EP1831573B1 - Hydraulische steueranordnung - Google Patents

Hydraulische steueranordnung Download PDF

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Publication number
EP1831573B1
EP1831573B1 EP05850157A EP05850157A EP1831573B1 EP 1831573 B1 EP1831573 B1 EP 1831573B1 EP 05850157 A EP05850157 A EP 05850157A EP 05850157 A EP05850157 A EP 05850157A EP 1831573 B1 EP1831573 B1 EP 1831573B1
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EP
European Patent Office
Prior art keywords
pressure
pump
control system
consumer
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP05850157A
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German (de)
English (en)
French (fr)
Other versions
EP1831573A1 (de
Inventor
Wolfgang Kauss
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1831573A1 publication Critical patent/EP1831573A1/de
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Publication of EP1831573B1 publication Critical patent/EP1831573B1/de
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/168—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load with an isolator valve (duplicating valve), i.e. at least one load sense [LS] pressure is derived from a work port load sense pressure but is not a work port pressure itself
    • 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
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—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

Definitions

  • the invention relates to a hydraulic control arrangement for pressure medium supply at least one hydraulic consumer.
  • Such, for example in the DE 199 30 618 A1 described control arrangements have a variable or constant pump with bypass pressure compensator, which are each controlled in response to the highest load pressure of the actuated hydraulic consumers so that the pump pressure is a certain pressure difference above the highest load pressure.
  • the hydraulic consumers the pressure medium flows through adjustable metering orifices, which are arranged between an outgoing of the variable displacement supply line and the hydraulic consumers. Associated by the metering orifices pressure balances is achieved that is independent of the load pressures of the hydraulic consumer, a certain pressure difference across the metering orifices when supplied by the pump pressure, so that the respective consumer flowing pressure fluid quantity depends only on the opening cross section of the respective metering orifice.
  • the pump regulator of the variable displacement pump or the bypass pressure compensator of the fixed displacement pump is adjusted in such a way that it delivers the required quantity of pressure medium - this is called demand flow control.
  • An LS control arrangement with LS level valve is in the WO 98/46883 A1
  • the individual pressure compensator assigned to the metering orifice in the closing direction is usually controlled by the highest load pressure of the hydraulic consumers and, in the opening direction, by the pressure downstream of the metering orifice.
  • the metering orifices so far opened up that the pressure medium supplied by the pump is smaller than the demand quantity, the pressure fluid quantities flowing to the individual hydraulic consumers are proportionally reduced independently of the respective load pressure of the hydraulic consumers.
  • Such a LUDV control is a special case of LS control. It is referred to a mere LS control when the individual pressure compensator is acted upon in the closing direction by the pressure before the metering orifice and in the opening direction of the pressure to the metering orifice, this pressure then, if the metering orifice of the pressure compensator is connected downstream, corresponds to the individual load pressure, with simultaneous actuation of a plurality of hydraulic consumers and not enough of the variable displacement pressure fluid supplied only the load pressure highest hydraulic consumer inflowing pressure medium quantity is reduced.
  • the highest load pressure leading LS line is connected via a flow control valve to the tank.
  • Such hydraulic control arrangements are used, for example, to supply the consumers of construction machines, for example a slewing gear, a jib, a spoon or a dipper stick of a mobile implement.
  • the pump is often driven by an internal combustion engine, this pump is assigned to all consumers.
  • the size of the pump is designed according to the available engine power, with the individual movements of the consumers to a large extent being coordinated with one another in view of good controllability.
  • the entire pump flow rate is required for a single motion. Accordingly, the maximum opening cross section of the metering orifice must be designed for this amount of pressure medium.
  • the control range of the gate will not be fully utilized at reduced or minimum engine speed.
  • the metering orifice must be opened only to a part of the maximum opening cross-section, so that only a partial stroke of the metering orifice is available for controlling this amount of pressure medium. Accordingly, the resolution of the metering orifice is comparatively low, so that the accuracy of the consumer movement at low speed often does not meet the requirements.
  • the invention has for its object to provide a hydraulic control arrangement, with which a sufficiently accurate control of a consumer is possible even at low flow rate of a variable displacement pump or a constant displacement pump.
  • the control arrangement according to the invention has a controllable depending on the load pressure of a consumer pump assembly and a metering orifice for adjusting the pressure medium flow to the consumer.
  • the load pressure is tapped via an LS line, which is connected by means of a current regulator with a pressure medium sink, for example a tank.
  • the current regulator can be adjusted as a function of the delivery rate, preferably the pump speed.
  • a volume flow dependent on the delivery quantity or pump speed flows out of the load-reporting line. This is increased with decreasing speed, so that due to the pressure drop in the load-sensing line, a lower pressure to the pump is reported and this adjusts accordingly.
  • the pressure drop across the metering orifice and thus the pressure medium flow rate flowing over it is reduced, so that the metering orifice must be opened further and the control range of the metering orifice is better utilized.
  • This concept according to the invention can be applied both in LUDV systems and in the aforementioned LS systems (pressure compensator of ⁇ p via metering orifice) also use in control arrangements in which only one consumer is controlled via a metering orifice (without pressure compensator).
  • a LUDV pressure compensator with an orifice plate is provided, which then generates a constant, larger pressure gradient when the flow controller is opened, as a result of which, as described above, the pressure drop across the metering orifice is reduced.
  • a diaphragm is not required.
  • the current regulator is driven as a function of the engine speed of a pump drive.
  • This engine is designed in a preferred embodiment as an internal combustion engine.
  • an additional nozzle is arranged in the LS line downstream of the flow regulator, via which the above-described pressure drop can be generated, which then leads to the lowering of the volume flow through the metering orifice.
  • This additional aperture makes it possible to more sensitively control several consumers of a control arrangement. Without this additional nozzle, however, only the load pressure highest consumers can be controlled more sensitive, because only in this affects the fully open individual pressure compensator not the pressure after the metering orifice, since this pressure corresponds to the highest load pressure or set in the LS line pressure. If the pump pressure changes, the pressure difference across the metering orifice changes as well.
  • the individual pressure balances downstream of the metering orifices regulate the lower pressure prevailing in the LS line. Accordingly, with the lower load consumers, the pressure before and after the metering orifices in the changed the same extent, if one adjusts the flow controller - the pressure difference across these orifices of low-load consumers then remains the same.
  • the pressure in the LS line is limited by a LS pressure relief valve.
  • This can be located either downstream or upstream of the flow regulator.
  • An LS pressure relief valve located downstream of the additional nozzle limits the pressure reported to the pump.
  • In the LS line upstream of this additional nozzle and thus on the backs of all individual pressure balances is then a slightly higher pressure to adjust the individual pressure compensators downstream of the metering orifice.
  • the pump on the other hand, only works by the control ⁇ p above the lower pressure determined by the pressure relief valve. This reduces the pressure difference across all metering orifices - in some cases even zero. There is a possibility that not only the consumer who is at the stop but all consumers stop.
  • the LS pressure relief valve limits the pressure on the backs of the individual pressure compensators.
  • the pump pressure is higher than the pressure on the backs of the individual pressure compensators by one through the additional nozzle, the adjustment of the flow regulator and the adjustment of the pump regulator or the bypass pressure balance (constant pump), so that the pressure difference across the metering orifices of the lower-load consumer is maintained, even if a consumer is pending an attack.
  • control arrangement according to the invention is used particularly advantageously in a construction machine, for example an excavator, wherein a slewing gear is to be moved at a comparatively low speed.
  • FIG. 1 is a diagram of a working according to the LUDV principle control arrangement 1, as used in a construction machine, such as an excavator.
  • a LUDV control arrangement 1 consumers of the excavator, such as the cylinders or hydraulic motors one slewing 2, a spoon 4, a spoon handle 6 and a boom 8 are supplied in response to the activation of a directional control valve block 10 with pressure medium.
  • This is in the present embodiment promoted by a fixed displacement pump 12 which is driven by an internal combustion engine 14.
  • the control of the internal combustion engine 14 by means of a control lever (throttle / accelerator pedal) 16 which is connected via a throttle cable 20 in operative connection with the motor 14 to adjust its speed.
  • the mobile control block 10 is composed of a plurality of directional control valve sections, wherein each of the consumers 2, 4, 6, 8 is associated with a directional valve section with a LUDV valve arrangement 22, 24, 26, and 28 respectively.
  • a bypass pressure compensator 30 and an LS pressure relief valve 32 are provided in an input section of the mobile control block 10.
  • the bypass pressure compensator 30 is arranged in a bypass channel 48, via which the inlet channel 36 is connected to the tank channel 44.
  • the bypass pressure compensator 30 is acted upon in the closing direction by the force of a spring and by the pressure present in the LS channel 38, which is picked off via an LS control channel 50.
  • the pressure in the supply line 36 In the opening direction of the pressure at the entrance of the bypass pressure compensator 30, d. h., The pressure in the supply line 36.
  • the spring of the bypass pressure compensator is selected so that in the supply line 36, a pressure is adjusted by a pump ⁇ p (for example, 10 bar) above the load pressure in the LS channel 38.
  • the pressure in the LS channel 38 is limited to a maximum value.
  • the LS pressure relief valve 32 is acted upon in the closing direction by the adjustable force of a spring, in the opening direction, the pressure acts at the input of the LS pressure relief valve 32, which is connected via a channel 52 to the LS channel 38.
  • Reference numerals 22 - consist essentially of a continuously adjustable directional control valve 54 and a LUDV pressure compensator 56.
  • a directional part 58 and a speed part are formed, which has a variable metering orifice 60, which are formed by the same spool.
  • pressure medium coming from the inlet channel 36 flows from an inlet chamber 62 via the metering orifice 60 into an intermediate chamber 64, from there via an opening cross-section of the LUDV pressure compensator 56 into a second intermediate chamber 66 and then via the directional part 54 into a consumer chamber 68 or 70 and from there via a feed channel 72 and a return channel 74 to two working ports A, B of the directional valve section.
  • the working port A is then connected via a supply line 76 with a bottom-side cylinder chamber 78 and the working port B via a return line 80 with an annular space of the consumer 8, that is connected to the boom actuating the lifting cylinder.
  • a control piston of the LUDV pressure compensator 56 is designed so that, when this pressure compensator 56 is fully opened, it creates a throttled connection between the intermediate chamber 64 and the LS channel 38. This is the case when the associated hydraulic consumer is operated alone or when in a simultaneous operation of several hydraulic consumers of the LUDV pressure compensator 56 associated hydraulic consumer has the highest load pressure.
  • the control piston of the LUDV pressure compensator 56 is provided with a diaphragm 84, via which the line section connected to the intermediate chamber 64 is connected to a rear chamber 86 of the LUDV pressure compensator 56, which is connected to the LS channel 38 via a signaling channel 88. Accordingly, the control piston of the LUDV pressure compensator 56 is acted upon in the closing direction by the pressure in the LS pressure channel 38, generally the highest load pressure and in the opening direction by the pressure in the intermediate chamber 64. As described above, the pressure drop across the metering orifice 60 is kept constant with respect to the load pressure via this LUDV valve arrangement 22 with the metering orifice 60 and the downstream LUDV pressure compensator 84. With regard to the further function, the sake of simplicity to the above-mentioned DE 199 30 618 A1 directed.
  • FIG. 3 shows a section through a concrete embodiment of the current controller 42.
  • the basic structure of such a current regulator 42 is known, so that only the essential components for understanding are described here.
  • the current regulator 42 essentially consists of a variable metering orifice 90 and a pressure compensator 92 connected upstream of it FIG. 3 is shown in a control position.
  • the metering orifice 90 and the pressure compensator 92 are received in a housing 94 on which an input port 96 and an output port 98 are formed.
  • the metering orifice 90 has an orifice bore 100 formed by a radially recessed portion of a housing bore 102 closed on one side.
  • the opening cross-section of the aperture bore 100 can be changed by means of a metering orifice valve 104, which is guided rotatably and sealed in a vertical bore 106 of the housing 94.
  • the in FIG. 3 overhead end portion 108 of the metering orifice protrudes from the housing and is connected to the throttle cable 20 via connecting means, not shown, so that actuation of the throttle cable is converted into rotation of the metering gate valve 104.
  • This is thus executed in the illustrated embodiment as a rotary valve, wherein according to the rotation of the opening cross-section of the aperture bore 100 is changed.
  • the metering orifice 104 may be received axially displaceable.
  • the pressure balance 92 has a pressure compensator piston 110, which is biased by a pressure balance spring 112 against a stop screw 113 screwed into a pressure balance bore 114.
  • the pressure compensator piston 110 is in one of its control positions.
  • the pressure balance piston 110 has two annular grooves 116, 120, the are separated from each other by a control collar forming a control edge 122.
  • stop screw side face opens an angular bore 124, on the other hand via a short radial leg in the annular groove 116 opens, which is hydraulically connected to the housing bore 102 and the pressure balance bore 114 crossing vertical bore.
  • the input port 96 opens in the region of the annular groove 120
  • the output port 98 is connected on the one hand with the housing bore 102 and on the other hand with a spring chamber for the spring 112 of the pressure compensator 92.
  • the pressure balance piston 110 in the opening direction (to the stopper screw 113) by the force of the pressure balance spring 112 and the pressure at the outlet 98, ie, the pressure downstream of the aperture bore 100 and in the closing direction by the pressure in the space between the right end face of the pressure compensator piston 110 and the stop screw 113 is acted upon, which corresponds to the pressure in the vertical bore 106 and thus upstream of the metering orifice 100.
  • the pressure medium volume flow through the metering orifice 100 is determined by the setting of the metering orifice slide 104, wherein the pressure drop across the metering orifice 90, more precisely above the orifice bore 100, is kept constant independent of the load pressure. D. h., When increasing the pump pressure, this pressure increase is throttled via the pressure compensator 92.
  • the slewing gear 2 is to be moved at a comparatively low speed and that the highest load pressure is applied to the slewing gear 2 or that only the slewing gear 2 is activated.
  • the LUDV pressure compensator 56 of the LUDV valve arrangement 22 is then completely opened - the corresponding load pressure of the slewing gear 2 then lies in the load signaling channel 38.
  • the flow rate is not adjustable, the constant pump 12 would rotate by the small pivoting of the control lever 16 only with comparatively low speed and accordingly only a small pressure medium flow through the metering orifice 60 and the fully open LUDV pressure compensator 56 flow to the rotating mechanism 2 and run from this over the directional control valve 54 and the tank channel 44 to the tank T out.
  • the control range of the valve spool of the directional control valve 54 would - as described above - not fully utilized. This is inventively prevented that the current regulator 42 is adjusted in response to the setting of the control lever 16 via the throttle cable 20 so that the control oil volume flow is increased via the current regulator 42.
  • This control oil volume flow generates a pressure gradient across the orifice 84 of the LUDV pressure compensator, so that correspondingly a lower load pressure is reported to the bypass pressure compensator 30. Since the pump pressure is always around the control ⁇ p above reported pressure, the pressure drop across the metering orifice changes accordingly with the adjustment of the flow regulator 42. The pressure medium flow flowing through the metering orifice 60 is reduced due to the smaller pressure difference and the driver must use the metering orifice 60 not shown Vorstell réelle readjust so that the consumer is moved at the desired low speed - the control range of the slide of the directional control valve 54 is thus utilized much better than the above-mentioned prior art.
  • FIG. 4 shows an improved embodiment in which in the area between the flow regulator 42 and the LUDV pressure compensators 56, a further nozzle 118 is provided.
  • this nozzle 118 is disposed downstream of the branch of the channel 52, in which the LS-pressure relief valve 32 is located.
  • the highest load pressure ie, the pressure upstream of the other nozzle 118 at.
  • a constant pressure gradient is generated via this nozzle 118 in dependence on the setting of the flow regulator 42, so that the pressure reported to the bypass pressure compensator 30 is lower than the highest load pressure or the load pressure of the single consumer.
  • the pump pressure is then adjusted via the predetermined control ⁇ p on this reduced pressure, so that correspondingly, the pressure drop across the metering orifice 60 and the pressure medium flow rate flowing thereabove is reduced. Accordingly, the pressure drop across the metering orifices of the lower-load consumer is reduced so that all consumers can be controlled more sensitively.
  • the LS pressure limiting valve 32 is then opened the connection to the tank channel 44 when the preset maximum load pressure is exceeded, thus limiting the pressure upstream of the nozzle 118.
  • This limited pressure is applied in the rearward spaces 86 of the LUDV pressure compensators 56.
  • the pump pressure then adjusts according to the pressure drop across the additional nozzle, the setting of the flow controller and the control ⁇ p the bypass pressure compensator to a higher value than it rests on the backs of the LUDV pressure compensator 56, so that the pressure difference across the metering orifice 60 of the lower-load consumer is maintained, even if the load pressurehighest consumers on a Stop stands.
  • the additional nozzle 118 is disposed upstream of the LS pressure relief valve 32, that is, the channel 52 branches off only downstream of this nozzle 118 from the LS channel 38 from.
  • This embodiment does not differ from the above-described embodiment with "normal" control of the consumer. A difference only arises when one of the consumers drives to the limit.
  • the control valve pressure reported to the pump 12 or more precisely to the bypass pressure compensator 30 is then limited via the LS pressure limiting valve 32.
  • the pressure upstream of the additional nozzle 118, and thus the pressure in the rear chambers 86 of the LUDV pressure compensators 56, is then higher than the limited pump pressure. This higher pressure is adjusted via the LUDV pressure compensators 56.
  • the pump pressure only adjusts by the control ⁇ p above the comparatively low pressure determined by the LS pressure relief valve 32.
  • the pressure difference across all orifices 60 is smaller, there is even the possibility that this pressure difference is 0 and all consumers stop.
  • control oil volume flow flowing through the flow regulator 42 is conducted back to the tank T.
  • inventive concept can also be used in LS systems.
  • a variable displacement pump with pump regulator can be used, which is adjusted in dependence on the pressure in the LS channel (38).
  • a hydraulic control arrangement for pressure medium supply at least one hydraulic consumer, with a LS pump arrangement and a metering orifice for adjusting the pressure medium volume flow to the consumer.
  • the LS line is connected via a current regulator with a pressure medium sink.
  • the current regulator is adjustable as a function of the pump speed in order to change the pressure drop across the metering orifice.

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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)
  • Operation Control Of Excavators (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP05850157A 2004-12-21 2005-12-14 Hydraulische steueranordnung Not-in-force EP1831573B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004061555A DE102004061555A1 (de) 2004-12-21 2004-12-21 Hydraulische Steueranordnung
PCT/DE2005/002262 WO2006066548A1 (de) 2004-12-21 2005-12-14 Hydraulische steueranordnung

Publications (2)

Publication Number Publication Date
EP1831573A1 EP1831573A1 (de) 2007-09-12
EP1831573B1 true EP1831573B1 (de) 2012-04-18

Family

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Application Number Title Priority Date Filing Date
EP05850157A Not-in-force EP1831573B1 (de) 2004-12-21 2005-12-14 Hydraulische steueranordnung

Country Status (6)

Country Link
US (1) US7946114B2 (ja)
EP (1) EP1831573B1 (ja)
JP (1) JP4801091B2 (ja)
AT (1) ATE554291T1 (ja)
DE (1) DE102004061555A1 (ja)
WO (1) WO2006066548A1 (ja)

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DE102012207422A1 (de) * 2012-05-04 2013-11-07 Robert Bosch Gmbh Hydraulische Steueranordnung mit Lastdruckminderungund hydraulischer Ventilblock dafür
CN109404353A (zh) * 2018-12-17 2019-03-01 广西柳工机械股份有限公司 平地机前轮驱动控制阀及液压系统
CN112360833B (zh) * 2020-11-11 2023-03-14 三一汽车起重机械有限公司 流量控制系统及流量控制方法、起重机

Family Cites Families (16)

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Publication number Priority date Publication date Assignee Title
DE3883690T2 (de) * 1987-10-05 1994-03-17 Hitachi Construction Machinery Hydraulisches Antriebssystem.
KR920010875B1 (ko) * 1988-06-29 1992-12-19 히다찌 겐끼 가부시기가이샤 유압구동장치
DE3914904C2 (de) * 1989-05-05 1995-06-29 Rexroth Mannesmann Gmbh Regelung für eine lastabhängig arbeitende Verstellpumpe
JP2578371B2 (ja) * 1989-09-22 1997-02-05 株式会社小松製作所 可変容量ポンプの容量制御装置
JPH0532457A (ja) 1991-07-26 1993-02-09 Kanebo Ltd 炭素繊維強化炭素複合材料及びその製造方法
JP3064574B2 (ja) 1991-09-27 2000-07-12 株式会社小松製作所 油圧掘削機における作業油量切換制御装置
JPH0532457U (ja) * 1991-10-02 1993-04-27 住友建機株式会社 建設機械のシヨツク低減回路
JP3403538B2 (ja) * 1995-03-03 2003-05-06 日立建機株式会社 建設機械の制御装置
JP3474301B2 (ja) 1995-03-07 2003-12-08 長谷川香料株式会社 ドコサヘキサエン酸類の安定化剤
DE19517974A1 (de) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung
JP3685287B2 (ja) * 1997-04-11 2005-08-17 株式会社小松製作所 可変容量型油圧ポンプの容量制御装置
DE19930618A1 (de) * 1999-07-02 2001-01-04 Mannesmann Rexroth Ag Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
JP3854027B2 (ja) 2000-01-12 2006-12-06 日立建機株式会社 油圧駆動装置
DE10006659B4 (de) 2000-02-15 2018-06-28 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine Hydropumpe
JP3460817B2 (ja) 2000-06-28 2003-10-27 株式会社小松製作所 油圧掘削車両の油圧制御装置
JP4128482B2 (ja) * 2002-04-30 2008-07-30 東芝機械株式会社 油圧制御システム

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ATE554291T1 (de) 2012-05-15
US20080053081A1 (en) 2008-03-06
DE102004061555A1 (de) 2006-06-22
JP2008524529A (ja) 2008-07-10
US7946114B2 (en) 2011-05-24
WO2006066548A1 (de) 2006-06-29
EP1831573A1 (de) 2007-09-12

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