EP2881594A1 - Système de commande hydraulique - Google Patents

Système de commande hydraulique Download PDF

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Publication number
EP2881594A1
EP2881594A1 EP14190832.7A EP14190832A EP2881594A1 EP 2881594 A1 EP2881594 A1 EP 2881594A1 EP 14190832 A EP14190832 A EP 14190832A EP 2881594 A1 EP2881594 A1 EP 2881594A1
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EP
European Patent Office
Prior art keywords
fluid flow
valve
flow path
metering orifice
pressure
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.)
Granted
Application number
EP14190832.7A
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German (de)
English (en)
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EP2881594B1 (fr
Inventor
Steffen Knapper
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2881594A1 publication Critical patent/EP2881594A1/fr
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Publication of EP2881594B1 publication Critical patent/EP2881594B1/fr
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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/028—Shuttle 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6058—Load sensing circuits with isolator 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/652—Methods of control of the load sensing pressure the load sensing pressure being different from the load pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85978—With pump
    • Y10T137/85986—Pumped fluid control

Definitions

  • the invention is based on a hydraulic control arrangement according to the preamble of claim 1.
  • a control arrangement which is designed in the form of a load-sensing (LS) control.
  • LS load-sensing
  • the highest load pressure is reported to a variable displacement pump and regulated so that in a pump line there is a pump pressure lying by a certain pressure difference Ap over the load pressure.
  • Adjustable metering orifices of the LS control for the consumers are assigned to individual pressure balances, which also maintain a constant pressure difference via the metering orifices of the load-pressure-lower hydraulic consumers.
  • the individual pressure compensators are arranged upstream of the metering orifices and throttle the fluid flow between the pump line and the metering orifices so strongly that the pressure upstream of the metering orifices is independent of the pump pressure only by a certain pressure difference above the individual load pressure.
  • the load pressure-highest consumer slows down because the pump pressure applied by its metering orifice drops and thus the pressure difference across this metering orifice becomes smaller.
  • the invention has for its object to provide a hydraulic control arrangement which corresponds in particular functionally about the LS control and / or the LUDV control, which is simple in design, has a low space requirement, has low energy requirements and is inexpensive.
  • a hydraulic control arrangement for consumers has a metering orifice for a respective consumer for controlling a quantity of fluid flow from a hydraulic pump to the respective consumer.
  • a respective metering orifice is fluidly connected to the input side of the hydraulic pump, in particular directly or indirectly via at least one further valve.
  • On the output side of a respective metering orifice a respective consumer is provided.
  • a respective metering orifice is assigned a respective detection orifice.
  • the detection apertures are arranged fluidly in series. Via the detection apertures, a flow-sensing (FS) fluid flow path extends from the hydraulic pump. The FS fluid flow path is thus connectable to the hydraulic pump upstream of the detection apertures.
  • FS flow-sensing
  • the fluid flow path then ends at a control device, in particular downstream of the detection apertures.
  • the control device serves to control a size of a fluid flow from the hydraulic pump to the metering orifices.
  • a respective detection orifice is designed in such a way that when it falls below a certain pressure difference above a respective metering orifice (undersupply), it blocks or controls the FS-fluid flow path.
  • the detection diaphragm assigned to the metering orifice opens or controls the FS fluid flow path.
  • the control device of the hydraulic pump for controlling the fluid flow from the hydraulic pump to the consumers or to the metering orifices can advantageously be influenced. In particular, it can thus be recognized by the control device with the FS fluid flow path, whether there is an insufficient supply.
  • the FS fluid flow path thus serves to transmit an FS signal.
  • This solution has the advantage that the control device of the hydraulic pump for controlling the fluid flow no longer uses the highest load pressure, as in the prior art described above, but makes the control of the hydraulic pump of the FS fluid flow path dependent, so whether it is open or closed is. If it is open, that is to say all detection apertures arranged fluidly in series are open, then there is no undersupply of an orifice or of a consumer. If, on the other hand, a detection orifice is closed, then the FS fluid flow path is blocked and the control device can, for example, control the hydraulic pump such that the undersupply of the metering orifices is counteracted.
  • the FS fluid flow path influences the control device in such a way that blockage or injection of the FS fluid flow path through at least one of the detection diaphragms results in a hearing of the fluid flow from the hydraulic pump to the consumers.
  • An opening or control of the FS fluid flow path through all the detection apertures advantageously results in a reduction of the fluid flow from the hydraulic pump to the consumers.
  • a respective detection panel may have a valve element.
  • the valve element is in this case preferably acted upon in the opening direction by the pressure medium upstream of its associated metering orifice and in the closing direction by the pressure medium downstream of its associated metering orifice and additionally by a spring force of a, in particular adjustable, detection spring.
  • the spring force of the detection spring of the detection aperture advantageously determines the pressure difference at which the valve slide of the detection aperture is actuated in the direction of the closed position.
  • control device may preferably be provided a pump control for adjusting a delivery volume of the hydraulic pump designed as a variable displacement pump.
  • control device is an inlet pressure compensator designed as a fixed displacement pump.
  • the pump control has the advantage that the variable displacement pump can be swung back when the FS fluid flow path is open, and thus there is no undersupply at the metering orifices. If, however, the FS fluid flow path is blocked, then the variable displacement pump can be pivoted by the pump control in the direction of increasing the delivery volume. It is conceivable that due to the FS fluid flow path, the control device may be formed without a volumetric flow regulator.
  • a respective metering orifice may be formed as a continuously adjustable directional control valve. This can lock in a neutral position, a pressure fluid connection between the associated consumer and the hydraulic pump and alsêtn in switching positions a pressure medium connection between the associated consumer and the hydraulic pump. With the directional valve thus an opening cross-section is adjustable.
  • a respective metering orifice is associated with an individual pressure compensator. This is preferably used to maintain an approximately constant pressure difference across the metering orifice.
  • a respective individual pressure compensator is provided in addition to a respective detection panel additionally a respective individual pressure compensator is provided.
  • the individual pressure compensator can be upstream or downstream of the metering orifice.
  • At least one individual pressure compensator together with the associated detection aperture is designed as an individual valve with a common valve element.
  • all individual pressure compensators are formed with their associated detection apertures as individual valves. This has the advantage that device technology simple and inexpensive only one valve must be used.
  • the individual valve may advantageously be upstream or downstream of the metering orifice.
  • the valve element of a respective individual valve is designed as a valve slide.
  • This can have a basic position and, starting from this, be displaceable in the direction of first switching positions. Furthermore, it can be displaceable in the direction of second switching positions which adjoin the first switching positions.
  • the valve spool can advantageously fulfill the functions of the detection panel and the individual pressure compensator.
  • the FS fluid flow path may be opened and locked in the home position.
  • a pressure medium connection between the hydraulic pump and the consumer can be controlled. In the first switching positions, the pressure medium connection between the hydraulic pump and the consumer can then be throttled or completely open.
  • the pressure medium connection between the hydraulic pump and the consumer is then preferably completely opened.
  • the pressure difference across the metering orifice is controlled by the individual valve in the first and second switching positions, in which the FS fluid flow path is completely open.
  • the pump control can swing back the swivel pump.
  • the valve element of the individual valve is in the basic position, wherein the FS fluid flow path is blocked and the pressure medium connection from the hydraulic pump to the metering orifice or to the consumer is completely opened.
  • the pump control can in this case then pivot the variable displacement pump in the direction of an increased delivery volume.
  • the valve slide of the individual valve of the highest-load consumer can preferably be positioned in the region of its first switching positions in the adjusted mode, since no excess pressure is provided by the hydraulic pump, in contrast to the prior art. This leads to an energy saving, since a control reserve for so-called extreme situations is no longer necessary.
  • valve element in a further embodiment of the individual valve, can be acted upon in the direction of the basic position by the spring force of the detection spring and the pressure medium downstream of the associated metering orifice. In the direction of the first and second switching positions, the valve element may be acted upon by the pressure medium upstream of the associated metering orifice.
  • control arrangement may be formed with an individual pressure compensator downstream of the metering orifice.
  • an FS fluid flow path can be provided in a control arrangement, which is in principle designed as LUDV control arrangement.
  • a respective metering orifice an individual pressure compensator with a valve spool.
  • This can lock in a basic position, a pressure medium connection between the metering orifice and the associated consumer and aufêtn starting from the basic position in the direction of first switching positions the pressure medium connection between the metering orifice and the associated consumer throttled.
  • the valve switch can continue to control the pressure medium connection between the metering orifice and the associated consumer in the direction of second switching positions.
  • valve spool of a respective individual pressure compensator of the further embodiment can also be acted upon in the direction of the first and second switching positions by the pressure medium downstream of the metering orifice and in the direction of the basic position of the highest load pressure of the consumer.
  • the individual pressure compensators of the further preferred embodiment can be connected to a common LS line.
  • the valve spool of a respective individual pressure compensator can then connect the LS line throttled in the second switching positions with a consumer line connected to the consumer downstream of the metering orifice.
  • the valve spool In the first switching positions and in the basic position, the valve spool can block or control the connection between the LS line and the consumer line.
  • the valve spool can be acted upon in the direction of the basic position via the LS line from the highest load pressure of the consumer.
  • the pump control may preferably have an adjusting cylinder for adjusting the delivery volume of the variable.
  • the adjusting cylinder is preferably regulated via a control valve.
  • a piston of the adjusting cylinder can further limit a cylinder space which can be charged to reduce the delivery volume of the variable displacement pump with pressure medium.
  • pressure medium can be discharged from the cylinder space.
  • the cylinder chamber is in particular directly connected to the FS fluid flow path, in particular throttled.
  • the control valve may have a valve slide, which is acted upon by a, in particular adjustable, valve spring with a spring force in the direction of a basic position. In the direction of switching positions, it can be acted upon with pressure medium of an output side of the hydraulic pump and thus with a pump pressure.
  • a pressure medium connection between the FS fluid flow path and the cylinder space is preferably controlled and directed between the output side of the hydraulic pump and the cylinder chamber.
  • the pressure medium connection between the FS fluid flow path and the cylinder chamber can be controlled and controlled between the output side of the hydraulic pump and the cylinder chamber.
  • the FS fluid flow path is connected via a throttle to a tank, whereby a defined pressure prevails in the FS fluid flow path even with a closed detection orifice.
  • the hydraulic control arrangement may be provided in a valve block. It is conceivable that the valve block is formed from valve disks, wherein in a respective valve disk, the valves are provided for a respective consumer.
  • the hydraulic control arrangement 1 has a valve block 2, which has valve disks 4, 6 and 8.
  • a respective valve disk 4 to 8 has two working ports A, B for connecting a hydraulic consumer, such as a hydraulic cylinder on.
  • the valve discs 4 to 8 are in this case configured the same and each have a metering orifice 10 and an individual valve 12.
  • a respective individual valve 12 in this case forms an individual pressure compensator, which is connected upstream of the respective metering orifice 10, and a detection diaphragm according to the invention.
  • the design of the metering orifices 10 will be explained with reference to the valve disk 4.
  • the metering orifice 10 is designed as a continuously adjustable 5/4-way valve.
  • a valve spool of the metering orifice 10 is spring-centered in a neutral position 0.
  • the valve slide can be adjusted starting from the neutral position 0 in the direction of a first switching position a or in the opposite direction starting from the neutral position 0 in the direction of second switching positions b. If the valve spool is moved further, starting from the second switching positions b, then it arrives in free or floating positions c.
  • In the first switching positions a is a pressure medium connection between a supply line 16 extending from an in FIG.
  • the individual valve 12 is also explained in more detail with reference to the valve disk 4. It is designed as a continuously adjustable 4/3-way valve. Via a detection spring 30, a valve spool is acted upon in the direction of a basic position 0 with a spring force. Starting from the basic position 0, it is displaceable in the direction of first shift positions a. Subsequent to the switching positions a, it is displaceable in the direction of second switching positions b.
  • a flow-sensing (FS) fluid flow path 32 extends across the individual valves 10 of the valve discs 4 through 8. Regarding this FS fluid flow path 32, the individual valves 12 are in series arranged.
  • the FS fluid flow path 32 is blocked and opened in the first and second switching positions a, b.
  • the FS fluid flow path 32 is only opened when all valve spools of the individual valves 12 are not in their neutral position 0. If, on the other hand, one of the valve spools or several of the valve spools of the individual valves 12 is in the basic position 0, the FS fluid flow path 32 is blocked.
  • the FS fluid flow path 32 is seen upstream of the individual valves 12 connected to the supply line 16 and extends through the individual valve 12 of the valve disc 8 to the individual valve 12 of the valve disc 6 and from here to the individual valve 12 of the valve disc 4. Downstream of the last individual valve 12 of Valve disk 4, the FS fluid flow path 32 is then connected to a pump control, not shown, designed as a variable displacement hydraulic pump.
  • valve spool of a respective individual valve 12 is, as already explained above, acted upon by the spring force of the detection spring 30 in the direction of the basic position 0.
  • the valve spool via a control line 34 from the pressure medium of Supply line 16 downstream of the individual valve 12 and upstream of the metering orifice 10 acted upon.
  • the FS fluid flow path 32 is blocked and the supply line 16 to the metering orifice 10 is completely opened.
  • the FS fluid flow path 32 is opened and the feed line 16 to the metering orifice is likewise completely open.
  • the FS fluid flow path 32 is then opened again and the feed line 16 to the metering orifice 10 is blocked.
  • the inventive hydraulic control arrangement according to FIG. 1 differs from conventional LS control arrangements, in particular by the fact that the FS fluid flow path 32 is provided, which is up and steuste of the detection orifices of the individual valves 12.
  • the FS fluid flow path 32 thus serves to transmit an FS signal, which is explained below, which is why a message of a load pressure, for example via LS reporting lines and a Shuttle valve cascade is reported to a pump control is no longer necessary.
  • the individual valves 12 are provided which, in contrast to individual pressure compensators, have an additional control edge for controlling the FS fluid flow path.
  • variable displacement pump not shown
  • the valve spools of the individual valves 12 are arranged in the second switching position b, whereby the FS fluid flow path 32 is opened.
  • This pressure medium is then forwarded from the supply line 16 to the pump control of the variable, which serves as an FS signal.
  • the FS fluid flow path 32 interacts with the pump control in such a way that when the FS fluid flow path 32 is open (FS signal open), the variable displacement pump pivots back.
  • the metering orifice 10 of the valve disc 8 is in its second switching position b, whereby a connected to the working ports A, B of the valve disc 8 consumer is supplied with pressure medium via the supply line 16.
  • the individual valves 12 of the valve disks 4 and 6 are in the second switching position b. If the load connected to the valve disk 8 is now in undersupply, that is to say the pressure difference across the metering orifice 10 is below a predetermined pressure difference, then the valve slide of the individual valve 12 of the valve disk 8 is moved into the basic position 0.
  • the FS fluid flow path 32 is therefore blocked by the individual valve 12 of the valve disc 8. There is thus no pressure fluid from the supply line 16 via the FS fluid flow path 32 for pump control.
  • the FS fluid flow path 32 interacts with the pump regulation such that in this case the variable displacement pump is pivoted in the direction of increasing the delivery volume.
  • the individual valve 12 of the valve disk 8 is completely or almost completely opened with respect to the feed line 16 to the metering orifice 10, for which reason it has minimal hydraulic losses, in contrast to a conventional LS control arrangement from the prior art.
  • valve spool of the individual valve 12 of the valve disk 8 is moved into its first switching position a.
  • the FS fluid flow path 32 is thus opened again and at the same time the supply line 16 to the metering orifice 10 of the valve disc 8 is fully or almost completely opened, which in turn leads to minimal hydraulic losses.
  • the pivot pump is swung back again.
  • both the valve spool of the metering orifice 10 of the valve disc 6 and the valve spool of the metering orifice 10 of the valve disc 8 are located, for example, in the second switching positions b.
  • the pressure difference of the metering orifices 10 of the valve disks 6 and 8 are in this case adjusted via the individual valves 12.
  • the consumer connected to the valve disk 6 should be the highest-load consumer, which is why the individual valve 12 of the valve disk 6 controls the FS fluid flow path 32.
  • his valve spool is in the home position 0 or in the first switching position a.
  • variable displacement pump is controlled with the pump control so that the required pressure difference is applied to the metering orifice 10.
  • the connection in the first valve disc 6 between the supply line 16 and the metering orifice 10 is thus completely open, which leads to minimal hydraulic losses.
  • the other individual valve 12 of the valve disc 8 with the load pressure-lower consumer then regulates the pressure difference across the metering orifice 10 of the valve disc 8 in a conventional manner by its valve slide in the switching positions a or b.
  • the FS fluid flow path 32 is thus completely opened via the individual valve 12 of the valve disc 8.
  • each individual valve 12 signals the FS signal via the FS fluid flow path 32 when the associated metering orifice 10 is not undersupplied. If there is no overall shortage, the FS signal is reported via the open FS fluid flow path 32 to the pump control, which pivots back the variable displacement pump accordingly. If only one hydraulic consumer is used, then For example, the individual valve 12 associated therewith is used to control the FS fluid flow path 32 and thus adjust the pump pressure to control the variable displacement pump. If several consumers are operated, then the individual valve 12 of the load-pressure-highest consumer is used to control the FS fluid flow path 32 and thus to control the variable displacement pump and the remaining individual valves 12 are used as conventional individual pressure compensators.
  • FIG. 2 a further illustration of the hydraulic control arrangement 1 is shown.
  • the valve discs 4, 6 and 8 are shown here as blocks. They serve as placeholders for those in the Figures 3 - 6 illustrated sections 36 of hydraulic control assemblies 1 different embodiments.
  • hydraulic consumers 38 are shown by way of example. These are differential cylinders, which are each connected to the working ports A, B of the valve disks 4-8.
  • variable displacement pump 40 with a pump control 42 shown.
  • This has an adjusting cylinder 44 with a piston 46.
  • the piston 46 can be acted upon via the cylinder chamber 48 with pressure medium in the direction of pivoting back of the variable displacement pump 40.
  • the piston 46 is acted upon by a spring force of a spring 50.
  • the pump control 42 further includes a control valve 52 which is designed as a continuously adjustable 3/2-way valve.
  • a valve spool is acted upon in the direction of a basic position 0 with a spring force of an adjustable valve spring 54.
  • the valve spool can be acted upon via a control line 56 from the pressure medium in the supply line 16, wherein the supply line 16 is connected on the output side to the variable displacement pump 40.
  • a pressure medium connection between the FS fluid flow path 32 and the cylinder chamber 48 of the adjusting cylinder 44 is opened by the control valve 52.
  • this connection is controlled and, on the other hand, a pressure medium connection between the supply line 16 and the cylinder chamber 48 is opened.
  • the FS fluid flow path 32 is in this case downstream of in FIG. 2 Not shown detection aperture connected to the control valve 52. Further, extending from the FS fluid flow path 32 downstream of the in FIG.
  • a branch line 58 which is connected via a throttle 60 directly to the cylinder chamber 48.
  • a further throttle 62 is provided, via which the branch line 58 and thus the FS fluid flow path 32 is connected to a tank 64.
  • FIG. 3 the section 36 of a second embodiment of the control arrangement 1 is shown.
  • the section 36 for the valve discs 4-8 provided.
  • the metering orifice 10 is in contrast to the embodiment of FIG. 1 designed as a 6/3-way valve.
  • a valve spool of the metering orifice 10 is spring-centered in a neutral position 0. Starting from the neutral position 0, it is displaceable in the direction of the first shift positions a. Conversely, it is displaceable starting from the neutral position 0 in the direction of second switching positions b.
  • the feed line 16 is connected via the metering orifice 10 to a connecting line 66, which in turn is connected in the first switching position a via the metering orifice 10 to the working line 18 for the working connection A.
  • the working line 20 for the working connection B is connected to the drainage line 22.
  • the second switching positions b the supply line 16 is again connected via the metering orifice 10 with the connecting line 66, which is then further connected via the metering orifice 10 with the working line 20 for the working port B.
  • the working line 18 is then connected to the drain line 22.
  • the individual valves 12 in their function as individual pressure balances regulate the pressure difference across the associated metering orifice such that it remains essentially the same and corresponds to a pressure equivalent of the spring force of the detection spring 30. If the fluid flow conveyed by the variable-displacement pump 40 is no longer sufficient, with which at least one metering orifice 10 is undersupplied, then the valve spool of that individual valve 12 is displaced in the direction of its basic position 0, whose metering orifice 10 is undersupplied. The valve spool of the individual valve 12 is thus moved to its normal position 0 when the pressure difference of the associated metering orifice 10 is less than the pressure equivalent of the detection spring 30. The FS fluid flow path 32 is thus disabled.
  • FS fluid flow path 32 is then connected to tank 64 via branch line 58.
  • the control valve 52 then regulates a delivery pressure of the variable displacement pump 40 to the value set by the valve spring 54, which in particular corresponds to the maximum permissible delivery pressure. This in turn leads to an increase in the delivery volume of the variable displacement pump 40 until there is no shortage of supply.
  • valve spool of a metering orifice 10 in the neutral position 0 the valve spool of the associated individual valve 12 is moved to its second switching position b.
  • the FS fluid flow path 32 is this individual valve 12 is open.
  • a delivery volume of the variable displacement pump 40 is adjusted to the lowest possible value, so that energy losses are at a standstill of the consumer 38 as low as possible.
  • FIG. 4 shows a portion 36 of a hydraulic control assembly 1 according to a third embodiment.
  • a respective individual valve 12 of the metering orifice 10 downstream The individual valve 12 is arranged in the connecting line 66.
  • the connecting line 66 In the basic position 0 of the individual valve 12, the connecting line 66 is completely opened. In the first switching position a, however, the connecting line 66 is throttled open and closed in the switching position b.
  • the FS fluid flow path 32 is controlled by the individual valve 12 according to the first and second embodiments.
  • the valve spool of the individual valve 12 is pressurized via the branch line 24, which branches off from the connecting line 66 between the individual valve 12 and the metering orifice 10, with pressure medium in the direction of the basic position 0. In the opposite direction, it is acted upon by pressure medium via the control line 34, which branches off from the feed line 16 upstream of the metering orifice 10.
  • An operation of the control arrangement according to FIG. 4 essentially corresponds to the operation of the control arrangement according to FIG. 3 ,
  • FIG. 5 is the section 36 of the control arrangement 1 from FIG. 2 shown according to a fourth embodiment.
  • This is based on a LUDV control arrangement with downstream individual pressure compensator.
  • the metering orifice 10 is corresponding to the Figures 3 and 4 educated.
  • an individual pressure compensator 68 and a detection diaphragm 70 are now provided separately from one another.
  • the individual pressure compensator 68 is in this case arranged in the connecting line 66. It is designed as a continuously adjustable 3/3-way valve.
  • the valve spool of the individual pressure compensator 68 can be brought into a basic position 0 here. Starting from this, it is displaceable in the direction of first switching positions a and subsequently further in the direction of second switching positions b.
  • a Load pressure signaling line 72 connected to the individual pressure compensator 68. From this branches off a control line 74, which acts on the valve spool of the individual pressure compensator 68 with pressure medium in the direction of its basic position 0. In the opposite direction of the valve spool is acted upon via a control line 76 with pressure medium, which branches off from the connecting line 66 between the metering orifice 10 and the individual pressure compensator 68.
  • the connecting line 66 In its first switching positions a of the individual pressure compensator 68, the connecting line 66 is opened throttled. In the second switching positions b, the connecting line 66 is completely opened and additionally the load pressure signaling line 72 throttled connected to the connecting line 66.
  • the connecting line 66 is controlled and the load pressure signaling line 72 separated from it.
  • the individual pressure compensators 68 of the valve discs 4 to 8 off FIG. 2 thus sharing the load pressure signaling line 72, see also FIG. 2 , in which then the highest load pressure is applied.
  • the detection panel 70 is designed as a 2/2-way valve.
  • a valve slide of the detection panel 70 is acted upon in the direction of a basic position 0 by the spring force of the detection spring 30. Starting from the basic position 0, it can be adjusted counter to the spring force in the direction of a switching position a.
  • the valve spool In addition to the spring force of the valve spool is acted upon in the direction of its basic position 0 via a control line 78 from the pressure medium of the connecting line 66 between the metering orifice 10 and the individual pressure compensator 68.
  • the valve spool via a control line 80 from the pressure medium of the supply line 16 upstream of the metering orifice 10 can be acted upon.
  • the detection panel 70 blocks the FS fluid flow path 32.
  • the switching position a of the FS fluid flow path 32 is open.
  • the control arrangement is in accordance with FIG. 2 in synopsis with FIG. 5 used in the usual way.
  • the FS fluid flow path 32 is then opened via the detection panel 70.
  • the detection panel 70 closes the FS fluid flow path 32, with which in turn the variable displacement pump 40 according to the embodiments FIG. 3 and 4 their delivery volume increased. Without the detection panel 70, the variable displacement 40 would a sub-supply no information about a too low fluid flow received.
  • the individual pressure compensator 68 which is assigned to the load-pressure-highest consumer, is in accordance with the embodiment FIG. 5 completely open, resulting in low energy losses according to the previous embodiments.
  • a further embodiment of a control arrangement 1 shows the section 36 according to FIG. 6 in synopsis with FIG. 2 ,
  • the metering orifice 10 is in this case accordingly FIG. 3 educated.
  • the detection panel 70 is corresponding FIG. 5 educated.
  • the valve spool of the detection valve 70 is acted upon in the direction of the basic position 0 by the pressure medium of the connecting line 66 by a control line 82 branches off from this.
  • the opposite direction of the valve spool is acted upon by the pressure medium of the supply line 16 upstream of the metering orifice 10 via a control line 84 branching off therefrom.
  • variable displacement 40 off FIG. 2 is then adjusted in the direction of increasing a delivery volume.
  • a hydraulic control arrangement for a plurality of consumers.
  • a metering orifice for controlling a fluid flow is provided.
  • a respective metering orifice is assigned a detection aperture.
  • the detection apertures are arranged fluidly in series.
  • a flow-sensing (FS) fluid flow path extends over the detection apertures. Upstream of the detection apertures, the fluid flow path is connected to a hydraulic pump and downstream of the detection apertures to a control device of the hydraulic pump. If a consumer is under-supplied with pressure medium, the corresponding detection panel closes the flow-sensing fluid flow path. In this case, the regulating device interacts with this FS fluid flow path in such a way that the fluid flow from the hydraulic pump is thereby increased. If none of the consumers are undersupplied, then the FS fluid flow path is Fully opened via the detection panels and the control device reduces the fluid flow from the hydraulic pump.

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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)
EP14190832.7A 2013-11-15 2014-10-29 Système de commande hydraulique Active EP2881594B1 (fr)

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DE102013223288.8A DE102013223288A1 (de) 2013-11-15 2013-11-15 Hydraulische Steueranordnung

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DE102014226182A1 (de) * 2014-12-17 2016-06-23 Robert Bosch Gmbh Steuerventilanordnung und hydraulisches Antriebssystem damit
DE102015218832A1 (de) * 2015-09-30 2017-03-30 Robert Bosch Gmbh Pumpen-Regler-Kombination mit Leistungsbegrenzung
DE102018202148B3 (de) * 2018-02-12 2019-03-07 Hawe Hydraulik Se Hydraulikventilverband mit Zwangsschaltung und Mobilhydrauliksystem
DE102018212077A1 (de) * 2018-07-19 2020-01-23 Deere & Company Verfahren zum Betreiben eines hydraulischen Verbrauchers an einem elektrisch betätigbaren Steuerventil
KR102577950B1 (ko) * 2018-12-26 2023-09-14 웨이차이 파워 컴퍼니 리미티드 유압 가변 펌프 세트 및 굴착기

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US5081839A (en) * 1990-01-29 1992-01-21 Caterpillar Inc. Pressure compensated hydraulic system
US5305789A (en) 1992-04-06 1994-04-26 Rexroth-Sigma Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves
DE102007045803A1 (de) 2007-08-22 2009-02-26 Robert Bosch Gmbh Hydraulische Steueranordnung
EP2078868A2 (fr) * 2008-01-09 2009-07-15 Husco International, Inc. Système de soupape de commande hydraulique doté d'une système de détection de charge
DE102009017506A1 (de) * 2008-04-25 2009-12-03 Husco International Inc., Waukesha Drucknachkompensiertes Hydrauliksteuerungsventil mit lastabhängiger Druckbegrenzung
DE102009034616A1 (de) 2009-07-27 2011-02-03 Robert Bosch Gmbh Wegeventilanordnung

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US5937645A (en) * 1996-01-08 1999-08-17 Nachi-Fujikoshi Corp. Hydraulic device
FR2744497B1 (fr) * 1996-02-07 1998-04-03 Rexroth Sigma Dispositif de distribution hydraulique multiple
DE10255738A1 (de) * 2002-11-07 2004-05-27 Bosch Rexroth Ag Hydraulisches Zweikreissystem
DE102004048684A1 (de) * 2004-10-06 2006-04-13 Bosch Rexroth Ag Hydraulische Steueranordnung
DE102006053897A1 (de) * 2006-11-15 2008-05-21 Robert Bosch Gmbh Hydraulisches Zweikreissystem und Zusammenschaltventilanordnung

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Publication number Priority date Publication date Assignee Title
US5081839A (en) * 1990-01-29 1992-01-21 Caterpillar Inc. Pressure compensated hydraulic system
US5305789A (en) 1992-04-06 1994-04-26 Rexroth-Sigma Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves
DE102007045803A1 (de) 2007-08-22 2009-02-26 Robert Bosch Gmbh Hydraulische Steueranordnung
EP2078868A2 (fr) * 2008-01-09 2009-07-15 Husco International, Inc. Système de soupape de commande hydraulique doté d'une système de détection de charge
DE102009017506A1 (de) * 2008-04-25 2009-12-03 Husco International Inc., Waukesha Drucknachkompensiertes Hydrauliksteuerungsventil mit lastabhängiger Druckbegrenzung
DE102009034616A1 (de) 2009-07-27 2011-02-03 Robert Bosch Gmbh Wegeventilanordnung

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CN104653530A (zh) 2015-05-27
CN104653530B (zh) 2018-02-13
US9726203B2 (en) 2017-08-08
US20150136251A1 (en) 2015-05-21
EP2881594B1 (fr) 2016-07-20
DE102013223288A1 (de) 2015-05-21

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