EP1355065B1 - Commande hydraulique - Google Patents

Commande hydraulique Download PDF

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Publication number
EP1355065B1
EP1355065B1 EP03075981A EP03075981A EP1355065B1 EP 1355065 B1 EP1355065 B1 EP 1355065B1 EP 03075981 A EP03075981 A EP 03075981A EP 03075981 A EP03075981 A EP 03075981A EP 1355065 B1 EP1355065 B1 EP 1355065B1
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EP
European Patent Office
Prior art keywords
valve
pressure
compensation
return
control device
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.)
Expired - Lifetime
Application number
EP03075981A
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German (de)
English (en)
Other versions
EP1355065A1 (fr
Inventor
Knud Meldgaard Jensen
Carl Christian Dixen
Henrik Kjer Kristiansen
Hans Jorgen Jensen
Jan Maiboll Buhl
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Danfoss Power Solutions ApS
Original Assignee
Sauer Danfoss ApS
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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 with a hydraulic motor, which is connected via two working lines with a control valve which is connected to a low pressure port and a compensation valve to a high pressure port.
  • the control valve releases flow paths depending on the desired actuating direction of the engine, on the one hand from the high-pressure connection to a working line and on the other hand from the other working line to the low-pressure connection. However, this release is throttled more or less, wherein the height of the throttle resistance is dependent on the actuating stroke (or a correspondingly different actuating movement) of the control valve.
  • the compensation valve serves as a pressure control valve. It is sometimes referred to as a pressure balance. It ensures that over the slide of the control valve almost always the same pressure drops.
  • the compensation valve is expediently formed by a slide which is removed on one side by a return spring and the load pressure and on the other side by the pressure in a line section between the compensation valve and the control valve. Of course, such a compensation valve can also be designed in other ways.
  • Such controllers usually work reliably. Problems occur when the engine is working with so-called negative loads. Such negative loads may occur, for example, when the engine is operated by an external weight, such as a load hanging from a crane hook. Another example is the dead weight of a vehicle, which rolls on an inclined plane or must be braked from a certain speed. In this case, the hydraulic system of the controller may tend to oscillate.
  • a return compensation valve in a working line between the engine and the control valve, which may also be designed as a pressure control valve or pressure compensator.
  • the return compensation valve ensures that only when the engine further hydraulic fluid is supplied under pressure, the engine can also be operated.
  • GB 2 044 366 A describes a hydraulic control with a hydraulic motor, which is connected via two working lines with a control valve.
  • the control valve is connected to a low pressure port and to a high pressure port.
  • each spring-loaded check valves which serve as load holding valves.
  • From each working line branches off an exhaust valve, which connect the engine at a correspondingly high pressure in the appropriate connection to the tank.
  • DE 198 02 430 A1 shows a hydraulic system for operating a reversible hydraulic consumer.
  • the consumer is connected via a control valve to a high pressure port and a low pressure port.
  • the control valve is designed as a conventional directional control valve whose spool is divided in the middle, so that two spools are formed, each with only one control section for one of the two pressure medium connections of the hydraulic consumer.
  • the invention has for its object to be able to ensure a stable operation with negative loads in both directions.
  • the flow characteristic here is the ratio of flow rate to pressure, which can be considered for the pressure either the pressure difference across the compensation valve or the rinseflußkompensationsventil or the pressure at the outlet of the compensation valve and the rinseflußkompensationsventils. If the flowcharts do not overlap or intersect, then there is no point where a critical situation can arise. It is always clear which of the compensation valves is ultimately responsible for controlling the hydraulic fluid.
  • the flow characteristics of the vomflußkompensationsventile and the compensation valve are parallel to each other. This gives you an almost identical control behavior when controlling positive and negative loads, which differs only by an offset. The control then becomes easier for an operator. The operation becomes easier the smaller the offset between the two curves. In an alternative, it is also conceivable that the curves start at the same point and diverge at a small angle.
  • the remindflußkompensationsventile in otherwise the same conditions on a larger flow than the compensation valve.
  • the scrubflußkompensationsventil takes over control and the compensation valve has no influence on the control of the amount of liquid. Since more fluid can flow out through the backflow compensation valve, it prevents the hydraulic system of the controller from being "inflated".
  • a suction valve arrangement opens between the engine and the scrubflußkompensationsventilen.
  • the backflow compensation valve which is responsible for a negative load in one direction, allows more fluid to flow out than may flow through the compensation valve. This cavitation phenomena could occur, which are prevented by the Nachsaugventilan Aunt.
  • the Nachsaugventilan Aunt allows that a sufficient amount of hydraulic fluid can be fed back into the circuit.
  • the Nachsaugventilan himself a switchable check valve.
  • the check valve When the check valve is closed, a connection of the low pressure line to the tank is interrupted, i. it is no longer possible to withdraw the hydraulic fluid from the tank. Since, however, enough negative fluid loads on the output side of the engine is discharged and this liquid in and of itself should pass through the low pressure port to the tank, this liquid can be circulated within the control so to speak. This results in a partially considerable energy saving. If one imagines that the flow characteristics of the compensation valve on the one hand and the scrubflußkompensationsventile run parallel on the other hand, then it is possible with the help of Nachsaugventilan Aunt to refill the area between the two flow characteristics.
  • the switchable check valve closes automatically with negative loads. So you are not more reliant to make a certain action to save energy, namely to close the check valve.
  • the check valve is automatically closed when the return compensation valves are put into operation. The closing does not have to lead to a complete blockage of the liquid flow.
  • the compensation valve has a lower spring tension than the remindflußkompensationsventile. This is a relatively simple way to provide the flow characteristics of the compensation valve on the one hand and the remindflußkompensationsventile other hand, with different flow characteristics.
  • the compensation valve is moved to the closed position at a lower pressure than the remindflußkompensationsventile.
  • control valve in the flow direction from the high pressure port to the engine has a greater flow resistance than in the flow direction from the engine to the low pressure port.
  • the rinseflußkompensationsventile each with a load-sensing connection, which acts in the opening direction, and with a Control terminal are provided, which acts in the closing direction and is connected to a portion of the working line leading to the control valve, and the remindflußkompensationsventil in the working line, flows through the hydraulic fluid to the motor, is acted upon by the load sensing port with the same pressure in the working line prevails.
  • a control 1 has a proportional valve 2 as a control valve, which is shown only schematically in Fig. 1.
  • the proportional valve 2 has two adjustable throttles A, B, which by an actuating handle 3 also shown only schematically can be adjusted.
  • the proportional valve 2 is connected to a high-pressure port P and to a low-pressure port T.
  • a compensation valve 4 is arranged, which has a return spring 5, which biases the compensation valve 4 in the opening direction.
  • the compensation valve 4 for example, have a slider which is loaded by the return spring 5 in the opening direction. In the closing direction of the slide via a line 6 with a pressure at a point 7 between the compensation valve 4 and the throttle A can be acted upon.
  • the compensation valve 4 can also be referred to as a pressure control valve or pressure compensator.
  • the proportional valve 2 is connected via working lines 8, 9 with a motor 10.
  • the engine 10 consists of two sub-drives, each of which can act on the wheels of a vehicle.
  • the engine 10 is provided with a brake 11 which can be released via a control line 12.
  • the pressure prevails behind the throttle A. Since the proportional valve 2 can conduct the pressure from the high pressure port P via the throttle B to the engine 10 in a manner not shown, a shuttle valve 13 is provided, which is the respective higher pressure behind the throttles A, B used to release the brake 11.
  • the compensation valve 4 is additionally acted upon by a load-sensing pressure LS in the opening direction, i. the load-sensing pressure LS acts in the same direction as the restoring spring 5.
  • the return spring 5 generates a force which, for example, corresponds to a pressure of 7 bar.
  • a Nachsaugventilan extract 20 with a Nachsaugventil 21 for the working line 8 and a Nachsaugventil 22 for the working line 9 is connected via a Nachsaug réelle 23 to the low pressure port T.
  • a check valve 24 which is biased by a spring 25
  • the check valve 26 has a magnetic drive 27 which can switch it from the illustrated open position to a closed position. In the closed position of the check valve 26 is a Nachsaugen from the low pressure port T is not possible.
  • the controller 1 operates as follows:
  • the pressure at point 7 decreases and the compensation valve 4 opens, so that hydraulic fluid can flow through the return compensation valve 14 to the engine 10.
  • the return compensation valve 14 is in the one direction of the pressure at the point 18, ie, the pressure in the working line 8, applied.
  • the return compensation valve 14 is acted upon by the pressure at the load-sensing connection LSA, which corresponds to the pressure downstream of the throttle A (ie also the pressure in the working line 8), so that the return compensation valve 14 is fully opened.
  • the return compensation valve 15 fully open. This is acted upon in the closing direction by the pressure at point 19, ie by the pressure in the working line 9.
  • the return compensation valve 15 In the opening direction acts on the return compensation valve 15, the force of the return spring 17 and the pressure in the load-sensing connection LSB, which is at least as large as the pressure at point 19.
  • the hydraulic fluid thus passes more or less freely through the remindflußkompensationsventil 15 and through the throttle B to the low-pressure connection T, wherein it can flow through the check valve 26 which is open. If the check valve 26 is closed, the hydraulic fluid can pass through the check valve 24 when it can overcome the force of the spring 25. This force corresponds for example to a pressure of 5 bar.
  • the thus driven vehicle can now enter a situation where the engine 10 is not driven, but is driven. This may be the case, for example, when the vehicle rolls down a gradient or is slowed down from a certain speed.
  • the engine promotes more hydraulic fluid in the working line 9, as he receives through the working line 8 from the high pressure port P. Accordingly, the pressure drops at point 18.
  • the return compensation valve 14 thus remains fully open. At point 19, however, the pressure increases because the hydraulic fluid flowing out must pass through the throttle B, which causes a correspondingly larger pressure drop at a larger amount of liquid.
  • the 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 is displaced against the force of the return spring 17 in a more throttled position.
  • the proportional valve 2 made available amount of liquid is determined exclusively via the remindflußkompensationsventil 15 and no longer through the compensation valve 4 on the input side of the proportional valve 2.
  • a characteristic 28 represents the behavior of the compensation valve 4, i. the amount of liquid in dependence on the position of the proportional valve 2 in the event that the vehicle is driven by the motor 10.
  • the flow characteristic 28 is thus the flow characteristic of the compensation valve. 4
  • a flow characteristic 29, however, is the flow characteristic of the rinseflußkompensationsventile 14, 15. This is the same for both rinseflußkompensationsventile 14, 15. It gives the flow depending on the Position of the proportional valve 2 in the event that the vehicle drives the motor 10 again.
  • the two vomflußkompensationsventile 14, 15 may be summarized in a unit 30.
  • the assembly 30 may for example be attached directly to the associated proportional valve 2.
  • the assembly 30 takes up little space to complete. But you can also arrange them directly on the engine 10.
  • Fig. 3 shows an embodiment of a controller in which the same and corresponding parts are provided with the same reference numerals.
  • the controller of Fig. 3 includes an input module 31, which with a number of known and therefore unspecified described valves, such as pressure maintenance and Overpressure valves, is provided. About this input module 31, the proportional valve 2 is connected to the high-pressure port P, in which connection the compensation valve 4 is arranged.
  • the proportional valve 2 has three working positions a, b, c. In the illustrated position b, the proportional valve 2 is in neutral position. In this case, the load sensing line LS is acted upon by the pressure at the low pressure port T. Accordingly, the brakes 11 would be actuated and the vehicle would be braked.
  • the motor acts driving, then passes in the position a of the proportional valve 2 hydraulic fluid under pressure from a pump 32 via the High-pressure port 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 hereby controlled along the flow characteristic 28 (FIG. 2), depending on how far the throttles of the proportional valve 2 be opened.
  • the pressure at point 9 also reaches the load-sensing line LSB, while the load-sensing line LSA is provided with the pressure at the low-pressure connection T. Accordingly the return compensation valve 15 is opened under the action of the pressure in the load sensing line LSB and the return spring 17 against the pressure at the point 19. The net effect is only the force of the return spring 17.
  • the return compensation valve 14 is fully opened because the pressure at point 18 substantially corresponds to the tank pressure and thus virtually no force is applied in the closing direction.
  • the check valve 26 is acted upon by the pressure at the low pressure port T on the one hand and on the other hand by the higher of the two pressures in the load sensing lines LSA, LSB.
  • the pressure in the load sensing line LSA is practically zero, as stated above. it also corresponds to the pressure at the low-pressure connection T.
  • the pressure in the load-sensing line LSB also drops, so that the check valve 26 is automatically moved to the closed position shown in FIG. 3 when a negative load occurs.
  • the sucking on the check valve 22 is thus carried out with hydraulic fluid, which wins directly from the low pressure port of the proportional valve 2.
  • the check valve is in this case loaded by a return spring 34, which shifts the check valve 26 in the illustrated position at correspondingly low pressures at the low pressure port T and in the load sensing lines LSA, LSB.

Claims (10)

  1. Commande hydraulique (1) comportant un moteur hydraulique (10) qui est-relié à une valve de commande (2) via deux conduits de travail (8, 9), ladite valve étant reliée à un raccord basse pression (T) et via une valve de compensation (4) à un raccord haute pression (P), caractérisée en ce que dans chaque conduit de travail est agencée une valve de compensation de reflux (14, 15), les valves de compensation de reflux (14, 15) présentant chacune une courbe caractéristique de débit (29) qui s'étend sans croisement avec la courbe caractéristique de débit (28) de la valve de compensation (4).
  2. Commande selon la revendication 1, caractérisée en ce que les courbes caractéristiques de débit (29) des deux valves de compensation de reflux (14, 15) sont identiques.
  3. Commande selon la revendication 1 ou 2, caractérisée en ce que les courbes caractéristiques de débit (28, 29) des valves de compensation de reflux (14, 15) et de la valve de compensation (4) s'étendent parallèlement l'une à l'autre.
  4. Commande selon l'une des revendications 1 à 3, caractérisée en ce que les valves de compensation de reflux (14, 15) présentent un débit supérieur à celui de la valve de compensation (4), pour des conditions par ailleurs identiques.
  5. Commande selon l'une des revendications 1 à 4, caractérisée en ce qu'un agencement de valve de re-aspiration (20) débouche entre le moteur (10) et les valves de compensation de reflux (14, 15).
  6. Commande selon la revendication 5, caractérisée en ce que l'agencement de valve de re-aspiration (20, 25, 26) comprend un clapet d'arrêt commutable (26).
  7. Commande selon la revendication 6, caractérisée en ce que le clapet d'arrêt commutable (26) se ferme automatiquement en cas de charges négatives.
  8. Commande selon l'une des revendications 1 à 7, caractérisée en ce que la valve de compensation (4) présente une précontrainte élastique inférieure à celle des valves de compensation de reflux (14, 15).
  9. Commande selon l'une des revendications 1 à 8, caractérisée en ce que dans la direction d'écoulement depuis le raccord haute pression (P) vers le moteur (10), la valve de commande (2) présente une résistance à l'écoulement supérieure à celle dans la direction d'écoulement depuis le moteur (10) vers le raccord basse pression (T).
  10. Commande selon l'une des revendications 1 à 9, caractérisée en ce que les valves de compensation de reflux (14, 15) sont pourvues chacune d'un raccord capteur de charge (LSA, LSB) qui agit dans la direction d'ouverture, ainsi que d'un raccord de commande qui agit dans la direction de fermeture et qui est relié à un tronçon du conduit de travail (8, 9), qui mène vers la valve de commande (2), et en ce que la valve de compensation de reflux (14, 15) dans le conduit de travail (8, 9) à travers lequel s'écoule le fluide hydraulique vers le moteur (10) est alimentée par le raccord capteur de charge (LSA, LSB) avec la même pression que celle régnant dans le conduit de travail (8, 9).
EP03075981A 2002-04-17 2003-04-03 Commande hydraulique Expired - Lifetime EP1355065B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10216958 2002-04-17
DE10216958A DE10216958B8 (de) 2002-04-17 2002-04-17 Hydraulische Steuerung

Publications (2)

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EP1355065A1 EP1355065A1 (fr) 2003-10-22
EP1355065B1 true EP1355065B1 (fr) 2006-05-24

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US (1) US6865886B2 (fr)
EP (1) EP1355065B1 (fr)
AT (1) ATE327440T1 (fr)
DE (2) DE10216958B8 (fr)

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Also Published As

Publication number Publication date
US20030196545A1 (en) 2003-10-23
DE10216958B8 (de) 2004-07-08
ATE327440T1 (de) 2006-06-15
EP1355065A1 (fr) 2003-10-22
DE50303427D1 (de) 2006-06-29
US6865886B2 (en) 2005-03-15
DE10216958B3 (de) 2004-01-08

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