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
  • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
  • F15B2211/205—Systems with pumps
  • F15B2211/2053—Type of pump
  • F15B2211/20546—Type of pump variable capacity
  • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/30—Directional control
  • F15B2211/305—Directional control characterised by the type of valves
  • F15B2211/30525—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
  • F15B2211/50—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
  • F15B2211/60—Circuit components or control therefor
  • F15B2211/605—Load sensing circuits
  • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
  • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
  • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
  • F15B2211/00—Circuits for servomotor systems
  • F15B2211/60—Circuit components or control therefor
  • F15B2211/63—Electronic controllers
  • F15B2211/6303—Electronic controllers using input signals
  • F15B2211/634—Electronic controllers using input signals representing a state of 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
  • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
  • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
  • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
• • 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
  • F15B2211/78—Control of multiple output members
  • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

• the invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1 and a pressure compensator for such a hydraulic control arrangement.
• Hydraulic control arrangements are used in particular in mobile working equipment, for example in wheel loaders or tractors, in order to supply their consumers, for example the working hydraulics, the steering, traction drives and / or additional equipment with pressure medium.
• DE 41 27 342 C2 hydraulic control arrangements are known, which are designed as LS system.
• the delivery rate of the pump is controlled so that in the pump line is applied by a certain pressure difference Ap over the highest load pressure of the consumer lying pump pressure.
• each consumer an adjustable metering orifice and an individual pressure compensator are assigned, via which the pressure medium flow to the load can be kept constant independent of the load depending on the position of the metering orifice.
• an inlet pressure compensator can be provided, via which a connection to the tank can be opened.
• These inlet pressure compensators are acted upon in the closing direction by a control pressure corresponding to the highest load pressure.
• the pressure difference at which the inlet pressure compensator opens is usually slightly larger than the pressure difference ⁇ p set by the pump.
• a so-called who-Beyond connection For attaching attachments or attachments without their own pressure medium supply, a so-called who-Beyond connection provided, which may have a pressure line, a return line and an LS line. This power beyond connection also makes the load sensing system of the implement suitable for the implement.
• DE 10 2004 048 684 is an example of a hydraulic control arrangement provided with a power beyond connection.
• the pump connection of a power beyond pressure compensator is provided in a flow path between the pressure connection of the pump and the pump connections of the pressure compensators of the other consumers.
• the Power Beyond pressure compensator is connected in series with the Power Beyond consumer.
• the invention has for its object to provide a hydraulic control arrangement, a suitable pressure compensator and a control method, which ensure at least one power Beyond- consumer to a power beyond connection a demand-pressure medium supply of all consumers when connecting.
• a hydraulic control arrangement having the features of patent claim 1 and a pressure compensator having the features of patent claim 15.
• a hydraulic control arrangement for controlling at least two consumers, which can be supplied with pressure medium via a pump with adjustable flow rate and to which an adjustable metering orifice is assigned in each case.
• This hydraulic control arrangement is preferably used in mobile work equipment and has a power beyond connection for connecting a power beyond consumer and an input pressure compensator, which is connected downstream of the pump.
• a connection to the tank can be opened and this is adjustable in response to a load pressure of the consumer or at least one power beyond consumer.
• the pump is preferably controlled as a function of the setting of the inlet pressure compensator, so that a demand-based supply of consumers takes place.
• an activation of the pump takes place as a function of the position of a control piston of the inlet pressure compensator, as a result of which precise control is possible in a cost-effective manner.
• Actuation of the pump as a function of the volume flow at a connection of the inlet pressure compensator enables the direct selection of hydraulic parameters for targeted influencing of the pump control with good dynamic properties.
• the pump control is also a signal for controlling the metering orifice at least one Usable by the consumer.
• the position and / or residual flow control of the inlet pressure compensator only has to compensate for relatively small control deviations.
• the largest of the load pressures act on the inlet pressure compensator in the closing direction, so that the load sensing system of the consumer can also be used by the power beyond consumer.
• the inlet pressure compensator closes the inlet pressure compensator in a spring-biased position the connection to at least one consumer and the tank and controls this when adjusting in the opening direction, the connection to at least one of the two consumers and further adjustment in the opening direction, the connection to the tank. A sufficient supply of all consumers is ensured when the residual volume flow flows through the controlled inlet pressure compensator to the tank.
• the inlet pressure compensator is preferably acted upon in the closing direction by the force of at least one spring and by the largest of the load pressures and in the opening direction by the pressure at the inlet of the inlet pressure compensator.
• the inlet pressure compensator is provided in the closing direction and for switching the control pressure difference with a spring assembly or a progressive spring, whereby a path-dependent change in the spring force on a control piston of the inlet pressure compensator can be realized.
• control arrangement for raising the control pressure difference is provided with a device for increasing the prestressing of the spring, which enlargement mechanically, hydraulically or electrically effected.
• the pump is preferably an electrically controllable variable displacement pump or a variable speed fixed displacement pump, whereby the pump control is inexpensive to implement.
• each metering orifice is preceded by an individual pressure balance, which can be acted upon in the opening direction by the respective associated load pressure of the associated consumer and a pressure compensating spring and in the closing direction by the pressure at the outlet of the individual pressure compensator.
• the result is a responsive load-sensing system.
• the metering orifices are preferably formed by electrically, hydraulically or mechanically adjustable directional control valves.
• a pressure compensator is further provided for one of the above control arrangements, wherein the control piston of this pressure compensator in the closing direction of a pressure compensator spring arrangement and in the opening direction of a load pressure can be acted upon.
• This pressure compensating spring arrangement preferably has two springs which can be brought into engagement one after the other, which allow small installation spaces for the inlet pressure compensator.
• control pressure difference is raised at the inlet pressure compensator with switching on of the power beyond consumer, so that in addition to the prioritization of the power beyond consumer at the same time an increase in the control pressure difference is ensured in order to allow safe operation of body equipment, even with increased pressure drops in the line system to the attachment.
• FIG. 14 shows an exemplary characteristic of the inlet pressure compensator for illustrating the pressure increase.
• Fig. 1 shows a hydraulic control arrangement of a mobile implement, such as a tractor.
• This control arrangement can be formed, for example , by a mobile control block, via which the hydraulic consumers of the working hydraulics of the working equipment, in the present case two double-acting cylinders 2,4 can be supplied with pressure medium supplied by a pump 6 and from the consumers 2, 4 to one Tank T is returned.
• the pump 6 is formed in the illustrated embodiment as an electrically controllable variable displacement pump whose pivot angle is adjustable via a pump regulator 8.
• a variable speed constant displacement pump or other may be used over a pump regulator controllable pump.
• a pump line 12 which branches into two supply lines 14, 18, wherein the supply line 14 to the cylinder 2 and the supply line 18 is assigned to the cylinder 4.
• an individual pressure compensator 16 is provided, wherein the direction of pressure fluid flow direction to the consumer or from the consumer and the pressure medium volume flow are adjustable by the directional control valve 24.
• an individual pressure compensator 20 is provided, wherein the pressure medium flow direction to the consumer or from the consumer and the pressure medium volume flow are adjustable by the directional control valve 38.
• B of the directional control valve 24 are a flow line 28, which is connected to a bo-side cylinder chamber 32 of the cylinder 2 is connected, and a return line 30 which is connected to a piston rod side annular space 34 of the cylinder 2 connected.
• a flow line 42 which is connected to a bottom-side cylinder chamber 46 of the cylinder, and a return line 44, which is connected to a piston rod side annular space 48 of the cylinder 4 connected.
• the control piston 26 of the directional control valve 24 and the control piston 40 of the directional control valve 38 are controlled via a pilot control device 54 or by manual operation.
• the pilot control device 54 or by manual actuation By operating the pilot control device 54 or by manual actuation, the control pressure difference is adjusted, so that the respective control piston 26 or 40 is displaced from the blocking position (0) shown in FIG. 1 into the indicated positions (a) or (b), in which either the cylinder space 32, 46 or the annular space 34, 48 is supplied with pressure medium, while the pressure medium is displaced from the respective other pressure medium space.
• an inlet orifice plate in the directional control valves 24, 38 is opened via an inlet control edge, wherein the opening cross section of the respective inlet orifice determines the pressure medium volume flow to the cylinder 2, 4.
• the pressure medium flowing back from the cylinder 2, 4 is returned to the tank T via a tank connection T at the respective directional control valve 24, 38 and a line 50 connected to it.
• the individual pressure compensators 16, 20 are each acted upon in the opening direction by the force of a pressure compensator spring 56, 58 and the load applied to the respective load 2, 4. In the closing direction acts on the pressure compensator slide of the individual pressure compensators 16, 20 respectively, the pressure in the supply line 14 and 18 between the output of the respective individual pressure compensator 16, 20th
• a current regulator is formed, via which the pressure drop across the metering orifice can be kept constant independent of the load ,
• a hydraulic control arrangement according to the above description of FIG. 1 essentially corresponds to the structure of the hydraulic control arrangement from DE 10 2004 048 684.
• an inlet pressure compensator 60 is provided, which is designed as a 3/3-way pressure balance.
• a power beyond connection 72 branches off from the section of the pump line 12 which is located between the pressure connection of the pump 6 and the input connection P of the inlet pressure compensator 60. Via this power beyond connection 72 it is possible to connect one or more additional hydraulic consumers 74 to the mobile working device, for example a loading wagon or a potato harvesting machine.
• the power beyond consumer 74 is also connected via a tank channel 76 to the tank T in fluid communication.
• the load pressure of the power beyond consumer 74 is tapped via a shuttle valve 80 a shuttle valve cascade of shuttle valve 78 and shuttle valve 80 of the LS line.
• the control piston 62 of the inlet pressure compensator 60 is acted upon in the closing direction by the force of a spring 64 and the highest of the load pressures of the two consumers 2, 4 and the power beyond consumer 74.
• the highest te of the load pressures of the consumer 2, 4 is tapped via a shuttle valve 78 and then fed to the shuttle valve 80, to which also the load pressure of the power beyond consumer 74 is applied.
• the pressure in the pump line 12 is applied to the control piston 62 of the inlet pressure compensator.
• the input port P of the inlet pressure compensator 60 is connected to the pump line 12 in pressure medium connection, the working port A of the inlet pressure compensator 60 opens into the inlet lines 14, 18.
• the tank port T of the inlet pressure compensator 60 is connected via a tank channel 66 with the tank line 50 in fluid communication.
• Fig. 1 illustrated blocking position (0) of the inlet pressure compensator 60 is no pressure medium connection between the pump port P, the working port A and the tank port T.
• the voltage of the spring 64 acts on the control piston 62 of the inlet pressure compensator 60 in the direction of its blocking position (0).
• the pump connection P and the working connection A are in pressure medium connection, while the pressure medium connection to the tank connection T is blocked.
• the working position (b) following the working position (a) the pump connection P, the working connection A and the tank connection T are in pressure medium connection.
• the position of the control piston 62 of the inlet pressure compensator 60 is detected by a position transducer 68 whose output signal is fed to a control unit 10 which controls the pump regulator 8.
• the control unit 10 is a setpoint yl EDWso n and Y 2 EDWsO i I supplied. Between these two setpoints becomes in response to the actuation of a power beyond control 81 switched. If the power beyond consumer 74 is either not connected to the power beyond port 72, or the power beyond consumer 74 is not acknowledged, then the setpoint yL is EDWsetpoint while the power beyond consumer is connected and confirmed 74 the setpoint value y2 EDWsetpoint is used.
• the power beyond driver 81 is initialized by a signal from an operator U PB .
• the respective desired value is compared with the output signal Y EDW of the displacement transducer 68 and fed to a controller 70 in the control unit 10.
• the target value Y 1 EDWyo ii i st i n such a manner selected so that is not connected or is not actuated power beyond consumer 74 with the setpoint yl EDWsol the position (a) of the inlet pressure i of the control slide 62 60 regarded as the target value is, while with connected and operated power Beyond- consumer 74 with the setpoint y2 EDWsoll the position (b) of the spool 62 of the input pressure compensator 60 is set.
• the inlet pressure compensator 60 In the position (a) of the inlet pressure compensator 60 ensures that the pressure medium from the pump 6 via the inlet pressure compensator 60 the consumers 2, 4 is supplied loss, while upon actuation of the power beyond consumer 74, the inlet pressure compensator 60 in the position (b ) is brought, in the appropriate adjustment of the pump 6, a small residual volume flow through the tank port T and the tank passage 66 flows. In this way, the power beyond consumer 74 is priori- siert, whereby even with a high volume flow demand of the power beyond consumer 74 both the consumers 2, 4 and the power beyond consumers 74 are adequately supplied with pressure medium, if the pump 6 is designed accordingly. With the hydraulic control arrangement according to the first embodiment is further ensured that at a deficiency of the consumer, the input pressure compensator 60 closes, whereby a prioritization of the power beyond consumer 74 against the consumers 2, 4 is secured.
• control unit 110 differs from the control unit 10 of the first embodiment in that at a state indicated by actuation of the power beyond control 81, in which the power beyond consumer 74 is connected and actuated, as setpoint instead of the setpoint Y EDWsoll of First embodiment, now a setpoint Q EDWsol i # representing the residual volume flow , is used. For the actual value is switched in the control unit 110 with connected and actuated power beyond consumer 74 from the path y EDW to the residual volume flow Q EDW .
• the advantage of the second exemplary embodiment consists in the direct measurement of the residual volume flow and the associated control of the pump regulator 8, which is more sensitive and precise compared to the first exemplary embodiment.
• a hydraulic control arrangement according to the third embodiment which is shown in FIGS. 5 and 6, differs from the hydraulic control arrangement according to the first embodiment. play in that now instead of the pilot control device 54, which causes a hydraulic actuation of the control piston 26, 40 of the directional control valves 24, 38, or a manual operation in the third embodiment, a joystick 254 is used by the output electrical signals, the operation of the control piston 26, 40 of the directional control valves 24, 38 takes place.
• the output signals of the joystick 254 are also supplied to the controller 210 so that, as shown in FIG. 6, in the controller 210, the controller 270 executes driving of the pump controller 8 on the basis of the operation of the joystick 254.
• a proportional pilot control of the pump 6 is possible, so that the control algorithm of the controller 270 for the position control of the inlet pressure compensator 60 only has to compensate for small deviations.
• the dynamic transmission characteristics of the hydraulic control assembly are improved.
• FIGs. 7 and 8 A hydraulic control arrangement according to the fourth embodiment is shown in Figs. 7 and 8.
• This hydraulic control arrangement differs from the hydraulic control arrangement of the second embodiment only in the use of the joystick 254, similar to the third embodiment. More precisely, in contrast to the second exemplary embodiment, the control unit 310 is now additionally supplied with the electrical output signals of the joystick 254, so that the control algorithm for the residual current control of the inlet pressure compensator 60 only has to compensate for small control deviations. As a result, similar to the third embodiment, the dynamic transmission characteristics of the hydraulic control device are improved.
• Figs. 9, 10 and 11 show fifth, sixth and seventh embodiments of the present invention.
• the bias of the spring 64 of the input pressure compensator 60 is changed mechanically (fifth embodiment), hydraulically (sixth embodiment) or electrically (seventh embodiment).
• the other hydraulic structure in the fifth, sixth and seventh embodiment corresponds to that of the first embodiment.
• the adjustment screw 490 When the power beyond consumer 74 is neither connected nor actuated, the adjustment screw 490 is in its rightmost position in FIG. 9, with the target position of the input pressure compensator being at position a. When the power beyond consumer 74 is connected and actuated, the adjusting screw 490 is in its left position in Fig. 9, with the position b of the control piston being the elevated bias position.
• a control piston 590 of an actuating cylinder 592 acts on the end remote from the control piston 62 end portion of the spring 64, a control piston 590 of an actuating cylinder 592, wherein a cylinder space of the actuating cylinder 592 via a switching valve 594 is pressurized to cause a movement of the control piston 62 in Fig. 10 to the left ,
• a spring 596 pushes the control piston of the switching valve 594 in a position in which the cylinder space of the actuating cylinder 592 is relieved to the tank, wherein the spring 64 has the lowest clamping.
• the cylinder chamber of the actuating cylinder 592 is supplied with pressure medium so that there builds a pressure through which the actuating piston 590 in Fig. 10 is moved to the left to additionally tension the spring 64.
• the actuating piston 590 In the rest position of the switching valve 594 and thus at unloaded cylinder space of the actuating cylinder 592 is the actuating piston 590 in its right position, wherein the position a of the input pressure compensator 60 is the target value.
• the adjusting piston 590 Upon pressurization of the cylinder space of the adjusting cylinder 592 via the switching valve 594, the adjusting piston 590 is brought to its left position in Fig. 10, wherein the position b of the input pressure compensator 60 is the desired position.
• an electric servomotor 690 is provided on which a threaded shaft 692 is provided.
• the opposite to the control piston 62 of the input pressure compensator 60 end portion of the spring 64 is changeable in its position by actuation of the servomotor 690.
• the position b of the inlet pressure compensator 60 is preset as the target position when the threaded shaft 692 is unscrewed to the servomotor 690.
• the position a of the control piston 62 of the inlet pressure compensator 60 is predetermined.
• the fifth, sixth and seventh embodiments have in common that with the use of only one spring an increase in the control pressure difference by increasing the spring preload can be realized. Therefore, conventional electronic control devices for the control unit 10 can be used, whereby only a small mechanical, electrical or hydraulic modifications necessary. _
• an additional spring 764 is activated in addition to the spring 64 in the eighth embodiment, starting from a predetermined displacement path of the control piston 62.
• FIG. 13 shows by way of example a structural design for the connection of the additional spring 764.
• the end portion of the control piston 62 of the inlet pressure compensator 60 opens and is held in a cylinder bore by means of the retaining ring 702.
• the spring 64 is likewise supported on this retaining ring 702, the opposite end section of which is supported on the spring housing 700 via a spring retaining means 704.
• a support rod 706 is provided which is fixed in the spring housing 700, for example via retaining rings.
• a spring plate 708 is slidably received, on which an end portion of the auxiliary spring 764 is supported.
• the opposite end portion of the auxiliary spring 764 is supported on the Federhaittation 704 from.
• the control piston 62 After covering a predetermined path, the control piston 62 runs on the spring plate 708. In a further movement of the control piston 62 to the right in Fig. 13, the spring plate 708 is taken from the control piston 62, wherein a compression of the auxiliary spring 764 is effected on the piston rod 106, so that both springs 64, 764 are effective. When the control piston 62 runs onto the support rod 706, further movement of the control piston 62 in FIG. 13 to the right is prevented.
• FIG. 14 shows an exemplary characteristic curve of the input pressure compensator 60 with pressure increase.
• the pressure difference of the inlet pressure compensator is plotted against the valve position or the control position. From this characteristic it can be seen that, starting from a certain valve position / control position, the pressure difference increases from the value ⁇ p EDW1 to the value ⁇ p EDW2 .
• a power beyond consumer 74 can be prioritized to maintain the function.
• an electronically, hydraulically or mechanically triggered increase in the pressure level takes place only when the power beyond consumer is activated.
• needs-based and energy-saving supply of all active consumers 2, 4, 74 is possible.
• the present invention is not limited to the fact that the consumers 2, 4 are connected in parallel, but the inlet pressure compensator can also be connected upstream of only one of the consumers 2, 4. In this case, the other consumer is directly connected to the pressure port of the pump and thus hydraulically prioritized.

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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)

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• 2006
  • 2006-02-23 DE DE102006008940A patent/DE102006008940A1/de not_active Withdrawn
• 2007
  • 2007-01-17 WO PCT/EP2007/000352 patent/WO2007096030A1/fr active Application Filing
  • 2007-01-17 AT AT07702809T patent/ATE467769T1/de active
  • 2007-01-17 DE DE502007003725T patent/DE502007003725D1/de active Active
  • 2007-01-17 EP EP07702809A patent/EP1989450B1/fr not_active Not-in-force
  • 2007-01-17 US US12/280,092 patent/US8286544B2/en not_active Expired - Fee Related

Non-Patent Citations (1)

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