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DE3644737A1 - Control arrangement for at least two hydraulic consumers fed by at least one pump - Google Patents

Control arrangement for at least two hydraulic consumers fed by at least one pump

Info

Publication number
DE3644737A1
DE3644737A1 DE19863644737 DE3644737A DE3644737A1 DE 3644737 A1 DE3644737 A1 DE 3644737A1 DE 19863644737 DE19863644737 DE 19863644737 DE 3644737 A DE3644737 A DE 3644737A DE 3644737 A1 DE3644737 A1 DE 3644737A1
Authority
DE
Germany
Prior art keywords
pressure
control
pump
control arrangement
arrangement according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
DE19863644737
Other languages
German (de)
Other versions
DE3644737C2 (en
Inventor
Norbert Dr Ing Kreth
Martin Dipl Ing Schmitt
Armin Ing Grad Stellwagen
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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
Priority claimed from DE19853532816 external-priority patent/DE3532816A1/en
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Priority to DE19863644737 priority Critical patent/DE3644737C2/en
Publication of DE3644737A1 publication Critical patent/DE3644737A1/en
Application granted granted Critical
Publication of DE3644737C2 publication Critical patent/DE3644737C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F15B11/16—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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/255—Flow control functions
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40561—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged upstream of the flow control means
    • 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
    • F15B2211/60—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
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate 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
    • F15B2211/70—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
    • F15B2211/76—Control of force or torque of the output member

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A pump supplies a plurality of consumers with pressure medium via in each case one directional control valve, a pressure balance for load-independent separation of the pump delivery quantity being provided between each branch line, branching off from the pump delivery line, and the directional control valve. In a control-pressure device common to all pressure balances, a control pressure passed on to all pressure balances is generated. The control signal is generated in a pressure transducer, which is acted upon by the pump pressure and the consumer pressure which is highest in each case. This signal is supplied to an amplifier as the actual value, and the pressure-regulating valve is driven in accordance with the difference between desired and actual value.

Description

Das Hauptpatent betrifft eine Steueranordnung mit den im Oberbegriff des Patentanspruchs angegebenen Merk­ malen.The main patent relates to a tax arrangement with the Merk specified in the preamble of the claim to paint.

Ausgehend von einer bekannten Steueranordnung (DE-OS 34 22 165), bei der jede den Wegeventilen zu den Ver­ brauchern vorgeschaltete Druckwaage zusätzlich zur ersten Druckdifferenz, die von dem Unterschied zwischen dem Druck am Einlaß und Auslaß des Wegeventils bestimmt ist, noch von einer zweiten Druckdifferenz beaufschlagt wird, die von dem Unterschied zwischen dem Pumpendruck und dem jeweils höchsten Verbraucherdruck bestimmt ist, um bei nicht ausreichender Pumpenfördermenge den Durch­ fluß durch alle Druckwaagen verhältnisgleich zu ver­ ringern, liegt dem Hauptpatent die Aufgabe zugrunde die Bauweise dieser Steueranordnung unter Verwendung von Seriengeräten zu vereinfachen und die Genauigkeit der Einstellung des Durchflusses an den Druckwaagen zu erhöhen.Starting from a known control arrangement (DE-OS 34 22 165), where each of the directional valves to Ver consumers upstream pressure compensator in addition to first pressure difference, which is the difference between the pressure at the inlet and outlet of the directional control valve is still acted upon by a second pressure difference that is the difference between the pump pressure and is determined to the highest consumer pressure in each case, to the through if the pump delivery is insufficient flow through all pressure balances proportionally ver wrestle, the main patent is based on the task using the design of this control arrangement of series devices to simplify and accuracy the setting of the flow on the pressure compensators to increase.

Die Lösung der Aufgabe besteht darin, die zweite Druck­ differenz mit Hilfe eines Druckregelventils zu erzeugen, dessen Regeldruckausgang gemeinsam an alle Druckwaagen geführt ist.The solution to the problem is the second pressure generate difference with the help of a pressure control valve, the control pressure output together to all pressure compensators is led.

Damit wird der Vorteil erzielt, daß durch die Verwen­ dung eines einzigen Ventils zum Erzeugen des Steuer­ drucks an allen Druckwaagen der gleiche Steuerdruck ansteht.This has the advantage that the use a single valve to generate the tax the same control pressure on all pressure compensators pending.

Die im Hauptpatent vorgegebene Lösung läßt sich aber auch in einer anderen Ausführungsform verwirklichen. Nach dem Zusatzpatent ist ein Druckaufnehmer von der zweiten Druckdifferenz beaufschlagt und ist das Druck­ regelventil von dem Druckaufnehmer elektrisch ange­ steuert.However, the solution specified in the main patent can be  realize in another embodiment. According to the additional patent, a pressure sensor is from second pressure difference and is the pressure control valve from the pressure transducer electrically controls.

Im Hauptpatent sind verschiedene Ausführungsformen der Druckwaagen dargestellt. Die Lösung nach dem Zu­ satzpatent, die Druckdifferenz elektrisch zu erfassen und damit den Steuerdruck zu erzeugen, gilt für alle Ausführungsformen des Hauptpatents in gleicher Weise.There are various embodiments in the main patent of the pressure compensators. The solution after closing Sentence patent to record the pressure difference electrically and thus generating the control pressure applies to everyone Embodiments of the main patent in the same way.

Eine der Fig. 1 des Hauptpatents entsprechende Aus­ führungsform ist nachstehend anhand der Zeichnung näher erläutert, in der ein Schaltschema der hydraulischen Steueranordnung dargestellt ist.One of the main patent corresponding to FIG. 1 is explained in more detail below with reference to the drawing, in which a circuit diagram of the hydraulic control arrangement is shown.

Eine mittels eines Förderstromreglers 1 dem Hubvolumen nach verstellbare Pumpe 2 saugt aus einem Tank 3 und fördert in eine Leitung 4, die sich in drei Zweiglei­ tungen 5, 6 und 7 aufteilt. Jede Zweigleitung führt zu einer Druckwaage 8, 9, 10 und über ein Wegeventil 11, 12, 13 zu je einem Verbraucher, wie beispielsweise einem Hubzylinder, der nicht dargestellt ist. Bei den Wegeventilen handelt es sich um die üblichen Drei­ stellungs/Fünfanschluß-Ventile, welche die Druckmittel­ wege zwischen dem zugehörigen Verbraucher und der Pumpe 2 bzw. einem Tank steuern. Bei den Druckwaagen 8 bis 10 handelt es sich ebenfalls um die übliche Bauart als Stromregelventile, bei denen der Regelkolben in Öff­ nungsrichtung vom Druck einer Regelfeder 14 und vom Druck auf der Ausgangsseite des Wegeventils über eine Leitung 15 und in Schließrichtung vom Druck auf der Eingangsseite des Wegeventils über die Leitung 16 be­ aufschlagt ist. A by means of a flow rate controller 1 the stroke volume adjustable pump 2 sucks from a tank 3 and promotes in a line 4 , the lines divided into three branches 5 , 6 and 7 . Each branch line leads to a pressure compensator 8 , 9 , 10 and via a directional valve 11 , 12 , 13 to a consumer, such as a lifting cylinder, which is not shown. The directional control valves are the usual three-position / five-port valves, which control the pressure medium paths between the associated consumer and the pump 2 or a tank. The pressure compensators 8 to 10 are also of the usual type as flow control valves, in which the control piston in the opening direction from the pressure of a control spring 14 and the pressure on the output side of the directional control valve via a line 15 and in the closing direction from the pressure on the input side of the Directional control valve via line 16 is opened.

Somit ist der Durchfluß des Strömungsmittels aus der betreffenden Zweigleitung zum Wegeventil und zum Ver­ braucher unabhängig von der Druckdifferenz, die zwi­ schen dem Eingang und dem Ausgang des Wegeventils herrscht. D.h., daß der eingestellte Volumenstrom auch bei Druckschwankungen konstant bleibt, so daß also trotz unterschiedlicher Belastungen am Verbraucher dessen Arbeitsgeschwindigkeit durch Änderung des Durch­ fluß-Widerstandes in der Druckwaage konstant gehalten wird.Thus, the flow of the fluid from the relevant branch line to the directional valve and to Ver users regardless of the pressure difference between two between the entrance and the exit of the directional valve prevails. This means that the set volume flow also remains constant with pressure fluctuations, so that despite different loads on the consumer its working speed by changing the through flow resistance in the pressure compensator is kept constant.

Da die Federn 14 und Leitungen 15 bzw. 16 der einzelnen Druckwaagen, 8, 9 und 10 einander entsprechen, sind sie in der Zeichnung mit gleichen Bezugszeichen versehen.Since the springs 14 and lines 15 and 16 of the individual pressure compensators 8 , 9 and 10 correspond to one another, they are provided with the same reference symbols in the drawing.

Der Förderstromregler 1 für die Verstellpumpe 2 wird von dem höchsten, an einem der Verbraucher auftreten­ den Druck angesteuert. Hierzu ist eine Wechselventil­ kette vorgesehen, die aus den Wechselventilen 18 und 19 besteht. Der jeweils höhere, am Ausgang der Wegeventile 12 und 13 anstehende Druck, also der jeweils höhere Verbraucherdruck, wird von dem Wechselventil 18 auf die Leitung 20 geschaltet. Das Wechselventil 19 ver­ gleicht den Verbraucherdruck in der Leitung 20 mit dem am Ausgang des Wegeventils 11 anstehenden Druck und führt den höheren Druck über die Leitung 21 auf den Förderstromregler 1, von dem entsprechend den Anforde­ rungen von Seiten der Verbraucher das Hubvolumen der Pumpe 2 eingestellt wird. Insoweit entspricht die An­ ordnung dem Stand der Technik.The flow regulator 1 for the variable displacement pump 2 is controlled by the highest pressure occurring at one of the consumers. For this purpose, a shuttle valve chain is provided, which consists of the shuttle valves 18 and 19 . The higher pressure at the outlet of the directional control valves 12 and 13 , that is the higher consumer pressure, is switched from the shuttle valve 18 to the line 20 . The shuttle valve 19 ver compares the consumer pressure in line 20 with the pressure present at the outlet of the directional control valve 11 and passes the higher pressure via line 21 to the flow rate regulator 1 , from which, according to the requirements of the consumer, the stroke volume of the pump 2 is set becomes. In this respect, the order corresponds to the state of the art.

Darüber hinaus ist eine Drucksteuereinrichtung 24 in der Ausführungsform als Druckregelventil vorgesehen, das an eine Pumpe 25, einen Tank T und an eine Leitung 26 angeschlossen ist, die mit Stelleinrichtungen 27 an jeder Druckwaage 8 bis 10 verbunden ist. Anstelle der Pumpe 25 kann der Anschluß des Druckregelventils 24 auch mit der Förderleitung 4 verbunden sein. Das Druck­ regelventil 24 wird bei Abfall der vorgegebenen Druck­ differenz zwischen dem Pumpendruck und dem höchsten, an einem der Verbraucher auftretenden Druck verstellt, um auf der Leitung 26 einen Steuerdruck Δp zu erzeugen.In addition, a pressure control device 24 is provided in the embodiment as a pressure control valve which is connected to a pump 25 , a tank T and to a line 26 which is connected to actuating devices 27 on each pressure compensator 8 to 10 . Instead of the pump 25 , the connection of the pressure control valve 24 can also be connected to the delivery line 4 . The pressure control valve 24 is adjusted in the event of a drop in the predetermined pressure difference between the pump pressure and the highest pressure occurring at one of the consumers in order to generate a control pressure Δ p on the line 26 .

Zu diesem Zweck ist ein Druckaufnehmer 33 vorgesehen, der von dem höchsten Verbraucherdruck in der Leitung 21 über die Leitung 31 und im Gegensinn vom Pumpendruck in der Förderleitung über die Leitung 32 druckbeauf­ schlagt ist. Die Druckdifferenz wird vom Druckaufnehmer 33 in eine elektrische Signalspannung U umgewandelt, die zur Ansteuerung des elektrisch betätigten Druck­ regelventils 24 verwendet wird. Zwischengeschaltet ist ein Anpaßverstärker 37, mit dem auch das Zeitverhalten beim Verstellen des Regelventils optimal an die vor­ liegende Aufgabe angepaßt wird. Die Signalverarbeitung kann analog oder digital durchgeführt werden. Vorzugs­ weise werden besondere Maßnahmen getroffen, um die Dämpfung des Systems zu erhöhen, ohne jedoch die Ver­ stellgeschwindigkeit oder die Pegelgenauigkeit zu ver­ schlechtern.For this purpose, a pressure transducer 33 is provided which is pressurized by the highest consumer pressure in line 21 via line 31 and in the opposite direction by the pump pressure in the delivery line via line 32 . The pressure difference is converted by the pressure sensor 33 into an electrical signal voltage U , which is used to control the electrically operated pressure control valve 24 . Intermediate is a matching amplifier 37 , with which the timing behavior when adjusting the control valve is optimally adapted to the task ahead. The signal processing can be carried out analog or digital. Preference, special measures are taken to increase the damping of the system, but without reducing the adjustment speed or the level accuracy.

Die Wirkungsweise dieser Anordnung ist wie folgt: Solange die Pumpenfördermenge in der Leitung 4 ausreicht, um die zugeschalteten Verbraucher mit der gewünschten Geschwindigkeit zu betätigen, ist das Druckregelventil 24 geschlossen; der Druck Δp ist Null und die Druck­ waagenfeder 14 wird zusätzlich durch die Feder 35 vor­ gespannt.The operation of this arrangement is as follows: as long as the pump delivery rate in line 4 is sufficient to actuate the connected consumers at the desired speed, the pressure control valve 24 is closed; the pressure Δ p is zero and the pressure balance spring 14 is additionally tensioned by the spring 35 before.

Reicht jedoch die Fördermenge der Pumpe 2 für den An­ trieb der betätigten Verbraucher nicht aus, so wird entsprechend dem Abfall der Druckdifferenz zwischen dem höchsten Lastdruck in der Leitung 31 und dem Pumpendruck in der Leitung 32 das Druckregelventil 24 elektrisch verstellt und der Steuerdruck in der Leitung 26 erhöht. Dies hat zur Folge, daß über die Stellein­ richtungen 27 der Durchfluß zu allen Verbrauchern verhältnisgleich verringert wird, also an allen Ver­ brauchern die Durchflußmengen im eingestellten Ver­ hältnis zueinander verringert werden, so daß die bei­ spielsweise von zwei Hubzylindern eines Werkzeuges oder Arbeitsmittels eingestellte Bahnkurve erhalten bleibt und nur die Stellgeschwindigkeit entsprechend verringert wird.However, the delivery rate of the pump 2 for the drive of the actuated consumer is not sufficient, the pressure control valve 24 is electrically adjusted and the control pressure in the line in accordance with the drop in the pressure difference between the highest load pressure in line 31 and the pump pressure in line 32 26 increased. The result of this is that the flow rate to all consumers is reduced proportionately by means of the adjusting devices 27 , that is to say the flow rates in the set ratio to one another are reduced at all consumers, so that the trajectory set for example by two lifting cylinders of a tool or working medium is obtained remains and only the actuating speed is reduced accordingly.

Claims (7)

1. Steueranordnung für mindestens zwei von mindestens einer Pumpe gespeiste hydraulische Verbraucher, bei der jedem Verbraucher ein richtungs- und geschwindigkeits­ steuerndes Wegeventil zugeordnet und zwischen dem jewei­ ligen Wegeventil und der Pumpe eine Druckwaage vorgesehen ist, die zur Einstellung eines lastunabhängigen Durch­ flusses von einer zwischen dem Eingang und dem Ausgang des zugehörigen Wegeventils herrschenden ersten Druck­ differenz und zur Verringerung des Durchflusses bei nicht ausreichender Pumpenfördermenge von einer von dem Pumpendruck und dem höchsten Verbraucherdruck bestimmten zweiten Druckdifferenz beaufschlagt ist, die mit Hilfe einer Drucksteuereinrichtung in ein Steuerdrucksignal umgesetzt wird und das an alle Druckwaagen geführt ist, nach Patent P 35 32 816, dadurch gekenn­ zeichnet, daß ein Druckaufnehmer (33) von der zweiten Druckdifferenz beaufschlagt ist und die Druck­ steuereinrichtung (24) von dem Druckaufnehmer elektrisch angesteuert ist.1.Control arrangement for at least two hydraulic consumers fed by at least one pump, in which each consumer is assigned a directional and speed-controlling directional control valve and a pressure compensator is provided between the respective directional control valve and the pump, which is used to set a load-independent flow of one between the input and the output of the associated directional valve prevailing first pressure difference and to reduce the flow when the pump delivery is insufficient, a second pressure difference determined by the pump pressure and the highest consumer pressure is applied, which is converted with the help of a pressure control device into a control pressure signal and to everyone Pressure compensators is guided, according to patent P 35 32 816, characterized in that a pressure sensor ( 33 ) is acted upon by the second pressure difference and the pressure control device ( 24 ) is electrically controlled by the pressure sensor. 2. Steueranordnung nach Anspruch 1, dadurch ge­ kennzeichnet, daß zwischen Druckaufnehmer und Drucksteuereinrichtung ein Anpaßverstärker mit Soll­ wertvorgabe angeordnet ist.2. Control arrangement according to claim 1, characterized ge indicates that between pressure transducers and pressure control device a matching amplifier with target value specification is arranged. 3. Steueranordnung nach Anspruch 2, dadurch ge­ kennzeichnet, daß der Anpaßverstärker analog arbeitet.3. Control arrangement according to claim 2, characterized ge indicates that the matching amplifier works analogously. 4. Steueranordnung nach Anspruch 2, dadurch ge­ kennzeichnet, daß der Anpaßverstärker digital arbeitet. 4. Control arrangement according to claim 2, characterized ge indicates that the matching amplifier works digitally.   5. Steueranordnung nach Anspruch 3 oder 4, dadurch gekennzeichnet, daß anstelle des Diffe­ renzdruckaufnehmers (33) zwei Absolutdruckaufnehmer eingesetzt werden und das dem Istwert entsprechende Signal im Anpaßverstärker erzeugt wird.5. Control arrangement according to claim 3 or 4, characterized in that instead of the differential pressure transducer ( 33 ) two absolute pressure transducers are used and the signal corresponding to the actual value is generated in the matching amplifier. 6. Steueranordnung nach Anspruch 1 bis 5, dadurch gekennzeichnet, daß zusätzliche Maßnahmen zur Verbesserung der Dynamik des Systems in die Regelungs­ struktur des Verstärkers (37) aufgenommen werden.6. Control arrangement according to claim 1 to 5, characterized in that additional measures to improve the dynamics of the system in the control structure of the amplifier ( 37 ) are added. 7. Steueranordnung nach Anspruch 6, dadurch ge­ kennzeichnet, daß zur Dämpfungserhöhung die Änderungsgeschwindigkeit einer der Absolutdrücke verwendet wird (nachgebende Druckrückführung).7. Control arrangement according to claim 6, characterized ge indicates that to increase damping the rate of change of one of the absolute pressures is used (yielding pressure feedback).
DE19863644737 1985-09-13 1986-12-30 Control arrangement for at least two hydraulic consumers fed by at least one pump Expired - Fee Related DE3644737C2 (en)

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DE19853532816 DE3532816A1 (en) 1985-09-13 1985-09-13 CONTROL ARRANGEMENT FOR AT LEAST TWO HYDRAULIC CONSUMERS SUPPLIED BY AT LEAST ONE PUMP
DE19863644737 DE3644737C2 (en) 1985-09-13 1986-12-30 Control arrangement for at least two hydraulic consumers fed by at least one pump

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5025625A (en) * 1988-11-10 1991-06-25 Hitachi Construction Machinery Co., Ltd. Commonly housed directional and pressure compensation valves for load sensing control system
FR2684726A1 (en) * 1991-12-07 1993-06-11 Rexroth Mannesmann Gmbh DEVICE FOR ADJUSTING THE PRESSURE OF A WORKING FLUID.
EP0603722A1 (en) * 1992-12-23 1994-06-29 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Hydraulic control system
EP0615024A3 (en) * 1993-03-12 1996-09-25 Orenstein & Koppel Ag Load-independent speed control of hydraulic actuators for construction machines.
EP0926349A3 (en) * 1997-12-17 2000-03-29 Husco International, Inc. Hydraulic control valve system with load sensing priority
DE102006057699A1 (en) * 2006-12-07 2008-06-12 Hydac Filtertechnik Gmbh Method for operating a hydraulic system and hydraulic system
EP4311944A1 (en) * 2022-07-25 2024-01-31 Deere & Company Arrangement for operating a hydraulic consumer

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2651325A1 (en) * 1976-02-02 1977-08-04 Caterpillar Tractor Co LOAD-CONTROLLED FLOW SYSTEM
DE3422165A1 (en) * 1983-06-14 1984-12-20 Linde Ag, 6200 Wiesbaden Hydraulic arrangement with a pump and at least two consumers of hydraulic energy acted upon by this pump
DE3532816A1 (en) * 1985-09-13 1987-03-26 Rexroth Mannesmann Gmbh CONTROL ARRANGEMENT FOR AT LEAST TWO HYDRAULIC CONSUMERS SUPPLIED BY AT LEAST ONE PUMP

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2651325A1 (en) * 1976-02-02 1977-08-04 Caterpillar Tractor Co LOAD-CONTROLLED FLOW SYSTEM
DE3422165A1 (en) * 1983-06-14 1984-12-20 Linde Ag, 6200 Wiesbaden Hydraulic arrangement with a pump and at least two consumers of hydraulic energy acted upon by this pump
DE3532816A1 (en) * 1985-09-13 1987-03-26 Rexroth Mannesmann Gmbh CONTROL ARRANGEMENT FOR AT LEAST TWO HYDRAULIC CONSUMERS SUPPLIED BY AT LEAST ONE PUMP

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5025625A (en) * 1988-11-10 1991-06-25 Hitachi Construction Machinery Co., Ltd. Commonly housed directional and pressure compensation valves for load sensing control system
FR2684726A1 (en) * 1991-12-07 1993-06-11 Rexroth Mannesmann Gmbh DEVICE FOR ADJUSTING THE PRESSURE OF A WORKING FLUID.
EP0603722A1 (en) * 1992-12-23 1994-06-29 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Hydraulic control system
EP0615024A3 (en) * 1993-03-12 1996-09-25 Orenstein & Koppel Ag Load-independent speed control of hydraulic actuators for construction machines.
EP0926349A3 (en) * 1997-12-17 2000-03-29 Husco International, Inc. Hydraulic control valve system with load sensing priority
DE102006057699A1 (en) * 2006-12-07 2008-06-12 Hydac Filtertechnik Gmbh Method for operating a hydraulic system and hydraulic system
US8661809B2 (en) 2006-12-07 2014-03-04 Hydac Filtertechnik Gmbh Method for operating a hydraulic system, and hydraulic system
EP4311944A1 (en) * 2022-07-25 2024-01-31 Deere & Company Arrangement for operating a hydraulic consumer

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