the piston 4 of the multi-surface cylinder 2 is guided in a cylinder housing 24 of the multi-surface cylinder 2. Based on the enlarged illustration in Figure 2 The multi-surface cylinder 2 is explained in more detail below.
  • the piston 4 of the multi-surface cylinder 2 has a piston section 26 which separates the annular third pressure chamber 20 from an air chamber 28 in the cylinder housing 24.
  • the air chamber 28 is preferably pressure-equalized with the surroundings of the hydraulic axis 1 via a cylinder vent 30.
  • a rod section 32 of the piston 4 passes through the cylinder housing 24 and thus the third pressure chamber 20 in a direction away from the air chamber 28.
  • the piston 4 has a cylindrical interior into which a guide rod 34 projects. This extends approximately coaxially to the cylinder housing 24 starting from a bottom surface 36 of the cylinder housing 24 which delimits the air chamber 28, passes through the piston section 26 via a through opening 38 and opens into the cylinder chamber of the piston 4.
  • the guide rod 34 has a radial collar 40 whose outer diameter approximately corresponds to the inner diameter of the cylinder chamber of the piston 4. With this, the guide rod 34 in the piston 22 separates the first pressure chamber 16 from the second annular pressure chamber 18. Due to the guide rod 34, the air chamber 28 is also annular.
  • the guide rod 34 is somewhat shorter in the axial direction than the cylinder housing 24 and ends approximately at the beginning of a through opening 42 in the cylinder housing 24, through which the rod section 32 of the piston 22 is slidably guided.
  • the first pressure chamber 16 within the piston 22 is delimited by an extension surface A1 which acts in the extension direction and points in the direction of the guide rod 34.
  • the third pressure chamber 20 is delimited by a first outer retraction surface A3 which is formed on the piston section 26 of the piston 22.
  • the second pressure chamber 18 is delimited by a second inner retraction surface A2 which in turn is formed opposite the extension surface A1 within the piston 22. It extends in a ring shape around the guide rod 34.
  • the retraction surfaces A2 and A3 act in a retraction direction of the piston 22. A sum of the retraction surfaces A2 and A3 corresponds approximately to the extension surface A1.
  • a first pressure channel 42 which passes through the guide rod 34 in the axial direction opens into the first pressure chamber 16 and is connected to a first pressure line 44 of the control block 8.
  • the second pressure chamber 18 is fluidically connected to a second pressure channel 46 which is also formed in the guide rod 34 and extends from the control block 8 in the direction of the radial collar 40 and opens approximately radially into the second pressure chamber 18 in front of the radial collar 40.
  • the second pressure channel 46 is connected to a second pressure line 48 of the control block 8.
  • the third pressure chamber 20 is connected to a third pressure line 50 which is connected on the one hand to the cylinder housing 24 and on the other hand to the control block 8.
  • the third pressure line 50 is connected to a pressure line 52 formed in the control block 8.
  • the first and second pressure lines 44, 48 open into an outer surface of the control block 8.
  • the opening area serves as a cylinder connection for the multi-surface cylinder 2 and is designed as a connection surface 53.
  • the hydraulic machine 14 is connected according to Figure 1 to the first pump connection A a first pump line 54 and to the second pump connection B a second pump line 56 is connected.
  • the first pump line 54 is connected to a Pump connection P of a first control valve 58.
  • this has a working connection X, which is connected to the pressure line 52, which in turn is fluidically connected to the third pressure chamber 20 of the multi-surface cylinder 2 from Figure 2 is in pressure medium connection.
  • the first control valve 58 is designed as a 2/2-way valve.
  • a valve piston of the first control valve 58 is acted upon by a spring force via a valve spring 60 in the direction of a closed position, in which a pressure medium connection between the pump connection P and the working connection X is separated.
  • valve slide of the control valve 58 can be acted upon by a force, in particular a magnetic force, via an actuator 62, which is, for example, an electric lifting magnet.
  • actuator 62 which is, for example, an electric lifting magnet.
  • the pump connection P is in pressure medium connection with the working connection X.
  • a second control valve 64 is provided in fluidic series with the first control valve 58, which also has a working connection X and a pump connection P.
  • the working connection X is connected to the pressure line 52 via a branch line 66.
  • the pump connection P of the second control valve 64 is connected to the first pressure line 44 via a further branch line 68 and is thus connected to the first pressure chamber 16, see Figure 2 , in pressure medium connection.
  • the second control valve 64 is also a 2/2-way valve, whereby, in contrast to the first control valve 58, its valve slide can be moved into an open position via the valve spring 60 and into a closed position via the actuator 62.
  • the valve slide of the second control valve 64 is thus in the open position in the de-energized state, in which the pump connection P is fluidically connected to the working connection X and thus the third pressure chamber 20 is fluidically connected to the first pressure chamber 16.
  • the second pressure line 48 which is fluidically connected to the second pressure chamber 18, can be connected to the first pump line 54 via a switching valve 70.
  • the switching valve 70 corresponds to the first control valve 58 and has a working connection X and a pump connection P.
  • the second pressure line 48 is connected to the working connection X and the pump connection P is connected to the first pump line 54 via a branch line 72.
  • the first pressure line 44 and thus also the branch line 68 are connected to the second pump line 56 via a shut-off valve 74.
  • This is in accordance with the first control valve 58 and has a working connection X to which the first pressure line 44 is connected and a pump connection P to which a branch line 76 is connected, which is connected to the second pump line 56.
  • the pump lines 54 and 56 connected to the hydraulic machine 14 can also be connected to a compensating reservoir 78, which can be designed as a hydraulic reservoir and is preferably arranged or formed in the control block 8. It would also be conceivable to connect this to the control block 8.
  • a first reservoir line 80 branches off from the first pump line 54 and a second reservoir line 82 branches off from the second pump line 56.
  • the first reservoir line 80 is connected to a pump connection P of a first reservoir valve 84 and the second reservoir line 82 is connected to a pump connection P of a second reservoir valve 86.
  • the reservoir valves 84 and 86 are designed to correspond to the first control valve 58 and each have a reservoir connection S.
  • a first suction line 90 is provided, which is arranged on the storage line 88 and on the first pump line 54.
  • a first check valve 92 closing in the direction of the equalizing reservoir 78 is arranged in the first suction line 90.
  • the first suction line 90 with the first check valve 92 thus branches off from the first pump line 54 in the pressure medium flow path between the first control valve 58 and the hydraulic machine 14.
  • a further second suction line 94 is arranged fluidically parallel to the second storage valve 86 between the equalizing reservoir 78 and the second pump line 56 and also has a second check valve 96 closing in the direction of the equalizing reservoir 78.
  • the second suction line 94 is thus connected to the second pump line 56 in the pressure medium flow path between the hydraulic machine 14 and the shut-off valve 74.
  • the design of the hydraulic axis 1 as a structural unit makes it extremely compact.
  • the hydraulic machine 14, the compensating reservoir 78, the control valves 58, 64, the switching valve 70, the shut-off valve 74 and the suction valves 92, 96 are arranged in the control block 8.
  • the multi-surface cylinder 2 and the drive unit 10 are simply connected to the control block.
  • hydraulic axis 1 The functionality of hydraulic axis 1 is explained in more detail below.
  • valve slide of the switching valve 70 and the shut-off valve 74 are in their open position.
  • the other valves 58, 64, 84 and 86 are de-energized.
  • the hydraulic machine 14 conveys pressure medium from its pump connection A to its pump connection B. It thus conveys pressure medium from the second pressure chamber 18 via the switching valve 70, the first pump line 54 to the second pump line 56 and from there via the shut-off valve 74 into the first pressure chamber 16.
  • the pressure chamber 16 is fluidically connected to the third pressure chamber 20 via the second control valve 64 and is pressure balanced.
  • the extension surface A1 of the piston 4, see Figure 2 is thus subjected to a higher pressure in the extension direction via the first pressure chamber 16 than the second retraction surface A2 of the piston 4 in the closing direction, which is why the piston 4 extends.
  • the pressure medium displaced from the third pressure chamber 20 is fed to the first pressure chamber 16 via the second control valve 64.
  • the extension surface A1 and the first retraction surface A3 are switched to regeneration.
  • the first control valve 58, the switching valve 70 and the shut-off valve 74 are energized via their actuator and thus their valve slide is in its open position. Furthermore, the second control valve 64 is energized, as a result of which its valve slide is in the closed position.
  • the second and third pressure chambers 18, 20 are connected together via the first control valve 58 and the switching valve 70.
  • the hydraulic machine 14 conveys pressure medium from its pump connection A to its pump connection B, thereby releasing pressure medium from the second and third pressure chambers 18, 20 and supplying the first pressure chamber 16 with it via the shut-off valve 74.
  • the piston 4 thus extends in the power mode.
  • the hydraulic machine 14 conveys pressure medium from its pump connection B to its pump connection A.
  • the shut-off valve 74 and the first storage valve 84 are energized, meaning that their valve slide is in its open position.
  • the second control valve 64 is also energized, meaning that its valve slide is in its closed position.
  • the first control valve 58, the switching valve 70 and the second storage valve 86 are not energized and their valve slide is in its closed position.
  • the hydraulic machine 14 now conveys pressure medium from the first pressure chamber 16 via the shut-off valve 74 into the first pump line 54 and from there via the first storage valve 84, the storage line 88 to the equalizing reservoir 78.
  • the hydraulic machine 14 When retracting in rapid traverse, the hydraulic machine 14 conveys pressure medium from its pump connection B to its pump connection A.
  • the shut-off valve 74 and the switching valve 70 are energized, meaning that their valve slide is in its open position.
  • the first and second control valves 58, 64 and the first and second storage valves 84, 86 are de-energized.
  • the valve slide of the second control valve 64 is thus in its open position.
  • the extension surface A1 and the first retraction surface A3 are connected via the second control valve 64, see Figure 2 , switched to regeneration.
  • the hydraulic machine 14 now conveys pressure medium from the first pressure chamber 16 via the shut-off valve 74 and the switching valve 70 to the second pressure chamber 18, whereby the piston 4 moves in the retraction direction.
  • Pressure medium displaced from the first pressure chamber 16 is additionally supplied to the third pressure chamber 20 by the regeneration via the second control valve 64.
  • the hydraulic machine delivers pressure medium from pump connection B to pump connection A.
  • the first control valve 58, the second control valve 64, the switching valve 70 and the shut-off valve 74 are energized.
  • the valve slide of the second control valve 64 is thus in its closed position and the valve slides of the first control valve 58, the switching valve 70 and the shut-off valve 74 are in their open position.
  • the storage valves 84 and 86 are de-energized, meaning that their valve slides are in the closed position.
  • the hydraulic machine 14 then delivers pressure medium from the first pressure chamber 16 via the shut-off valve 74 into the first pump line 54 and from there further via the first control valve 58 to the third pressure chamber 20 and via the switching valve 70 to the second pressure chamber 18. Missing compression volume is sucked in from the compensating accumulator 78 via the second check valve 96.
  • the piston 4 then retracts in the power gear.
  • the hydraulic machine 14 delivers pressure medium from the pump connection A to the pump connection B.
  • the first and second control valves 58, 64, the switching valve 70 and the second storage valve 86 are energized.
  • the valve slide of the second control valve 64 is thus in its closed position and the valve slides of the first control valve 58, the switching valve 70 and the second storage valve 86 are in their open position.
  • the valve slide of the shut-off valve 74 and the first storage valve 84 are each de-energized in their closed position.
  • the hydraulic machine 14 thus delivers pressure medium from the second and third pressure chambers 18, 20 into the second pump line 56 and from there via the second storage valve 86 and the storage line 88 to the equalizing storage 78, which charges it.
  • the first control valve 58 and the switching valve 70 are energized, whereby their valve slides are in their open position. All other valves 74, 84, 86 and 64 are de-energized. The valve slide of the second control valve 64 is thus also in its open position.
  • the hydraulic machine 14 conveys pressure medium from its pump connection B to its pump connection A. Pressure medium is thus supplied from the equalizing reservoir 78 via the second check valve 96 into the first pump line 54 and from there it passes through the switching valve 70, the first control valve 58 and the second control valve 64 into the pressure chambers 16 to 20. These are pressure balanced by the opened valves 58, 64 and 70.
  • the retraction surfaces A2 and A3 and the extension surface A1, see Figure 2 are thus preloaded with the same pressure.
  • the hydraulic axis 98 additionally has a control valve 100 and a compensating reservoir 102 with a third reservoir valve 104.
  • the control valve 100 is designed as a 4/3-way valve and has a first storage connection S1, a second storage connection S2, a first working connection X1 and a second working connection X2.
  • a valve slide of the control valve 100 is spring-centered via two valve springs 106 and 108 in its middle closed position, in which the connections S1, S2, X1 and X2 are separated from one another.
  • the valve slide can be displaced in the direction of first open positions via an electrical actuator 110, in which the first working connection X1 is connected to the first storage connection S1 and the second working connection X2 is connected to the second storage connection S2.
  • the valve slide can be displaced with a further electrical actuator 112, starting from its closed position, in the direction of second open positions, in which the first working connection X1 is connected to the second storage connection S2 and the second working connection X2 is connected to the first storage connection S1.
  • the first working connection X1 is connected via a branch line 114 to the branch line 66 and thus to the pressure line 52 connected to the third pressure chamber 20.
  • the second working connection X2 of the control valve 100 is connected to the first pressure line 44 via a branch line 116 and is thus in pressure medium connection with the first pressure chamber 16.
  • the second storage connection S2 is connected to the storage line 88 via a branch line 118 and is thus in pressure medium connection with the compensation storage 78.
  • the first storage connection S1 is connected to a storage line 120, which in turn is connected to a storage connection S of the compensation storage 102.
  • the storage line 120 is connected to the second pump line 56 via the third storage valve 104.
  • the third storage valve 104 is connected in accordance with the first Control valve 58 and thus has a pump connection P and a working connection X.
  • the pump connection P is connected to the second pump line 56 via a branch line 122 and the working connection X is connected to the storage line 120 via a branch line 124.
  • the control valve 100 is continuously adjustable and is used for the fine positioning of the piston 4 of the multi-surface cylinder 2.
  • a storage charging mode can be carried out.
  • the third accumulator valve 104 is energized, whereby its valve slide is in its open position. All other valves except the second control valve 64 are de-energized, whereby its valve slide is in its closed position, corresponding to the valve slide of the other valves 58, 70, 84, 86, 74, 100.
  • the hydraulic machine 14 conveys pressure medium from the pump connection A to the pump connection B and thus from the first equalizing accumulator 78 via the first check valve 92 into the second pump line 56 and from there via the third accumulator valve 104 into the second equalizing accumulator 102. This continues until the desired pressure in the equalizing accumulator 102 is reached. After the desired pressure is reached, the current supply to the third storage valve 104 is interrupted and its valve slide is moved to its closed position, whereby the pressure medium remains in the equalizing reservoir 102.
  • the switching valve 70 and the second control valve 64 are energized.
  • the valve slide of the switching valve 70 is in its open position and the valve slide of the control valve 64 is in its closed position.
  • the valve slides of the first control valve 58, the shut-off valve 74 and the storage valves 84, 86 and 104 are also in their closed position.
  • the hydraulic machine 14 is not driven in this case.
  • the control valve 100 either the first pressure chamber 16 can be connected to the equalizing accumulator 102 or the third pressure chamber 20 can be connected to the equalizing accumulator 120.
  • the valve slide of the control valve 100 is in the open positions in which the second working connection X2 is connected to the first accumulator connection S1.
  • the third pressure chamber 20 is then in pressure medium connection with the second pressure chamber 18 via the control valve 100, the branch line 118, the first check valve 92, the switching valve 70. Pressure medium can therefore flow from the third pressure chamber 20 to the second pressure chamber 28.
  • the valve slide of the control valve 100 is in the open position in which the first working connection X1 is connected to the first accumulator connection S1 and the second working connection X2 is connected to the second accumulator connection S2.
  • the first pressure chamber 16 is then in pressure medium connection with the second pressure chamber 18 via the control valve 100, the branch line 118, the first check valve 92 and the switching valve 70, whereby pressure medium can then flow from the first pressure chamber 16 into the second pressure chamber 18.
  • the control valve thus makes it possible to control the position of the piston 4 by alternately connecting the pressure chambers 16 and 20 with the second compensating reservoir 102.

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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)
  • Actuator (AREA)

Claims (10)

  1. Circuit hydraulique pour un cylindre à surfaces multiples (2) qui présente un piston (4) avec deux surfaces de recul (A2, A3) et une surface de sortie (A1), dans lequel le circuit (6) présente une machine hydraulique (14) et des soupapes de commande (58, 64) pour commuter entre une vitesse d'avance rapide et une vitesse d'avance de travail du piston (4), dans lequel pour la vitesse d'avance rapide, les soupapes de commande (58, 64) permettent de commuter la première surface de recul (A3) et la surface de sortie (A1) en mode régénération, et dans lequel pour la vitesse d'avance de travail, les soupapes de commande (58, 64) permettent d'interconnecter les deux surfaces de recul (A2, A3) ensemble, la machine hydraulique (14) étant réversible, dans lequel une première soupape de commande (58) des soupapes de commande (58, 64) est prévue sur le trajet d'écoulement de fluide sous pression entre la machine hydraulique (14) et la première surface de recul (A3), et une deuxième soupape de commande (64) des soupapes de commande (58, 64) est prévue fluidiquement en série avec la première soupape de commande (58) sur le trajet d'écoulement de fluide sous pression entre celles-ci et la surface de sortie (A1), dans lequel une soupape d'arrêt (74) est prévue sur le trajet d'écoulement de fluide sous pression entre la machine hydraulique (14) et la surface de sortie (A1), et dans lequel un réservoir de compensation (78) est prévu, caractérisé en ce que le réservoir de compensation (78) est raccordé par l'intermédiaire d'une première soupape de stockage (84) à un trajet d'écoulement de fluide sous pression entre la machine hydraulique (14) et la première soupape de commande (58) et par l'intermédiaire d'une deuxième soupape de stockage (86) à un trajet d'écoulement de fluide sous pression entre la machine hydraulique (14) et la soupape d'arrêt (74), et en ce que fluidiquement en parallèle à une soupape de stockage (84, 86) respective, un clapet antiretour (92, 96) fermant en direction du réservoir de compensation (78) est prévu.
  2. Circuit hydraulique selon la revendication 1, dans lequel une soupape de commutation (70) est prévue sur le trajet d'écoulement de fluide sous pression entre la machine hydraulique (14) et la deuxième surface de recul (A2).
  3. Circuit hydraulique selon la revendication 1 ou 2, dans lequel une soupape de régulation (100) est prévue par laquelle la première surface de recul (A3) peut être raccordée au premier réservoir de compensation (78) et la surface de sortie (A1) peut être raccordée à un deuxième réservoir de compensation (102), et par laquelle la première surface de recul (A3) peut être raccordée au deuxième réservoir de compensation (102) et la surface de sortie (A1) peut être raccordée au premier réservoir de compensation (78).
  4. Circuit hydraulique selon la revendication 2 ou 3, dans lequel la soupape de commutation (70) est disposée fluidiquement en parallèle à la première soupape de commande (58).
  5. Circuit hydraulique selon l'une quelconque des revendications précédentes, dans lequel une vitesse de rotation et/ou une cylindrée de la machine hydraulique (14) sont réglables.
  6. Axe hydraulique qui présente sous forme d'unité modulaire un circuit hydraulique (6) selon l'une quelconque des revendications précédentes, le cylindre à surfaces multiples (2) pouvant être commandé par l'intermédiaire du circuit (6) et présentant deux surfaces de recul (A2, A3) et une surface de sortie (A1), un bloc de commande (8) présentant les soupapes (58, 64, 70, 74, 84, 86, 100) et une unité d'entraînement (10) pour la machine hydraulique (14).
  7. Axe hydraulique selon la revendication 6, dans lequel au moins deux raccords de cylindre pour le cylindre à surfaces multiples (2) sur le bloc de commande (8) sont réalisés en tant que surfaces de raccordement (53) ou alésages.
  8. Axe hydraulique selon la revendication 6 ou 7, dans lequel au moins un réservoir de compensation (78, 102) est monté sur le bloc de commande (8).
  9. Axe hydraulique selon l'une quelconque des revendications 6 à 8, dans lequel le bloc de commande (8) est utilisé comme carter de machine pour la machine hydraulique (14).
  10. Axe hydraulique selon la revendication 9, dans lequel le raccordement de la machine hydraulique (14) dans le bloc de commande (8) est réalisé par des manchons filetés.
EP13005039.6A 2012-10-22 2013-10-22 Circuit hydraulique pour un axe hydraulique et axe hydraulique Active EP2722165B1 (fr)

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DE102012020581.3A DE102012020581A1 (de) 2012-10-22 2012-10-22 Hydraulische Schaltung für eine hydraulische Achse und eine hydraulische Achse

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DE102013227053B4 (de) 2013-12-23 2023-04-20 Robert Bosch Gmbh Hydraulische Achse
DE102015225436A1 (de) 2015-12-16 2017-06-22 Robert Bosch Gmbh Ventilblock, Zylinder, Kompaktachse und Kompaktachsen-Baukasten
DE102016212306A1 (de) 2016-07-06 2018-01-11 Robert Bosch Gmbh Zwischenblock und Kompaktachse mit einem Zwischenblock
DE102016118854A1 (de) * 2016-10-05 2018-04-05 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
DE102016223099A1 (de) * 2016-11-23 2018-05-24 Robert Bosch Gmbh Elektrohydraulische Anordnung und Hydraulische Achse
CN107931603B (zh) * 2017-11-24 2023-12-29 南通巨能锻压机床有限公司 一种干粉制品框架式液压机顶缸机构
DE102018201484A1 (de) 2017-12-21 2019-06-27 Robert Bosch Gmbh Hydrostatischer Antrieb
DE102018205821A1 (de) * 2018-04-17 2019-10-17 Robert Bosch Gmbh Vibrationsantreiben mit einem Mehrflächenzylinder
DE102018217820A1 (de) 2018-10-18 2020-04-23 Robert Bosch Gmbh Hydraulische Steueranordnung und hydraulische Achse
DE102018218218A1 (de) 2018-10-24 2020-04-30 Robert Bosch Gmbh Servohydraulischer Antrieb
DE102019202683A1 (de) 2019-02-28 2020-09-03 Robert Bosch Gmbh Nachfülleinheit zum Nachfüllen von Hydrauliköl in ein mit einem Niederdruckspeicher druckvorgespanntes hydraulisches System und druckvorgespanntes hydraulisches System mit einer solchen Nachfülleinheit
CN115352010B (zh) * 2022-07-20 2024-09-13 宁波伯乐智能机械有限公司 一种注塑机整机用液压控制系统

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CN103775401A (zh) 2014-05-07
DE102012020581A1 (de) 2014-04-24
CN103775401B (zh) 2018-04-10
EP2722165A3 (fr) 2018-01-10

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