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EP3077674B1 - Système hydraulique - Google Patents

Système hydraulique Download PDF

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Publication number
EP3077674B1
EP3077674B1 EP14805265.7A EP14805265A EP3077674B1 EP 3077674 B1 EP3077674 B1 EP 3077674B1 EP 14805265 A EP14805265 A EP 14805265A EP 3077674 B1 EP3077674 B1 EP 3077674B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
control valve
port
hydraulic machine
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
EP14805265.7A
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German (de)
English (en)
Other versions
EP3077674A1 (fr
Inventor
Patric BUECKER
Ruslan Rudik
Gottfried Hendrix
Markus Kopf
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
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Filing date
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Publication of EP3077674A1 publication Critical patent/EP3077674A1/fr
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Publication of EP3077674B1 publication Critical patent/EP3077674B1/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
    • F15B11/04—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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/27—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
    • F15B2211/61—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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle

Definitions

  • the invention relates to a hydraulic arrangement with at least one adjustable hydraulic machine whose displacement volume is adjustable via a control cylinder of the arrangement, and with a control valve, in particular a pressure control valve for regulating the pressure at the pressure connection of the hydraulic machine, wherein the actuating cylinder can be controlled via the control valve.
  • EP 1 219 831 A2 is a hydraulic arrangement with a variable in their stroke volume over zero hydraulic pump is known, which takes positive pressure volume of a first main line and outputs in a second main line negative pressure takes the second main line and discharges pressure medium in the first main line.
  • the stroke volume of the hydraulic pump is adjusted according to an electro-proportional (EP) control.
  • EP control is superimposed on a pressure control, with a first pressure regulator for limiting the pressure in the first main line and a second pressure regulator for limiting the pressure in the second main line.
  • Hydraulic arrangements for powerful drive units for driving hydraulic axes are known from the prior art. Such hydraulic axes are used in a variety of industrial automation applications, such as in presses, injection molding machines or bending machines. If the hydraulic axis used for pressing, it may for example be designed as a differential cylinder, in which a piston separates a cylinder chamber from an annular space. The cylinder chamber is then driven, for example, by a hydraulic machine with a certain amount of pressure medium. In order to improve a dynamics of the adjustment of the piston, the annular space can be acted upon by an adjustable, other hydraulic machine with a constant pressure and thus hydraulically clamped. In order to keep the pressure of the annulus constant, the adjustable other hydraulic machine is adjusted in its stroke volume a hydromechanical pressure control valve so that the pressure at the pressure port of the other hydraulic machine has a specific value.
  • Conventional hydromechanical pressure control valves fail, however, when changing the operating mode of conveyor or pump operation on a sip or motor operation of the other hydraulic machine, since this must reverse the operating principle of the pressure control valve.
  • the Pump operation for example, must be set to a higher displacement volume to deliver more fluid if the pressure in the annulus is too low.
  • the displacement volume in engine operation at too low a pressure in the annulus, the displacement volume must be reduced in order to effect a stronger accumulation of pressure medium.
  • Conventional hydromechanical pressure control valves can only control the pump operation of the adjustable, other hydraulic machine.
  • a cylinder space of the differential cylinder is connected to a constant hydraulic machine, which is driven by an adjustable hydraulic machine.
  • the latter is connected on the one hand with a tank and on the other hand via a pressure medium line with imprinted pressure with an annular space of the differential cylinder.
  • the pressurization of the pressure medium line and the annular space via a hydraulic pump, wherein the pressure in the annular space is limited by a pressure relief valve, can be throttled over the pressure medium from the pressure medium line to the tank.
  • DE 40 08 792 A1 shows a further embodiment of a hydraulic arrangement is shown, in which a cylinder space of the differential cylinder is connected to two hydraulic machines in the form of adjustable hydraulic pumps, which are drivable via a common drive shaft.
  • One of the variable displacement pumps is connected to a tank and the other to the annular space of the differential cylinder, whereby the piston of the differential cylinder is hydraulically clamped independently of its operating direction on both sides.
  • the invention has the object to provide a device engineering simpler configured hydraulic arrangement with which a hydraulic machine is energy-efficiently controlled in different modes.
  • a hydraulic arrangement has a first hydraulic machine with adjustable displacement volume and a control cylinder with a control piston for adjusting the displacement volume.
  • the actuating piston adjoins at least one actuating chamber of the actuating cylinder, which may be referred to below as the first actuating chamber.
  • About the actuating piston can also be acted upon in the actuating cylinder two acted upon by pressure medium, acting in opposite directions adjusting chambers separated from each other.
  • the hydraulic arrangement has a first control valve, via the control function in a first operating mode of the first hydraulic machine, a pressure medium supply into the first actuating chamber and a pressure medium discharge is controllable out of it.
  • an operating parameter of the first hydraulic machine can be controlled via a stroke of the actuating cylinder or actuating piston and the associated adjustment of the displacement volume.
  • the hydraulic arrangement to an operable, in particular switchable means on the actuation, in particular circuit the control function of the first valve can be deactivated and a control function of a second control valve of the arrangement can be activated.
  • the second control valve via the second control valve, the pressure medium supply and pressure fluid removal of the first control chamber in a second mode of operation of the first hydraulic machine can be controlled.
  • the means in cooperation with the first and the second control valve offers a device-technically simple solution to regulate the first hydraulic machine in their various modes with different control functions.
  • Each further operating mode is then preferably associated with a further control valve, which via the means or another means can be activated or deactivated according to the other operating mode.
  • the means is electromagnetically actuated.
  • the first hydraulic machine is designed as an adjustable axial piston machine in swash plate construction, the swash plate is arranged on a pivotable pivoting cradle, wherein the actuating piston or the actuating cylinder is connected to the pivoting cradle.
  • the hydraulic arrangement proves to be particularly advantageous in a development in which the first operating mode is a motor operation and the second operating mode is a pump operation, and a different rotational direction of a drive shaft of the first hydraulic machine is assigned to both operating modes.
  • the arrangement has a second hydraulic machine, wherein the arrangement is configured such that the first hydraulic machine has a different mode of operation than the second hydraulic machine.
  • a drive shaft of the second hydraulic machine is rotatably connected to the drive shaft of the first hydraulic machine, whereby rotational directions of the two hydraulic machines are in the same direction.
  • a first cylinder space of a hydraulic cylinder of the arrangement in particular an annular space of a differential cylinder, and via the second hydraulic machine a second cylinder space of the hydraulic cylinder, in particular of the differential cylinder, can be acted upon with pressure medium via the first hydraulic machine.
  • the clamping according to the invention by the regulation of the pressure and not by throttling excessively generated pressure as shown in the prior art.
  • the arrangement is more energy efficient operable and the cost of re-cooling the pressure medium is reduced.
  • Such a hydraulic arrangement is particularly suitable for industrial automation applications, in particular for direct or indirect drives for presses, Injection molding machines or bending machines, the hydraulic consumer, in particular the hydraulic cylinder, speed-controlled is supplied with pressure medium.
  • a high-pressure or working pressure of the first hydraulic machine or a pressure dependent thereon can be regulated via the pressure medium supply and the pressure medium discharge.
  • a valve body of the first control valve against a pressure equivalent of a setpoint generator of the first control valve with the high pressure or the pressure dependent thereon or the auxiliary pressure is applied.
  • the activation of the control function of the second control valve thus takes place via the admission of its valve body with an actual value of the pressure to be regulated. Accordingly, the deactivation of the control function of the second control valve is effected by a non-admission of the valve body.
  • a nominal value of the setpoint generator of the first control valve is greater than a desired value of the setpoint generator of the second control valve.
  • valve body of the first control valve is acted upon by the actuation, in the same effective direction as the pressure equivalent of the setpoint generator of the first control valve, with the high pressure or the pressure dependent thereon or with the auxiliary pressure.
  • the valve body of the first control valve is acted upon on both sides by the same pressure and, apart from the pressure equivalent already mentioned, pressure balanced.
  • the pressure equivalent now causes that the valve body of the first control valve is fixed in its initial position, whereby the control function of the first control valve is deactivated during actuation. Since only a small pressure equivalent of the setpoint generator is necessary to set, it is achieved via the pressure balanced compensation described that even a lower setpoint than the second control valve can be set at the first control valve.
  • the means is formed via a valve which has a high-pressure connection which can be fluidly connected to a high-pressure connection of the first hydraulic machine or to an auxiliary pressure medium source. Furthermore, the valve has a tank connection, which is fluidically connected to a pressure medium sink. Furthermore, the valve has a working connection, which can be fluidically connected to the first setting chamber via working connections of the control valves.
  • all said valves are arranged on the first hydraulic machine, so that the hydraulic arrangement is designed to be particularly compact.
  • the valve is preferably designed simply as a 3/2-way switching valve device or it is preferably formed via a continuously adjustable 3/3-way proportional valve with transition positions.
  • the first control valve has a high-pressure connection, which is fluidically connected to the high-pressure connection of the valve, and a first working connection, which is fluidically connected to the first adjustment chamber.
  • the second control valve has a tank connection, which is fluidically connected to the pressure-medium sink, and a first work connection, which is fluidically connected to a second work connection of the first control valve, and a second work connection, which is fluidically connected to the work connection of the valve ,
  • At least one of the setpoint generator preferably both, an adjustable spring, via which the associated valve body is biased with the aforementioned pressure equivalent in its initial position in which the working ports of the associated control valve fluidly connected to each other and from the other terminal the associated control valve are fluidically separated.
  • the working ports are then fluidly separated in the case of the first control valve from the pressure port and in the case of the second control valve from the tank port.
  • the valve can be switched via its actuation into a switching position in which the pressure port of the valve is connected to its working port and the tank port of the valve is shut off. About this switching position, the control function of the second control valve is then activated and deactivated the first control valve.
  • the valve has a spring-loaded starting position, in particular, in which its working connection is fluidically connected to its tank connection and its pressure connection is shut off. In this initial position, the control function of the second control valve is deactivated, as already mentioned, and that of the first control valve is activated.
  • the 3/3-way proportional valve is preferably designed such that in its transitional positions its working connection is throttled fluidically connected to its tank connection and pressure connection.
  • the valve body of the 3/3-way proportional valve on a negative overlap with the two said ports associated pressure chambers. If a transitional position is taken, then a pressure is tapped between the pressure and the tank connection, which is then present over the working ports of the two control valves in the first control chamber.
  • valve body of the 3/3-way proportional valve is biased by a spring arrangement in one of the transition positions, in particular centered, and the spring assembly is in contact with a Rücckoppelungshebelan extract, via which a position of the actuating piston or the adjusting cylinder to the valve body of the 3/3-way proportional valve is enburgmeldbar.
  • the arrangement has a pressure medium source which can be connected to the pressure connection of the valve independently of or dependent on the operating mode, preferably via a check valve opening towards the pressure connection of the valve.
  • a particular adjustable stop is provided on the actuating cylinder. This is preferably adjusted so that a stroke of the adjusting cylinder or the adjusting piston - depending on which is designed to adjust the displacement volume is movable - starting from a zero position in only one direction is possible.
  • a stroke of the adjusting cylinder or the adjusting piston - depending on which is designed to adjust the displacement volume is movable - starting from a zero position in only one direction is possible.
  • FIG. 1 has a hydraulic arrangement 1, a first hydraulic machine 2 and a second hydraulic machine 4, the drive shafts 6 and 8 are rotatably connected to each other.
  • Both hydraulic machines 2, 4 are designed with adjustable displacement and arranged so that in left-handed drive shafts 6, 8, the first hydraulic machine 2 as a mode of operation of the engine and the second hydraulic machine 4 as a mode pumping operation.
  • the hydraulic machines 2, 4 reverse modes. Both hydraulic machines 2, 4 are coupled via a drive shaft 10 with a variable speed operable electric motor 12 and driven by this.
  • the hydraulic machines 2, 4 are operated in the open hydraulic circuit, wherein a low pressure port S of the first hydraulic machine 2 is fluidically connected to a tank T and its high pressure port P to a working port B of a designed as a differential cylinder hydraulic cylinder 14.
  • a low pressure port S of the hydraulic machine 4 is connected to the tank T and its high pressure port P to a working port A of the hydraulic cylinder 14.
  • the latter has a piston 16, which separates a fluidically connected to the working port cylinder chamber 18 from an annular space 20 connected to the working port B.
  • On the piston 16 is a piston rod 22, which defines the annular space 20 radially inward and a cylinder housing of the hydraulic cylinder 14 passes through to the outside.
  • a ratio of an annular space-side piston surface to a bottom-side piston surface of the piston 16 in the illustrated embodiment is about 1:10.
  • a punch of a hydraulic press is driven (not shown).
  • a cylinder axis 24 is oriented vertically so that a weight of the piston 16 and the piston rod 22 on the pressure medium in the annular space 20 loads. In principle, a horizontal alignment or alignment of the cylinder axis between vertical and horizontal is possible.
  • the arrangement 1 has an actuating cylinder 26 with an actuating piston 28 arranged axially displaceable therein.
  • the actuating cylinder 26 has a first actuating chamber 30, which is separated via the actuating piston 28 by a counteracting second actuating chamber 32.
  • a piston rod 34 attached to the actuating piston 28 passes through the second actuating chamber 32 and a cylinder housing of the actuating cylinder 26 and is coupled to an adjustable lifting element of the hydraulic machine 2 for adjusting its displacement volume. Since the first hydraulic machine 2 is designed as an axial piston machine in swash plate construction, this lifting element is a swash plate, which, because it is pivotable, is also called pivoting cradle.
  • the adjusting piston 28 is centered via two oppositely acting springs in the position V g0 .
  • a pressure medium line 40 From a pressure medium line 38 opening into the high-pressure connection P of the first hydraulic machine 2 branches off a pressure medium line 40, in which a check valve 42 is arranged, which opens from the pressure medium line 38 to the pressure medium line 40.
  • the pressure medium line 40 is connected to the second actuating chamber 32 of the actuating cylinder 26.
  • a feed of the second actuating chamber 32 with pressure medium via the pressure medium line 40 causes a reduction of the displacement volume of the hydraulic machine 2 in the direction V g0 .
  • From the pressure medium line 40 branches off a pressure medium line 44, which is connected to a high pressure port P of a 3/3-way proportional valve 46.
  • the unactuated initial position (a) of the high pressure port P of the 3/3-way proportional valve 46 is shut off and the working port A is connected to the tank port T.
  • a pressure medium line 50 and to the tank port T a pressure medium line 52 is connected to the working port A of the 3/3-way proportional valve 46.
  • the high-pressure port P is connected to the working port A of the directional proportional valve 46 and the tank port T shut off.
  • transition positions (c) are the ports P and T of the 3/3-way proportional valve 46 in throttled pressure fluid connection with the working port A.
  • the piston rod 34 via a feedback lever assembly 54 and a spring assembly 56 with a valve body 58 of the 3/3-way proportional valve 46th coupled.
  • the valve body 58 is centered on two equally strong and opposing springs of the spring assembly 56 in a middle of the transition positions (c).
  • pages of the valve body to which the spring assembly 56 engages relieved via each a pressure medium line 60 and a damping nozzle 62 to the tank T. Actuating forces acting on the valve body 58 are thus those of the electromagnet 48 and the spring arrangement 56 in the case of displacement volumes of V g > V g0 .
  • the arrangement has a first control valve 64 for regulating the pressure at the high-pressure port P of the first hydraulic machine 2 in its engine operation mode and a second control valve 66 for controlling this pressure in the operating mode pump operation.
  • Both control valves 64, 66 each have a first working port A 1 and a second working port A 2 .
  • the first control valve 64 also has a high pressure port P and the second control valve 66 a tank port T. Both control valves 64, 66 are designed as a continuously adjustable 3/2-way valve.
  • the high pressure port P of the first control valve 64 is fluidly connected via the pressure medium line 44 to the high pressure port P of the 3/3-way proportional valve 46 and the first working port A 1 of the first control valve 64 is connected via a pressure medium line 68 to the first actuating chamber 30 of the actuating cylinder 26. Also in the pressure medium line 68, a damping nozzle 62 is arranged.
  • the tank connection T of the second control valve 66 is fluidically connected to the tank T via a pressure medium line 70 and the first working connection A 1 of the second control valve 66 is fluidically connected to the second working connection A 2 of the first control valve 64.
  • the second working port A 2 of the second control valve 66 is fluidly connected to the working port A of the 3/3-way proportional valve 46.
  • the two control valves 64, 66 more precisely whose valve body 72, 74, as follows acted upon with pressure medium:
  • the valve body 72 of the first control valve 64 is permanently connected via the pressure medium line 44 to the high pressure port P of the first hydraulic machine 2 or a dependent thereon pressure or pending in the pressure medium line 40 auxiliary pressure p H , against a pressure equivalent of a designed as an adjustable spring setpoint generator 76, acted upon.
  • the valve body 74 of the second control valve 66 is acted upon by a pending in the pressure medium line 50 pressure against a pressure equivalent of a setpoint generator 78, which is also designed as an adjustable spring.
  • the setpoint generator 76, 78 bias the valve body 72, 74 respectively in their initial position (a), in which the working ports A 1 , A 2 of the respective control valve connected to each other and the other terminal of the working ports A 1 , A 2 is separated. Equivalent to the pressure equivalent acting on it Each valve body 72, 74 with the pressure in the pressure medium line 70, which is connected to the tank T, applied.
  • Both working ports A 1 , A 2 of the first control valve 64 are connected via a bypass line 80 and a damping nozzle 62 arranged therein in permanent pressure medium connection.
  • the two control valves 64, 66 are in their initial positions (a), so that the first actuating chamber 30 is connected to the working port A of the 3/3-way proportional valve 46.
  • the high-pressure port P of the 3/3-way proportional valve 46 is connected to the second actuating chamber 32. Due to the different piston surfaces of the piston 28 - the piston surface defining the second actuating chamber 32 is reduced by the cross-sectional area of the piston rod 34 - there is a tendency for the piston 28 to move in the direction of increasing the displacement volume V g .
  • any displacement of the piston 28 is transmitted to the valve body 58 and results in a return of the 3/3-way proportional valve 46 in the starting position (a), in which the working port A is connected to the tank port T.
  • the 3/3-way proportional valve 46 responds to the increase in the displacement volume V g with the connection of the first control chamber 30 with the pressure medium sink T, whereby pressure fluid from the first control chamber 30 can flow to the tank T out and the displacement volume V is held g0 ,
  • control function of the second control valve 66 is deactivated and only the first control valve 64 can regulate the pressure.
  • the deactivation of the control function of the second control valve 66 is therefore based on the fact that this is not acted upon by the pressure to be controlled.
  • the first control valve 64 As long as in the pressure medium line 44 of set at the setpoint generator 76 of the first control valve 64 value of 150 bar is not reached, the first control valve remains in its initial position (a), so that the first control chamber 30 can flow no pressure medium. Consequently, the displacement volume of the hydraulic machine 2 remains at V g0 . From the value of 150 bar in the pressure medium line 44, the first control valve 64 responds. There follows a regulation of the displacement volume of the first hydraulic machine 2 via the latter control valve 64, which is based on FIG. 2 is described.
  • FIG. 2 result from the capacity of the second hydraulic machine 4 and the swallowing power of the first hydraulic machine 2 pressure fluid flow rates Q 2 , Q 1 in the cylinder chamber 18 in and out of the annulus 20 out.
  • the second hydraulic machine 4 is thus in pump mode, the first hydraulic machine 2 in engine operation.
  • the solenoid 48 is de-energized, whereby the control function of the second control valve 66 is deactivated as described.
  • the pressure in the annular space 20 exceeds the value to be regulated of 150 bar. This is in the pressure medium line 44 to a pressure that exceeds the pressure equivalent of the setpoint generator 76 of the first control valve 64.
  • valve body 72 of this control valve 64 is moved out of the starting position (a) out into a control position, in which the high-pressure port P with the first working port A 1 in fluid communication device. Accordingly, the first actuating chamber 30 is supplied via the first working port A 1 and the pressure medium line 68 pressure medium, which leads to the displacement of the adjusting piston 28 in the direction of the maximum displacement volume V gmax .
  • n of the electric motor 12 and constant displacement volume of the second hydraulic machine 4 a movement speed of the piston 16 remains the same, resulting in increasing displacement volume V g of the first hydraulic machine 2, a pressure drop in the annular space 20 and the pressure medium line 44 results.
  • the pressure in the pressure medium line 44 drops again in the direction of 150 bar clearlyregelnden.
  • the feedback of the position of the actuating piston 28 to the valve body 58 of the 3/3-way proportional valve 46 takes place permanently in accordance with the above-described mode of operation.
  • the pressure medium volume flowing in via the control positions of the first control valve 64 of the first actuating chamber 30 is reduced by a bypass volume flow via the bypass line 80 and the damping nozzle 62.
  • the bypass line 80 thus causes a small leakage current, which causes the valve body 72 of the first control valve 64 always performs small control movements. As a result, a breakaway force of the valve body 72 is minimized. This has a positive effect on the response of the first control valve 64.
  • FIG. 3 shows the extended piston 16 at the stop. Accordingly, the annulus 20 is minimally small and the cylinder space 18 is maximally large. Via a position sensor 88, this operating state is detected. The speed n of the still left-rotating electric motor 12 is then greatly reduced via a control unit 92, wherein the first hydraulic machine 2 continue to operate in the engine mode and the second hydraulic machine 4 in the pump mode. The second control valve 66 is still in its initial position (A). As before, the solenoid 48 is de-energized, so that the valve body 58 can take only the transition positions (c) and the starting position (a).
  • the displacement of the adjusting piston 28 ends with the adjustment of the first hydraulic machine 2 in its displacement volume V g0 .
  • the speed n of the electric motor 12 is adjusted via the control device 92 such that a leakage from the cylinder chamber 18 and the second hydraulic machine 4 connected therein is compensated out and the piston 16 is held down with a pressure acting in the cylinder chamber 18 of 100 bar.
  • the piston rod 22 now according to FIG. 4 be retracted again.
  • the annular space 20 has to be filled with pressure medium via the first hydraulic machine 2 and pressure medium has to be removed from the cylinder space 18 via the second hydraulic machine 4.
  • the first hydraulic machine 2 must be switched from its first operating mode, the engine operation, to its second operating mode, the pump operation.
  • the second hydraulic machine 4 must change to engine operation. This is done solely by the fact that the direction of rotation of the electric motor 12 is switched from left to right. Since now another mode of action of the pressure control for the first hydraulic machine 2 is to be provided in pump operation, the electromagnet 48 is energized.
  • the pressure medium line 50 via the switching position (b) of the 3/3-way proportional valve 46 is connected to the pressure medium line 44 and the pressure applied there acts on the pressure medium line 50 to the valve body 74 of the second control valve 66.
  • the setpoint of the setpoint generator 76 of the first control valve 64 is higher than the desired value of the setpoint generator 78 of the second control valve. This is here by the desired value of the second control valve 66 of 120 bar given.
  • both actuating chambers 30, 32 of the actuating cylinder 26 are depressurized, whereby the actuating piston 28 is in its position V g0 .
  • the first hydraulic machine 2 pressure medium in the annulus 20 To move the piston 16 in FIG. 5 against gravity (in FIG. 4 to the left) must be promoted by the first hydraulic machine 2 pressure medium in the annulus 20.
  • the first actuating chamber 30 must be filled with pressure medium in order to achieve a displacement volume V g > 0.
  • the first hydraulic machine 2 can not deliver the quantity of pressure medium necessary to build up pressure and to fill the first actuating chamber 30. There is a need for an external auxiliary pressure source.
  • an auxiliary pump 82 is provided, whose pressure port is connected via a pressure medium line with an auxiliary pressure port P H of the first hydraulic machine 2.
  • a spring-loaded check valve 84 is arranged, which is connected via a pressure medium line 86 to the pressure medium line 40 and opens to this.
  • the auxiliary pump 82 is coupled via a drive shaft 88 with the first hydraulic machine 2 and is consequently also driven via the electric motor 12.
  • the auxiliary pump 82 designed as a fixed displacement pump supplies a pressure of 35 bar. At a given speed thus 35 bar with opening of the check valve 84 in the pressure medium lines 86, 40 and 44 are on. This pressure is present in the second actuating chamber 32 and is reported via the switching position (b) of the 3/3-way proportional valve 46 in the pressure medium line 50. Due to the low pressure of 35 bar, both control valves 64, 66 are still in their initial positions (a). As a result, the pressure of 35 bar is also present in the first actuating chamber 30. Since the effective piston ring surface on the control piston 28 is smaller than the piston bottom surface, there is an imbalance of forces on the control piston 28, as a result of which the displacement volume in the direction V gmax is increased. This results in a pressure build-up in the pressure medium lines 38, 40 and 44 to the second control valve 66 responsive to the set value of 120 bar.
  • the second hydraulic machine 4 Since the second hydraulic machine 4 continues to be operated in the engine mode, the pressure in the cylinder chamber 18 decreases to atmospheric pressure. So that it does not fall below it, the second hydraulic machine 4 sucks pressure medium via a check valve 86.
  • the pressure in the annular space 20 is equal to the load pressure of the stationary piston 16 and the piston rod 22 including load and thus less than 120 bar, since this pressure value only occurs in the above-described clamped retraction of the piston rod 22.
  • both control valves 64, 66 are in their initial positions (a). Since the second control valve 66 is activated when the solenoid 48 is energized and the pressure of 100 bar is less than the target value of 120 bar set at the setpoint generator 78, the control piston 28 is extended to V gmax .
  • One advantage of the first embodiment is based on the fact that the electromagnetically operable 3/3-way proportional valve 46 together with the feedback lever assembly 54 and the spring assembly 56 is often provided by default for the construction of an adjustable hydraulic machine. Such prepared hydraulic machines are then to supplement the said control valves 64, 66 with only little effort.
  • a hydraulic arrangement 101; 201 correspond substantially to the first embodiment of the foregoing description. Since deviations from the first embodiment are provided only in the range of the above-described valve 46 and the adjusting cylinder 26, a representation of the hydraulic cylinder 14, the second hydraulic machine 4, the electric motor 12, the hydraulic pump 82 and the periphery of the four components mentioned omitted. About the embodiments consistent components of the arrangements 1; 101; 201 are provided with the same reference numerals. To shorten the description, only the differences of the embodiments will be discussed.
  • the hydraulic assembly 101 an actuatable means 146, which is designed as a 3/2-way switching valve.
  • the 3/2-way switching valve 146 can be switched to the already discussed in the first embodiment switching position (b), whereby the pressure medium line 44 connected to the pressure medium line 50 and the tank port T of the 3/2-way switching valve 146 is shut off.
  • the second control valve 66 is activated with its control function. Via a spring 156, the valve 146 in its initial position (a), which also corresponds to the starting position (a) of the first embodiment, biased.
  • the first control valve 64 is active with its control function and the pressure medium line 50 is connected via the pressure medium line 52 to the tank T, whereas it is shut off against the pressure medium line 44.
  • the initial position (a) relieves the 3/2-way switching valve 146, the first actuating chamber 30 through the working ports A 1 , A 2 to the tank T out.
  • the device constructed simple valve 146 eliminates the need for the feedback lever assembly 54 and the spring assembly 56 according to the first embodiment. Since these two components are usually formed over a device complex assembly, the second embodiment provides according to FIG. 6 A considerable device simplification compared to the first embodiment.
  • a further device-technical simplification brings the use of the valve 146 to a control cylinder 126 of the first hydraulic machine 2 with it. It follows that a return spring in the first actuating chamber 30, as was necessary in the first embodiment, can be dispensed with.
  • the third embodiment according to FIG. 7 corresponds to the second embodiment according to FIG. 6 up to a changed pressurizing of the valve body 72 of the first control valve 64.
  • the valve body 72 in the direction mentioned above a pressure medium line 250 with the pressure in the pressure medium line 50 loaded.
  • it is on actuation of the 3/2-way switching valve 146 in its switching position (b), so if the second control valve 66 is to be activated in its control function, loaded on both sides with the pressure in the pressure medium line 44.
  • the valve body 72 is biased independently of the pressure in the pressure medium line 44 in the starting position (a) and thus deactivated in its control function.
  • a setpoint at the setpoint generator 76 can be set, which is less than or equal to the setpoint of the setpoint generator 78 of the second control valve 66.
  • This changed pressure medium loading of the valve body 72 thus increases the flexibility of the hydraulic arrangement 201 with respect to the pressure regulation in the different operating modes pump operation and engine operation of the first hydraulic machine 2.
  • a hydraulic arrangement with an adjustable hydraulic machine and a first operating mode of the hydraulic machine, in particular an engine operation associated control valve, via the control of a control chamber of a control cylinder of the hydraulic machine can be acted upon with pressure medium.
  • a second operating mode of the hydraulic machine in particular for a pump operation, a second control valve for pressure medium to the actuating chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (15)

  1. Système hydraulique comprenant une première machine hydraulique (2) à volume de refoulement réglable (Vg), laquelle comporte un cylindre de réglage (26 ; 126) doté d'un piston de réglage (28) pour le réglage du volume de refoulement (Vg), piston de réglage au moyen duquel une chambre de réglage (30) est formée dans le cylindre de réglage (26 ; 126), comprenant une première soupape de régulation (64) par le biais de la fonction de régulation de laquelle, dans un premier mode de fonctionnement de la première machine hydraulique (2), une alimentation en fluide sous pression dans la chambre de réglage (30) et une évacuation de fluide sous pression hors de la chambre de réglage (30) peuvent être commandées, dans lequel un moyen (46 ; 146) pouvant être actionné, par le biais de l'actionnement duquel la fonction de régulation de la première soupape de régulation (64) peut être désactivée et une fonction de régulation d'une deuxième soupape de régulation (66) du système peut être activée, par le biais de laquelle, dans un deuxième mode de fonctionnement de la première machine hydraulique (2), l'alimentation en fluide sous pression et l'évacuation de fluide sous pression dans et à partir de la chambre de réglage (30) peuvent être commandées.
  2. Système selon la revendication 1, dans lequel le premier mode de fonctionnement est un fonctionnement de moteur et le deuxième mode de fonctionnement est un fonctionnement de pompe, et un autre sens de rotation d'un arbre d'entraînement (6) de la première machine hydraulique est associé aux deux modes de fonctionnement.
  3. Système selon la revendication 2, comprenant une deuxième machine hydraulique (4), dans lequel le système (1 ; 101 ; 201) est conçu de telle sorte que la première machine hydraulique (2) présente un autre des deux modes de fonctionnement que celui de la deuxième machine hydraulique (4).
  4. Système selon l'une des revendications précédentes, dans lequel, par le biais de l'alimentation en fluide sous pression et de l'évacuation de fluide sous pression, une haute pression (p) de la première machine hydraulique (2) ou une pression dépendante de celle-ci peut être régulée, et dans lequel, par le biais de l'actionnement, un corps (74) de la deuxième soupape de régulation (66) peut être soumis à la haute pression (p) ou à la pression dépendante de celle-ci ou à une pression auxiliaire (pH) du système à l'encontre d'un équivalent de pression d'un transmetteur de valeur de consigne (78) de la deuxième soupape de régulation (66), et dans lequel, indépendamment de l'actionnement, un corps (72) de la première soupape de régulation (64) est soumis à la haute pression (p) ou à la pression dépendante de celle-ci ou à la pression auxiliaire (pH) à l'encontre d'un équivalent de pression d'un transmetteur de valeur de consigne (76) de la première soupape de régulation (64).
  5. Système selon la revendication 4, dans lequel une valeur de consigne de la première soupape de régulation (64) est supérieure à une valeur de consigne de la deuxième soupape de régulation (66).
  6. Système selon la revendication 4, dans lequel le corps (72) de la première soupape de régulation (64) est, par le biais de l'actionnement, soumis à la haute pression (p) ou à la pression dépendante de celle-ci ou à la pression auxiliaire (pH) en agissant de manière identique à l'équivalent de pression du transmetteur de valeur de consigne (76) de la première soupape de régulation (64).
  7. Système selon la revendication 6, dans lequel une valeur de consigne de la première soupape de régulation (64) est inférieure ou égale à une valeur de consigne de la deuxième soupape de régulation (66).
  8. Système selon l'une des revendications précédentes, dans lequel le moyen est réalisé par le biais d'une soupape (46 ; 146) qui comporte un raccord haute pression (P) qui peut être relié, en particulier est relié, fluidiquement à un raccord haute pression (P) de la première machine hydraulique (2) ou à une source de fluide sous pression auxiliaire (82), et qui comporte un raccord de réservoir (T) qui peut être relié, en particulier est relié, fluidiquement à un puits de fluide sous pression (T), et qui comporte un raccord de travail (A) qui peut être relié, en particulier est relié, à la chambre de réglage (30) par le biais de raccords de travail (A1, A2) des soupapes de régulation (64, 66).
  9. Système selon la revendication 8, dans lequel la première soupape de régulation (64) comporte un raccord haute pression (P) qui peut être relié, en particulier est relié, fluidiquement au raccord haute pression (P) de la soupape (46 ; 146), et comporte un premier raccord de travail (A1) qui peut être relié, en particulier est relié, fluidiquement à la chambre de réglage (30).
  10. Système selon la revendication 8 ou 9, dans lequel la deuxième soupape de régulation (66) comporte un raccord de réservoir (T) qui peut être relié, en particulier est relié, fluidiquement au puits de fluide sous pression (T), et comporte un premier raccord de travail (A1) qui peut être relié, en particulier est relié, fluidiquement à un deuxième raccord de travail (A2) de la première soupape de régulation (66), et comporte un deuxième raccord de travail (A2) qui peut être relié, en particulier est relié, fluidiquement au raccord de travail (A) de la soupape (46 ; 146).
  11. Système selon la revendication 4 ou une revendication s'y rapportant, dans lequel les transmetteurs de valeur de consigne (76, 78) comprennent respectivement un ressort réglable par le biais duquel le corps de soupape (72, 74) associé peut être précontraint dans une position initiale (a) dans laquelle les raccords de travail (A1, A2) de la soupape de régulation (64, 66) associée sont reliés fluidiquement l'un à l'autre et sont séparés fluidiquement de l'autre raccord (P, T) de la soupape de régulation (64, 66) associée.
  12. Système selon l'une des revendications 8 à 11, dans lequel la soupape (46 ; 146) peut être commutée dans une position de commutation (b) par le biais de l'actionnement, position dans laquelle le raccord haute pression (P) de la soupape (46 ; 146) est relié à son raccord de travail (A) et le raccord de réservoir (T) de la soupape (46 ; 146) est fermé.
  13. Système selon l'une des revendications 8 à 12, dans lequel la soupape présente une position initiale (a) dans laquelle le raccord de travail (A) de la soupape (46 ; 146) est relié fluidiquement à son raccord de réservoir (T) et le raccord haute pression (P) de la soupape (46 ; 146) est fermé.
  14. Système selon l'une des revendications 8 à 13, dans lequel la soupape est réalisée sous forme de soupape de commutation à 3/2 voies (146), ou dans lequel la soupape (46) est réalisée sous forme de soupape proportionnelle à 3/3 voies (46) réglable en continu et présentant des positions de transition (c) dans lesquelles le raccord de travail (A) de la soupape proportionnelle à 3/3 voies (46) est relié fluidiquement de manière étranglée à son raccord de réservoir (T) et à son raccord haute pression (P) .
  15. Système selon la revendication 14, dans lequel un corps (58) de la soupape proportionnelle à 3/3 voies (46) peut être précontraint, en particulier est précontraint, par le biais d'un ensemble de ressorts (56), dans l'une des positions de transition (c), et dans lequel l'ensemble de ressorts (56) est en appui contre un levier d'un ensemble de levier de rétroaction (54) par le biais duquel une position du piston de réglage (28) ou du cylindre de réglage (26) peut être renvoyée, en particulier est renvoyée, au corps (58) de la soupape proportionnelle à 3/3 voies (46).
EP14805265.7A 2013-12-02 2014-11-28 Système hydraulique Active EP3077674B1 (fr)

Applications Claiming Priority (2)

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DE102013224657.9A DE102013224657A1 (de) 2013-12-02 2013-12-02 Hydraulische Anordnung
PCT/EP2014/075885 WO2015082321A1 (fr) 2013-12-02 2014-11-28 Système hydraulique

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EP3077674B1 true EP3077674B1 (fr) 2019-06-19

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DE112017002163A5 (de) * 2016-04-25 2019-01-17 MAE Maschinen- und Apparatebau Götzen GmbH Hydraulische Achse für eine Presse
DE102016223099A1 (de) * 2016-11-23 2018-05-24 Robert Bosch Gmbh Elektrohydraulische Anordnung und Hydraulische Achse
DE102018210685A1 (de) * 2018-06-29 2020-01-02 Robert Bosch Gmbh Hydrostatischer Fahrantrieb und Verfahren zur Steuerung des hydrostatischen Fahrantriebes
DE102018210720A1 (de) * 2018-06-29 2020-01-02 Robert Bosch Gmbh Hydrostatischer Fahrantrieb mit Druckabschneidung und Verfahren zum Kalibrieren der Druckabschneidung
DE202018003042U1 (de) * 2018-06-29 2019-10-01 M A E Maschinen- Und Apparatebau Götzen Gmbh Hydraulischer Zylinderantrieb und hydraulischer Pressenantrieb
DE102018212854B4 (de) * 2018-08-01 2021-11-25 Danfoss Power Solutions Gmbh & Co. Ohg Hochdruckschutzsystem
DE102018218113A1 (de) * 2018-10-23 2020-04-23 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102022214389A1 (de) * 2022-12-23 2024-07-04 Magna powertrain gmbh & co kg Anordnung und Verfahren zur bedarfsgerechten Verteilung von Kühl-/Schmierölströmen im elektrischen Traktionsantrieb

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Publication number Publication date
CN105934585A (zh) 2016-09-07
DE102013224657A1 (de) 2015-06-03
ES2746213T3 (es) 2020-03-05
CN105934585B (zh) 2018-07-17
WO2015082321A1 (fr) 2015-06-11
EP3077674A1 (fr) 2016-10-12

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