EP1711714A1 - Circuit arrangement - Google Patents

Circuit arrangement

Info

Publication number
EP1711714A1
EP1711714A1 EP04801211A EP04801211A EP1711714A1 EP 1711714 A1 EP1711714 A1 EP 1711714A1 EP 04801211 A EP04801211 A EP 04801211A EP 04801211 A EP04801211 A EP 04801211A EP 1711714 A1 EP1711714 A1 EP 1711714A1
Authority
EP
European Patent Office
Prior art keywords
section
pressure
series
parallel
circuit arrangement
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
EP04801211A
Other languages
German (de)
French (fr)
Other versions
EP1711714B1 (en
Inventor
Gerd Anton Thiry
Alois Hoffmann
Harald BÄR
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP1711714A1 publication Critical patent/EP1711714A1/en
Application granted granted Critical
Publication of EP1711714B1 publication Critical patent/EP1711714B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—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
    • 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
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—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
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • 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
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • 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
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot 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
    • F15B2211/60—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
    • F15B2211/70—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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • 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 circuit arrangement with a load-sensing system in which individual consumers are arranged both in series to form a series section and in parallel to form a parallel section in a hydraulic supply circuit with at least one supply pump and a return line for fluid, wherein the load sensing system determines the highest load pressure in each case in the row and parallel section.
  • load pressure - signaling system is also used as a synonym for load-sensing system, with the system mentioned being a hydraulic control system with pressure and volume flow adjustment, to meet the current requirements of one or more consumers.
  • load-sensing systems which are common on the market, can be implemented with a constant pump as well as with a variable displacement pump.
  • the respective consumers can in principle be arranged in series and / or parallel to one another in the supply circuit.
  • the same liquid flow flows through the consumers and the pressures add up.
  • the return flow of one consumer forms the inflow of the next consumer, so that each consumer has the entire volume flow available in succession.
  • the series connection is used in particular where there are consumers with low load pressures.
  • the speed of the consumers is preferably regulated independently of the load pressure by means of a proportional flow controller consisting of a proportional throttle valve and a bypass pressure compensator.
  • a proportional flow controller consisting of a proportional throttle valve and a bypass pressure compensator.
  • Load pressure is determined and the pump pressure is raised by a certain amount above this load pressure, for example by means of a rotary pressure compensator.
  • a rotary pressure compensator In a system that consists of a combination of parallel and series connection described above, however, no higher pressure can be built up than is required for the series connection section, since there the excess fluid (oil) via the bypass pressure compensators Tank is led. This is particularly undesirable if higher pressures are required in the parallel section, for example, for the function to be able to ensure a work machine and its parts.
  • the object of the invention is to further improve the known circuit arrangements with a load-sensing system, while maintaining the advantages, in such a way that consumers of the parallel section can be actuated independently of the pressure level of the consumers of the row section and that in the parallel section for the consumers there are higher pressures available if they are needed.
  • a related problem is solved by a circuit arrangement with the features of claim 1 in its entirety.
  • the respective highest load pressure is passed as a control pressure to a valve unit such that, if the load pressure of the parallel section is higher than the load pressure of the row section, the valve unit throttles the return flow for fluid until the If the pressure of the supply pump rises to or above the pressure required in the parallel section, it is ensured that the consumers of the parallel section can be actuated independently of the pressure level of the consumers of the row section. In this respect, it is also possible to ensure sufficient fluid pressure for the respective consumer in the parallel section, regardless of the number of consumers in the row section.
  • the circuit arrangement mentioned is energy-saving, since the pump pressure is only increased to the extent necessary depending on the load pressure.
  • the valve unit consists of a hydraulically controllable proportional slide valve, preferably a 2-V valve. Proportional slide valve formed. Due to the proportional slide valve, it is possible to raise the pump pressure of the supply pump only as far as necessary, which benefits the energy-saving operation of the overall system and thus the circuit arrangement.
  • a circulating pressure compensator is connected in the supply circuit between the supply pump and the return, to which the highest load pressure is applied overall. If no consumer is active or is required, the fluid (oil) can be returned to the tank with low pressure loss via the circulating pressure compensator, which in turn benefits energy-saving operation.
  • circuit arrangement according to the invention is explained in more detail using an exemplary embodiment according to the drawing.
  • the only figure in the manner of a circuit diagram shows the essential components of the circuit arrangement according to the invention.
  • the circuit arrangement according to the invention is equipped with a load-sensing system, which is designated LS in the circuit diagram.
  • the circuit arrangement is further characterized in that individual consumers 10 are arranged one behind the other as row consumers of a row section in the fluid flow direction.
  • a parallel consumer 14 is connected in the hydraulic supply circuit 12.
  • the row consumers 10 are formed from individual hydraulic motors and the parallel consumer 14 from a conventional hydraulic working cylinder.
  • the hydraulic supply circuit 12 ends at its free ends in a supply pump P and in a tank T.
  • the line of the supply circuit 12 connected to the tank T forms the so-called return 16 of the circuit arrangement.
  • the load-sensing system LS it is possible to determine the highest load pressure in each case in the series and parallel sections, which is shown in the circuit diagram with the LS series and LS parallel.
  • the highest load pressure in each case is passed on as control pressure to a valve unit 18 for actuation thereof.
  • the valve unit is referenced 18 in the return line 16 so strongly throttled for fluid until the pressure of the supply pump P is at or above 'the pressure required for this consumer 14 increases in the parallel section. It is thus possible to operate the parallel consumer 14 independently of the pressure level of the series consumer 10 and to control it in such a way, which was not possible with the previously known circuit arrangements with a load-sensing system.
  • the series or parallel section consists of at least one consumer 10, 14, preferably two series 10 consumers of the series section being arranged in the fluid flow direction before the parallel section with a parallel consumer 14.
  • the above-mentioned valve unit 18, which the control processed by the load-sensing system, consists of a hydraulically controllable proportional slide valve, preferably a 2-way proportional slide valve.
  • a bypass pressure compensator 20, 22 is assigned to each consumer 10 of the row section.
  • One control pressure line for the valve unit 18 is connected to a shuttle valve 24 of the series section and the other control pressure line to a shuttle valve 26 of the parallel section and to a shuttle valve 28 of the load-sensing system LS. How the interconnection is carried out in detail follows directly from the circuit arrangement according to the figure. Furthermore, the control inputs of the respective bypass pressure compensators 20, 22 of the series section are each connected to the assigned output of the shuttle valve 24 assigned to the series section. As can further be seen from the circuit diagram, the output of the pressure compensator 20 is connected in a fluid-carrying manner to the input of the pressure compensator 22 and the output of the pressure compensator 22 opens into the return line 16, which is connected on the input side to the valve unit 18.
  • the connection of the first consumer 10 to the supply circuit 12 takes place in a branch to the row section, the supply in question being able to be shut off via a proportional throttle valve 30.
  • the output of the first consumer 10 in series opens onto the input side of a further proportional throttle valve 32, to which the second consumer 10 is connected on the output side.
  • the respective outlet of the consumer 10 is secured by a check valve 34.
  • the input of the proportional throttle valve 32 is connected in a fluid-carrying manner to the connecting line 36 between the two pressure compensators 20, 22.
  • the fluid pressure at the outlet side of the two proportional throttle valves 30, 32 is supplied as a control pressure both to the one side of the pressure compensators 20, 22 and to the shuttle valve 24.
  • the fluid pressure on the input side is applied to the pressure compensators 20, 22 mentioned.
  • a circulation pressure compensator 38 is connected between the supply pump P and the return 16 in the supply circuit 12.
  • the control pressures for this circulation pressure compensator 38 are in turn formed on the one hand by the load-sensing system LS and on the other hand by the input pressure at the pressure compensator 38 itself.
  • the outlet of the pressure compensator 38 is fluid-carrying with the return 16 connected and the inlet side to the supply pump P.
  • the relevant pump supply pressure is also present via line 40 at the inlet of a 4/3-way valve 42.
  • the load-sensing system LS is protected by a pressure limiting valve 44 and is connected to the entire LS side of the shuttle valve 28 via a throttle or orifice 46.
  • the outlet side of the 4/3-way valve 42 opens into the parallel valve 26 in two parallel lines and into two mutually unlockable check valves 48, which in turn are connected on the outlet side to the piston and rod chamber of the working cylinder as parallel consumers 14.
  • the consumers 10, 14 are arranged both in series and in parallel to one another. As explained, all rows of consumers 10 are equipped with a bypass pressure compensator 20, 22. The highest load pressure in each case in the row section and the parallel section are determined separately from one another and as control pressures, as described, to a hydraulically controlled first 2-way proportional slide valve 18 reported. If the pressure of the parallel consumers 14 is higher than that of the series consumers 10, this valve 18 throttles the return line 16 of the series section until the pump pressure of the supply pump P rises above the pressure required in the parallel section. The overall highest load pressure is always on the circulating pressure compensator 38. The circuit arrangement mentioned is energy-saving, since the pump pressure is only raised as far as required, depending on the load pressure. The advantages can be summarized as follows:
  • Parallel consumers 14 can be actuated independently of the pressure level of the series consumers 10, the pump pressure of the supply pump P is raised by the 2-way proportional slide valve 18 only as far as required - if no consumer 10, 14 is active, the fluid becomes over with a low pressure loss the circulation pressure compensator 38 led to the tank T.

Abstract

A circuit arrangement includes a load sensing system (LS) with individual loads ( 10,14 ) arranged in series forming a series section, and in parallel forming a parallel section. A hydraulic supply circuit ( 12 ) includes a supply pump (P) and a runback ( 16 ) for fluid. The load sensing system (LS) determines the highest load pressure in the series section and the parallel section. The loads of the parallel section can be actuated independently from the pressure level of the loads of the series section due to the highest load pressure being transferred as a control pressure to a valve unit ( 18 ) such that, as long as the load pressure of the parallel section is higher than the load pressure of the series section, the valve unit restricts the runback ( 16 ) so that the pressure of the supply pump (P) matches or exceeds the pressure required in the parallel section. Sufficient fluid pressure for the load in the parallel section is ensured independently of the number of loads in the series section.

Description

Schaltungsanordnung circuitry
Die Erfindung betrifft eine Schaltungsanordnung mit einem Load-Sensing- System, bei der einzelne Verbraucher sowohl in Reihe unter Bildung einer Reihensektion als auch parallel unter Bildung einer Parallelsektion zueinander angeordnet in einen hydraulischen Versorgungskreis mit mindestens einer Versorgungspumpe und einem Rücklauf für Fluid geschaltet sind, wobei das Load-Sensing-System den jeweils höchsten Lastdruck bei der Reihen- und Parallelsektion ermittelt.The invention relates to a circuit arrangement with a load-sensing system in which individual consumers are arranged both in series to form a series section and in parallel to form a parallel section in a hydraulic supply circuit with at least one supply pump and a return line for fluid, wherein the load sensing system determines the highest load pressure in each case in the row and parallel section.
Als Synonym für Load-Sensing-System findet auch der Begriff Lastdruck - Meldesystem Anwendung, wobei es sich bei dem genannten System um ein hydraulisches Steuerungssystem mit Druck- und Volumenstromanpassung handelt, und zwar an die momentanen Anforderungen eines oder mehrerer Verbraucher. Dahingehende Load-Sensing-Systeme, die marktüblich sind, lassen sich sowohl mit einer Konstantpumpe als auch mit einer Verstell- pumpe realisieren.The term load pressure - signaling system is also used as a synonym for load-sensing system, with the system mentioned being a hydraulic control system with pressure and volume flow adjustment, to meet the current requirements of one or more consumers. Such load-sensing systems, which are common on the market, can be implemented with a constant pump as well as with a variable displacement pump.
Ferner können in hydraulischen Systemen und Steuerungen die jeweiligen Verbraucher prinzipiell in Reihe und/oder parallel zueinander im Versorgungskreis angeordnet sein. Bei der üblichen Reihenschaltung werden die Verbraucher vom gleichen Flüssigkeitsstrom durchflössen und die Drücke addieren sich. Der Rücklauf des einen Verbrauchers bildet den Zulauf des nächsten Verbrauchers, so dass jedem Verbraucher der gesamte Volumenstrom in Hintereinanderab- folge zur Verfügung steht. Die Reihenschaltung kommt insbesondere dort zur Anwendung, wo Verbraucher mit geringen Lastdrücken vorhanden sind.Furthermore, in hydraulic systems and controls, the respective consumers can in principle be arranged in series and / or parallel to one another in the supply circuit. In the usual series connection, the same liquid flow flows through the consumers and the pressures add up. The return flow of one consumer forms the inflow of the next consumer, so that each consumer has the entire volume flow available in succession. The series connection is used in particular where there are consumers with low load pressures.
Die Geschwindigkeit der Verbraucher wird vorzugsweise über Proportionalstromregler, bestehend aus Proportional-Drosselventil und Bypass- Druckwaage, lastdruckunabhängig geregelt. Bei dieser Anordnung können die Geschwindigkeiten beider Verbraucher unabhängig voneinander eingestellt werden, was für eine Vielzahl von Anwendungsfällen sinnvoll ist.The speed of the consumers is preferably regulated independently of the load pressure by means of a proportional flow controller consisting of a proportional throttle valve and a bypass pressure compensator. With this arrangement, the speeds of both consumers can be set independently of one another, which is useful for a large number of applications.
Parallel geschaltete Verbraucher unterliegen hingegen alle dem gleichen Eingangsdruck und die Volumenströme addieren sich. Um alle Verbraucher gleichzeitig mit maximaler Geschwindigkeit zu betreiben, muß die Versorgungspumpe dann entsprechend groß dimensioniert sein, was bei der Reihenschaltung, wie dargelegt, nicht notwendig ist.However, consumers connected in parallel are all subject to the same inlet pressure and the volume flows add up. In order to operate all consumers at maximum speed at the same time, the supply pump must then be of a correspondingly large size, which is not necessary for the series connection, as explained.
In einem Load-Sensing-System der genannten Art wird der höchsteIn a load-sensing system of the type mentioned, the highest
Lastdruck ermittelt und der Pumpendruck um einen bestimmten Betrag über diesen Lastdruck angehoben, beispielsweise mittels einer Umlauf- Druckwaage. In einem System, das aus einer Kombination aus Parallel- und oben beschriebener Reihenschaltung besteht, kann sich jedoch kein höhe- rer Druck aufbauen, als für die Reihenschaltungs-Sektion erforderlich ist, da dort das überschüssige Fluid (Öl) über die Bypass-Druckwaagen zum Tank geführt wird. Dies ist insbesondere dann unerwünscht, wenn in der Parallelsektion höhere Drücke benötigt werden, beispielsweise um die Funktion einer Arbeitsmaschine und deren Teile dahingehend sicherstellen zu können.Load pressure is determined and the pump pressure is raised by a certain amount above this load pressure, for example by means of a rotary pressure compensator. In a system that consists of a combination of parallel and series connection described above, however, no higher pressure can be built up than is required for the series connection section, since there the excess fluid (oil) via the bypass pressure compensators Tank is led. This is particularly undesirable if higher pressures are required in the parallel section, for example, for the function to be able to ensure a work machine and its parts.
Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, unter Beibehalten der Vorteile die bekannten Schaltungsanordnungen mit Load-Sensing-System dahingehend weiter zu verbessern, dass Verbraucher der Parallelsektion unabhängig vom Druckniveau der Verbraucher der Reihensektion betätigbar sind und dass in der Parallelsektion für die dortigen Verbraucher höhere Drücke zur Verfügung stehen, sofern diese benötigt werden. Eine dahingehende Aufgabe löst eine Schaltungsanordnung mit den Merkmalen des Patentanspruches 1 in seiner Gesamtheit.Based on this prior art, the object of the invention is to further improve the known circuit arrangements with a load-sensing system, while maintaining the advantages, in such a way that consumers of the parallel section can be actuated independently of the pressure level of the consumers of the row section and that in the parallel section for the consumers there are higher pressures available if they are needed. A related problem is solved by a circuit arrangement with the features of claim 1 in its entirety.
Dadurch, dass gemäß dem kennzeichnenden Teil des Patentanspruches 1 der jeweils höchste Lastdruck als Steuerdruck an eine Ventileinheit derart weitergeleitet ist, dass, sofern der Lastdruck der Parallelsektion höher liegt als der Lastdruck der Reihensektion, die Ventileinheit den Rücklauf für Fluid so stark androsselt, bis der Druck der Versorgungspumpe auf oder über den in der Parallelsektion benötigten Druck ansteigt, ist gewährleistet, dass die Verbraucher der Parallelsektion unabhängig vom Druckniveau der Verbrau- eher der Reihensektion betätigbar sind. Insoweit ist es auch möglich, unabhängig von der Anzahl der Verbraucher in der Reihensektion genügend Fluiddruck für den jeweiligen Verbraucher in der Parallelsektion sicherzustellen. Die genannte Schaltungsanordnung arbeitet energiesparend, da der Pumpendruck lastdruckabhängig immer nur insoweit angehoben wird, wie erforderlich.Characterized in that according to the characterizing part of claim 1, the respective highest load pressure is passed as a control pressure to a valve unit such that, if the load pressure of the parallel section is higher than the load pressure of the row section, the valve unit throttles the return flow for fluid until the If the pressure of the supply pump rises to or above the pressure required in the parallel section, it is ensured that the consumers of the parallel section can be actuated independently of the pressure level of the consumers of the row section. In this respect, it is also possible to ensure sufficient fluid pressure for the respective consumer in the parallel section, regardless of the number of consumers in the row section. The circuit arrangement mentioned is energy-saving, since the pump pressure is only increased to the extent necessary depending on the load pressure.
Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Schaltungsanordnung ist die Ventileinheit aus einem hydraulisch steuerbaren Proportionalschieberventil, vorzugsweise einem 2-VVege- Proportionalschieberventil gebildet. Aufgrund des Proportionalschieberventils ist es möglich, den Pumpendruck der Versorgungspumpe nur so weit anzuheben, wie erforderlich, was dem energiesparenden Betrieb des Gesamtsystems und somit der Schaltungsanordnung zugute kommt.In a preferred embodiment of the circuit arrangement according to the invention, the valve unit consists of a hydraulically controllable proportional slide valve, preferably a 2-V valve. Proportional slide valve formed. Due to the proportional slide valve, it is possible to raise the pump pressure of the supply pump only as far as necessary, which benefits the energy-saving operation of the overall system and thus the circuit arrangement.
Bei einer weiteren bevorzugten Ausführungsform der erfindungsgemäßen Schaltungsanordnung ist zwischen der Versorgungspumpe und dem Rücklauf eine Umlauf-Druckwaage in den Versorgungskreislauf geschaltet, an der insgesamt der höchste Lastdruck anliegt. Wenn somit kein Verbraucher aktiv ist oder benötigt wird, kann das Fluid (Öl) mit geringem Druckverlust über die Umlauf-Druckwaage zum Tank rückgeführt werden, was wiederum einem energiesparenden Betrieb zugute kommt.In a further preferred embodiment of the circuit arrangement according to the invention, a circulating pressure compensator is connected in the supply circuit between the supply pump and the return, to which the highest load pressure is applied overall. If no consumer is active or is required, the fluid (oil) can be returned to the tank with low pressure loss via the circulating pressure compensator, which in turn benefits energy-saving operation.
Weitere vorteilhafte Ausführungsformen sind Gegenstand der sonstigen Un- teransprüche.Further advantageous embodiments are the subject of the other subclaims.
Im folgenden wird die erfindungsgemäße Schaltungsanordnung anhand eines Ausführungsbeispiels nach der Zeichnung näher erläutert. Dabei zeigt die einzige Figur in der Art einer Schaltplandarstellung die wesentlichen Komponenten der erfindungsgemäßen Schaltungsanordnung.In the following the circuit arrangement according to the invention is explained in more detail using an exemplary embodiment according to the drawing. The only figure in the manner of a circuit diagram shows the essential components of the circuit arrangement according to the invention.
Die erfindungsgemäße Schaltungsanordnung ist mit einem Load-Sensing- System ausgestattet, das in dem Schaltplan mit LS bezeichnet ist. Die Schal- tungsanordnung ist des weiteren dadurch charakterisiert, dass einzelne Verbraucher 10 als Reihenverbraucher einer Reihensektion in Fluidströmungs- richtung hintereinander angeordnet sind. Neben den Reihenverbrauchern 10 und parallel zu diesen sowie unter Bildung einer Parallelsektion ist in den hydraulischen Versorgungskreis 12 ein Parallelverbraucher 14 geschal- tet. Die Reihenverbraucher 10 sind aus einzelnen hydraulischen Motoren gebildet und der Parallelverbraucher 14 aus einem üblichen hydraulisch arbeitenden Arbeitszylinder. Der genannte hydraulische Versorgungskreis 12 mündet an seinen freien Enden in eine Versorgungspumpe P sowie in einen Tank T. Die an den Tank T angeschlossene Leitung des Versorgungskreises 12 bildet den sog. Rücklauf 16 der Schaltungsanordnung.The circuit arrangement according to the invention is equipped with a load-sensing system, which is designated LS in the circuit diagram. The circuit arrangement is further characterized in that individual consumers 10 are arranged one behind the other as row consumers of a row section in the fluid flow direction. In addition to the row consumers 10 and parallel to them and with the formation of a parallel section, a parallel consumer 14 is connected in the hydraulic supply circuit 12. tet. The row consumers 10 are formed from individual hydraulic motors and the parallel consumer 14 from a conventional hydraulic working cylinder. The hydraulic supply circuit 12 ends at its free ends in a supply pump P and in a tank T. The line of the supply circuit 12 connected to the tank T forms the so-called return 16 of the circuit arrangement.
Mittels des Load-Sensing-Systems LS ist es möglich, den jeweils höchsten Lastdruck bei der Reihen- und der Parallelsektion zu ermitteln, was in dem Schaltplan mit LS-Reihe und LS-Parallel wiedergegeben ist. Der jeweils höchste Lastdruck, sei es von der Reihen- oder der Parallelsektion, wird als Steuerdruck an eine Ventileinheit 18 zu deren Ansteuerung weitergeleitet. Liegt dann beispielsweise der Lastdruck der Parallelsektion mit den Parallelverbrauchern 14 höher als der Lastdruck der Reihensektion mit den Rei- henverbrauchern 10, wird die Ventileinheit 18 bezogen auf den Rücklauf 16 für Fluid so stark angedrosselt, bis der Druck der Versorgungspumpe P auf oder über'den in der Parallelsektion benötigten Druck für diesen Verbraucher 14 ansteigt. Somit ist es möglich, den Parallel Verbraucher 14 unabhängig vom Druckniveau der Reihenverbraucher 10 zu betätigen und dergestalt anzusteuern, was mit den bisher bekannten Schaltungsanordnungen mit Load-Sensing-System nicht möglich war.Using the load-sensing system LS, it is possible to determine the highest load pressure in each case in the series and parallel sections, which is shown in the circuit diagram with the LS series and LS parallel. The highest load pressure in each case, be it from the series section or the parallel section, is passed on as control pressure to a valve unit 18 for actuation thereof. Then is, for example, the load pressure of the parallel section of the parallel loads 14 is higher than the load pressure of the series section with the tire henverbrauchern 10, the valve unit is referenced 18 in the return line 16 so strongly throttled for fluid until the pressure of the supply pump P is at or above 'the pressure required for this consumer 14 increases in the parallel section. It is thus possible to operate the parallel consumer 14 independently of the pressure level of the series consumer 10 and to control it in such a way, which was not possible with the previously known circuit arrangements with a load-sensing system.
Die Reihen- oder Parallelsektion besteht mindestens aus einem Verbraucher 10,14, wobei vorzugsweise zwei in Reihe geschaltete Verbraucher 10 der Reihensektion in Fluidströmungsrichtung vor der Parallelsektion mit einem Parallel Verbraucher 14 angeordnet sind. Es sind hier aber auch andere Verbrauchergestaltungen denkbar, beispielsweise nur ein Verbraucher 10 für die Reihensektion und zwei oder mehr Verbraucher für die Parallelsektion (nicht dargestellt). Die vorstehend erwähnte Ventileinheit 18, die die Steu- erdrücke des Load-Sensing-Systems verarbeitet, besteht aus einem hydraulisch steuerbaren Proportionalschieberventil, vorzugsweise aus einem 2- Wege-Proportionalschieberventil. Des weiteren ist jedem Verbraucher 10 der Reihensektion eine Bypass-Druckwaage 20,22 zugeordnet.The series or parallel section consists of at least one consumer 10, 14, preferably two series 10 consumers of the series section being arranged in the fluid flow direction before the parallel section with a parallel consumer 14. However, other consumer designs are also conceivable here, for example only one consumer 10 for the row section and two or more consumers for the parallel section (not shown). The above-mentioned valve unit 18, which the control processed by the load-sensing system, consists of a hydraulically controllable proportional slide valve, preferably a 2-way proportional slide valve. Furthermore, a bypass pressure compensator 20, 22 is assigned to each consumer 10 of the row section.
Die eine Steuerdruckleitung für die Ventileinheit 18 ist an ein Wechselventil 24 der Reihensektion angeschlossen und die andere Steuerdruckleitung an ein Wechselventil 26 der Parallelsektion sowie an ein Wechselventil 28 des Load-Sensing-Systems LS. Wie die Verschaltung im einzelnen vorge- nommen ist, ergibt sich unmittelbar aus der Schaltungsanordnung nach der Figur. Ferner sind die Steuereingänge der jeweiligen Bypass-Druckwaagen 20,22 der Reihensektion jeweils an den zugeordneten Ausgang des der Reihensektion zugeordneten Wechselventils 24 angeschlossen. Wie sich des weiteren aus der Schaltplandarstellung ergibt, ist der Ausgang der Druckwaage 20 fluidführend mit dem Eingang der Druckwaage 22 verbunden und der Ausgang der Druckwaage 22 mündet in die Rücklaufleitung 16, die eingangsseitig an die Ventileinheit 18 angeschlossen ist.One control pressure line for the valve unit 18 is connected to a shuttle valve 24 of the series section and the other control pressure line to a shuttle valve 26 of the parallel section and to a shuttle valve 28 of the load-sensing system LS. How the interconnection is carried out in detail follows directly from the circuit arrangement according to the figure. Furthermore, the control inputs of the respective bypass pressure compensators 20, 22 of the series section are each connected to the assigned output of the shuttle valve 24 assigned to the series section. As can further be seen from the circuit diagram, the output of the pressure compensator 20 is connected in a fluid-carrying manner to the input of the pressure compensator 22 and the output of the pressure compensator 22 opens into the return line 16, which is connected on the input side to the valve unit 18.
In Fluidströmungsrichtung vor der Druckwaage 20 erfolgt in einem Ab- zweig zu der Reihensektion der Anschluß des ersten Verbrauchers 10 an den Versorgungskreis 12, wobei die dahingehende Versorgung über ein Proportional-Drosselventil 30 absperrbar ist. Der Ausgang des in Reihe ersten Verbrauchers 10 mündet auf die Eingangsseite eines weiteren Propor- tional-Drosselventils 32, an den der zweite Verbraucher 10 ausgangsseitig angeschlossen ist. Der jeweilige Ausgang des Verbrauchers 10 ist über ein Rückschlagventil 34 abgesichert. Des weiteren ist der Eingang des Propor- tional-Drosselventils 32 fluidführend an die Verbindungsleitung 36 zwischen den beiden Druckwaagen 20,22 angeschlossen. Der anstehende Fluiddruck an der Ausgangsseite der beiden Proportional-Drosselventile 30,32 wird als Steuerdruck sowohl auf die jeweils einen Seiten der Druckwaagen 20,22 geführt als auch zum Wechselventil 24. Auf der gegenüberliegenden Seite der Druckwaagen 20,22 liegt als Steuerdruck der eingangs- seitige Fluiddruck bei den genannten Druckwaagen 20,22 an.In the branch of fluid flow upstream of the pressure compensator 20, the connection of the first consumer 10 to the supply circuit 12 takes place in a branch to the row section, the supply in question being able to be shut off via a proportional throttle valve 30. The output of the first consumer 10 in series opens onto the input side of a further proportional throttle valve 32, to which the second consumer 10 is connected on the output side. The respective outlet of the consumer 10 is secured by a check valve 34. Furthermore, the input of the proportional throttle valve 32 is connected in a fluid-carrying manner to the connecting line 36 between the two pressure compensators 20, 22. The fluid pressure at the outlet side of the two proportional throttle valves 30, 32 is supplied as a control pressure both to the one side of the pressure compensators 20, 22 and to the shuttle valve 24. On the opposite side of the pressure compensators 20, 22, the fluid pressure on the input side is applied to the pressure compensators 20, 22 mentioned.
Zwischen der Versorgungspumpe P und dem Rücklauf 16 ist in den Versorgungskreis 12 eine Umlauf-Druckwaage 38 geschaltet. Die Steuerdrücke für diese Umlauf-Druckwaage 38 sind wiederum auf der einen Seite über das Load-Sensing-System LS gebildet und auf der anderen Seite über den Ein- gangsdruck an der Druckwaage 38 selbst. Der Ausgang der Druckwaage 38 ist fluidführend mit dem Rücklauf 16 verbunden und die Eiήgangsseite mit der Versorgungspumpe P. Der dahingehende Pumpenversorgungsdruck steht auch über die Leitung 40 am Eingang eines 4/3-Wege-Ventils 42 an. Das Load-Sensing-System LS ist über ein Druckbegrenzungsventil 44 abge- sichert und ist über eine Drossel oder Blende 46 mit der LS - Gesamtseite des Wechselventils 28 verbunden.A circulation pressure compensator 38 is connected between the supply pump P and the return 16 in the supply circuit 12. The control pressures for this circulation pressure compensator 38 are in turn formed on the one hand by the load-sensing system LS and on the other hand by the input pressure at the pressure compensator 38 itself. The outlet of the pressure compensator 38 is fluid-carrying with the return 16 connected and the inlet side to the supply pump P. The relevant pump supply pressure is also present via line 40 at the inlet of a 4/3-way valve 42. The load-sensing system LS is protected by a pressure limiting valve 44 and is connected to the entire LS side of the shuttle valve 28 via a throttle or orifice 46.
Die Ausgangsseite des ,4/3-Wege-Ventils 42 mündet in zwei parallelen Strängen in das Wechselventil 26 ein sowie in zwei gegenseitig entsperrba- re Rückschlagventile 48, die ausgangsseitig wiederum an dem Kolben- und Stangenraum des Arbeitszylinders als Parallelverbraucher 14 angeschlossen sind.The outlet side of the 4/3-way valve 42 opens into the parallel valve 26 in two parallel lines and into two mutually unlockable check valves 48, which in turn are connected on the outlet side to the piston and rod chamber of the working cylinder as parallel consumers 14.
Mit der erfindungsgemäßen Ventilanordnung mit einem Load-Sensing- System sind die Verbraucher 10,14 sowohl in Reihe als auch parallel zueinander angeordnet. Alle Reihen Verbraucher 10 sind, wie dargelegt, mit einer Bypass-Druckwaage 20,22 ausgestattet. Der jeweils höchste Lastdruck in der Reihensektion und der Parallelsektion werden getrennt voneinander ermittelt und als Steuerdrücke, wie beschrieben, an ein hydraulisch gesteu- ertes 2-Wege-Proportionalschieberventil 18 gemeldet. Liegt der Druck der Parallelverbraucher 14 über dem der Reihenverbraucher 10, so drosselt dieses Ventil 18 den Rücklauf 16 der Reihensektion so stark an, bis der Pumpendruck der Versorgungspumpe P über den in der Parallelsektion benötigten Druck ansteigt. Der insgesamt höchste Lastdruck liegt dabei immer an der Umlauf-Druckwaage 38 an. Die genannte Schaltungsanordnung arbeitet energiesparend, da der Pumpendruck lastdruckabhängig immer nur so weit angehoben wird, wie erforderlich. Zusammenfassend lassen sich die Vorteile wie folgt beschreiben:With the valve arrangement according to the invention with a load-sensing system, the consumers 10, 14 are arranged both in series and in parallel to one another. As explained, all rows of consumers 10 are equipped with a bypass pressure compensator 20, 22. The highest load pressure in each case in the row section and the parallel section are determined separately from one another and as control pressures, as described, to a hydraulically controlled first 2-way proportional slide valve 18 reported. If the pressure of the parallel consumers 14 is higher than that of the series consumers 10, this valve 18 throttles the return line 16 of the series section until the pump pressure of the supply pump P rises above the pressure required in the parallel section. The overall highest load pressure is always on the circulating pressure compensator 38. The circuit arrangement mentioned is energy-saving, since the pump pressure is only raised as far as required, depending on the load pressure. The advantages can be summarized as follows:
Parallelverbraucher 14 können unabhängig vom Druckniveau der Reihenverbraucher 10 betätigt werden, der Pumpendruck der Versorgungspumpe P wird durch das 2-Wege- Proportionalschieberventil 18 nur so weit angehoben wie erforderlich, - wenn kein Verbraucher 10,14 aktiv ist, wird das Fluid mit geringem Druckverlust über die Umlauf-Druckwaage 38 zum Tank T geführt. Parallel consumers 14 can be actuated independently of the pressure level of the series consumers 10, the pump pressure of the supply pump P is raised by the 2-way proportional slide valve 18 only as far as required - if no consumer 10, 14 is active, the fluid becomes over with a low pressure loss the circulation pressure compensator 38 led to the tank T.

Claims

P a t e n t a n s p r ü c h e Patent claims
1 . Schaltungsanordnung mit einem Load-Sensing-System (LS), bei der einzelne Verbraucher (10,14) sowohl in Reihe unter Bildung einer Reihen- Sektion als auch parallel unter Bildung einer Parallelsektion zueinander angeordnet in einen hydraulischen Versorgungskreis (12) mit mindestens einer Versorgungspumpe (P) und einem Rücklauf (16) für Fluid geschaltet sind, wobei das Load-Sensing-System (LS) den jeweils höchsten Lastdruck bei der Reihen- und Parallelsektion ermittelt, dadurch ge- kennzeichnet, dass der jeweils höchste Lastdruck als Steuerdruck an eine Ventileinheit (18) derart weitergeleitet ist, dass, sofern der Lastdruck der Parallelsektion höher liegt als der Lastdruck der Reihensektion, die Ventileinheit den Rücklauf (16) für Fluid so stark androsselt, bis der Druck der Versorgungspumpe (P) auf oder über den in der Parallelsekti- on benötigten Druck ansteigt.1 . Circuit arrangement with a load-sensing system (LS), in which individual consumers (10, 14) are arranged in a hydraulic supply circuit (12) with at least one supply pump both in series with the formation of a series section and in parallel with the formation of a parallel section (P) and a return line (16) for fluid, the load-sensing system (LS) determining the highest load pressure in each case in the series and parallel section, characterized in that the highest load pressure in each case as a control pressure to one Valve unit (18) is forwarded in such a way that if the load pressure of the parallel section is higher than the load pressure of the row section, the valve unit throttles the return (16) for fluid until the pressure of the supply pump (P) is at or above that in the Parallel section required pressure increases.
2. Schaltungsanordnung nach Anspruch 1 , dadurch gekennzeichnet, dass die Reihen- oder die Parallelsektion mindestens aus einem Verbraucher (10,14) besteht und dass vorzugsweise zwei in Reihe geschaltete Ver- braucher (10) der Reihensektion in Fluidströmungsrichtung vor der Parallelsektion mit einem Parallelverbraucher (14) angeordnet sind.2. Circuit arrangement according to claim 1, characterized in that the series or parallel section consists of at least one consumer (10, 14) and that preferably two series consumers (10) of the series section in the direction of fluid flow before the parallel section with a parallel consumer (14) are arranged.
3. Schaltungsanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Ventileinheit (18) aus einem hydraulisch steuerbaren Pro- portionalschieberventil, vorzugsweise einem 2-Wege-Proportional- schieberventil gebildet ist. 3. Circuit arrangement according to claim 1 or 2, characterized in that the valve unit (18) is formed from a hydraulically controllable proportional slide valve, preferably a 2-way proportional slide valve.
4. Schaltungsanordnung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass jedem Verbraucher (10) der Reihensektion eine By- pass-Druckwaage (20,22) zugeordnet ist.4. Circuit arrangement according to one of claims 1 to 3, characterized in that each consumer (10) of the series section is assigned a bypass pressure compensator (20, 22).
5. Schaltungsanordnung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die eine Steuerdruckleitung für die Ventileinheit (18) an ein Wechselventil (24) der Reihensektion angeschlossen ist und die andere Steuerdruckleitung an mindestens ein Wechselventil (26) der Parallelsektion und an mindestens ein Wechselventil (28) des Load- Sensing-Systems (LS).5. Circuit arrangement according to one of claims 1 to 4, characterized in that the one control pressure line for the valve unit (18) is connected to a shuttle valve (24) of the series section and the other control pressure line to at least one shuttle valve (26) of the parallel section and at least a shuttle valve (28) of the load sensing system (LS).
6. Schaltungsanordnung nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass die Steuereingänge der jeweiligen Bypass-Druckwaage (20,22) der Reihensektion jeweils an den Ausgang des der Reihensektion zuge- ordneten Wechselventils (24) angeschlossen sind.6. Circuit arrangement according to claim 4 or 5, characterized in that the control inputs of the respective bypass pressure compensator (20, 22) of the series section are each connected to the output of the shuttle valve (24) assigned to the series section.
7. Schaltungsanordnung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass zwischen der Versorgungspumpe (P) und dem Rücklauf (1 6) eine Umlauf-Druckwaage (38) in den Versorgungskreis (12) geschaltet ist, an der insgesamt der höchste Lastdruck anliegt.7. Circuit arrangement according to one of claims 1 to 6, characterized in that between the supply pump (P) and the return (1 6), a circulation pressure compensator (38) is connected to the supply circuit (12), at which the highest load pressure is applied.
8. Schaltungsanordnung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass zwischen dem in Fluidströmungsrichtung ersten Verbraucher (10) der Reihensektion und der Versorgungspumpe (P) ein Proportional-Drosselventil (30) angeordnet ist, ebenso wie ein weiteres Proportional-Drosselventil (32) zwischen dem jeweils vorangehenden und dem jeweils nachfolgenden Verbraucher (10) einer Reihensektion. 8. Circuit arrangement according to one of claims 1 to 7, characterized in that a proportional throttle valve (30) is arranged between the first consumer (10) of the series section and the supply pump (P) in the fluid flow direction, as well as a further proportional throttle valve ( 32) between the preceding and the following consumer (10) of a row section.
9. Schaltungsanordnung nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, dass zwischen dem Wechselventil (26) der Parallelsektion und dem zugeordneten Verbraucher (14) gegenseitig entsperrbare Rückschlagventile (48) angeordnet sind.9. Circuit arrangement according to one of claims 5 to 8, characterized in that mutually unlockable check valves (48) are arranged between the shuttle valve (26) of the parallel section and the associated consumer (14).
10. Schaltungsanordnung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der jeweilige Verbraucher (10) der Reihensektion ein hydraulischer Motor und der Verbraucher (14) der Parallelsektion ein hydraulischer Arbeitszylinder ist. 10. Circuit arrangement according to one of claims 1 to 9, characterized in that the respective consumer (10) of the row section is a hydraulic motor and the consumer (14) of the parallel section is a hydraulic working cylinder.
EP04801211A 2004-02-05 2004-12-08 Circuit arrangement Not-in-force EP1711714B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004005606A DE102004005606B3 (en) 2004-02-05 2004-02-05 circuitry
PCT/EP2004/013927 WO2005075833A1 (en) 2004-02-05 2004-12-08 Circuit arrangement

Publications (2)

Publication Number Publication Date
EP1711714A1 true EP1711714A1 (en) 2006-10-18
EP1711714B1 EP1711714B1 (en) 2008-06-11

Family

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EP04801211A Not-in-force EP1711714B1 (en) 2004-02-05 2004-12-08 Circuit arrangement

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US (1) US7426884B2 (en)
EP (1) EP1711714B1 (en)
JP (1) JP4777910B2 (en)
AT (1) ATE398240T1 (en)
DE (2) DE102004005606B3 (en)
WO (1) WO2005075833A1 (en)

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JP4081487B2 (en) 2004-12-28 2008-04-23 東芝機械株式会社 Hydraulic control valve
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DE102006060335B3 (en) * 2006-12-20 2008-08-21 Sauer-Danfoss Aps Hydraulic valve arrangement for deck crane of lorry, has continuous auxiliary supply channel guided through valve modules, and auxiliary valve modules attached to channel, where one auxiliary module has structure without compensation device
DE102007014550A1 (en) * 2007-03-27 2008-10-09 Hydac Filtertechnik Gmbh valve assembly
DE102009028816A1 (en) * 2009-08-21 2011-02-24 Deere & Company, Moline Hydraulic arrangement
DE102009052077A1 (en) * 2009-11-05 2011-05-12 Robert Bosch Gmbh Hydraulic control arrangement with variable via a LS-valve control pressure drop
US8596417B2 (en) * 2011-07-05 2013-12-03 Honeywell International Inc. Lubrication systems with nozzle blockage detection systems
CN103398034B (en) * 2013-08-15 2015-08-26 中机美诺科技股份有限公司 A kind of hydraulic control system for Sowing machine for potatoes
DE102014004932B3 (en) * 2014-04-05 2015-05-13 Hydac Fluidtechnik Gmbh circuitry
DE102014110007B4 (en) * 2014-07-16 2016-02-04 Gebr. Heller Maschinenfabrik Gmbh Clamping unit and chuck unit of a clamping device and method for performing a clamping or releasing movement for clamping or releasing a workpiece
SG10201704185YA (en) * 2017-05-23 2018-12-28 Hock Hai Low Method of aligning a flat or profiled metal sheet
DE102017005479A1 (en) 2017-06-08 2018-12-13 Hydac Systems & Services Gmbh Pressure supply device

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JPS63115903A (en) * 1986-11-05 1988-05-20 Kobe Steel Ltd Oil pressure control device
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Publication number Publication date
DE502004007371D1 (en) 2008-07-24
JP4777910B2 (en) 2011-09-21
DE102004005606B3 (en) 2005-10-06
WO2005075833A8 (en) 2005-11-17
US7426884B2 (en) 2008-09-23
WO2005075833A1 (en) 2005-08-18
ATE398240T1 (en) 2008-07-15
US20070137192A1 (en) 2007-06-21
JP2007520674A (en) 2007-07-26
EP1711714B1 (en) 2008-06-11

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