EP1643138A1 - Commande hydraulique - Google Patents

Commande hydraulique Download PDF

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Publication number
EP1643138A1
EP1643138A1 EP05021173A EP05021173A EP1643138A1 EP 1643138 A1 EP1643138 A1 EP 1643138A1 EP 05021173 A EP05021173 A EP 05021173A EP 05021173 A EP05021173 A EP 05021173A EP 1643138 A1 EP1643138 A1 EP 1643138A1
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EP
European Patent Office
Prior art keywords
pressure
control
line
compensator
arrangement according
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
EP05021173A
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German (de)
English (en)
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EP1643138B1 (fr
Inventor
Armin Stellwagen
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Bosch Rexroth AG
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Bosch Rexroth AG
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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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—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
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/57—Control of a differential pressure
    • 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
    • F15B2211/575—Pilot pressure control
    • F15B2211/5756—Pilot pressure control for opening a 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
    • F15B2211/6055—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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load pressure
    • 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
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a consumer according to the preamble of patent claim 1.
  • Such hydraulic control arrangements are used for example in cranes, mobile work equipment, aerial work platforms or drilling rigs for controlling hydraulic consumers, such as hydraulic cylinders or hydraulic motors.
  • different control concepts such as the LS system are used, in which the highest load pressure of the driven load is reported to a variable and this is controlled so that in a pump line is present at a certain pressure difference Ap over the load pressure lying pump pressure.
  • the adjustable metering orifices of a LS control are assigned individual pressure balances, which maintain a pressure difference independent of the load pressure via the respective metering orifices.
  • these individual pressure compensators are arranged upstream of the metering orifice, in the special case of a LUDV control the individual pressure compensators are provided downstream of the metering orifices.
  • DE 102 16 958 B3 shows a control system designed as an LS system, in which connections of a hydraulic motor can be connected to a variable displacement pump or a tank via a continuously adjustable directional control valve.
  • the continuously adjustable directional control valve forms an inlet and a flow meter orifice, wherein the inlet orifice is preceded by an individual pressure compensator.
  • In the pressure medium flow and the pressure medium return are each one Expander scale arranged, of which when driving the consumer only the return pressure compensator lying in the return is effective, which is in the flow "discharge pressure balance" is then fully open and thus ineffective. With the effective discharge pressure compensator, the pressure medium volume flow in the return is regulated when the load is pulled, so that no uncontrolled operating state can occur.
  • a corresponding solution is also disclosed in US 4,184,410.
  • a disadvantage of such hydraulic control arrangements is that the control of the return pressure compensator located in the return is relatively expensive, since this must be acted upon by the pressure in a line leading to the tank and on the other by the applied pressure between the flow meter and the discharge pressure balance.
  • the object of the invention to provide a hydraulic control arrangement, which allows a simple pressure fluid flow control in the process with low device complexity.
  • the hydraulic control arrangement has an outlet pressure balance arranged in the respective return, which is acted upon in the opening direction - not by the tank pressure as in the prior art described above - but by a constant low pressure in a feed line leading to the consumer.
  • the channel guidance between the metering orifice and the metering orifice and the pressure compensator-containing control block and the drainage pressure compensator-containing sink module much easier be configured because no own tank line must be performed to the sink module, so that it is connected only via a flow line and a return line with the directional control valve containing control block.
  • This constant pressure can be adjusted for example via a pressure relief valve.
  • This is connected via a Lastmelde Koch and a nozzle to the flow line and forms together with the inlet pressure compensator a pilot-operated pressure reducing valve.
  • This regulates in the supply line a pressure which is higher by the pressure equivalent of the pressure compensator spring than the value set at the pressure limiting valve.
  • D. h. In the flow to the consumer, the flow control is replaced by a pressure control.
  • This pressure limiting valve is preferably designed to be adjustable, so that a lowering is possible even with a positive load.
  • a pilot-operated check valve is provided in the region between the discharge pressure balance and the associated working port of the consumer, which is preferably also unlocked from said control pressure.
  • the discharge pressure balance is in the pressure medium flow, it is bypassable by means of a bypass line, in which a bypass check valve opening in the direction of the consumer is arranged.
  • a directional control valve which acts in a spring-biased basic position, the discharge pressure compensator in the opening direction with the constant pressure in the supply line, while in the closing direction of the pressure compensator respectively the pressure between the discharge pressure compensator and the adjustable drain metering orifice is effective.
  • the discharge pressure balance is acted upon in each case in the opening direction with the constant pressure in the flow. In the case in which the "discharge pressure balance" is arranged in the pressure medium flow, this pressure balance is then fully open, while throttling the draining pressure medium volume flow at a pulling load.
  • the drain pressure compensator practically vorumblende directional control valve is acted upon in the direction of its basic position by the flow pressure and in the direction of its switching position of the pressure between the drain metering and the discharge pressure balance.
  • the control arrangement according to the invention is preferably designed as a LS control arrangement with a variable displacement pump which can be controlled as a function of a load pressure signal of the load tapped via an LS line.
  • this load pressure signal is differently limited as a function of the pressure medium flow direction, so that, for example, when lifting a load, a higher load pressure signal is allowed than is the case when lowering a load.
  • the consumer is a hydraulic cylinder over which, for example, a crane arm is supported.
  • the control arrangement 1 shown in Figure 1 is used to control a designed as a differential cylinder lifting cylinder 2, via which a crane arm 4 of a crane or a boom of a mobile device is supported.
  • the control arrangement 1 is designed as a LS system, wherein pressure medium is sucked via a variable displacement pump 6 from a tank T and conveyed via a control block 8 to the lifting cylinder 2 and is returned by this via a drain module 10 and the control block 8 to the tank T.
  • the variable displacement pump 6 is controlled by means of a pump controller 12 in response to the tapped via an LS line 14 highest load pressure of all supplied by the variable displacement 6 consumers so that it generates at its output a pressure by a predetermined difference ⁇ p above this highest load pressure of all consumers.
  • the pump regulator 12 is acted upon by the pump pressure and in terms of increasing the stroke volume of the highest load pressure and a spring in terms of a reduction of the stroke volume.
  • the difference between the pump pressure and the highest load pressure then corresponds to the force of this spring (for example, 20 bar).
  • variable displacement pump 6 The output of the variable displacement pump 6 is connected to a pump port P of the control block 8, the tank T is connected to a tank port T and two working ports A, B of the control block 8 via two working lines, which are mentioned in the following flow line 16 and return line 18, with an annular space 20 and a cylinder chamber 22 of the lifting cylinder 2 connected.
  • control block 8 pressure fluid from the working port A flows into the annulus 20 and from the cylinder chamber 22 via the sink module 10 and the control block 8 back to the tank T.
  • the line 16 is then the flow line, while the line 18 is the return line.
  • the control block 8 can also be controlled so that the line 18 (here called return line) the flow line and the line 16 (here called feed line) is the return line.
  • the control block 8 shown in Figure 1 has a continuously adjustable directional control valve 26 which is hydraulically pilot operated in the illustrated embodiment. This precontrol can be done, for example, by means of pressure reducing valves, not shown, via which a control supply pressure is reduced to a suitable control pressure.
  • the continuously adjustable directional control valve 26 has a pressure port P and two working ports A, B, which are shut off in the illustrated spring-biased home position (0).
  • a tank connection T of the directional control valve 26 is connected via a tank channel 28 to the tank connection T of the control block 8 (closed center system).
  • the pressure port P of the control block 8 is connected to the input port P of the directional control valve 26 via an inlet channel 30, in which an individual or inlet pressure compensator 32 is arranged. This is acted upon in the opening direction by the force of a pressure compensator spring 34 and the pressure in the respective flow line 16 and 18, which is tapped via a signaling line 36. In the closing direction, the pressure compensator 32 is acted upon by the pressure at the input P of the directional control valve, which is tapped via a control channel 38 from the inlet channel 30.
  • a metering orifice 40 between the inlet connection P and the working connection A of the directional control valve 26 is opened via a control edge. Accordingly, a drain metering orifice 42 between the working port B and the tank port T of the directional control valve 26 is opened. The pressure downstream of the inlet metering orifice 40 is reported to the reporting line 36.
  • the metering orifice is between the input port P and the working port B, while the drain metering orifice is between the working port A and the tank port T. In these control positions, the pressure is also reported downstream of the metering orifice in the reporting line 36.
  • the pressure relief valve 48 limits in the control positions (a) and the pressure limiting valve 50 in the control positions (b) of the directional control valve 26 via the line 36 to the individual pressure compensator 32 and to the pump controller 12 reported pressure to the value set at the respective pressure relief valve.
  • the two working ports A, B of the continuously variable directional valve are connected via a flow channel 52 and a return passage 54 to the working ports A, B of the control block 8, to which the flow line 16 and the return line 18 are connected.
  • the sink module 10 is arranged. This has according to Figure 1, a pressure port P ', a working port A' and a control port X, which is connected via a line 56 to the flow line 16.
  • the input port P ' is connected via a channel 58, which forms part of the return line 18 to the working port A'.
  • a discharge pressure compensator 60 is provided, which in the opening direction by the force of a weak spring 61 (eg 3 bar) and the pressure in a control line 62 is applied, which is connected to the line 56.
  • a weak spring 61 eg 3 bar
  • a control line 62 is applied, which is connected to the line 56.
  • In the closing direction acts on the pressure compensator piston (not shown) of the pressure compensator 60, the pressure in the region between the input port P 'and the discharge pressure compensator 60.
  • This control pressure is tapped via a line 64 from the channel 58.
  • a pilot-operated check valve 66 is provided, which is unlocked via a Entsperrkanal 68 which is connected to the line 56.
  • the discharge pressure compensator 60 can be bypassed by means of a bypass line 70, which branches off in the area between the input port P 'and the discharge pressure compensator 60 from the channel 58 and re-opens in the area between the latter and the check valve.
  • a bypass check valve 72 is provided which opens in the direction of the cylinder chamber 22 and blocks a flow of pressure medium in the opposite direction.
  • the directional control valve 26 is displaced by appropriate control of the control block 8 in one of his (b) marked control positions, in which the input port P of the directional control valve 26 is connected to the working port B, while the working port A connected to the tank T. is.
  • the variable displacement pump 6 delivers depending on the maximum load pressure of the consumer pressure medium via the inlet pressure compensator 32, the directional control valve 26, the working port B of the control block 8, the input port P 'of the sink module 10, the opening bypass check valve 72, the check valve 66 and the working port A' of the sink module 10 in the cylinder chamber 22, so that the lifting cylinder 2 extends.
  • control block 8 is reversed and the directional control valve 26 is moved to one of its (a) marked control positions in which the pressure medium is conveyed into the annular space 20 and displaced from the cylinder chamber 22.
  • the inlet orifice plate 40 and the drain measuring orifice 42 of the directional control valve 26 are matched to one another in such a way that, given a pressure difference across the inlet orifice plate 40, the annulus 20 of the lifting cylinder would flow a larger quantity of pressure medium than the area ratio from the cylinder chamber 22 the drain metering orifice 42 is displaced at the pressure difference predetermined by the discharge pressure compensator 60.
  • the pressure in the annular space 20 therefore increases until the pressure limiting valve 48 responds and limits the pressure in the signaling line 36 to the value set at it.
  • the inlet pressure compensator 32 now works together with the pressure relief valve 48 as a pilot-operated pressure reducing valve and regulates in the flow line 16 a pressure which is higher by the pressure equivalent of the pressure compensator spring 34 than the value set at the pressure relief valve 48.
  • the flow control is replaced by a pressure control, so that the discharge pressure compensator 60 is applied via the line 56 and the control line 62 in the opening direction with a constant pressure.
  • the coordination between the metering orifice and the drain metering aperture does not have to be very accurate.
  • the inlet metering orifice 40 must simply be one piece larger than the metering orifice 42.
  • the pressure limiting valve 48 is set to a pressure such that, taking into account the pressure equivalent of the pressure compensator spring 34, the pressure in the supply line 16 is so high that it is sufficient to open the pilot-operated check valve 66 via the line 56 and the Entsperrkanal 68 and open to keep.
  • the pressure relief valve 48 is set to 25 bar and the pressure equivalent of the pressure compensator spring 34 is 10 bar, then the inlet pressure compensator 32 in the supply line 16 regulates a pressure of 35 bar. But to open the check valve 66 may already suffice 30 bar. Of course, the pump controller 12 is set so that the pump pressure is slightly higher than 35 bar at a message of 25 bar.
  • the discharge pressure compensator 60 is thus acted upon in the opening direction by the constant pressure in the supply line 16 and by the force of the weak spring 61.
  • the discharge pressure compensator 60 is acted upon by the pressure in the line 18, that is, by the pressure upstream of the drain metering orifice 42.
  • the discharge pressure compensator 60 therefore in each case opens so far that the pressure upstream of the drain metering orifice 42 is equal to the pressure in the supply line 16 plus the pressure equivalent of the spring 61. Because the pressure in the flow line is constant, is then the pressure upstream of the drain metering orifice 42 is constant.
  • the pressure downstream of the drain metering orifice 42 is the constant tank pressure. Thus, the pressure difference across the drain metering orifice 42 is constant.
  • the displaced from the cylinder chamber 22 of the lifting cylinder 2 pressure medium quantity and thus the lowering speed of the crane arm 4 can be independent of load control by proportional adjustment of the drain measuring aperture.
  • FIG. 2 shows another embodiment of a sink module 10, in which instead of the bypass line 70 with the check valve 72, a 3/2-way valve 74 is used.
  • the basic structure of the sink module 10 is the same as in the embodiment of Figure 1.
  • the discharge pressure compensator 60 is arranged, between which and the working port A ', the pilot-operated check valve 66 is formed.
  • the control pressure required for unlocking is tapped via the unlocking channel 68 from the control line 62 connected to the control connection X.
  • the pressure compensator 60 is acted upon by the spring 61 in the illustrated embodiment, a force corresponding to a pressure of 5 bar in the opening direction and in the closing direction of the pressure in the line 64, which is tapped from the channel 58.
  • the 3/2-way valve 74 is biased by means of a 10bar spring 76 and the pressure in the control line 62 in a basic position (a), in which the control line 62 is connected to a pressure compensator channel 78 through which the discharge pressure compensator 60 in addition to the force of Spring 61 is acted upon in the opening direction.
  • the 3/2-way valve 74 is acted upon in the direction of its switching position (b) by the pressure in the channel 58, which corresponds to the pressure in the conduit 64.
  • the 3/2-way valve 74 is thus displaced against the force of the 10bar spring 76 in its switching position (b) when the pressure difference between the pressure in the channel 58 and the pressure in the control line 62 is more than 10 bar.
  • the channel 58 is connected to the pressure compensator channel 78, so that the discharge pressure compensator 60 is pressure-balanced on the front side and experiences an excess of force in the opening direction by the 5bar spring 61.
  • the lower pressure in the annular space 20 is then present at the control connection X of the sink module 10, while the right-hand control surface of the 3/2 directional control valve 74 is acted upon by the pressure downstream of the directional control valve 26 - the 3/2-way valve is acted upon Switched with (b) switching position, in which the pressure compensator 60 - as described above - from the 5bar spring 61 completely is controlled and has no effect.
  • the pressure medium can then flow via the channel 58, the pressure compensator 60, the opening check valve 66 and the working port A 'in the cylinder chamber 22.
  • the directional control valve 26 To lower the directional control valve 26 is moved in one of its (a) marked control positions, so that the pressure medium is conveyed into the annular space 20 and displaced from the cylinder chamber 22. In normal operation (no pulling load), the 3/2-way valve 74 is then biased by the force of the 10bar spring 76 and the pressure in the flow line 16 in its designated (a) switching position and the discharge pressure compensator 60 remains in its open position.
  • the pressure applied to the inlet pressure compensator 32 in the opening direction pressure when lifting the load (extension of the lifting cylinder 2) via the lifting-pressure limiting valve 50 to a relatively high value (250 bar) limited while lowering the maximum load signal pressure via the drain pressure relief valve 48 to a much lower value (25 bar) is set.
  • the pilot-operated check valve 66 is releasable with a control pressure corresponding to about 50 bar in the illustrated embodiment.
  • the pressure compensator spring 34 is selected so that the supply pressure compensator 32 starts at a pressure of about 25 bar with the flow control.
  • a sink module 10 is provided only in the line 18 (return line).
  • a corresponding drain module can also be arranged in the supply line 16, which then becomes correspondingly effective in order to bring about a sequence control when lifting the load m. This may be necessary, for example, when over the lifting cylinders 22 when lifting the load a dead center is run over.
  • a hydraulic control arrangement for controlling a consumer, with an adjustable metering orifice and an associated inlet pressure compensator and a drain module arranged in the drain from the consumer. This has a discharge pressure balance, which is acted upon according to the invention in the opening direction by a constant low pressure in the flow.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Control Of Fluid Pressure (AREA)
EP05021173A 2004-10-04 2005-09-28 Commande hydraulique Not-in-force EP1643138B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004048642A DE102004048642A1 (de) 2004-10-04 2004-10-04 Hydraulische Steueranordnung

Publications (2)

Publication Number Publication Date
EP1643138A1 true EP1643138A1 (fr) 2006-04-05
EP1643138B1 EP1643138B1 (fr) 2008-06-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05021173A Not-in-force EP1643138B1 (fr) 2004-10-04 2005-09-28 Commande hydraulique

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Country Link
EP (1) EP1643138B1 (fr)
AT (1) ATE398239T1 (fr)
DE (2) DE102004048642A1 (fr)
DK (1) DK1643138T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007116846A1 (fr) * 2006-03-27 2007-10-18 Kabushiki Kaisha Toyota Jidoshokki Appareil de commande hydraulique
EP3135924A1 (fr) * 2015-08-24 2017-03-01 HAWE Hydraulik SE Commande hydraulique
CN111255776A (zh) * 2020-05-07 2020-06-09 上海建工集团股份有限公司 超高层建筑整体钢平台模架液压控制系统及方法
IT202100000431A1 (it) * 2021-01-12 2022-07-12 Bosch Gmbh Robert Sistema di controllo per un cilindro attuatore di una gru

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018001303A1 (de) * 2018-02-20 2019-08-22 Hydac Fluidtechnik Gmbh Ventilvorrichtung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19800721A1 (de) * 1998-01-12 1999-07-15 Danfoss As Steuervorrichtung für einen hydraulischen Motor
US20030141132A1 (en) * 2002-01-31 2003-07-31 Kowalyk Vladimir M. Integral over-running load control valve on tractor remote valve section for agricultural loader boom circuit
DE10216958B3 (de) * 2002-04-17 2004-01-08 Sauer-Danfoss (Nordborg) A/S Hydraulische Steuerung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19800721A1 (de) * 1998-01-12 1999-07-15 Danfoss As Steuervorrichtung für einen hydraulischen Motor
US20030141132A1 (en) * 2002-01-31 2003-07-31 Kowalyk Vladimir M. Integral over-running load control valve on tractor remote valve section for agricultural loader boom circuit
DE10216958B3 (de) * 2002-04-17 2004-01-08 Sauer-Danfoss (Nordborg) A/S Hydraulische Steuerung

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007116846A1 (fr) * 2006-03-27 2007-10-18 Kabushiki Kaisha Toyota Jidoshokki Appareil de commande hydraulique
AU2007236781B2 (en) * 2006-03-27 2009-11-05 Kabushiki Kaisha Toyota Jidoshokki Hydraulic control apparatus
US8109198B2 (en) 2006-03-27 2012-02-07 Kabushiki Kaisha Toyota Jidoshokki Hydraulic control apparatus
EP3135924A1 (fr) * 2015-08-24 2017-03-01 HAWE Hydraulik SE Commande hydraulique
CN111255776A (zh) * 2020-05-07 2020-06-09 上海建工集团股份有限公司 超高层建筑整体钢平台模架液压控制系统及方法
CN111255776B (zh) * 2020-05-07 2020-07-17 上海建工集团股份有限公司 超高层建筑整体钢平台模架液压控制系统及方法
IT202100000431A1 (it) * 2021-01-12 2022-07-12 Bosch Gmbh Robert Sistema di controllo per un cilindro attuatore di una gru

Also Published As

Publication number Publication date
ATE398239T1 (de) 2008-07-15
EP1643138B1 (fr) 2008-06-11
DE102004048642A1 (de) 2006-04-06
DK1643138T3 (da) 2008-09-22
DE502005004381D1 (de) 2008-07-24

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