EP2024647A1 - Mecanisme d'entrainement hydrostatique avec equilibrage des volumes - Google Patents

Mecanisme d'entrainement hydrostatique avec equilibrage des volumes

Info

Publication number
EP2024647A1
EP2024647A1 EP07725766A EP07725766A EP2024647A1 EP 2024647 A1 EP2024647 A1 EP 2024647A1 EP 07725766 A EP07725766 A EP 07725766A EP 07725766 A EP07725766 A EP 07725766A EP 2024647 A1 EP2024647 A1 EP 2024647A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic pump
working
pressure
valve
line
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.)
Withdrawn
Application number
EP07725766A
Other languages
German (de)
English (en)
Inventor
Seppo Tikkanen
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP2024647A1 publication Critical patent/EP2024647A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • 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
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—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
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means

Definitions

  • the invention relates to a hydrostatic drive with a double-acting hydraulic cylinder and a volume flow compensation.
  • a disadvantage of the hydrostatic drive known from DE 103 43 016 A1 is that the ratio between the sum of the delivery volumes of the two hydraulic pumps and the delivery volume of the hydraulic pump in a closed circuit must be in the same ratio as the piston surfaces of the working piston are to each other. Consequently, if two identical hydraulic pumps are used, their respective delivery volume must be adjusted by the corresponding adjusting devices so that this condition is met. Conversely, it is necessary, when using two identical hydraulic pumps, as can be advantageously realized by using a double pump, to use a double-acting hydraulic cylinder whose piston surfaces have a corresponding ratio. In general, the two hydraulic pumps of a double pump unit are identical, so that the area ratio of the two piston surfaces would have to be 2: 1. Commercially available double-acting hydraulic cylinders However, usually have a deviating area ratio of the piston surfaces and thus different flow rates during displacement of the working piston.
  • the hydrostatic drive comprises a first hydraulic pump and a second hydraulic pump and a double-acting hydraulic cylinder.
  • the respective first connections of the first and the second hydraulic pump are connected together to a first working chamber of the hydraulic cylinder.
  • only the second connection of the second hydraulic pump is connected to a second working chamber.
  • the second connection of the first hydraulic pump is connected to a pressure medium reservoir.
  • Delivery volume of both hydraulic pumps to the delivery volume of the second hydraulic pump may differ from the area ratio of the first piston surface to the second piston surface. As a result, there may be a difference in the oil balance.
  • the invention is a
  • Removal valve provided by which compensated for this difference in the oil flow balance and pressure fluid is discharged at a first conveying direction and thus a flow equalization is achieved.
  • the removal valve preferably connects the first working chamber or the second working chamber with a pressure medium reservoir.
  • a purge valve as a sampling valve.
  • the flushing valve is switched in response to the pressures in the first and the second working chamber, respectively, such that it connects the second or the first working chamber to the pressure medium reservoir.
  • a volume flow compensation by removal of pressure medium can thus be carried out by the flush valve in each case on the side of the hydrostatic drive connected to the current suction side of the hydraulic pumps.
  • a feed device can be used to connect the first or the second working chamber with the pressure medium reservoir.
  • a feed pump is preferably provided. This promotes, in particular on the suction side of the first and the second hydraulic pump, a volume of pressure required for volume flow compensation in the hydrostatic circuit of the hydrostatic drive.
  • the first and the second hydraulic pump are jointly adjustable in their delivery volume.
  • the bleed valve is connected via a first working line and / or via a second working line to the first and / or the second working chamber and at least in one of the two working lines a load-holding valve is provided, through which the working piston of Hydraulic cylinder can be fixed in a certain position.
  • the load-holding valve preferably interrupts the working line in at least one direction, so that a discharge of pressure medium from the first working chamber and / or the second working chamber is prevented.
  • At least one load-holding valve can be brought into its open position by using a setting pressure of an adjusting device.
  • the control pressure is for this purpose taken from the adjusting device for adjusting the delivery volume of the first hydraulic pump and the second hydraulic pump. The control of the load-holding valve thus takes place automatically depending on conveying direction.
  • the set pressures are usually one
  • the pressure medium reservoir is designed as a hydraulic accumulator.
  • a hydraulic accumulator as pressure medium reservoir allows z. B. recover a portion of the energy expended in operating the hydraulic cylinder, for example, when lifting a load subsequent thereto during the lowering of the load.
  • a hydraulic accumulator offers the advantage that the pressure medium stored in it is under a pressure which prevents the possible occurrence of cavitation on the suction side of the hydraulic pump connected thereto.
  • the connection between the hydraulic accumulator and the first hydraulic pump is preferably provided with a shut-off valve, which can be acted upon by an actuating pressure of the adjusting device and thus adjustable between its open and closed position. The operation is carried out by Use of the setting pressure again automatically and taking into account the conveying direction.
  • a particularly compact arrangement results if at least the removal valve and / or the at least one load-holding valve and / or the check valve are arranged in a pump unit which comprises the first and the second hydraulic pump.
  • FIG. 1 shows a first embodiment of a hydrostatic drive according to the invention
  • FIG. 2 shows a second embodiment of a hydrostatic drive according to the invention with load-holding valves.
  • FIG. 3 shows a third exemplary embodiment of a hydrostatic drive according to the invention with a hydraulic accumulator as pressure medium reservoir;
  • Fig. 4 shows a fourth embodiment of a hydrostatic drive according to the invention with an additional hydraulic accumulator to reduce pressure fluctuations.
  • the hydrostatic drive 1 shown in Fig. 1 comprises a double-acting hydraulic cylinder 2, in which a working piston 3 is arranged displaceably.
  • the working piston 3 has a first piston surface 4 and a second piston surface 5.
  • the first piston surface 4 and the second piston surface 5 are oriented in the opposite direction.
  • On the side of the second piston surface 5 is the working piston 3 a Piston rod 6 connected.
  • the second piston surface 5 is smaller than the first piston surface. 4
  • the first piston surface 4 can be acted upon in a first working chamber 7 of the hydraulic cylinder 2 with a first working pressure acting there. Accordingly, the second piston surface 5 can be acted upon in a second working chamber 8 of the hydraulic cylinder 2 with a second working pressure.
  • the first working chamber 7 is connected to a first working line 9 and the second working chamber 8 is connected to a second working line 10.
  • a first hydraulic pump 11 and a second hydraulic pump 12 are provided.
  • the first hydraulic pump 11 For generating volume flows for actuating the hydraulic cylinder 2, a first hydraulic pump 11 and a second hydraulic pump 12 are provided.
  • the first hydraulic pump 11 For generating volume flows for actuating the hydraulic cylinder 2, a first hydraulic pump 11 and a second hydraulic pump 12 are provided.
  • the first hydraulic pump 11 For generating volume flows for actuating the hydraulic cylinder 2, a first hydraulic pump 11 and a second hydraulic pump 12 are provided.
  • the first hydraulic pump 11 and the second hydraulic pump 12 are realized according to a preferred embodiment in the form of a double pump, so that the adjustment of the delivery volume of the first hydraulic pump 11 and the hydraulic pump 12 takes place together.
  • the first working line 9 branches off to the first and the second hydraulic pump 11, 12 in a first working line branch 9a and a second
  • the first working line branch 9a is connected to the first connection 13 of the first hydraulic pump 11. Accordingly, the second working line branch 9b is connected to the first connection 14 of the second hydraulic pump 12.
  • Working line 9 and the first hydraulic pump 11 additionally arranged in an open circuit.
  • the second connection 15 of the first hydraulic pump 11 can be connected to a tank volume 18 via a suction line 17 for this purpose.
  • the first hydraulic pump 11 and the second hydraulic pump 12 are driven by a common drive shaft 19 by a drive machine, not shown.
  • the respective adjustment mechanisms of the first hydraulic pump 11 and the second hydraulic pump 12 are connected to an adjusting device 20.
  • the adjusting device 20 comprises a control cylinder 21, in which an actuating piston 22 is arranged displaceably.
  • Control piston 22 is acted upon by a first control pressure in a first control pressure chamber 23 of the actuating cylinder 21 and a second control pressure in a second control pressure chamber 24 in the opposite direction.
  • first hydraulic pump 11 and the second hydraulic pump 12 are changed together in their delivery volume.
  • the set delivery volume of the first hydraulic pump 11 and the second hydraulic pump 12 are always in a fixed predetermined relationship to each other.
  • the delivery volume of the first hydraulic pump 11 is equal to the delivery volume of the second hydraulic pump 12th
  • the control pressure control valve 25 is in the illustrated embodiment, a 4/3-way valve, which is centered by a set of springs. From this centered position, in which all four connections of the control pressure control valve 25 are separated from each other, the control pressure control valve 25 can be deflected in the direction of a first end position or in the direction of a second end position by electromagnets.
  • the first control pressure line 26 is connected to the first control pressure chamber 23.
  • the second control pressure line 27 is connected to the second control pressure chamber 24.
  • the first control pressure chamber 23 is acted upon via the first connecting line 28 with a control pressure and the second control pressure chamber 24 via the second control pressure chamber 27 in an inner tank volume 18 'relaxed, which is preferably connected to the tank volume 18.
  • the reverse pressure actuation control valve 25 the second actuating pressure chamber 24 is connected to the first connecting line 28 and the first actuating pressure chamber 23 with the expansion line 29.
  • the maximum available setting pressure is the adjusting pressure control valve 25 in the manner already mentioned via the first connecting line 28, respectively.
  • first hydraulic pump 11 and the second hydraulic pump 12 which are preferably designed in the manner already mentioned as a double pump, comprises the thus formed
  • the feed device 31 is used for Nachellen leaked by leakage from the circuit pressure medium, and generating an initial pressure at startup of the drive 1.
  • the feed pump 32 is also connected via the drive shaft 19 to the drive machine and is as a constant pump intended to be promoted in one direction only. The feed pump 32 sucks this over a
  • feed pressure line 34 To limit the maximum available feed pressure is the feed pressure line 34 by a
  • Supply pressure limiting valve 35 secured.
  • the feed pressure limiting valve 35 is acted upon in the direction of its closed position by a compression spring.
  • the pressure prevailing in the feed pressure line 34 acts on a measuring surface of the feed pressure limiting valve 35. If the feed pressure in the feed pressure line 34 exceeds a critical value predetermined by the pressure spring, the feed pressure limiting valve 35 is adjusted in the direction of its open position due to the hydrostatic force. In the open position, the feed pressure line 34 is connected via a further expansion line 36 to the inner tank volume 18 '.
  • the feed pressure line 34 of the feed device 31 is also connected via a first feed line 37 to the first working line 9. Furthermore, the
  • Supply pressure line 34 is connected via a second feed line 38 to the second working line 10.
  • a first and second check valve 39, 40 is arranged in the first supply line 37 and the second supply line 38 so that they open in the direction of the first working line 9 and on the second working line 10 back. If the pressure set in the feed device 31 by the feed pressure limiting valve 35 exceeds the pressure in the first working line 9 or in the second working line 10, then pressure medium from the feed device 31 will be in the first Working line 9 and the second working line 10 supplied.
  • a second connecting line 41 and a third connecting line 42 is provided parallel to the first feed line 37 and the second feed line 38.
  • the second connecting line 41 connects the first working line 9 with the feed pressure line 34.
  • a first pressure limiting valve 43 is provided in the second connecting line 41.
  • the first pressure relief valve 43 is biased as the feed pressure relief valve 35 in the direction of its closed position by means of a compression spring. The prevailing in the first working line 9 first working pressure acts in the opposite direction to the first pressure relief valve 43. If the first working pressure exceeds the set by the compression spring maximum pressure, the first pressure relief valve 43 is brought into its open position. In the open position of the
  • the first working line 9 is connected to the feed pressure line 34.
  • the first working line 9 is relaxed in the direction of the feed device 31.
  • a second pressure limiting valve 44 is arranged, which releases the second working line 10 into the feed device 31 when a critical pressure in the second working line 10 is exceeded.
  • a removal valve is provided in the hydrostatic drive 1. In the illustrated, preferred
  • the removal valve is designed as a purge valve 45.
  • the purge valve 45 is designed as a 3/3-way valve.
  • An output port of the purge valve 45 is connected to the feed pressure line 34.
  • the purge valve 45 is held in its middle position by a first centering spring 48 and a second centering spring 49.
  • the two input ports of the purge valve 45 are connected via a first extraction line 46 and a second extraction line 47 to the first working line 9 and the second working line 10. From the first extraction line 46 branches off a first line branch 50, which acts on a measuring surface on the purge valve 45 to the pressure of the first working line 9.
  • the hydrostatic force generated at the measuring surface by the first working pressure acts in the same direction as the first one
  • the second sampling line 47 is connected to the feed pressure line 34.
  • a flow-through connection is made from the second working line 10 into the feed device 31.
  • the purge valve 45 is constructed symmetrically in the illustrated embodiment. Accordingly, a second line branch 51 is provided, which connects the second removal line 47 with a further measuring surface of the purge valve 45, wherein the second working pressure acting there acts on the purge valve 45 in the same direction with the second centering spring 49. If the resulting force thus generated exceeds the force generated in the opposite direction by the first working pressure and the first centering spring 48, the purge valve 45 is brought into its second switching position. In the second switching position is a flow-through connection between the first extraction line 46 and the feed pressure line 34 made.
  • first piston surface 4 and the second piston surface 5 are in a relationship to one another, which is slightly smaller than 2.
  • first piston surface 4 and the second piston surface 5 are in a relationship to one another, which is slightly smaller than 2.
  • Hydraulic cylinders such as those used for generating the force on a boom and a stick of an excavator.
  • a compensation line 52 connected to the suction line 17.
  • a check valve 53 is arranged, which opens in the direction of the suction line 17 back.
  • the ratio of the total delivery volume of the hydraulic pumps 11, 12 to the delivery volume of the second hydraulic pump 12 deviates from the area ratio of the first piston surface 4 to the second piston surface 5.
  • the resulting difference volume flow is discharged via the removal valve, which is designed as a purge valve 45 in the illustrated embodiment.
  • the removal valve which is designed as a purge valve 45 in the illustrated embodiment.
  • pressure medium volume taken from the first working chamber 7 through the first hydraulic pump 11 and the second hydraulic pump 12 is too small in relation to the volume flow flowing into the second working chamber 8.
  • pressure medium is supplied to the instantaneous suction side of the first hydraulic pump 11 and the second hydraulic pump 12 by the feed pump 32 and the then opening first check valve 39.
  • a purge valve is generally provided in a closed hydraulic circuit to selectively remove pressure fluid from the circuit. This removed
  • the purge valve 45 is a hydraulically actuated 3/3-way valve.
  • the use of a purge valve 45 as a bleed valve allows the connection of any hydraulic cylinder 2.
  • FIG. 2 shows a second exemplary embodiment of the hydrostatic drive 1 'according to the invention.
  • the matching with the elements of the first embodiment components are provided with the same reference numerals, so that a further detailed description can be omitted.
  • one load-holding valve 55, 56 is provided in the first working line 9 and in the second working line 10.
  • the first load-holding valve 55 is arranged in the first working line 9.
  • the second load-holding valve 56 is arranged in the second working line 10.
  • the two load-holding valves 55, 56 are of identical construction.
  • the first load-holding valve 55 is held by a first biasing spring 57 in its initial position.
  • the check valve in the initial position of the first load-holding valve 55 opens in the direction of the first working chamber 7 and locks at a directed out of the first working chamber 7 volume flow.
  • the first load-holding valve 55 like the second load-holding valve 56, is pressure-compensated in order to enable the load-holding valves 55, 56 to be adjusted counter to the force of the first and second biasing springs 57, 58.
  • in each case acts on the side of the first working chamber 7 and the second working chamber 8 working pressure both in the same direction with the first and second biasing spring 57, 58 and in the opposite direction to the first and second load-holding valve 55, 56 in the opposite direction pressurized surfaces of the first
  • load holding valve 55 and the second load-holding valve 56 differ, so that a slight adjustment of the load-holding valves 55, 56 in their respective second switching position is possible.
  • Compensation lines 59 ', 59' ' provided. Accordingly, second compensation lines 60 ', 60 "are provided on the second load-holding valve 56.
  • a first control line 61 is provided.
  • the first control line 61 connects the first load-holding valve 55 with the first control pressure line 26.
  • the second control pressure line 27 is connected via a second control line 62 to the second load-holding valve 56.
  • the two load-holding valves 55, 56 are actuated hydraulically.
  • electrically control the load-holding valves The control with a corresponding control signal then takes place in accordance with the control of the control pressure control valve 25th
  • first extraction line 46 and the second extraction line 47 are connected to the first working line 9 and the second working line 10 with respect to the first pressure relief valve 43 and the second pressure relief valve 44 on the oriented to the hydraulic cylinder 2 section
  • the arrangement in the embodiment of FIG. 2 is reversed.
  • the second connecting line 41, the first removal line 46 and the first feed line 37 are connected in series with the first working line 9.
  • the first load-holding valve 55 is arranged between the connection points of the first extraction line 46 and the second connection line 41. The arrangement with respect to the second working line 10 is accordingly.
  • the modified arrangement is also taken into account by connecting the second and third connecting lines 41, 42 to the feed pressure line 34 via a feed pressure line section 34 'and the first connecting line 28.
  • first load-holding valve 55 and the second load-holding valve 56 By providing the first load-holding valve 55 and the second load-holding valve 56 in the first working line 9 or the second working line 10, it is possible to clamp the working piston 3 hydraulically in any position and thus to prevent an unwanted movement. In the initial positions of the first load-holding valve 55 and the second load-holding valve 56, escape of pressure medium from the first working chambers 7 or the second working chamber 8 is not possible due to the non-return valve arranged in the load-holding valve 55, 56. Once the actuator piston 22 returns to its original position and the
  • Control pressure chambers 23, 24 are relaxed, is on the first control line 61 and the second control line 62 is no sufficient control pressure to the first load-holding valve 55 and the second load-holding valve 56 to bring the respective load-holding valve 55 and 56 in its open position. If, in contrast, an actuating pressure chamber of the adjusting device 20 is subjected to an actuating pressure, the first load-holding valve 55 will be moved into its second position when the first actuating pressure chamber 23 is acted upon via the first control line 61
  • Hydraulic accumulator 63 and the first hydraulic pump 11 is preferably arranged a check valve 64.
  • the check valve 64 is in turn pressure compensated via third compensation lines 65 ', 65' '.
  • the control of the blocking valve 64 via a third control line 66, which branches off from the second control line 62.
  • the check valve 64 is thus brought in a promotion of pressure medium in the direction of the first working chamber 7 in its open position.
  • the check valve 64 may be like the two
  • Load holding valves 55, 56 are also electrically controlled.
  • a hydraulic accumulator 63 which is embodied, for example, as a hydraulic diaphragm accumulator, has the advantage that when pumping pressure medium from the first working chamber 7 out towards the second working chamber 8, it is not necessary to work only against the counterpressure by the second hydraulic pump 12 , but due to the hydraulic accumulator 63 and by the first hydraulic pump 11 must be promoted against pressure. This improves the uniformity of the load for the first hydraulic pump 11 and the second hydraulic pump 12.
  • the removal of pressure medium from the first working chamber 7 given the opportunity to part of the energy released, for example, when lowering a load in the form of pressure energy in to store the first hydraulic accumulator 63. In a reversal of the conveying direction, this pressure energy is released, so that only a reduced pressure difference must be generated by the first hydraulic pump 11.
  • a second hydraulic accumulator 67 is provided in FIG. 4. With the second hydraulic accumulator 64, the first connecting line 28 is connected.
  • the second pressure accumulator 67 serves to reduce pressure fluctuations in the feed device 31. Such pressure fluctuations can occur in particular at low speeds of the engine, since the funded by the feed pump 32 pressure fluid quantity is directly related to the speed of the drive machine.

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

Abstract

L'invention concerne un mécanisme d'entraînement hydrostatique comprenant une première et une deuxième pompes (11, 12) hydrauliques ainsi qu'un vérin (2) hydraulique à double effet. Le vérin (2) hydraulique à double effet présente une première chambre (7) de travail et une deuxième chambre (8) de travail. La première chambre (7) de travail est délimitée par une première surface (4) de piston d'un piston (3) de travail et la deuxième chambre (8) de travail par une deuxième surface (5) de piston du piston (3) de travail. La première chambre (7) de travail est reliée avec un premier raccord (13) de la première pompe (11) hydraulique et un premier raccord (14) de la deuxième pompe (12) hydraulique. La deuxième chambre (8) de travail est reliée à un deuxième raccord (16) de la deuxième pompe (12) hydraulique. Un autre raccord (15) de la première pompe (11) hydraulique est relié à un réservoir à fluide sous pression. Le rapport entre la première surface (4) de piston et la deuxième surface (5) de piston est différent du rapport entre le volume refoulé total des deux pompes (11, 12) hydrauliques et le volume refoulé de la deuxième pompe (12) hydraulique. Une soupape (45) de prélèvement destinée à prélever du fluide sous pression est prévue pour équilibrer les volumes.
EP07725766A 2006-06-02 2007-06-01 Mecanisme d'entrainement hydrostatique avec equilibrage des volumes Withdrawn EP2024647A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006025987 2006-06-02
PCT/EP2007/004886 WO2007140947A1 (fr) 2006-06-02 2007-06-01 Mécanisme d'entraînement hydrostatique avec équilibrage des volumes

Publications (1)

Publication Number Publication Date
EP2024647A1 true EP2024647A1 (fr) 2009-02-18

Family

ID=38468828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07725766A Withdrawn EP2024647A1 (fr) 2006-06-02 2007-06-01 Mecanisme d'entrainement hydrostatique avec equilibrage des volumes

Country Status (6)

Country Link
US (1) US8033107B2 (fr)
EP (1) EP2024647A1 (fr)
JP (1) JP2009539043A (fr)
KR (1) KR20090014137A (fr)
CN (1) CN101341342B (fr)
WO (1) WO2007140947A1 (fr)

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US8033107B2 (en) 2011-10-11
CN101341342A (zh) 2009-01-07
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JP2009539043A (ja) 2009-11-12
KR20090014137A (ko) 2009-02-06
US20090064676A1 (en) 2009-03-12

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