EP1355065A1 - Hydraulische Steuerung - Google Patents
Hydraulische Steuerung Download PDFInfo
- 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
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- EP
- European Patent Office
- Prior art keywords
- valve
- compensation
- pressure
- flow
- control
- Prior art date
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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
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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
- F15B11/042—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"
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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
- 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
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- 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
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- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- 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
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- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- 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
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- 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
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- 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
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- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- F15B2211/35—Directional control combined with flow control
- F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
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- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- F15B2211/405—Flow control characterised by the type of flow control means or valve
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- 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
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- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
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- 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
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- 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
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
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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
- 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
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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
- 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
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- 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
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- 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
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- F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure valve
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- 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
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- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
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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
- 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
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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
- F15B2211/00—Circuits for servomotor systems
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- 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
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- 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
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- 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
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- 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
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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
- 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.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- Fig. 1
- eine schematische Darstellung einer hydraulischen Steuerung,
- Fig. 2
- eine schematische Darstellung von Kennlinien und
- Fig. 3
- ein Ausführungsbeispiel einer hydraulischen Steuerung.
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.
- Steuerung nach Anspruch 1, dadurch gekennzeichnet, daß die Durchflußkennlinien (29) der beiden Rückflußkompensationsventile (14, 15) gleich sind.
- Steuerung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Durchflußkennlinien (28, 29) der Rückflußkompensationsventile (14, 15) und des Kompensationsventils (4) parallel zueinander verlaufen.
- 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.
- Steuerung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß zwischen dem Motor (10) und den Rückflußkompensationsventilen (14, 15) eine Nachsaugventilanordnung (20) mündet.
- Steuerung nach Anspruch 5, dadurch gekennzeichnet, daß die Nachsaugventilanordnung (20, 25, 26) ein schaltbares Sperrventil (26) aufweist.
- Steuerung nach Anspruch 6, dadurch gekennzeichnet, daß das schaltbare Sperrventil (26) bei negativen Lasten automatisch schließt.
- Steuerung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß das Kompensationsventil (4) eine geringere Federvorspannung als die Rückflußkompensationsventile (14, 15) aufweist.
- 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.
- 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.
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)
Publication Number | Publication Date |
---|---|
EP1355065A1 true EP1355065A1 (de) | 2003-10-22 |
EP1355065B1 EP1355065B1 (de) | 2006-05-24 |
Family
ID=28458876
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03075981A Expired - Lifetime EP1355065B1 (de) | 2002-04-17 | 2003-04-03 | Hydraulische Steuerung |
Country Status (4)
Country | Link |
---|---|
US (1) | US6865886B2 (de) |
EP (1) | EP1355065B1 (de) |
AT (1) | ATE327440T1 (de) |
DE (2) | DE10216958B8 (de) |
Cited By (5)
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WO2006089863A1 (en) * | 2005-02-23 | 2006-08-31 | John Deere Forestry Oy | A compensating coupling in the control of a motor |
WO2009150062A2 (de) * | 2008-06-13 | 2009-12-17 | Zf Friedrichshafen Ag | Hydraulikversorgungssystem zur versorgung eines hydraulischen verbrauchers mit wenigstens einem verbrauchsbereich |
EP3135924A1 (de) * | 2015-08-24 | 2017-03-01 | HAWE Hydraulik SE | Hydrauliksteuerung |
EP2636908A3 (de) * | 2012-03-05 | 2017-04-26 | Robert Bosch Gmbh | Steueranordnung |
CN114412850A (zh) * | 2021-12-27 | 2022-04-29 | 湖南中联重科应急装备有限公司 | 伸缩马达液压***、伸缩梯架和云梯消防车 |
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DE102004025322A1 (de) | 2004-05-19 | 2005-12-15 | Sauer-Danfoss Aps | Hydraulische Ventilanordnung |
US7906690B2 (en) * | 2004-07-21 | 2011-03-15 | Dow Global Technologies Inc. | Batch, semi-continuous or continuous hydrochlorination of glycerin with reduced volatile chlorinated hydrocarbon by-products and chloracetone levels |
DE102004048642A1 (de) * | 2004-10-04 | 2006-04-06 | Bosch Rexroth Aktiengesellschaft | Hydraulische Steueranordnung |
US7204084B2 (en) * | 2004-10-29 | 2007-04-17 | Caterpillar Inc | Hydraulic system having a pressure compensator |
DE102004063044B4 (de) | 2004-12-22 | 2006-12-21 | Sauer-Danfoss Aps | Hydraulische Steuerung |
DE102005011395A1 (de) | 2005-03-11 | 2006-09-14 | Bosch Rexroth Ag | Hydraulische Steueranordnung |
US7204185B2 (en) * | 2005-04-29 | 2007-04-17 | Caterpillar Inc | Hydraulic system having a pressure compensator |
US7243493B2 (en) * | 2005-04-29 | 2007-07-17 | Caterpillar Inc | Valve gradually communicating a pressure signal |
US7194856B2 (en) * | 2005-05-31 | 2007-03-27 | Caterpillar Inc | Hydraulic system having IMV ride control configuration |
US7302797B2 (en) * | 2005-05-31 | 2007-12-04 | Caterpillar Inc. | Hydraulic system having a post-pressure compensator |
US7210396B2 (en) * | 2005-08-31 | 2007-05-01 | Caterpillar Inc | Valve having a hysteretic filtered actuation command |
US7331175B2 (en) * | 2005-08-31 | 2008-02-19 | Caterpillar Inc. | Hydraulic system having area controlled bypass |
US20100043418A1 (en) * | 2005-09-30 | 2010-02-25 | Caterpillar Inc. | Hydraulic system and method for control |
US7614336B2 (en) * | 2005-09-30 | 2009-11-10 | Caterpillar Inc. | Hydraulic system having augmented pressure compensation |
US7320216B2 (en) * | 2005-10-31 | 2008-01-22 | Caterpillar Inc. | Hydraulic system having pressure compensated bypass |
DE102006060326B4 (de) * | 2006-12-20 | 2008-11-27 | Sauer-Danfoss Aps | Hydraulische Ventilanordnung |
US7621211B2 (en) * | 2007-05-31 | 2009-11-24 | Caterpillar Inc. | Force feedback poppet valve having an integrated pressure compensator |
US8479504B2 (en) | 2007-05-31 | 2013-07-09 | Caterpillar Inc. | Hydraulic system having an external pressure compensator |
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US8631650B2 (en) | 2009-09-25 | 2014-01-21 | Caterpillar Inc. | Hydraulic system and method for control |
US8763388B2 (en) * | 2009-10-13 | 2014-07-01 | Caterpillar Inc. | Hydraulic system having a backpressure control valve |
CN103697001B (zh) * | 2013-12-16 | 2016-03-16 | 长沙中联消防机械有限公司 | 工程机械及其液压驱动*** |
CN103671335B (zh) * | 2013-12-19 | 2015-12-02 | 杭叉集团股份有限公司 | 负载敏感电比例多路阀 |
DE102017210011A1 (de) | 2017-06-14 | 2018-12-20 | Robert Bosch Gmbh | Ventilanordnung für einen Fahrantrieb |
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- 2002-04-17 DE DE10216958A patent/DE10216958B8/de not_active Withdrawn - After Issue
-
2003
- 2003-04-02 US US10/405,174 patent/US6865886B2/en not_active Expired - Lifetime
- 2003-04-03 EP EP03075981A patent/EP1355065B1/de not_active Expired - Lifetime
- 2003-04-03 DE DE50303427T patent/DE50303427D1/de not_active Expired - Lifetime
- 2003-04-03 AT AT03075981T patent/ATE327440T1/de not_active IP Right Cessation
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GB2044366A (en) * | 1979-03-26 | 1980-10-15 | Sperry Corp | Hydraulic Systems for Actuators |
US6244158B1 (en) * | 1998-01-06 | 2001-06-12 | Fps, Inc. | Open center hydraulic system with reduced interaction between branches |
DE19802430A1 (de) * | 1998-01-23 | 1999-07-29 | Mannesmann Rexroth Ag | Hydraulisches System zum Betreiben eines reversierbaren hydraulischen Verbrauchers |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006089863A1 (en) * | 2005-02-23 | 2006-08-31 | John Deere Forestry Oy | A compensating coupling in the control of a motor |
WO2009150062A2 (de) * | 2008-06-13 | 2009-12-17 | Zf Friedrichshafen Ag | Hydraulikversorgungssystem zur versorgung eines hydraulischen verbrauchers mit wenigstens einem verbrauchsbereich |
WO2009150062A3 (de) * | 2008-06-13 | 2010-03-18 | Zf Friedrichshafen Ag | Hydraulikversorgungssystem zur versorgung eines hydraulischen verbrauchers mit wenigstens einem verbrauchsbereich |
EP2636908A3 (de) * | 2012-03-05 | 2017-04-26 | Robert Bosch Gmbh | Steueranordnung |
EP3135924A1 (de) * | 2015-08-24 | 2017-03-01 | HAWE Hydraulik SE | Hydrauliksteuerung |
CN114412850A (zh) * | 2021-12-27 | 2022-04-29 | 湖南中联重科应急装备有限公司 | 伸缩马达液压***、伸缩梯架和云梯消防车 |
CN114412850B (zh) * | 2021-12-27 | 2024-01-23 | 湖南中联重科应急装备有限公司 | 伸缩马达液压***、伸缩梯架和云梯消防车 |
Also Published As
Publication number | Publication date |
---|---|
DE50303427D1 (de) | 2006-06-29 |
ATE327440T1 (de) | 2006-06-15 |
EP1355065B1 (de) | 2006-05-24 |
DE10216958B3 (de) | 2004-01-08 |
US20030196545A1 (en) | 2003-10-23 |
DE10216958B8 (de) | 2004-07-08 |
US6865886B2 (en) | 2005-03-15 |
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