CN102612430A - Prestressed hydraulic drive with variable-speed pump - Google Patents

Prestressed hydraulic drive with variable-speed pump Download PDF

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Publication number
CN102612430A
CN102612430A CN2010800427717A CN201080042771A CN102612430A CN 102612430 A CN102612430 A CN 102612430A CN 2010800427717 A CN2010800427717 A CN 2010800427717A CN 201080042771 A CN201080042771 A CN 201080042771A CN 102612430 A CN102612430 A CN 102612430A
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CN
China
Prior art keywords
master cylinder
switch
valve
hydraulic press
drive device
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Application number
CN2010800427717A
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Chinese (zh)
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CN102612430B (en
Inventor
S·施密特
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • 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
    • F15B2211/30—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • 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
    • F15B2211/78—Control of multiple output members
    • F15B2211/782—Concurrent control, e.g. synchronisation of two or more actuators
    • 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

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

Abstract

The present invention relates to a hydraulic drive with a hydraulic machine (1) activated with variable speed by an electric drive motor (2), a main cylinder (4) for carrying out a sequence of movements while building up force and a secondary cylinder (8) for carrying out a rapid sequence of movements. According to the invention, the hydraulic machine (1), mechanically activated by the drive motor (2), uses one of its pressure connections to prestress at least one piston side of the main cylinder (4) with a predetermined permanent pressure, this hydraulic machine (1) bringing about a reciprocating movement of the main cylinder (4) and of the secondary cylinder (8) on the basis of one of the two sequences of movements by selectively circulating pressure medium in a closed circuit in which the hydraulic machine (1) is included.

Description

The fluid pressure drive device of the precharge of band variable speed pump
Technical field
The present invention relates generally to as described in the preamble, the fluid pressure drive device that is preferred for forcing press, plastics machinery, bending machinery etc. according to Patent right requirement 1.
Such drive unit designs in order to realize following at least two motion processes: promptly quick converting motion (hereinafter referred to as " fast travel ") and the working motion (hereinafter referred to as " pressure stroke ") that applies power.
Background technology
From prior art, for example according to known such, the fluid pressure drive device that is used for forcing press of document EP 0 785 861 B1.This drive unit is driven by one, produce predetermined constant pressure in the primary pressure pipe-line system hydrostatic machine and one are by hydraulic motor and mechanically be connected to the hydraulic transformer that the hydraulic pump on the hydraulic motor forms and form.The hydraulic motor of this preferred tunable joint is connected on the primary pressure pipe-line system, and is therefore driven by the hydrostatic machine.This same adjustable hydrostatic pump applies hydraulic coupling for the second pressure pipe-line system, and pressure cylinder is installed in the said second pressure pipe-line system, and the cylinder space of said pressure cylinder is connected on two hydraulic joints of hydraulic pump through valve.
At last, two cylinder spaces of this of pressure cylinder are connected with the primary pressure pipe-line system through pressure pipeline, so that apply this primary pressure (precharge pressure that is equivalent to the pressure cylinder requirement) in advance to pressure piston.
Yet what be difficult to technically confirm is: the design of layout that will have the hydraulic transformer of said structure is converted into practice.The number of the consumption of its structure and the hydraulic part of demand and harmonious has each other so reduced the economy of this known fluid pressure drive device, thereby makes it not be widely accepted in professional domain.
Summary of the invention
In view of this prior art, task of the present invention is, a kind of such fluid pressure drive device is provided, and it can be realized with the hydraulic part number that reduces, and the energy consumption that however is in operation is lower.
The fluid pressure drive device of the characteristic of this task through having Patent right requirement 1 solves.The theme that other favourable design of the present invention is the subordinate claim.
Therefore, the present invention relates to a kind of fluid pressure drive device, it has a hydraulic press that is triggered by electric drive motor variable speed ground, be used to implement master cylinder and the secondary cylinder that is used to implement quick motion process of the motion process of the power of setting up.According to the present invention; On two piston areas by preferably affacting, the further predetermined permanent compressions that preferably produced by external pressure source of this master cylinder pressurize in advance or compress; Wherein hydraulic press is linked into circulation selected in the closed loop wherein through pressure medium and carries in the middle of this hydraulic press, according to one of two motion processes cause master cylinder and secondary cylinder stroke motion.
Through exerting pressure in advance to this drive unit; Preferably reduce the compression volume that to carry significantly by means of the hydraulic press of also this motion process being responsible for or through external pressure source; Wherein the precharge pressure of drive unit and as the combination of the variable speed pump (hydraulic press) of the electric servo operation of precharge mechanism that is used for two cylinders and hydraulic drive mechanism has realized having fluid pressure drive device short cycle, the saving energy economically.
Description of drawings
Next according to the preferred embodiment of the invention the present invention is carried out detailed explanation with reference to accompanying drawing.
Accompanying drawing illustrates:
Fig. 1 is by the fluid pressure drive device of one of the present invention's the preferred embodiment schematic diagram at (under the precharge pressure state) under the halted state;
Fig. 2 is that the fluid pressure drive device by Fig. 1 is in the schematic diagram in " fast travel " state downwards;
Fig. 3 is that the fluid pressure drive device by Fig. 1 is in the schematic diagram in " pressure stroke " state;
Fig. 4 is the schematic diagram that is in the recompression stage by the fluid pressure drive device of Fig. 1; And
Fig. 5 is that the fluid pressure drive device by Fig. 1 is in the schematic diagram in " fast travel " (backhaul stage) state upwards.
The specific embodiment
As what can find out from whole accompanying drawings, have the pressure medium source of hydraulic press 1 form that drives as the variable speed of pump according to fluid pressure drive device of the present invention, said for this reason hydraulic press mechanically is connected to motor 2.Hydraulic press 1 is on the pressure pipeline system that is connected to the hydraulic circuit that forms closed loop on its two compression fittings.
Specifically, first connects pipeline 3 is connected on first compression fittings of hydraulic press 1, and said first connects directly the lead 4a of pressure chamber of piston side of master cylinder 4 of pipeline.Second pipeline 5 is connected on second compression fittings of hydraulic press 1, and said second pipeline is connected with the 4b of pressure chamber (annular compartment hereinafter referred to as) of the piston rod side of master cylinder 4 through valve 6.Valve 6 is current be configured to reversal valve and also especially be configured to have first position of the switch, 3/2 reversing switch valve of second switch position and the 3rd position of the switch, in said first position of the switch, only allow hydraulic fluid to flow towards hydraulic press 1 from the annular compartment 4b of master cylinder 4; Hydraulic fluid can flow towards both direction in said second switch position; Second pipeline 5 is fully closed in the 3rd position of the switch.
5 branch roads 7 are installed in second pipeline between hydraulic press 1 and reversing switch valve 6 above-mentioned, the lead 8a of pressure chamber of piston rod side of secondary cylinder 8 of said branch road.At this, the diameter of the piston 8b of secondary cylinder 8 is significantly less than the diameter of the piston 4c of master cylinder 4, thereby for the comparable volume flow of hydraulic fluid, the stroke of secondary cylinder 8 is greater than the stroke of master cylinder 4.In addition, the annular side of cylinder 4,8 has the piston side area identical that amounts to master cylinder 4 in ideal conditions.
Bypass duct or short circuit pipeline 9 are set at last, and said bypass duct or short circuit pipeline couple together the 4a of piston chamber and its annular compartment 4b of master cylinder 4.Are connected in this bypass duct 9 in the middle of the short circuit valve 10, said short circuit valve is current to be configured to the reversing switch valve and preferable configuration is 2/2 reversing switch valve.Bypass duct 9 complete (that is to say on both direction) is opened in first position of the switch of this short circuit valve 10, wherein in the second switch position, only allows fluid to flow to the 4a of piston chamber of master cylinder 4 through bypass duct 9 from annular compartment 4b.
In the concrete embodiment of the present invention, the fluid pressure drive device with said structure is contained in the forcing press.The piston rod 8c of the piston rod 4d of master cylinder 4 and secondary cylinder 8 is connected with the depression bar 11 of supporting movably for this reason, on said depression bar, is fixed with drift 12 or stamping tool.
Much be used to avoid the safety device that descends unintentionally of overvoltage condition or depression bar 11 in principle in addition according to hydraulic system of the present invention, yet they show no longer in detail in the drawings.Like this, the annular compartment 8a of secondary cylinder 8 can guarantee safety through two centre valves that be connected in series, that monitored (Sitzventil) (not shown).Can prevent the decline of top drift 12 thus reliably.In addition, can guarantee that the plunger shaft 4a that prevents master cylinder 4 by mistake exerts pressure.The release of being monitored of reversal valve 6,10 shown in this can pass through itself or the electric drive motor 2 through hydraulic press 1 is carried out.
For the leakage loss in the bucking-out system, pressure accumlator 13 is being connected on first pressure pipeline 3 between the 4a of piston chamber of hydraulic press 1 and master cylinder 4 through valve 14.The 2/2 reversing switch valve that this valve 14 through reversal valve, preferably has first position of the switch and a second switch position provides, and the connection in said first position of the switch between the external pressure source 13 and first pressure pipeline 3 discharges fully; In said second switch position, only allow liquid to flow into first pressure pipeline 3 from external pressure source 13.
In the duty according to fluid pressure drive device of the present invention, the 4a of pressure chamber of the piston side of master cylinder 4 stably is applied in the hydraulic coupling of predetermined, constant (particularly conditioned) through pressure medium source at least.At this, the circulation of pressure medium in the pressure circuit of closed loop that move through of two cylinders 4,8 carries the hydraulic press 1 that drives by variable speed to control.
For these two cylinders 4; The control of 8 motion process; Conclusive is from corresponding annular chamber 4b; The pressure medium of 8a is through the injection or the discharge of the hydraulic press 1 of variable speed driving, and wherein the whole motion process of forcing press impulse stroke can be by means of (constant) pump control of valve 6,10 and variable speed driving under these two cylinders are participated in.
Working method according to fluid pressure drive device of the present invention can illustrate and describe as follows:
When stopping (in the retrieving position of depression bar 11) at fluid pressure drive device according to Fig. 1, reversing switch valve 6 is in and wherein only allows the position of the switch of fluid from the annular compartment 4b outflow of master cylinder 4; And short circuit valve 10 is in the position of the switch that bypass duct 9 is wherein opened fully.In addition, the electric drive motor 2 of hydraulic press 1 is closed.
In this (static) state, the weight of depression bar 11 is by the internal pressure support of the 8a of piston chamber of secondary cylinder 8, and at the annular compartment and the 4a of piston chamber of master cylinder 4, is in pressure balance through short circuit valve 10 among the 4b.
In order to get into downward fast travel state, switch to the total blockage position and drive hydraulic press 1 according to Fig. 2 valve 6 from this (static) state.Pressure medium can only be drawn out of and be admitted to the 4a of piston chamber of main piston 4 from the annular compartment 8a of secondary cylinder 8 through pipeline 5 thus.While master cylinder chamber 4a, the pressure balance between the 4b keeps through the short circuit valve 10 that still always opens wide fully.
Because secondary cylinder 8 is less than master cylinder 4; And 1 volume to the annular side of secondary cylinder 8 of pump works; Even so when hydraulic press 1 was designed to low capacity, the moving downward of depression bar 11 (and also having recovery movement later on) also can be carried out with higher relatively speed under predetermined volume flow.In addition, can also further improve speed through (permission) momentary overload of electric drive motor 2 and further improve later pressure.
In case drift 12 has arrived workpiece to be processed 15, short circuit valve 10 just switches to and only allows therein from the position of the switch of master cylinder 4 annular compartment 4b outflow; And valve 6 switches to and allows fluid to flow to the position of the switch of hydraulic press 1 from annular compartment 4b therein.From now on, under this state, because master cylinder chamber 4a according to Fig. 3; The pressure balance of passing through short circuit valve 10 between the 4b no longer takes place; The internal pressure of annular compartment 4b also reduces through hydraulic press 1, otherwise the internal pressure of the 4a of piston chamber of master cylinder 4 is held in other words and improves.That is to say, replace the significant compression of the piston side of master cylinder 4, actual pressure produces through the release of the annular side of cylinder 4,8.Because master cylinder chamber 4a, the pressure balance between the 4b no longer exists, the pressurization campaign of the continuation of master cylinder 4 when keeping identical volume flow, also adopt than before fast travel the time with respect to the obvious littler speed of descending motion.
When finishing to pressure process, valve 6 switches in the position of the switch according to Fig. 4, after this connects pipeline 5 inner liquid and flows towards both direction, that is to say, can flow out and can flow to the annular compartment 4b of master cylinder 4 from the annular compartment 4b of master cylinder 4.Master cylinder chamber 4a in this case, the pressure balance between the annular compartment 8a of 4b and secondary cylinder 8 realizes with branch road 7 through connecting pipeline 5, wherein can recover energy through electric drive motor 2 simultaneously.
Be recoverable to depression bar 11 at last, method is: as shown in Figure 5, valve 6 switches to the position of the switch that only allows therein from the annular space 4a outflow of master cylinder 4; And short circuit valve 10 switches to the position of the switch that bypass duct 9 (on both direction) is therein opened fully.
If driving hydraulic press 1 under this state; So that make the plunger shaft 4a sucking-off of pressure medium from master cylinder 4; Then the pressure medium of sucking-off is at two master cylinder chamber 4a, is pressed towards the annular compartment 8a of secondary cylinder 8 during complete pressure balance between the 4b, and it makes depression bar 11 regain once more with higher speed.
In above-mentioned fluid pressure drive device, hydraulic press 1 can be connected to the duty valve in other words on the valve piece (further not illustrating) of safety valve that contains drive unit with flange.Can also install above that and be used to move pump motor.This unit further is installed on the hydraulic cylinder, and a kind of compact especially driving shaft is provided thus.
List of numerals
Figure BPA00001560009000061

Claims (7)

1. fluid pressure drive device; It has the hydraulic press (1) that triggered by electric drive motor (2) variable speed ground, be used to implement master cylinder (4) and the secondary cylinder (8) that is used to implement quick motion process of the motion process of the power of setting up; It is characterized in that; For at least one piston side of said master cylinder (4) applies by external pressure source (13) and/or on its compression fittings, set up, the predetermined permanent compression of hydraulic press (1) that mechanically triggered by drive motor (2); Wherein said hydraulic press (1) also is connected to circulation selected in the loop of closed loop wherein through pressure medium and carries in the middle of hydraulic press (1), cause the stroke motion of said master cylinder (4) and secondary cylinder (8) respectively according to one of two motion processes.
2. according to the described fluid pressure drive device of claim 1; It is characterized in that the annular compartment (4b) that the other compression fittings of said hydraulic press (1) is connected to the piston rod side of said master cylinder (4) is gone up and is connected on the annular compartment (8a) of piston rod side of said secondary cylinder (8).
3. according to the described fluid pressure drive device of claim 2, it is characterized in that middle valve, the preferred middle reversing switch valve (6) that connects of connecting in the connection pipeline (5) of the closed loop between said hydraulic press (1) and master cylinder annular compartment (4b).
4. according to the said fluid pressure drive device of claim 3; It is characterized in that; Said valve (6) is 3/2 a reversing switch valve with first position of the switch, second switch position and the 3rd position of the switch, in said first position of the switch, only allows hydraulic fluid to flow to said hydraulic press (1) from master cylinder annular compartment (4b); Hydraulic fluid can flow towards both direction in said second switch position; Connecting pipeline (5) total blockage described in said the 3rd position of the switch.
5. according to claim 3 or 4 described fluid pressure drive devices, it is characterized in that connecting the bypass duct in said master cylinder piston chamber (4a) and the loop of the closed loop of master cylinder annular compartment (4b), and be connected in the said bypass duct in the middle of the short circuit valve (10).
6. according to the fluid pressure drive device of claim 5; It is characterized in that; Said short circuit valve (10) is 2/2 reversing switch valve; Said short circuit valve is opened said bypass duct (9) fully in first position of the switch, and in the second switch position, only allows fluid to flow to the piston chamber (4a) of said master cylinder (4) through bypass duct (9) from annular compartment (4b).
7. according to each described fluid pressure drive device in the above-listed claim, it is characterized in that (4b 8a) has piston side (4a) area identical that amounts to said master cylinder (4) to the piston rod side of two cylinders (4,8).
CN201080042771.7A 2009-09-25 2010-07-27 The fluid pressure drive device of the precharge with variable speed pump Active CN102612430B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009043034.2 2009-09-25
DE200910043034 DE102009043034A1 (en) 2009-09-25 2009-09-25 Prestressed hydraulic drive with variable speed pump
PCT/EP2010/004578 WO2011035828A1 (en) 2009-09-25 2010-07-27 Prestressed hydraulic drive with variable-speed pump

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CN102612430A true CN102612430A (en) 2012-07-25
CN102612430B CN102612430B (en) 2016-04-27

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EP (1) EP2480405B1 (en)
CN (1) CN102612430B (en)
DE (1) DE102009043034A1 (en)
TW (1) TWI519717B (en)
WO (1) WO2011035828A1 (en)

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EP2480405B1 (en) 2013-06-19

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