EP1355065A1 - Hydraulic control - Google Patents

Hydraulic control Download PDF

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Publication number
EP1355065A1
EP1355065A1 EP20030075981 EP03075981A EP1355065A1 EP 1355065 A1 EP1355065 A1 EP 1355065A1 EP 20030075981 EP20030075981 EP 20030075981 EP 03075981 A EP03075981 A EP 03075981A EP 1355065 A1 EP1355065 A1 EP 1355065A1
Authority
EP
European Patent Office
Prior art keywords
valve
compensation
pressure
flow
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20030075981
Other languages
German (de)
French (fr)
Other versions
EP1355065B1 (en
Inventor
Knud Meldgaard Jensen
Carl Christian Dixen
Henrik Kjer Kristiansen
Hans Jorgen Jensen
Jan Maiboll Buhl
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.)
Danfoss Power Solutions ApS
Original Assignee
Sauer Danfoss Nordborg ApS
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Application filed by Sauer Danfoss Nordborg ApS filed Critical Sauer Danfoss Nordborg ApS
Publication of EP1355065A1 publication Critical patent/EP1355065A1/en
Application granted granted Critical
Publication of EP1355065B1 publication Critical patent/EP1355065B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-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
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40561—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged upstream of the flow control means
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/421—Flow control characterised by the type of actuation mechanically
    • F15B2211/423—Flow control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure 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
    • F15B2211/60—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
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using 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
    • F15B2211/60—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
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/605—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
    • F15B2211/70—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
    • F15B2211/7058—Rotary 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
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7121—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in series
    • 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
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means
    • 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation

Definitions

  • the invention relates to a hydraulic control a hydraulic motor that has two working lines is connected to a control valve that with a Low pressure connection and via a compensation valve is connected to a high pressure connection.
  • the control valve here depends on the desired direction of actuation of the motor flow paths free, on the one hand from the high pressure connection to a management and on the other hand from the other Working line for low pressure connection. This release is more or less throttled, the level of the throttle resistance depends on Actuation stroke (or a corresponding other actuation movement) of the control valve.
  • the compensation valve serves as a pressure control valve. It does occasionally also known as a pressure compensator. It ensures that practical over the spool of the control valve always the same pressure drops.
  • the compensation valve is expediently by a slide formed on one side by a return spring and the load pressure and on the other side of that Pressure in a line section between the compensation valve and the control valve is removed. Naturally such a compensation valve can also be trained in another way.
  • the invention is based, with negative Ensure stable operation in both directions to be able to.
  • the flow characteristic is the ratio of Flow rate to pressure, one for pressure either the pressure difference across the compensation valve or the reflux compensation valve or the pressure at Output of the compensation valve or the reflux compensation valve can watch. If the flow characteristics neither cover nor cut, then there is no point in being a critical situation can arise. It is always clearly regulated which of the Compensation valves ultimately for controlling the Hydraulic fluid is "responsible".
  • the backflow compensation valves under otherwise identical conditions a larger one Flow as the compensation valve. So that will ensured that through the backflow compensation valves or the reflux compensation valve that the Control takes over, more and more liquid flows can than through the compensation valve. In case of a negative load it is clear that the backflow compensation valve the control takes over and the compensation valve no influence on the control of the amount of liquid Has. Because through the backflow compensation valve prevents more liquid from flowing out that the hydraulic system of the control "inflated" becomes.
  • the backflow compensation valve that is responsible for a negative load in one direction is to drain more fluid than through that Compensation valve can flow under certain circumstances. In order to symptoms of cavitation could occur that can be prevented by the suction valve arrangement.
  • the suction valve arrangement enables a sufficient amount of hydraulic fluid back in the circuit can be fed.
  • the suction valve arrangement preferably has switchable shut-off valve.
  • the switchable shut-off valve preferably closes automatically with negative loads. So you are not more reliant on a certain one to save energy Action, namely the check valve close.
  • the check valve is then automatically closed when the return compensation valves are in operation be taken. The closing does not have to a complete blockage of the fluid flow to lead.
  • the compensation valve preferably has a lower one Spring tension as the backflow compensation valves on. This is a relatively easy way to get around Flow characteristics of the compensation valve on the one hand and the reflux compensation valves on the other hand to provide different flow characteristics.
  • the Compensation valve is in at a lower pressure Closed position moves as the backflow compensation valves.
  • control valve in the flow direction from the high pressure connection to the engine greater flow resistance than in the direction of flow from the engine to the low pressure connection.
  • the backflow compensation valves each with a load sensor connection, that works in the opening direction, and with one Control connection are provided in the closing direction acts and connected to a section of the work management which leads to the control valve and the backflow compensation valve in the work management, through the hydraulic fluid flows to the engine through which The load sensor connection is pressurized with the same pressure who is in the management team. So that will easily ensured that the compensation valve or the return compensation valve, the should not intervene in the control, fully open becomes. So you close the influence of this valve practically almost out. This results in a highly stable Control option.
  • a controller 1 has a proportional valve 2 as Control valve on that in Fig. 1 only schematically is shown.
  • the proportional valve 2 has two adjustable chokes A, B on, also by one only schematically shown operating handle 3 can be adjusted.
  • the proportional valve 2 is with a high pressure connection P and with a low pressure connection T connected.
  • a compensation valve 4 is arranged, which has a return spring 5, which is the compensation valve 4 biased in the opening direction.
  • the compensation valve 4 for example Have slide which of the return spring 5 in Opening direction is loaded.
  • the slide via a line 6 with a pressure on one Point 7 between the compensation valve 4 and the Throttle A can be applied.
  • the proportional valve 2 is via working lines 8, 9 connected to a motor 10.
  • the motor 10 consists of two partial drives, each can act on the wheels of a vehicle.
  • the motor 10 is provided with a brake 11, which has a Control line 12 can be solved.
  • In the control line there is pressure behind the throttle A. Because that Proportional valve 2 in a manner not shown the pressure from the high pressure connection P also via the throttle B can lead to the motor 10 is a shuttle valve 13 provided that the higher pressure behind each Chokes A, B used to release the brake 11.
  • the compensation valve 4 is also from a Load sensing pressure LS applied in the opening direction, i.e. the load sensing pressure LS acts in the same direction as that Return spring 5.
  • the return spring 5 generates a Force that corresponds to a pressure of 7 bar, for example.
  • a backflow compensation valve 14 In the working line 8 is a backflow compensation valve 14 is arranged and in the working line 9 a reflux compensation valve 15 is arranged. Both Backflow compensation valves 14, 15 are by return springs 16, 17 acted upon in the opening direction. Both return springs 16, 17 generate a force that corresponds to a pressure of, for example, 8 bar.
  • a pressure in a load sensor connection acts in the same direction LSA for the backflow compensation valve 14 and LSB for the backflow compensation valve 15.
  • the reflux compensation valve acts in the closing direction 14 a pressure at a point 18 between the proportional valve 2 and the reflux compensation valve 14. In the same way acts on the Backflow compensation valve 15 the pressure at one point 19 between the proportional valve 2 and the reflux compensation valve 15th
  • a suction valve assembly 20 with a suction valve 21 for the working line 8 and a suction valve 22 for the working line 9 is via a suction line 23 connected to the low pressure port T.
  • a suction line 23 connected to the low pressure port T.
  • the Check valve 26 has a magnetic drive 27 which it from the open position shown to a closed position Position can switch. In the closed Position of the check valve 26 is a suction the low pressure connection T is not possible.
  • the controller 1 works as follows:
  • the return compensation valve 14 is in one direction from the pressure at point 18, i.e. from the pressure in the working line 8. In the other direction is the return compensation valve 14 but acted upon by the pressure at the load sensor connection LSA, which corresponds to the pressure after throttle A. (also the pressure in the working line 8), so that the return compensation valve 14 is fully opened becomes.
  • the return compensation valve is in the same way 15 fully open. This is in Closing direction from the pressure at point 19, i.e. from pressure in the work line 9, acted upon.
  • a characteristic curve 28 gives the behavior of the compensation valve 4 again, i.e. the amount of liquid depending from the position of the proportional valve 2 for the case that the vehicle is driven by the engine 10 is.
  • the flow characteristic 28 is thus the flow characteristic of the compensation valve 4.
  • a flow characteristic 29, however, is the flow characteristic the backflow compensation valves 14, 15. This is for both reflux compensation valves 14, 15 equal. It gives the flow depending on the Position of the proportional valve 2 for the case again, that the vehicle drives the engine 10.
  • the two reflux compensation valves 14, 15 can be combined in one unit 30.
  • the unit 30 can, for example, directly on the associated proportional valve 2 are attached.
  • the assembly 30 takes up little space. But you can also do it arrange directly on the motor 10.
  • the refill valve arrangement 20 can, so to speak the area between the two flow characteristics Fill in 28, 29. So you make sure that in the Control 1 no cavitation occurs.
  • Fig. 3 shows an embodiment of a controller, at the same and corresponding parts with the are provided with the same reference numerals.
  • the 3 contains an input module 31, that with a number of known and therefore valves not described in detail, such as pressure maintenance and Pressure relief valves is provided.
  • this input module 31 is the proportional valve 2 with the high pressure connection P connected, in this connection the compensation valve 4 is arranged.
  • the proportional valve 2 has three working positions a, b, c on. In the position b shown the proportional valve 2 is in the neutral position. In In this case, the load sensing line LS with the pressure on Low pressure connection T is applied. Accordingly the brakes 11 would be applied and the vehicle would be slowed down.
  • the slide of the proportional valve 2 in the Position a is moved, then the high pressure connection P with the working line 9 and the low pressure connection T connected to the working line 8.
  • the load sensing line LSB with the pressure acted on at point 9 and the load sensing line LSA the pressure at the low pressure connection T.
  • the motor is driving, then comes into position a of the proportional valve 2 hydraulic fluid under pressure from a pump 32 via the high pressure connection P, the compensation valve 4, the proportional valve 2, the working line 9 and the return compensation valve 15 to the engine 10.
  • the compensation valve 4 is along the flow characteristic curve 28 (Fig. 2) controlled, depending on how wide open the throttles of the proportional valve 2 become.
  • the pressure at point 9 also reaches the load sensing line LSB, while the load sensing line LSA with the Pressure at the low pressure port T is provided. Accordingly the return compensation valve 15 under the effect of the pressure in the load sensing line LSB and the return spring 17 opened against the pressure at point 19. In the end, only "net” works the return spring 17.
  • the return compensation valve 14 opens completely because of pressure at the point 18 corresponds essentially to the tank pressure and thus practically no force applied in the closing direction becomes.
  • the motor 10 is exposed to a negative load is, for example, if the vehicle from a certain Speed should be slowed down and that Vehicle thus drives the engine 10, then more Hydraulic fluid output by the engine 10 as can be supplied by the proportional valve 2. Accordingly, the pressure at point 18 rises and that Backflow compensation valve 14 controls the flow corresponding to the flow characteristic curve 29 (Fig. 2). Since the Pressure at point 7 drops - the hydraulic fluid becomes aspirated by the motor 10 so to speak - opens that Compensation valve 4 completely, so that the proportional valve 2 provided liquid only through the backflow compensation valve 14 is determined. The compensation valve does the amount that has always done it. But since the backflow compensation valve 14 is now determining something Oil is missing and this oil is refilled.
  • the check valve 26 is of the pressure at the low pressure connection T on the one hand and on the other hand from the higher of the two Pressures applied in the load sensing lines LSA, LSB.
  • the pressure in the load sensing line LSA as stated above, practically 0, i.e. it corresponds to the pressure on Low pressure connection T. Also the pressure in the load sensing line LSB drops, so that the check valve 26 at A negative load automatically occurs in the Fig. 3 shown closed position is moved. The suction via the check valve 22 is therefore carried out with hydraulic fluid, which one immediately comes from the low pressure connection of the proportional valve 2 wins.
  • the check valve is here by a return spring 34 charged, the correspondingly low Press on the low pressure connection T and in the load sensing lines LSA, LSB the check valve 26 in the illustrated Position shifts.

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Abstract

The hydraulic control system includes a hydraulic motor (10) connected to a control valve which is connected to a low-pressure connection (T) and, via a compensating valve, to a high-pressure connection (P). A return flow compensating valve (14,15) is installed in each working line, each valve having a flow characteristic line which extends towards the flow characteristic line of the compensating valve (4) without intersecting. The flow characteristic lines of the return flow compensating valves are equal, and the flow characteristic lines of the return flow valves and compensating valve may be parallel.

Description

Die Erfindung betrifft eine hydraulische Steuerung mit einem hydraulischen Motor, der über zwei Arbeitsleitungen mit einem Steuerventil verbunden ist, das mit einem Niederdruckanschluß und über ein Kompensationsventil mit einem Hochdruckanschluß verbunden ist.The invention relates to a hydraulic control a hydraulic motor that has two working lines is connected to a control valve that with a Low pressure connection and via a compensation valve is connected to a high pressure connection.

Das Steuerventil gibt hierbei in Abhängigkeit von der gewünschten Betätigungsrichtung des Motors Strömungspfade frei, und zwar einerseits vom Hochdruckanschluß zu einer Arbeitsleitung und andererseits von der anderen Arbeitsleitung zum Niederdruckanschluß. Diese Freigabe erfolgt allerdings mehr oder weniger gedrosselt, wobei die Höhe des Drosselwiderstandes abhängig ist vom Betätigungshub (oder einer entsprechend anderen Betätigungsbewegung) des Steuerventils. Das Kompensationsventil dient hierbei als Druckregelventil. Es wird gelegentlich auch als Druckwaage bezeichnet. Es sorgt dafür, daß über dem Schieber des Steuerventils praktisch immer der gleiche Druck abfällt. Das Kompensationsventil wird dabei zweckmäßigerweise durch einen Schieber gebildet, der auf einer Seite von einer Rückstellfeder und dem Lastdruck und auf der anderen Seite von dem Druck in einem Leitungsabschnitt zwischen dem Kompensationsventil und dem Steuerventil abgenommen wird. Natürlich kann ein derartiges Kompensationsventil auch auf andere Weise ausgebildet sein. The control valve here depends on the desired direction of actuation of the motor flow paths free, on the one hand from the high pressure connection to a management and on the other hand from the other Working line for low pressure connection. This release is more or less throttled, the level of the throttle resistance depends on Actuation stroke (or a corresponding other actuation movement) of the control valve. The compensation valve serves as a pressure control valve. It does occasionally also known as a pressure compensator. It ensures that practical over the spool of the control valve always the same pressure drops. The compensation valve is expediently by a slide formed on one side by a return spring and the load pressure and on the other side of that Pressure in a line section between the compensation valve and the control valve is removed. Naturally such a compensation valve can also be trained in another way.

Derartige Steuerungen arbeiten in der Regel zuverlässig. Probleme treten dann auf, wenn der Motor mit sogenannten negativen Lasten arbeitet. Derartige negative Lasten können beispielsweise auftreten, wenn der Motor durch ein äußeres Gewicht betätigt wird, beispielsweise eine Last, die an einem Kranhaken hängt. Ein anderes Beispiel ist das Eigengewicht eines Fahrzeugs, das auf einer schiefen Ebene abrollt oder aus einer gewissen Geschwindigkeit abgebremst werden muß. In diesem Fall kann das hydraulische System der Steuerung zu Schwingungen neigen.Such controls usually work reliably. Problems occur when the engine with so-called negative loads works. Such negative For example, loads can occur when the engine is operated by an external weight, for example a load hanging on a crane hook. Another Example is the dead weight of a vehicle that is on rolls on an inclined plane or from a certain one Speed must be slowed down. In this case the hydraulic system of the controller can vibrate tend.

Es ist daher bekannt, in einer Arbeitsleitung zwischen dem Motor und dem Steuerventil ein Rücklaufkompensationsventil anzuordnen, das ebenfalls als Druckregelventil oder Druckwaage ausgebildet sein kann. Das Rücklaufkompensationsventil sorgt dafür, daß nur dann, wenn dem Motor weiterhin Hydraulikflüssigkeit unter Druck zugeführt wird, der Motor auch betätigt werden kann.It is therefore known to work between a return compensation valve to the motor and the control valve to arrange, also as a pressure control valve or pressure compensator can be formed. The return compensation valve ensures that only if hydraulic fluid under pressure to the engine is supplied, the motor can also be operated.

Allerdings läßt sich auch hier beobachten, daß das System zu Schwingungen neigt.However, it can also be observed here that the system tends to vibrate.

Der Erfindung liegt die Aufgabe zugrunde, bei negativen Lasten in beiden Richtungen einen stabilen Betrieb gewährleisten zu können.The invention is based, with negative Ensure stable operation in both directions to be able to.

Diese Aufgabe wird bei einer hydraulischen Steuerung der eingangs genannten Art dadurch gelöst, daß in jeder Arbeitsleitung ein Rückflußkompensationsventil angeordnet ist, wobei die Rückflußkompensationsventile jeweils eine Durchflußkennlinie aufweisen, die kreuzungsfrei zur Durchflußkennlinie des Kompensationsventils verläuft.This task is done with a hydraulic control of the type mentioned solved in that in each Working line arranged a backflow compensation valve is, the reflux compensation valves each have a flow characteristic that is free of crossings runs to the flow characteristic of the compensation valve.

Man verwendet also zunächst in jeder Arbeitsleitung ein eigenes Rückflußkompensationsventil. Damit ist gewährleistet, daß in beiden Arbeitsrichtungen negative Lasten gesteuert werden können. Darüber hinaus sorgt man aber dafür, daß die Rücklaufkompensationsventile einerseits und das Kompensationsventil andererseits, also die beiden Ventile oder Ventilgruppen auf beiden Seiten des Steuerventils, aufeinander abgestimmt sind. Die beiden Rückflußkompensationsventile einerseits und das Kompensationsventil andererseits haben Durchflußkennlinien, die sich nicht decken und die kreuzungsfrei zueinander verlaufen. Damit wird unabhängig von der Richtung, in der das Steuerventil betätigt wird, immer sichergestellt, daß nur ein Kompensationsventil, also entweder das Kompensationsventil oder eines der Rückflußkompensationsventile, tätig werden kann. Damit wird das System stabil und zwar auch bei negativen Lasten. Die Durchflußkennlinie ist hierbei das Verhältnis von Durchflußmenge zu Druck, wobei man für den Druck entweder die Druckdifferenz über das Kompensationsventil bzw. das Rückflußkompensationsventil oder den Druck am Ausgang des Kompensationsventils bzw. des Rückflußkompensationsventils ansehen kann. Wenn sich die Durchflußkennlinien weder überdecken noch schneiden, dann gibt es keinen Punkt, in dem eine kritische Situation entstehen kann. Es ist immer klar geregelt, welches der Kompensationsventile letztendlich für die Steuerung der Hydraulikflüssigkeit "zuständig" ist. So you first use it in every work management own backflow compensation valve. This ensures that negative loads in both directions can be controlled. In addition, you care but that the return compensation valves on the one hand and the compensation valve on the other hand the two valves or valve groups on both sides of the control valve are coordinated. The two reflux compensation valves on the one hand and that Compensation valve, on the other hand, have flow characteristics, that do not coincide and that do not cross each other run. So regardless of the direction, in which the control valve is actuated, always ensured that only one compensation valve, so either the compensation valve or one of the backflow compensation valves, can act. So that will the system is stable, even with negative loads. The flow characteristic is the ratio of Flow rate to pressure, one for pressure either the pressure difference across the compensation valve or the reflux compensation valve or the pressure at Output of the compensation valve or the reflux compensation valve can watch. If the flow characteristics neither cover nor cut, then there is no point in being a critical situation can arise. It is always clearly regulated which of the Compensation valves ultimately for controlling the Hydraulic fluid is "responsible".

Hierbei ist bevorzugt, daß die Durchflußkennlinien der beiden Rückflußkompensationsventile gleich sind. Damit wird das Verhalten bei der Bewältigung von negativen Lasten in beide Richtungen gleich.It is preferred that the flow characteristics of two reflux compensation valves are the same. In order to becomes the behavior when coping with negative Loads the same in both directions.

Vorzugsweise verlaufen die Durchflußkennlinien der Rückflußkompensationsventile und des Kompensationsventils parallel zueinander. Damit bekommt man bei der Steuerung von positiven und negativen Lasten ein annähernd gleiches Steuerungsverhalten, das sich lediglich durch einen Offset unterscheidet. Die Steuerung wird dann für einen Bediener einfacher. Die Bedienung wird dabei um so einfacher, je kleiner der Offset zwischen den beiden Kurven ist. In einer Alternative ist auch vorstellbar, daß die Kurven im gleichen Punkt starten und unter einem kleinen Winkel auseinanderlaufen.The flow characteristics of the Backflow compensation valves and the compensation valve parallel to each other. So you get at the Approximate control of positive and negative loads same control behavior that only distinguished by an offset. The controller will then easier for an operator. The service is the easier the smaller the offset between the two curves. An alternative is also imaginable that the curves start at the same point and diverge at a small angle.

Vorzugsweise weisen die Rückflußkompensationsventile bei ansonsten gleichen Bedingungen einen größeren Durchfluß als das Kompensationsventil auf. Damit wird sichergestellt, daß durch die Rückflußkompensationsventile bzw. das Rückflußkompensationsventil, das die Steuerung übernimmt, immer mehr Flüssigkeit fließen kann als durch das Kompensationsventil. Im Falle einer negativen Last ist also klar, daß das Rückflußkompensationsventil die Steuerung übernimmt und das Kompensationsventil keinen Einfluß auf die Steuerung der Flüssigkeitsmenge hat. Da durch das Rückflußkompensationsventil mehr Flüssigkeit abfließen kann, wird verhindert, daß das hydraulische System der Steuerung "aufgepumpt" wird. Preferably, the backflow compensation valves under otherwise identical conditions a larger one Flow as the compensation valve. So that will ensured that through the backflow compensation valves or the reflux compensation valve that the Control takes over, more and more liquid flows can than through the compensation valve. In case of a negative load it is clear that the backflow compensation valve the control takes over and the compensation valve no influence on the control of the amount of liquid Has. Because through the backflow compensation valve prevents more liquid from flowing out that the hydraulic system of the control "inflated" becomes.

Vorzugsweise mündet zwischen dem Motor und den Rückflußkompensationsventilen eine Nachsaugventilanordnung. Wie angegeben, kann durch das Rückflußkompensationsventil, das bei einer negativen Last in einer Richtung zuständig ist, mehr Flüssigkeit abfließen als durch das Kompensationsventil unter Umständen zufließen kann. Damit könnten Kavitationserscheinungen auftreten, die durch die Nachsaugventilanordnung verhindert werden. Die Nachsaugventilanordnung ermöglicht es, daß eine ausreichende Menge von Hydraulikflüssigkeit wieder in den Kreislauf eingespeist werden kann.Preferably opens between the engine and the backflow compensation valves a suction valve arrangement. As indicated, the backflow compensation valve, that is responsible for a negative load in one direction is to drain more fluid than through that Compensation valve can flow under certain circumstances. In order to symptoms of cavitation could occur that can be prevented by the suction valve arrangement. The suction valve arrangement enables a sufficient amount of hydraulic fluid back in the circuit can be fed.

Bevorzugterweise weist die Nachsaugventilanordnung ein schaltbares Sperrventil auf. Wenn das Sperrventil geschlossen wird, dann ist eine Verbindung der Niederdruckleitung zum Tank unterbrochen, d.h. das Nachsaugen der hydraulischen Flüssigkeit kann nicht mehr aus dem Tank erfolgen. Da aber bei negativen Lasten genügend Hydraulikflüssigkeit auf der Ausgangsseite des Motors abgegeben wird und diese Flüssigkeit an und für sich durch den Niederdruckanschluß zum Tank gelangen sollte, kann diese Flüssigkeit sozusagen innerhalb der Steuerung im Kreis geführt werden. Dies ergibt eine teilweise erhebliche Energieeinsparung. Wenn man sich vorstellt, daß die Durchflußkennlinien des Kompensationsventils einerseits und der Rückflußkompensationsventile andererseits parallel verlaufen, dann ist es mit Hilfe der Nachsaugventilanordnung möglich, den Bereich zwischen den beiden Durchflußkennlinien nachzufüllen.The suction valve arrangement preferably has switchable shut-off valve. When the check valve is closed then there is a connection of the low pressure line interrupted to the tank, i.e. sucking up the hydraulic fluid can no longer come out of the Tank. But there is enough for negative loads Hydraulic fluid on the output side of the engine is released and this liquid in and of itself should reach the tank through the low pressure connection, this liquid can be found within the control system be guided in a circle. This results in a partial considerable energy savings. If you imagine that the flow characteristics of the compensation valve on the one hand and the reflux compensation valves on the other hand run parallel, then it is with help the suction valve arrangement possible, the area between refill the two flow characteristics.

Bevorzugterweise schließt das schaltbare Sperrventil bei negativen Lasten automatisch. Man ist also nicht mehr darauf angewiesen, zur Energieeinsparung eine bestimmte Handlung vorzunehmen, nämlich das Sperrventil zu schließen. Das Sperrventil wird automatisch dann geschlossen, wenn die Rücklaufkompensationsventile in Betrieb genommen werden. Das Schließen muß dabei nicht zu einer vollständigen Blockierung des Flüssigkeitsstroms führen.The switchable shut-off valve preferably closes automatically with negative loads. So you are not more reliant on a certain one to save energy Action, namely the check valve close. The check valve is then automatically closed when the return compensation valves are in operation be taken. The closing does not have to a complete blockage of the fluid flow to lead.

Vorzugsweise weist das Kompensationsventil eine geringere Federspannung als die Rückflußkompensationsventile auf. Dies ist eine relativ einfache Möglichkeit, um die Durchflußkennlinien des Kompensationsventils einerseits und der Rückflußkompensationsventile andererseits mit unterschiedlichen Durchflußkennlinien zu versehen. Das Kompensationsventil wird bei einem geringeren Druck in Schließstellung bewegt als die Rückflußkompensationsventile.The compensation valve preferably has a lower one Spring tension as the backflow compensation valves on. This is a relatively easy way to get around Flow characteristics of the compensation valve on the one hand and the reflux compensation valves on the other hand to provide different flow characteristics. The Compensation valve is in at a lower pressure Closed position moves as the backflow compensation valves.

In einer alternativen oder zusätzlichen Ausgestaltung kann vorgesehen sein, daß das Steuerventil in Strömungsrichtung vom Hochdruckanschluß zum Motor einen größeren Strömungswiderstand als in Strömungsrichtung vom Motor zum Niederdruckanschluß aufweist. Auch damit lassen sich die Druckverhältnisse so gestalten, daß die Durchflußkennlinien von Kompensationsventil einerseits und Rückflußkompensationsventilen andererseits unterschiedlich ausgebildet sind, so daß sie weder aufeinanderliegen noch sich kreuzen.In an alternative or additional embodiment can be provided that the control valve in the flow direction from the high pressure connection to the engine greater flow resistance than in the direction of flow from the engine to the low pressure connection. With that too the pressure ratios can be designed so that the Flow characteristics of the compensation valve on the one hand and reflux compensation valves, on the other hand are trained so that they are neither on top of each other still cross each other.

In einer bevorzugten Ausgestaltung ist vorgesehen, daß die Rückflußkompensationsventile mit je einem Lastfühlanschluß, der in Öffnungsrichtung wirkt, und mit einem Steueranschluß versehen sind, der in Schließrichtung wirkt und mit einem Abschnitt der Arbeitsleitung verbunden ist, der zum Steuerventil führt, und das Rückflußkompensationsventil in der Arbeitsleitung, durch die Hydraulikflüssigkeit zum Motor strömt, durch den Lastfühlanschluß mit dem gleichen Druck beaufschlagt wird, der in der Arbeitsleitung herrscht. Damit wird auf einfache Weise sichergestellt, daß das Kompensationsventil bzw. das Rücklaufkompensationsventil, das nicht in die Steuerung eingreifen soll, vollständig geöffnet wird. Man schließt also den Einfluß dieses Ventils praktisch nahezu aus. Dies ergibt eine hochstabile Steuerungsmöglichkeit.In a preferred embodiment it is provided that the backflow compensation valves, each with a load sensor connection, that works in the opening direction, and with one Control connection are provided in the closing direction acts and connected to a section of the work management which leads to the control valve and the backflow compensation valve in the work management, through the hydraulic fluid flows to the engine through which The load sensor connection is pressurized with the same pressure who is in the management team. So that will easily ensured that the compensation valve or the return compensation valve, the should not intervene in the control, fully open becomes. So you close the influence of this valve practically almost out. This results in a highly stable Control option.

Die Erfindung wird im folgenden anhand von bevorzugten Ausführungsbeispielen in Verbindung mit der Zeichnung näher beschrieben. Hierin zeigen:

Fig. 1
eine schematische Darstellung einer hydraulischen Steuerung,
Fig. 2
eine schematische Darstellung von Kennlinien und
Fig. 3
ein Ausführungsbeispiel einer hydraulischen Steuerung.
The invention is described below with reference to preferred embodiments in conjunction with the drawing. Show here:
Fig. 1
a schematic representation of a hydraulic control,
Fig. 2
a schematic representation of characteristics and
Fig. 3
an embodiment of a hydraulic control.

Eine Steuerung 1 weist ein Proportionalventil 2 als Steuerventil auf, das in Fig. 1 lediglich schematisch dargestellt ist. Das Proportionalventil 2 weist zwei verstellbare Drosseln A, B auf, die von einer ebenfalls nur schematisch dargestellten Betätigungshandhabe 3 verstellt werden können. Das Proportionalventil 2 ist mit einem Hochdruckanschluß P und mit einem Niederdruckanschluß T verbunden. In der Verbindung zum Hochdruckanschluß P ist ein Kompensationsventil 4 angeordnet, das eine Rückstellfeder 5 aufweist, die das Kompensationsventil 4 in Öffnungsrichtung vorspannt. Hierzu kann das Kompensationsventil 4 beispielsweise einen Schieber aufweisen, der von der Rückstellfeder 5 in Öffnungsrichtung belastet ist. In Schließrichtung ist der Schieber über eine Leitung 6 mit einem Druck an einem Punkt 7 zwischen dem Kompensationsventil 4 und der Drossel A beaufschlagbar. Wenn also die Drossel A geschlossen ist, dann steigt der Druck am Punkt 7 so weit an, daß das Kompensationsventil 4 geschlossen wird. Wenn die Drossel A geöffnet wird, dann sinkt der Druck am Punkt 7 ab und die Rückstellfeder 5 kann das Kompensationsventil 4 weiter öffnen. Aus diesem Grund kann das Kompensationsventil 4 auch als Druckregelventil oder Druckwaage bezeichnet werden.A controller 1 has a proportional valve 2 as Control valve on that in Fig. 1 only schematically is shown. The proportional valve 2 has two adjustable chokes A, B on, also by one only schematically shown operating handle 3 can be adjusted. The proportional valve 2 is with a high pressure connection P and with a low pressure connection T connected. In connection to the high pressure connection P a compensation valve 4 is arranged, which has a return spring 5, which is the compensation valve 4 biased in the opening direction. For this can the compensation valve 4, for example Have slide which of the return spring 5 in Opening direction is loaded. In the closing direction the slide via a line 6 with a pressure on one Point 7 between the compensation valve 4 and the Throttle A can be applied. So when the throttle A is closed then the pressure at point 7 rises so far that the compensation valve 4 is closed. When throttle A is opened, the pressure drops at point 7 and the return spring 5 can the compensation valve 4 open further. Because of this, can the compensation valve 4 also as a pressure control valve or pressure compensator.

Das Proportionalventil 2 ist über Arbeitsleitungen 8, 9 mit einem Motor 10 verbunden. Im vorliegenden Fall besteht der Motor 10 aus zwei Teilantrieben, die jeweils auf die Räder eines Fahrzeugs wirken können. Der Motor 10 ist mit einer Bremse 11 versehen, die über eine Steuerleitung 12 gelöst werden kann. In der Steuerleitung herrscht der Druck hinter der Drossel A. Da das Proportionalventil 2 in nicht näher dargestellter Weise den Druck vom Hochdruckanschluß P auch über die Drossel B zum Motor 10 leiten kann, ist ein Wechselventil 13 vorgesehen, das den jeweils höheren Druck hinter den Drosseln A, B zum Lösen der Bremse 11 verwendet. The proportional valve 2 is via working lines 8, 9 connected to a motor 10. In the present case the motor 10 consists of two partial drives, each can act on the wheels of a vehicle. The motor 10 is provided with a brake 11, which has a Control line 12 can be solved. In the control line there is pressure behind the throttle A. Because that Proportional valve 2 in a manner not shown the pressure from the high pressure connection P also via the throttle B can lead to the motor 10 is a shuttle valve 13 provided that the higher pressure behind each Chokes A, B used to release the brake 11.

Das Kompensationsventil 4 wird zusätzlich von einem Lastfühldruck LS in Öffnungsrichtung beaufschlagt, d.h. der Lastfühldruck LS wirkt in gleicher Richtung wie die Rückstellfeder 5. Die Rückstellfeder 5 erzeugt eine Kraft, die beispielsweise einem Druck von 7 bar entspricht.The compensation valve 4 is also from a Load sensing pressure LS applied in the opening direction, i.e. the load sensing pressure LS acts in the same direction as that Return spring 5. The return spring 5 generates a Force that corresponds to a pressure of 7 bar, for example.

In der Arbeitsleitung 8 ist ein Rückflußkompensationsventil 14 angeordnet und in der Arbeitsleitung 9 ist ein Rückflußkompensationsventil 15 angeordnet. Beide Rückflußkompensationsventile 14, 15 werden durch Rückstellfedern 16, 17 in Öffnungsrichtung beaufschlagt. Beide Rückstellfedern 16, 17 erzeugen eine Kraft, die einem Druck von beispielsweise 8 bar entspricht. In die gleiche Richtung wirkt jeweils ein Druck in einem Lastfühlanschluß LSA für das Rückflußkompensationsventil 14 und LSB für das Rückflußkompensationsventil 15.In the working line 8 is a backflow compensation valve 14 is arranged and in the working line 9 a reflux compensation valve 15 is arranged. Both Backflow compensation valves 14, 15 are by return springs 16, 17 acted upon in the opening direction. Both return springs 16, 17 generate a force that corresponds to a pressure of, for example, 8 bar. In the A pressure in a load sensor connection acts in the same direction LSA for the backflow compensation valve 14 and LSB for the backflow compensation valve 15.

In Schließrichtung wirkt auf das Rückflußkompensationsventil 14 ein Druck an einem Punkt 18 zwischen dem Proportionalventil 2 und dem Rückflußkompensationsventil 14. In gleicher Weise wirkt in Schließrichtung auf das Rückflußkompensationsventil 15 der Druck an einem Punkt 19 zwischen dem Proportionalventil 2 und dem Rückflußkompensationsventil 15.The reflux compensation valve acts in the closing direction 14 a pressure at a point 18 between the proportional valve 2 and the reflux compensation valve 14. In the same way acts on the Backflow compensation valve 15 the pressure at one point 19 between the proportional valve 2 and the reflux compensation valve 15th

Eine Nachsaugventilanordnung 20 mit einem Nachsaugventil 21 für die Arbeitsleitung 8 und einem Nachsaugventil 22 für die Arbeitsleitung 9 ist über eine Nachsaugleitung 23 mit dem Niederdruckanschluß T verbunden. Allerdings ist zwischen dem Niederdruckanschluß T und der Nachsaugleitung 23 noch die Parallelschaltung eines Rückschlagventils 24, das durch eine Feder 25 vorgespannt ist, und eines Sperrventils 26 angeordnet. Das Sperrventil 26 weist einen Magnetantrieb 27 auf, der es aus der dargestellten geöffneten Position in eine geschlossene Position umschalten kann. In der geschlossenen Position des Sperrventils 26 ist ein Nachsaugen aus dem Niederdruckanschluß T nicht möglich.A suction valve assembly 20 with a suction valve 21 for the working line 8 and a suction valve 22 for the working line 9 is via a suction line 23 connected to the low pressure port T. Indeed is between the low pressure port T and the Nachsaugleitung 23 still the parallel connection of one Check valve 24, which is biased by a spring 25 and a check valve 26 is arranged. The Check valve 26 has a magnetic drive 27 which it from the open position shown to a closed position Position can switch. In the closed Position of the check valve 26 is a suction the low pressure connection T is not possible.

Die Steuerung 1 arbeitet wie folgt:The controller 1 works as follows:

Solange die beiden Drosseln A, B des Proportionalventils 2 geschlossen sind, herrscht auch in dem Lastfühlanschluß LS der Druck 0, so daß die Bremse 11 den Motor 10 festhält. Sobald das Proportionalventil 2 betätigt wird, die Drosseln A, B also geöffnet werden, steigt der Druck in der Lastfühlleitung LS, so daß die Bremsen 11 gelöst werden.As long as the two throttles A, B of the proportional valve 2 are closed, there is also in the load sensor connection LS the pressure 0 so that the brake 11 the motor 10 holds. As soon as the proportional valve 2 is actuated the chokes A, B are opened, increases the pressure in the load sensing line LS, so that the brakes 11 can be solved.

Wenn die beiden Drosseln A, B des Proportionalventils 2 geöffnet werden, dann sinkt der Druck am Punkt 7 und das Kompensationsventil 4 öffnet, so daß Hydraulikflüssigkeit durch das Rücklaufkompensationsventil 14 zum Motor 10 fließen kann. Das Rücklaufkompensationsventil 14 ist zwar in die eine Richtung vom Druck am Punkt 18, d.h. vom Druck in der Arbeitsleitung 8, beaufschlagt. In der anderen Richtung ist das Rücklaufkompensationsventil 14 aber vom Druck am Lastfühlanschluß LSA beaufschlagt, der dem Druck nach der Drossel A entspricht (also ebenfalls dem Druck in der Arbeitsleitung 8), so daß das Rücklaufkompensationsventil 14 vollständig geöffnet wird. In gleicher Weise ist das Rücklaufkompensationsventil 15 vollständig geöffnet. Dieses wird in Schließrichtung vom Druck am Punkt 19, d.h. vom Druck in der Arbeitsleitung 9, beaufschlagt. In Öffnungsrichtung wirkt auf das Rücklaufkompensationsventil 15 die Kraft der Rückstellfeder 17 und der Druck im Lastfühlanschluß LSB, der mindestens so groß ist wie der Druck am Punkt 19. Die Hydraulikflüssigkeit gelangt also mehr oder weniger ungehindert durch das Rückflußkompensationsventil 15 und durch die Drossel B zum Niederdruckanschluß T, wobei sie durch das Sperrventil 26, das geöffnet ist, abfließen kann. Falls das Sperrventil 26 geschlossen ist, kann die Hydraulikflüssigkeit durch das Rückschlagventil 24 treten, wenn sie die Kraft der Feder 25 überwinden kann. Diese Kraft entspricht beispielsweise einem Druck von 5 bar.If the two throttles A, B of the proportional valve 2 opened, then the pressure at point 7 and the compensation valve 4 opens so that hydraulic fluid through the return compensation valve 14 to Motor 10 can flow. The return compensation valve 14 is in one direction from the pressure at point 18, i.e. from the pressure in the working line 8. In the other direction is the return compensation valve 14 but acted upon by the pressure at the load sensor connection LSA, which corresponds to the pressure after throttle A. (also the pressure in the working line 8), so that the return compensation valve 14 is fully opened becomes. The return compensation valve is in the same way 15 fully open. This is in Closing direction from the pressure at point 19, i.e. from pressure in the work line 9, acted upon. In the opening direction acts on the return compensation valve 15 Force of the return spring 17 and the pressure in the load sensor connection LSB that is at least as large as the pressure at point 19. The hydraulic fluid gets more or less unhindered by the backflow compensation valve 15 and through throttle B to the low pressure connection T, being opened by the check valve 26 is, can drain off. If the check valve 26 is closed, the hydraulic fluid can the check valve 24 kick when the force of Spring 25 can overcome. This force corresponds, for example a pressure of 5 bar.

Das so angetriebene Fahrzeug kann nun in eine Situation gelangen, wo der Motor 10 nicht antreibt, sondern getrieben wird. Dies kann beispielsweise der Fall sein, wenn das Fahrzeug ein Gefälle hinabrollt oder aus einer gewissen Geschwindigkeit herabgebremst wird. In diesem Fall fördert der Motor mehr Hydraulikflüssigkeit in die Arbeitsleitung 9, als er durch die Arbeitsleitung 8 aus dem Hochdruckanschluß P erhält. Dementsprechend sinkt der Druck am Punkt 18. Das Rücklaufkompensationsventil 14 bleibt also vollständig geöffnet. Am Punkt 19 steigt hingegen der Druck an, weil die abfließende Hydraulikflüssigkeit durch die Drossel B treten muß, was bei einer größeren Flüssigkeitsmenge einen entsprechend größeren Druckabfall verursacht. Gleichzeitig ist der Druck in der Lastfühlleitung LSB (Druck zwischen der Drossel B und dem Niederdruckanschluß) der Tankdruck, so daß das Rücklaufkompensationsventil 15 gegen die Kraft der Rückstellfeder 17 in eine stärker gedrosselte Stellung versetzt wird. Der Durchfluß durch die Steuerung 1, d.h. die Steuerung des Motors 10, erfolgt also nach wie vor über das Proportionalventil 2. Allerdings wird die dem Proportionalventil 2 zur Verfügung gestellte Flüssigkeitsmenge ausschließlich über das Rückflußkompensationsventil 15 bestimmt und nicht mehr durch das Kompensationsventil 4 auf der Eingangsseite des Proportionalventils 2.The vehicle driven in this way can now be put into a situation get where the motor 10 does not drive, but driven becomes. This can be the case, for example, when the vehicle rolls down a slope or out of a certain speed is slowed down. In this In the event the engine delivers more hydraulic fluid into the Working line 9 when he made the way through the working line 8 the high pressure port P receives. Accordingly decreases the pressure at point 18. The return compensation valve 14 therefore remains fully open. At point 19 rises the pressure on the other hand, because the hydraulic fluid draining off through throttle B must occur, which at a a larger amount of liquid causes greater pressure drop. At the same time Pressure in the load sensing line LSB (pressure between the Throttle B and the low pressure connection) the tank pressure, so that the return compensation valve 15 against the Force the return spring 17 into a more throttled Position is moved. The flow through the controller 1, i.e. the control of the motor 10 takes place still via the proportional valve 2. However the proportional valve 2 is made available Liquid quantity only via the reflux compensation valve 15 determined and no more through the compensation valve 4 on the input side of the proportional valve 2.

Dies soll anhand der Durchflußkennlinien erläutert werden, die in Fig. 2 dargestellt sind. Nach oben ist hierbei der Durchfluß F aufgetragen und nach rechts eine Auslenkung X des Schiebers des Proportionalventils 2. Mit anderen Worten entspricht die Größe X auch dem Gegendruck, den die Rücklaufkompensationsventile 14, 15 bzw. das Kompensationsventil 4 an den Punkten 18, 19 bzw. 4 "sehen".This should be explained using the flow characteristics, which are shown in Fig. 2. Is up here the flow F is plotted and a to the right Deflection X of the slide of the proportional valve 2. In other words, the size X also corresponds to that Back pressure that the return compensation valves 14, 15th or the compensation valve 4 at points 18, 19 or 4 "see".

Eine Kennlinie 28 gibt das Verhalten des Kompensationsventils 4 wieder, d.h. die Flüssigkeitsmenge in Abhängigkeit von der Stellung des Proportionalventils 2 für den Fall, daß das Fahrzeug über den Motor 10 angetrieben ist. Die Durchflußkennlinie 28 ist also die Durchflußkennlinie des Kompensationsventils 4.A characteristic curve 28 gives the behavior of the compensation valve 4 again, i.e. the amount of liquid depending from the position of the proportional valve 2 for the case that the vehicle is driven by the engine 10 is. The flow characteristic 28 is thus the flow characteristic of the compensation valve 4.

Eine Durchflußkennlinie 29 ist hingegen die Durchflußkennlinie der Rückflußkompensationsventile 14, 15. Diese ist für beide Rückflußkompensationsventile 14, 15 gleich. Sie gibt den Durchfluß in Abhängigkeit von der Stellung des Proportionalventils 2 für den Fall wieder, daß das Fahrzeug den Motor 10 antreibt.A flow characteristic 29, however, is the flow characteristic the backflow compensation valves 14, 15. This is for both reflux compensation valves 14, 15 equal. It gives the flow depending on the Position of the proportional valve 2 for the case again, that the vehicle drives the engine 10.

Es ist klar zu erkennen, daß die beiden Durchflußkennlinien 28, 29 nicht deckungsgleich sind und sich auch nicht kreuzen. Sie sind vielmehr parallel zueinander geführt. Dadurch wird sichergestellt, daß die Flüssigkeitssteuerung durch die Steuerung 1 entweder durch das Kompensationsventil 4 erfolgt und zwar bei positiven Lasten, oder ausschließlich durch eines der beiden Rückflußkompensationsventile 14, 15 bei negativen Lasten.It can be clearly seen that the two flow characteristics 28, 29 are not congruent and also do not cross. Rather, they are parallel to each other guided. This ensures that fluid control through controller 1 either through that Compensation valve 4 takes place and that with positive Loads, or only by one of the two Backflow compensation valves 14, 15 with negative loads.

Wenn eine negative Last auftritt, dann wird das Sperrventil 26 geschlossen. In diesem Fall kann die Nachsaugventilanordnung 20 Flüssigkeit zwar nicht mehr vom Niederdruckanschluß T nachsaugen. Sie kann aber die benötigte Flüssigkeit über die Leitung 23 vom niederdruckseitigen Ende der Drossel B über das Ventil 21 in die Arbeitsleitung 8 nachsaugen, so daß hier keine Kavitationserscheinungen entstehen. Da die Hydraulikflüssigkeit über eine kürzere Strecke im Kreis geführt werden kann, ergibt sich hier bei negativen Lasten eine kleine Energieersparnis. Vor allem wird aber eine effektive Nachfüllung erzielt.If a negative load occurs, then the check valve 26 closed. In this case, the suction valve arrangement 20 Liquid no longer from Refill low pressure connection T. But it can do the required Liquid via line 23 from the low pressure side End of throttle B via valve 21 in suck up the working line 8 so that there are no cavitation phenomena here arise. Because the hydraulic fluid be guided in a circle over a shorter distance can result in a negative load small energy savings. Above all, it will be effective Refill achieved.

Durch die unterschiedlichen Durchflußkennlinien 28, 29 sorgt man also dafür, daß der Durchfluß bei einer gegebenen Schieberauslenkung des Proportionalventils 2 unterschiedlich ist in Abhängigkeit davon, ob es sich um eine positive oder um eine negative Last handelt. Damit wird sichergestellt, daß das Kompensationsventil 4 einerseits und die Rückflußkompensationsventile 14, 15 nicht darum "kämpfen", wer zuständig ist. Es ist vielmehr klar geregelt, daß bei einer positiven Last ausschließlich das Kompensationsventil 4 und bei einer negativen Last ausschließlich eines der beiden Rückflußkompensationsventile 14, 15 zuständig ist. Im einfachsten Fall läßt sich dies durch unterschiedliche Vorspannungen der Rückstellfedern 5 einerseits und 16, 17 andererseits erreichen. Beispielsweise kann die Feder 5 so vorgespannt sein, daß sie einem Druck von 7 bar entspricht, während die Federn 16, 17 so vorgespannt sind, daß sie einem Druck von 8 bar entsprechen.Due to the different flow characteristics 28, 29 So you make sure that the flow at a given Slider deflection of the proportional valve 2 different depends on whether it is a positive or a negative burden. In order to it is ensured that the compensation valve 4 on the one hand and the backflow compensation valves 14, 15 not "fighting" over who is responsible. It is much more clearly regulated that with a positive load only the compensation valve 4 and a negative Load only one of the two backflow compensation valves 14, 15 is responsible. In the simplest This can be done by different preloads the return springs 5 on the one hand and 16, 17 on the other hand, achieve. For example, the spring 5 be biased so that it corresponds to a pressure of 7 bar, while the springs 16, 17 are biased so that they correspond to a pressure of 8 bar.

Die beiden Rückflußkompensationsventile 14, 15 können in einer Baueinheit 30 zusammengefaßt sein. Die Baueinheit 30 kann beispielsweise direkt am zugehörigen Proportionalventil 2 angebracht werden. Die Baueinheit 30 nimmt wenig Bauraum in Anspruch. Man kann sie aber auch unmittelbar am Motor 10 anordnen.The two reflux compensation valves 14, 15 can be combined in one unit 30. The unit 30 can, for example, directly on the associated proportional valve 2 are attached. The assembly 30 takes up little space. But you can also do it arrange directly on the motor 10.

Durch die Nachfüllventilanordnung 20 läßt sich sozusagen der Bereich zwischen den beiden Durchflußkennlinien 28, 29 ausfüllen. Man sorgt also dafür, daß in der Steuerung 1 keine Kavitation entsteht.The refill valve arrangement 20 can, so to speak the area between the two flow characteristics Fill in 28, 29. So you make sure that in the Control 1 no cavitation occurs.

Fig. 3 zeigt eine Ausführungsform einer Steuerung, bei der gleiche und einander entsprechende Teile mit den gleichen Bezugszeichen versehen sind.Fig. 3 shows an embodiment of a controller, at the same and corresponding parts with the are provided with the same reference numerals.

Die Steuerung der Fig. 3 enthält ein Eingangsmodul 31, das mit einer Reihe von an sich bekannten und daher nicht näher beschriebenen Ventilen, wie Druckhalte- und Überdruckventilen, versehen ist. Über dieses Eingangsmodul 31 ist das Proportionalventil 2 mit dem Hochdruckanschluß P verbunden, wobei in dieser Verbindung das Kompensationsventil 4 angeordnet ist.3 contains an input module 31, that with a number of known and therefore valves not described in detail, such as pressure maintenance and Pressure relief valves is provided. About this input module 31 is the proportional valve 2 with the high pressure connection P connected, in this connection the compensation valve 4 is arranged.

Das Proportionalventil 2 weist drei Arbeitsstellungen a, b, c auf. In der dargestellten Stellung b befindet sich das Proportionalventil 2 in Neutralstellung. In diesem Fall ist die Lastfühlleitung LS mit dem Druck am Niederdruckanschluß T beaufschlagt. Dementsprechend würden die Bremsen 11 betätigt sein und das Fahrzeug wäre gebremst.The proportional valve 2 has three working positions a, b, c on. In the position b shown the proportional valve 2 is in the neutral position. In In this case, the load sensing line LS with the pressure on Low pressure connection T is applied. Accordingly the brakes 11 would be applied and the vehicle would be slowed down.

Wenn der Schieber des Proportionalventils 2 in die Stellung a verschoben wird, dann wird der Hochdruckanschluß P mit der Arbeitsleitung 9 und der Niederdruckanschluß T mit der Arbeitsleitung 8 verbunden. Gleichzeitig wird die Lastfühlleitung LSB mit dem Druck am Punkt 9 beaufschlagt und die Lastfühlleitung LSA mit dem Druck am Niederdruckanschluß T. Wenn in diesem Fall der Motor antreibend wirkt, dann gelangt in der Stellung a des Proportionalventils 2 Hydraulikflüssigkeit unter Druck von einer Pumpe 32 über den Hochdruckanschluß P, das Kompensationsventil 4, das Proportionalventil 2, die Arbeitsleitung 9 und das Rücklaufkompensationsventil 15 zum Motor 10. Das Kompensationsventil 4 wird hierbei entlang der Durchflußkennlinie 28 (Fig. 2) gesteuert und zwar in Abhängigkeit davon, wie weit die Drosseln des Proportionalventils 2 geöffnet werden. Der Druck am Punkt 9 gelangt auch zur Lastfühlleitung LSB, während die Lastfühlleitung LSA mit dem Druck am Niederdruckanschluß T versehen ist. Dementsprechend wird das Rücklaufkompensationsventil 15 unter der Wirkung des Drucks in der Lastfühlleitung LSB und der Rückstellfeder 17 gegen den Druck am Punkt 19 geöffnet. Im Endeffekt wirkt "netto" lediglich die Kraft der Rückstellfeder 17. Das Rücklaufkompensationsventil 14 wird vollständig geöffnet, weil der Druck am Punkt 18 im wesentlichen dem Tankdruck entspricht und somit praktisch keine Kraft in Schließrichtung aufgebracht wird.If the slide of the proportional valve 2 in the Position a is moved, then the high pressure connection P with the working line 9 and the low pressure connection T connected to the working line 8. At the same time, the load sensing line LSB with the pressure acted on at point 9 and the load sensing line LSA the pressure at the low pressure connection T. If in this case the motor is driving, then comes into position a of the proportional valve 2 hydraulic fluid under pressure from a pump 32 via the high pressure connection P, the compensation valve 4, the proportional valve 2, the working line 9 and the return compensation valve 15 to the engine 10. The compensation valve 4 is along the flow characteristic curve 28 (Fig. 2) controlled, depending on how wide open the throttles of the proportional valve 2 become. The pressure at point 9 also reaches the load sensing line LSB, while the load sensing line LSA with the Pressure at the low pressure port T is provided. Accordingly the return compensation valve 15 under the effect of the pressure in the load sensing line LSB and the return spring 17 opened against the pressure at point 19. In the end, only "net" works the return spring 17. The return compensation valve 14 opens completely because of pressure at the point 18 corresponds essentially to the tank pressure and thus practically no force applied in the closing direction becomes.

Wenn nun der Motor 10 einer negativen Last ausgesetzt wird, beispielsweise wenn das Fahrzeug aus einer gewissen Geschwindigkeit abgebremst werden soll und das Fahrzeug somit den Motor 10 antreibt, dann wird mehr Hydraulikflüssigkeit durch den Motor 10 ausgegeben als durch das Proportionalventil 2 geliefert werden kann. Dementsprechend steigt der Druck am Punkt 18 an und das Rückflußkompensationsventil 14 steuert den Durchfluß entsprechend der Durchflußkennlinie 29 (Fig. 2). Da der Druck am Punkt 7 sinkt - die Hydraulikflüssigkeit wird durch den Motor 10 sozusagen abgesaugt - öffnet das Kompensationsventil 4 vollständig, so daß die dem Proportionalventil 2 zur Verfügung gestellte Flüssigkeit ausschließlich durch das Rückflußkompensationsventil 14 bestimmt wird. Das Kompensationsventil leistet die Menge, die es immer geleistet hat. Da aber das Rückflußkompensationsventil 14 jetzt bestimmend ist, wird etwas Öl fehlen und dieses Öl wird nachgefüllt.If now the motor 10 is exposed to a negative load is, for example, if the vehicle from a certain Speed should be slowed down and that Vehicle thus drives the engine 10, then more Hydraulic fluid output by the engine 10 as can be supplied by the proportional valve 2. Accordingly, the pressure at point 18 rises and that Backflow compensation valve 14 controls the flow corresponding to the flow characteristic curve 29 (Fig. 2). Since the Pressure at point 7 drops - the hydraulic fluid becomes aspirated by the motor 10 so to speak - opens that Compensation valve 4 completely, so that the proportional valve 2 provided liquid only through the backflow compensation valve 14 is determined. The compensation valve does the amount that has always done it. But since the backflow compensation valve 14 is now determining something Oil is missing and this oil is refilled.

Das Sperrventil 26 ist vom Druck am Niederdruckanschluß T einerseits und andererseits vom höheren der beiden Drücke in den Lastfühlleitungen LSA, LSB beaufschlagt. The check valve 26 is of the pressure at the low pressure connection T on the one hand and on the other hand from the higher of the two Pressures applied in the load sensing lines LSA, LSB.

Der Druck in der Lastfühlleitung LSA ist, wie oben ausgeführt, praktisch 0, d.h. er entspricht dem Druck am Niederdruckanschluß T. Auch der Druck in der Lastfühlleitung LSB sinkt ab, so daß das Sperrventil 26 bei Auftreten einer negativen Last automatisch in die in Fig. 3 dargestellte geschlossene Position bewegt wird. Das Nachsaugen über das Rückschlagventil 22 erfolgt also mit Hydraulikflüssigkeit, die man unmittelbar aus dem Niederdruckanschluß des Proportionalventils 2 gewinnt. Das Sperrventil ist hierbei durch eine Rückstellfeder 34 belastet, die bei entsprechend niedrigen Drücken am Niederdruckanschluß T und in den Lastfühlleitungen LSA, LSB das Sperrventil 26 in die dargestellte Position verschiebt.The pressure in the load sensing line LSA, as stated above, practically 0, i.e. it corresponds to the pressure on Low pressure connection T. Also the pressure in the load sensing line LSB drops, so that the check valve 26 at A negative load automatically occurs in the Fig. 3 shown closed position is moved. The suction via the check valve 22 is therefore carried out with hydraulic fluid, which one immediately comes from the low pressure connection of the proportional valve 2 wins. The check valve is here by a return spring 34 charged, the correspondingly low Press on the low pressure connection T and in the load sensing lines LSA, LSB the check valve 26 in the illustrated Position shifts.

Wie oben erwähnt, kann man die unterschiedlichen Durchflußkennlinien 28, 29 dadurch realisieren, daß man die Rückflußkompensationsventile 14, 15 mit stärkeren Rückstellfedern 16, 17 ausrüstet als das Kompensationsventil 4, das eine dementsprechend schwächere Rückstellfeder 5 aufweist. Man kann aber auch dafür sorgen, daß die Drosseln im Proportionalventil 2, die vom Hochdruckanschluß P zum Motor 10 leiten, einen größeren Strömungswiderstand aufweisen als die Drosseln, die Hydraulikflüssigkeit vom Motor 10 zum Niederdruckanschluß P leiten.As mentioned above, you can see the different flow characteristics 28, 29 by realizing that Backflow compensation valves 14, 15 with stronger return springs 16, 17 equips as the compensation valve 4, which is a correspondingly weaker return spring 5 has. But you can also make sure that the throttles in the proportional valve 2 from the high pressure connection Route P to motor 10, a larger one Exhibit flow resistance than the throttles that Hydraulic fluid from the engine 10 to the low pressure connection P lead.

Claims (10)

Hydraulische Steuerung mit einem hydraulischen Motor, der über zwei Arbeitsleitungen mit einem Steuerventil verbunden ist, das mit einem Niederdruckanschluß und über ein Kompensationsventil mit einem Hochdruckanschluß verbunden ist, dadurch gekennzeichnet, daß in jeder Arbeitsleitung ein Rückflußkompensationsventil (14, 15) angeordnet ist, wobei die Rückflußkompensationsventile (14, 15) jeweils eine Durchflußkennlinie (29) aufweisen, die kreuzungsfrei zur Durchflußkennlinie (28) des Kompensationsventils (4) verläuft.Hydraulic control with a hydraulic motor which is connected via two working lines to a control valve which is connected to a low pressure connection and via a compensation valve to a high pressure connection, characterized in that a return flow compensation valve (14, 15) is arranged in each working line, the Backflow compensation valves (14, 15) each have a flow characteristic (29) which runs without crossing to the flow characteristic (28) of the compensation valve (4). Steuerung nach Anspruch 1, dadurch gekennzeichnet, daß die Durchflußkennlinien (29) der beiden Rückflußkompensationsventile (14, 15) gleich sind.Control according to claim 1, characterized in that the flow characteristics (29) of the two reflux compensation valves (14, 15) are the same. Steuerung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Durchflußkennlinien (28, 29) der Rückflußkompensationsventile (14, 15) und des Kompensationsventils (4) parallel zueinander verlaufen.Control according to claim 1 or 2, characterized in that the flow characteristics (28, 29) of the reflux compensation valves (14, 15) and the compensation valve (4) run parallel to one another. Steuerung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Rückflußkompensationsventile (14, 15) bei ansonsten gleichen Bedingungen einen größeren Durchfluß als das Kompensationsventil (4) aufweisen. Control according to one of claims 1 to 3, characterized in that the backflow compensation valves (14, 15) have a greater flow than the compensation valve (4) under otherwise identical conditions. Steuerung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß zwischen dem Motor (10) und den Rückflußkompensationsventilen (14, 15) eine Nachsaugventilanordnung (20) mündet.Control according to one of claims 1 to 4, characterized in that a suction valve arrangement (20) opens between the motor (10) and the reflux compensation valves (14, 15). Steuerung nach Anspruch 5, dadurch gekennzeichnet, daß die Nachsaugventilanordnung (20, 25, 26) ein schaltbares Sperrventil (26) aufweist.Control according to claim 5, characterized in that the suction valve arrangement (20, 25, 26) has a switchable shut-off valve (26). Steuerung nach Anspruch 6, dadurch gekennzeichnet, daß das schaltbare Sperrventil (26) bei negativen Lasten automatisch schließt.Control according to claim 6, characterized in that the switchable shut-off valve (26) closes automatically in the event of negative loads. Steuerung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß das Kompensationsventil (4) eine geringere Federvorspannung als die Rückflußkompensationsventile (14, 15) aufweist.Control according to one of claims 1 to 7, characterized in that the compensation valve (4) has a lower spring preload than the backflow compensation valves (14, 15). Steuerung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß das Steuerventil (2) in Strömungsrichtung vom Hochdruckanschluß (P) zum Motor (10) einen größeren Strömungswiderstand als in Strömungsrichtung vom Motor (10) zum Niederdruckanschluß (T) aufweist.Control according to one of claims 1 to 8, characterized in that the control valve (2) has a greater flow resistance in the flow direction from the high-pressure connection (P) to the motor (10) than in the flow direction from the motor (10) to the low-pressure connection (T). Steuerung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die Rückflußkompensationsventile (14, 15) mit je einem Lastfühlanschluß (LSA, LSB), der in Öffnungsrichtung wirkt, und mit einem Steueranschluß versehen sind, der in Schließrichtung wirkt und mit einem Abschnitt der Arbeitsleitung (8, 9) verbunden ist, der zum Steuerventil (2) führt, und das Rückflußkompensationsventil (14, 15) in der Arbeitsleitung (8, 9), durch die Hydraulikflüssigkeit zum Motor (10) strömt, durch den Lastfühlanschluß (LSA, LSB) mit dem gleichen Druck beaufschlagt wird, der in der Arbeitsleitung (8, 9) herrscht.Control according to one of claims 1 to 9, characterized in that the backflow compensation valves (14, 15) are each provided with a load-sensing connection (LSA, LSB) which acts in the opening direction and with a control connection which acts in the closing direction and with a section the working line (8, 9), which leads to the control valve (2), and the backflow compensation valve (14, 15) in the working line (8, 9), through which hydraulic fluid flows to the motor (10), through the load sensing connection (LSA , LSB) is subjected to the same pressure that prevails in the working line (8, 9).
EP03075981A 2002-04-17 2003-04-03 Hydraulic control Expired - Lifetime EP1355065B1 (en)

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US20030196545A1 (en) 2003-10-23
DE10216958B8 (en) 2004-07-08
DE10216958B3 (en) 2004-01-08
US6865886B2 (en) 2005-03-15
EP1355065B1 (en) 2006-05-24
ATE327440T1 (en) 2006-06-15
DE50303427D1 (en) 2006-06-29

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