EP1023508B1 - System for controlling, independently of load pressure, and holding the load of a plurality of rotational and/or translational users - Google Patents

System for controlling, independently of load pressure, and holding the load of a plurality of rotational and/or translational users Download PDF

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Publication number
EP1023508B1
EP1023508B1 EP98961094A EP98961094A EP1023508B1 EP 1023508 B1 EP1023508 B1 EP 1023508B1 EP 98961094 A EP98961094 A EP 98961094A EP 98961094 A EP98961094 A EP 98961094A EP 1023508 B1 EP1023508 B1 EP 1023508B1
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EP
European Patent Office
Prior art keywords
load
pressure
throttle
valve
pump
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.)
Expired - Lifetime
Application number
EP98961094A
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German (de)
French (fr)
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EP1023508A1 (en
Inventor
Volker BÖSEBECK
Michael Holtmann
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CNH Industrial Baumaschinen GmbH
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O&K Orenstein and Koppel GmbH
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271—Actuators and supports therefor and protection therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices

Definitions

  • the invention relates to a system for load pressure independent Control and load maintenance of several rectifier and / or translational consumer of an eau and / or work machine with at least one regulated pump as well at least one containing a spring-loaded control piston Secondary pressure balance.
  • DE 34 43 354 A1 describes a hydraulic system, the one driven, for example, by a diesel engine Pump has, the pressure medium via directional valves To consumers.
  • the speed controller of the injection pump of the diesel engine is pressurized with the help Actuating cylinder affected by the purpose Speed increase of the engine generated pressure in acts on a control line.
  • This pressure will work together one of the way valves for a single acting Consumer and a pressure control valve controlled so that when operating a conventional directional valve a constant pressure is generated in the line.
  • the Actuation of the other directional valve for the single-acting Consumers have a special control edge Effect, making a proportional to the deflection of the Control spool generates increasing pressure in the line becomes.
  • the speed of the internal combustion engine and thus the pump increased and adjusted so that the Consumers just receive the required amount of pressure medium. This is an economical operation possible.
  • LSC Linde Synchro Control
  • the system works on the load-sensing principle. It significantly improves simultaneous operation various functions of hydraulic systems with open circuit.
  • the Linde Synchro Control (LSC) valves are individual valve sections. The right combination for different machines is achieved in that the individual sections are mounted on corresponding valve plates. These valve plates only contain the connection channels, such as. the input channel from the pump, Connection channels to and from the valves, the return line and the connection of the return to the tank. In the Valve sections are the actual functional elements accommodated.
  • the valves themselves are piston-type have a spring-centered closed center position and are operated hydraulically.
  • the maximum Piston stroke is adjustable, and since the pressure drop at the Control edges is kept constant, this means that the maximum oil flow that should flow through the valve, can be limited at the end stops of the valve.
  • a pressure compensator is arranged inside the valve piston.
  • the shuttle valves for the LS signal are located inside the pressure compensators and move in with them the valve piston.
  • a generic control system for load pressure independent Control of several consumers of a mobile hydraulic Construction machine is known from EP 0 326 150 A1.
  • This Control system has a spring-loaded control piston containing pressure compensator.
  • the object of the invention is that in the current systems realized functional separation between the Signal generation, load holding and pressure compensation functions by reducing external individual components to optimize to an inexpensive, assembly-friendly and bring about construction that is not susceptible to faults.
  • Such systems are used for load-independent systems Control and regulation of consumer speeds for mobile construction and work machines, such as. Excavators, wheel bearings, graders and the like at least two consumers, e.g. Hydraulic cylinder, one unaffected by the load pressures impressed from the outside Work movement without mutual interference must have.
  • the lower housing part Is part of the control valve.
  • a secondary pressure compensator is used related to the load holding function, in the opposite of the Function with conventional load compensators with separate Load holding function the signal carrying the load pressure in the consumer-side channels not for forwarding to the pressure regulator of the feed pump, as it hereby arranged without additional in the consumer channels Load holding valves to an unwanted drop the load due to the leakage of the feed pump pressure regulator or the pressure relief valve of the load sensing line comes.
  • this is avoided by that to the pressure regulator of the feed pump and the compensators of consumers with lower loads a pressure signal is reported by the pump self-generated and maintained and in his Pressure level corresponds to the highest consumer pressure.
  • FIG. 1 is the schematic structure of an inventive Control system using the example of a consumer shown.
  • the secondary pressure compensator with load holding function is divided into two components, namely an upper housing part 78 and a lower housing part 86.
  • the lower Housing part 86 is preferably part of the Control valves 7, 8, 9, i.e. forms a unified with this Casing.
  • Figure 2 shows an example for two translational consumers 16, 17 (hydraulic cylinder) schematically the structure of the tax system.
  • the system accordingly has two Secondary pressure compensators, the housing of each in two Housing parts 78, 79 and 86, 87 are divided, i.e. the Formation of the second secondary pressure compensator corresponds to that the secondary pressure compensator 78 shown in FIG. 1, 86th
  • a pump 1 generates a pressure level in the system that by a preselectable control difference ⁇ p LS above the input pressure signal of the pressure regulator 2 of the pump 1 lies. This pressure level is present when the inlet throttle 7 is open under the piston crown 37 of the first secondary pressure compensator 78, 86.
  • the inlet pressure level of the pressure regulator 2 in the line 20 drops via a load-sensing bypass valve 3 to the tank pressure level p r .
  • the outlet throttle 9 is opened.
  • the consumption-side pressure signal p L1 is present in the outlet channel 22 of the secondary pressure compensator 78, 86 and propagates through the channel 29, a shuttle valve 32, a channel 31 and a damping nozzle 30 to the spring-loaded piston head 27 of the secondary pressure compensator 78, 86.
  • the consumer-side pressure signal p L1 which acts on the spring-loaded piston head 27 of the secondary pressure compensator 78, 86, keeps the two-part control piston 72, 73 on its valve set 36, as a result of which no leakage flow can escape from the pressure-carrying consumer-side channel 22 into the inlet channel 33.
  • the inlet throttle 7 also opens with a corresponding phase shift, as a result of which the pump pressure p P , which is initially at the level of the control pressure difference ⁇ p LS , builds up on the active surface of the piston head 37.
  • the seat valve seats 36, 53 of the piston heads and the piston heads 27, 44 of the two-part control pistons of the secondary pressure compensators 78, 86 and 79, 87 are surface-balanced.
  • the pressure signal limited to the consumer load pressure p L1 is forwarded to the pressure regulator 2 of the pump 1 via the pump pressure-carrying channel 24, the inlet nozzle 21, the check valve 34 and the channels 25, 4 and 20.
  • the pump 1 supplies an output pressure p p which has the preselected control difference ⁇ p LS compared to the pressure input signal in line 20.
  • a further check valve 23 opens and thus ensures that the pressure signal in the channel 35 corresponds to the value of the consumer pressure p does not exceed L1 . This ensures that the pressure signal generated by the pump 1 and passed on to the pressure regulator 2 of the pump 1 and the secondary pressure compensator 79, 87 is limited by the level of the respective load pressure.
  • the valve seat 36 of the two-part control piston 72, 73 of the secondary pressure compensator 78, 86 opens due to the excess pressure on the piston crown surface 37, whereby a volume flow Q V1 flows through the inlet throttle 7, the opened valve seat 36 and an outlet throttle 9 to the consumer 16.
  • the resulting volume flow Q V1 is determined by the variable opening cross-section A D1 of the inlet throttle 7 and the differential pressure ⁇ p LS - p F1 that drops as a result according to the following equation:
  • Q V1 K ° A D1 ° ⁇ ⁇ p LS - p F1 ,
  • the pump pressure signal present in the channel 35 and limited to the consumer pressure level p L1 is forwarded to the second secondary pressure compensator 79, 87 via the check valve 34, the channel 25 and the lines 4, 5.
  • the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87 and is effective via the channel 42, the shuttle valve 49 and the channel 48 and the damping nozzle 47 on the active surface 44 of the two-part control piston head 74, 75 is and thus holds the valve seat 53 of the two-part control piston 74, 75 securely closed.
  • the outlet throttle 12 is first opened, as a result of which the load pressure p L2 through the channel 46 on the shuttle valve 49 becomes effective.
  • the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87, which becomes active via the channel 42, the shuttle valve 49, the channel 48 and the damping nozzle 47 on the active surface of the control piston head 44 and thus the Valve seat 53 of the two-part control piston 74, 75 holds securely closed.
  • the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87, which becomes active via the channel 42, the shuttle valve 49 and the channel 48 on the active surface of the control piston head 44 and thus the valve seat 53 of the two-part Control piston 74, 75 holds securely closed.
  • the outlet throttle 12 is first opened, as a result of which the load pressure p L2 takes effect via the channel 46 in the lower chamber of the shuttle valve 49. Since it is presupposed that p L1 ⁇ p L2 , the load pressure p L2 prevails in the lower chamber of the shuttle valve 49 and acts via the channel 48 and the damping nozzle 47 on the head 44 of the two-part control piston 74, 75.
  • the inlet throttle 10 is opened with the cross section A D2 .
  • the pressure potential p L1 + ⁇ p LS offered by the pump 1 becomes effective under the piston crown 54 of the two-part control piston 74, 75 of the pressure compensator 79, 87. Since the sum of the current load pressure p L2 and equivalent pressure p F2 of the spring acting on the piston head 44 is greater than the pressure signal p L1 + ⁇ p LS which acts on the piston head 54 from the pump 1, the valve seat 53 of the two-part control piston 74, 75 remains initially closed.
  • the pump pressure signal p L1 + ⁇ p LS is forwarded via the nozzle 38, the check valve 51 and the load signal line 42 and 5 to the pump regulator 2, which then reacts with a pressure increase in the pump outlet pressure p P in line 19.
  • the pressure in the line 51 and in the load signaling line 42 can at most reach the load pressure level p L2 , since this leads to the opening of the check valve 40 and thus to the connection to the load-carrying consumer channel 46 or 39.
  • the pressure level at the pump outlet 19 thus increases to p L2 + ⁇ p LS .
  • the load pressure signal p L2 is likewise forwarded to the secondary pressure compensator 78, 87 of the consumer 16 via the load signaling line 5. Since it is presupposed that p L2 > p L1 , the load signal p L2 also acts on the piston head 27 of the two-part control piston 72, 73 of the secondary pressure compensator 78 via the channel 25, the shuttle valve 32, the channel 31 and the damping nozzle 30.
  • the increased pressure signal of the pump 1 acts on the active surface of the piston head 37 of the secondary pressure compensator 78, 86, which in turn sets the constant pressure drop ⁇ p LS -p F1 via the inlet throttle 7.
  • control concept shown is thus able to regardless of the applied load pressures via the inlet throttles 7, 10 preselected consumer speeds to keep constant.
  • the secondary pressure compensators shown include 78, 86 and 79, 87 in addition to the load holding function all signal generating and signal comparing Functions, whereby no external logic elements, such as Check or shuttle valves are necessary.
  • the two-part control pistons 72, 73 and 74, 75 Integrated seat valve function is implemented with mobile hydraulic Construction and work machines often required Load holding function without additional external components.
  • Figure 4 shows an exemplary embodiment with two secondary pressure compensators 78, 86 and 79, 87 with two consumers 16, 17.
  • FIG. 5 shows the opening characteristic using a diagram the outlet throttle in relation to the inlet throttle, the phase shift also depending the specified parameters is shown.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Description

Die Erfindung betrifft ein System zur lastdruckunabhängigen Steuerung und Lasthaltung mehrerer rctatorischer und/oder translatorischer Verbraucher einer Eau- und/oder Arbeitsmaschine mit mindestens einer geregelten Pumpe sowie mindestens einer einen federbelasteten Regelkolben beinhaltenden Sekundärdruckwaage.The invention relates to a system for load pressure independent Control and load maintenance of several rectifier and / or translational consumer of an eau and / or work machine with at least one regulated pump as well at least one containing a spring-loaded control piston Secondary pressure balance.

Für Steuerschieber, die nach dem Wirkprinzip der lastdruckunabhängigen Durchflußverteilung mit Sekundärdruckwaage arbeiten, gibt es unterschiedliche Anordnungen der Signalerzeugung und -weiterleitung.For spool valves that work according to the principle of load pressure independent Flow distribution with secondary pressure compensator work, there are different arrangements of the Signal generation and transmission.

Die zur Zeit bekannten Systeme der lastdruckunabhängigen Durchflußverteilung weisen eine funktionale und räumliche Trennung zwischen der Sekundärwaage, die die Funktion der Druckkompensation übernimmt, der Signalerzeugung und -weiterleitung sowie der Lasthaltefunktion auf. Durch die funktionale und räumliche Trennung der Funktionseinheiten steigt die Anzahl der Einzelkomponenten des Systems und somit auch der Kosten-, Montage- und Wartungsaufwand.The currently known systems of load pressure independent Flow distribution have a functional and spatial Separation between the secondary scales, which function the Pressure compensation takes over, the signal generation and forwarding and the load holding function. Through the functional and spatial separation of the functional units the number of individual components of the system and hence the cost, assembly and maintenance costs.

Bei Steuerschiebern nach dem Prinzip der lastdruckunabhängigen Durchflußverteilung (LUDV) gibt es unterschiedliche Möglichkeiten des Abgriffes und der Weiterleitung des sogenannten Load-Sensing(LS)-Signales. Einerseits besteht die Möglichkeit, dieses Signal über ein aufwendiges, in die Schiebersektionen integriertes System von Meldeleitungen an den Pumpenregler weiterzuleiten. Andererseits besteht die Möglichkeit, in die Kompensatorkolben weitere Kolben einzubauen, die mit einer relativ schwachen Feder ausgerüstet sind. Die Kompensatorkolben können auch so ausgebildet sein, daß sie über eine Steueröffnung das Load-Sensing-Signal weiterleiten. Die erstgenannte Ausführung ist aufwendig, während die beiden letztgenannten bezüglich der Signalabgabe derart empfindlich sind, daß über die Steuerkanten bei den kleinen Ölströmen ein druckgenaues Weiterleiten des Load-Sensing-Signales nicht immer gewährleistet ist. Dies bewirkt eine ungenaue Ansteuerung des Pumpenreglers, was sich wiederum negativ auf die Gesamtsteuerung, d.h. die Ansteuerung einzelner oder mehrerer Verbraucher, auswirkt.For spool valves on the principle of load pressure independent Flow distribution (LUDV) there are different Possibilities of tapping and forwarding the so-called load sensing (LS) signal. On the one hand, there is the possibility of using a complex, system integrated in the slide sections Forward signal lines to the pump controller. on the other hand there is the possibility in the compensator piston install more pistons with a relative weak spring are equipped. The compensator pistons can also be designed so that they have a Forward the load sensing signal to the control opening. The first-mentioned execution is complex, while the two the latter so sensitive to signal delivery are that over the control edges with the small oil flows a pressure-accurate forwarding of the load-sensing signal is not always guaranteed. This causes one imprecise control of the pump controller, which in turn negative for overall control, i.e. the control single or multiple consumers.

In DE 34 43 354 A1 ist eine Hydraulikanlage beschrieben, die über eine beispielsweise von einem Dieselmotor angetriebene Pumpe verfügt, die Druckmittel über Wege-Ventile Verbrauchern zuleitet. Der Drehzahlregler der Einspritzpumpe des Dieselmotors wird mit Hilfe eines druckbeaufschlagten Stellzylinders beeinflußt, auf den der zwecks Drehzahlanhebung der Brennkraftmaschine erzeugte Druck in einer Steuerleitung einwirkt. Dieser Druck wird im Zusammenwirken eines der Wege-Ventile für einen einfach wirkenden Verbraucher und eines Druckregelventiles so gesteuert, daß beim Betätigen eines üblichen Wege-Ventiles in der Leitung ein konstanter Druck erzeugt wird. Beim Betätigen des anderen Wege-Ventiles für den einfach wirkenden Verbraucher kommt eine spezielle Steuerkante zur Wirkung, wodurch ein proportional zur Auslenkung des Steuerschiebers ansteigender Druck in der Leitung erzeugt wird. Dadurch wird die Drehzahl der Brennkraftmaschine und damit der Pumpe erhöht und so eingestellt, daß die Verbraucher gerade die benötigte Druckmittelmenge erhalten. Auf diese Weise ist ein wirtschaftlicher Betrieb möglich.DE 34 43 354 A1 describes a hydraulic system, the one driven, for example, by a diesel engine Pump has, the pressure medium via directional valves To consumers. The speed controller of the injection pump of the diesel engine is pressurized with the help Actuating cylinder affected by the purpose Speed increase of the engine generated pressure in acts on a control line. This pressure will work together one of the way valves for a single acting Consumer and a pressure control valve controlled so that when operating a conventional directional valve a constant pressure is generated in the line. At the Actuation of the other directional valve for the single-acting Consumers have a special control edge Effect, making a proportional to the deflection of the Control spool generates increasing pressure in the line becomes. As a result, the speed of the internal combustion engine and thus the pump increased and adjusted so that the Consumers just receive the required amount of pressure medium. This is an economical operation possible.

Aus der US-A 2,892,312 ist eine hydraulische Anlage für Traktoren bekannt, die mit Arbeitszylindern zum Betreiben von mehreren Arbeitsgeräten ausgerüstet ist, wobei diese Arbeitszylinder von einer Pumpe gespeist werden, deren Förderdruck lastunabhängig gesteuert wird, und wobei die Arbeitszylinder unter Verwendung eines Steuerschiebers und eines Steuerventiles jeweils separat angesteuert werden.From US-A 2,892,312 is a hydraulic system for Tractors known to operate with working cylinders is equipped by several tools, these Working cylinders are fed by a pump, the Delivery pressure is controlled independently of the load, and the Working cylinder using a spool and a control valve can be controlled separately.

Einem Linde-Bericht aus "Technik und Wissenschaft" Nr. 63, 1969, Seiten 5-8, ist die Beschreibung der Linde-Synchro-Control (LSC) für mobile Hydraulikanwendungen zu entnehmen. Das System arbeitet nach dem Load-Sensing-Prinzip. Es verbessert erheblich die gleichzeitige Betätigung verschiedener Funktionen von Hydrauliksystemen mit offenem Kreislauf. Die Linde-Synchro-Control(LSC)-Ventile sind einzelne Ventilsektionen. Die geeignete Kombination für verschiedene Maschinen wird dadurch erreicht, daß man die Einzelsektionen auf entsprechende Ventilplatten montiert. Diese Ventilplatten beinhalten lediglich die Verbindungskanäle, wie z.B. den Eingangskanal von der Pumpe, Verbindungskanäle zu und von den Ventilen, die Rücklaufleitung und den Anschluß des Rücklaufes zum Tank. In den Ventilsektionen sind die eigentlichen Funktionselemente untergebracht. Die Ventile selbst sind in Kolbenbauart ausgeführt, haben eine federzentrierte geschlossene Mittelstellung und werden hydraulisch betätigt. Der maximale Kolbenhub ist einstellbar, und da das Druckgefälle an den Steuerkanten konstant gehalten wird, bedeutet dies, daß der maximale Ölstrom, der durch das Ventil fließen soll, an den Endanschlägen des Ventiles begrenzt werden kann. Eine Druckwaage ist im Inneren des Ventilkolbens angeordnet. Die Wechselventile für das LS-Signal befinden sich im Inneren der Druckwaagen und bewegen sich mit diesen in den Ventilkolben.A Linde report from "Technology and Science" No. 63, 1969, pages 5-8, is the description of the Linde Synchro Control (LSC) for mobile hydraulic applications remove. The system works on the load-sensing principle. It significantly improves simultaneous operation various functions of hydraulic systems with open circuit. The Linde Synchro Control (LSC) valves are individual valve sections. The right combination for different machines is achieved in that the individual sections are mounted on corresponding valve plates. These valve plates only contain the connection channels, such as. the input channel from the pump, Connection channels to and from the valves, the return line and the connection of the return to the tank. In the Valve sections are the actual functional elements accommodated. The valves themselves are piston-type have a spring-centered closed center position and are operated hydraulically. The maximum Piston stroke is adjustable, and since the pressure drop at the Control edges is kept constant, this means that the maximum oil flow that should flow through the valve, can be limited at the end stops of the valve. A pressure compensator is arranged inside the valve piston. The shuttle valves for the LS signal are located inside the pressure compensators and move in with them the valve piston.

Ein gattungsgemäßes Steuersystem zur lastdruckunabhängigen Steuerung mehrerer Verbraucher einer mobilhydraulischen Baumaschine ist aus EP 0 326 150 A1 bekannt. Dieses Steuersystem weist eine einen federbelasteten Regelkolben beinhaltende Druckwaage auf.A generic control system for load pressure independent Control of several consumers of a mobile hydraulic Construction machine is known from EP 0 326 150 A1. This Control system has a spring-loaded control piston containing pressure compensator.

Aus DE 296 04 215 Ul ist ein Lasthalte- bzw. Senkbremsventil bekannt, bei dem die die Lasthaltefunktion erzeugenden Bauteile sowie Steuerungselemente im Bereich des Regelkolbens vorgesehen sind.DE 296 04 215 Ul describes a load holding or lowering brake valve known, in which the generating the load holding function Components and control elements in the area of Control piston are provided.

Aufgabe der Erfindung ist es, die bei den derzeitigen Systemen verwirklichte funktionale Trennung zwischen der Signalerzeugungs-, der Lasthalte- und der Druckkompensationsfunktion durch Reduzierung externer Einzelkomponenten zu optimieren, um eine kostengünstige, montagegerechte und störungsunanfällige Konstruktion herbeizuführen.The object of the invention is that in the current systems realized functional separation between the Signal generation, load holding and pressure compensation functions by reducing external individual components to optimize to an inexpensive, assembly-friendly and bring about construction that is not susceptible to faults.

Diese Aufgabe wird mit einem System der eingangs bezeichneten Art erfindungsgemäß dadurch gelöst, daß sämtliche Steuerungselemente zur Signalerzeugung und zum Signalvergleich des Load-Sensing-Signales in einem oberen Gehäuseteil und die die Lasthaltefunktion erzeugenden Bauteile in einem mit dem oberen Gehäuseteil lösbar verbundenen unteren Gehäuseteil vorgesehen sind.This task is described with a system of the beginning Art solved according to the invention in that all Control elements for signal generation and signal comparison of the load-sensing signal in an upper part of the housing and the components generating the load holding function in a detachably connected to the upper housing part lower housing part are provided.

Durch diese Aufteilung der jeweiligen Sekundärdruckwaage in jeweils zwei Gehäuseteile und insbesondere die Integration sämtlicher Steuerungselemente in den oberen Gehäuseteil, der leicht vom unteren Gehäuseteil abmontiert werden kann, da er z.B. einfach angeflanscht ist, ist die Montage des Systems ausgesprochen kostengünstig und einfach durchzuführen, insbesondere ist es auch möglich, auf einfache Weise eine Nachrüstung, Umrüstung oder Reparatur durchzuführen. Durch die Aufteilung in zwei Gehäuseteile, in denen sämtliche Funktionsbauteile angeordnet sind, werden diese funktional und räumlich zusammengefaßt, wodurch gegenüber bekannten Systemen eine wesentliche Optimierung erreicht wird.This division of the respective secondary pressure compensator in two housing parts and in particular the integration all control elements in the upper housing part, which is easily removed from the lower part of the housing because it e.g. just flanged on is that Installation of the system is extremely inexpensive and simple perform, in particular it is also possible to easy retrofitting, retrofitting or repair perform. By dividing it into two housing parts, in which all functional components are arranged, these are summarized functionally and spatially, whereby a significant optimization compared to known systems is achieved.

Anwendungen finden derart ausgeführte Systeme zur lastdruckunabhängigen Steuerung und Regelung von Verbrauchergeschwindigkeiten bei mobilen Bau- und Arbeitsmaschinen, wie z.B. Bagger, Radlager, Grader und dergl., bei denen mindestens zwei Verbraucher, z.B. Hydraulikzylinder, eine von den jeweils von außen aufgeprägten Lastdrücken unbeeinflußte Arbeitsbewegung ohne gegenseitige Beeinflussung aufweisen müssen.Such systems are used for load-independent systems Control and regulation of consumer speeds for mobile construction and work machines, such as. Excavators, wheel bearings, graders and the like at least two consumers, e.g. Hydraulic cylinder, one unaffected by the load pressures impressed from the outside Work movement without mutual interference must have.

Vorteilhaft ist dabei vorgesehen, daß das untere Gehäuseteil Bestandteil des Steuerventiles ist.It is advantageously provided that the lower housing part Is part of the control valve.

Weitere zweckmäßige Ausgestaltungen ergeben sich aus den übrigen Unteransprüchen. Further expedient configurations result from the other subclaims.

Beim erfindungsgemäßen System wird eine Sekundärdruckwaage mit Lasthaltefunktion verwandt, bei der entgegen der Funktion bei konventionellen Lastkompensatoren mit separater Lasthaltefunktion das lastdruckführende Signal in den verbraucherseitigen Kanälen nicht zur Weiterleitung an den Druckregler der Förderpumpe benutzt wird, da es hierdurch ohne zusätzliche in den Verbraucherkanälen angeordnete Lasthalteventile zu einem ungewollten Absinken der Last infolge der Leckage des Druckreglers der Förderpumpe bzw. des Druckentlastungsventiles der Load-Sensing-Leitung kommt. Dies wird erfindungsgemäß dadurch vermieden, daß an die Druckregler der Förderpumpe und die Kompensatoren der jeweils niedriger belasteten Verbraucher jeweils ein Drucksignal gemeldet wird, das von der Pumpe selbst erzeugt und aufrechterhalten wird und in seinem Druckniveau jeweils dem höchsten Verbraucherdruck entspricht.In the system according to the invention, a secondary pressure compensator is used related to the load holding function, in the opposite of the Function with conventional load compensators with separate Load holding function the signal carrying the load pressure in the consumer-side channels not for forwarding to the pressure regulator of the feed pump, as it hereby arranged without additional in the consumer channels Load holding valves to an unwanted drop the load due to the leakage of the feed pump pressure regulator or the pressure relief valve of the load sensing line comes. According to the invention, this is avoided by that to the pressure regulator of the feed pump and the compensators of consumers with lower loads a pressure signal is reported by the pump self-generated and maintained and in his Pressure level corresponds to the highest consumer pressure.

Die Erfindung ist nachstehend anhand der Zeichnung beispielhaft näher erläutert. Diese zeigt in:

Fig. 1
eine schematische Darstellung einer Sekundärdruckwaage mit integrierter Lasthaltefunktion,
Fig. 2
ein schematisches Steuerungskonzept für zwei translatorische Verbraucher,
Fig. 3
ein Ausführungsbeispiel einer Sekundär-Druckwaage mit integrierter Lasthaltefunktion,
Fig. 4
ein Ausführungsbeispiel eines Steuerungssystems mit zwei translatorischen Verbrauchern und in
Fig. 5
eine Öffnungscharakteristik der Ablaufdrossel im Verhältnis zur Zulaufdrossel.
The invention is explained in more detail below with reference to the drawing. This shows in:
Fig. 1
a schematic representation of a secondary pressure compensator with an integrated load holding function,
Fig. 2
a schematic control concept for two translational consumers,
Fig. 3
an embodiment of a secondary pressure compensator with integrated load holding function,
Fig. 4
an embodiment of a control system with two translational consumers and in
Fig. 5
an opening characteristic of the outlet throttle in relation to the inlet throttle.

In Figur 1 ist der schematische Aufbau eines erfindungsgemäßen Steuerungssystems am Beispiel eines Verbrauchers dargestellt. Die Sekundärdruckwaage mit Lasthaltefunktion ist in zwei Bauteile gegliedert, nämlich ein oberes Gehäuseteil 78 und ein unteres Gehäuseteil 86. Das untere Gehäuseteil 86 ist dabei bevorzugt Bestandteil des Steuerventiles 7, 8, 9, d.h. bildet mit diesem ein einheitliches Gehäuse.In Figure 1 is the schematic structure of an inventive Control system using the example of a consumer shown. The secondary pressure compensator with load holding function is divided into two components, namely an upper housing part 78 and a lower housing part 86. The lower Housing part 86 is preferably part of the Control valves 7, 8, 9, i.e. forms a unified with this Casing.

Figur 2 zeigt beispielhaft für zwei translatorische Verbraucher 16, 17 (Hydraulikzylinder) schematisch den Aufbau des Steuersystems. Das System weist entsprechend zwei Sekundärdruckwaagen auf, deren Gehäuse jeweils in zwei Gehäuseteile 78, 79 bzw. 86, 87 unterteilt sind, d.h. die Ausbildung der zweiten Sekundärdruckwaage entspricht derjenigen der in Figur 1 gezeigten Sekundärdruckwaage 78, 86. Figure 2 shows an example for two translational consumers 16, 17 (hydraulic cylinder) schematically the structure of the tax system. The system accordingly has two Secondary pressure compensators, the housing of each in two Housing parts 78, 79 and 86, 87 are divided, i.e. the Formation of the second secondary pressure compensator corresponds to that the secondary pressure compensator 78 shown in FIG. 1, 86th

Unter der Annahme, daß zunächst nur ein Verbraucher 16 betätigt wird, stellt sich das Regel- und Steuerungskonzept wie folgt dar: Von einer Pumpe 1 wird ein Druckniveau im System erzeugt, daß um eine vorwählbare Regeldifferenz ΔpLS über dem Eingangsdrucksignal des Druckreglers 2 der Pumpe 1 liegt. Dieses Druckniveau steht bei geöffneter Zulaufdrossel 7 unter dem Kolbenboden 37 der ersten Sekundärdruckwaage 78, 86 an.Assuming that only one consumer 16 is actuated at first, the control concept is as follows: A pump 1 generates a pressure level in the system that by a preselectable control difference Δp LS above the input pressure signal of the pressure regulator 2 of the pump 1 lies. This pressure level is present when the inlet throttle 7 is open under the piston crown 37 of the first secondary pressure compensator 78, 86.

Bei nicht geöffneter Zulaufdrossel 7 sinkt das Eingangsdruckniveau des Druckreglers 2 in der Leitung 20 über ein Load-Sensing-Bypassventil 3 bis auf Tankdruckniveau pr ab.If the inlet throttle 7 is not open, the inlet pressure level of the pressure regulator 2 in the line 20 drops via a load-sensing bypass valve 3 to the tank pressure level p r .

Bei vereinfachender Annahme, daß pr ~ 0 bar beträgt, bedeutet dies, daß bei Öffnungsbeginn einer der dargestellten Zulaufdrosseln 7, 10 zunächst ein Druckniveau in Höhe der Regeldruckdifferenz von p = ΔpLS unter dem jeweiligen Kolbenboden 37, 54 der zugehörigen Sekundärdruckwaage 78, 86 bzw. 79, 87 ansteht.With a simplified assumption that p r is ~ 0 bar, this means that when one of the inlet throttles 7, 10 begins to open, a pressure level at the level of the control pressure difference of p = Δp LS below the respective piston crown 37, 54 of the associated secondary pressure compensator 78, 86 or 79, 87 is pending.

Mit einer entsprechenden Phasenvoreilung zum Öffnungsbeginn der Zulaufdrossel 7 wird die Ablaufdrossel 9 geöffnet. Dadurch steht das verbrauchsseitige Drucksignal pL1 im Ablaufkanal 22 der Sekundärdruckwaage 78, 86 an und pflanzt sich über den Kanal 29, ein Wechselventil 32, einen Kanal 31 und eine Dämpfungsdüse 30 bis auf den federbelasteten Kolbenkopf 27 der Sekundärdruckwaage 78, 86 fort.With a corresponding phase advance at the start of opening of the inlet throttle 7, the outlet throttle 9 is opened. As a result, the consumption-side pressure signal p L1 is present in the outlet channel 22 of the secondary pressure compensator 78, 86 and propagates through the channel 29, a shuttle valve 32, a channel 31 and a damping nozzle 30 to the spring-loaded piston head 27 of the secondary pressure compensator 78, 86.

Durch das verbraucherseitige Drucksignal pL1, das auf den federbelasteten Kolbenkopf 27 der Sekundärdruckwaage 78, 86 wirkt, wird der zweiteilige Regelkolben 72, 73 auf seinem Ventilsatz 36 gehalten, wodurch kein Leckagestrom aus dem druckführenden verbraucherseitigen Kanal 22 in den Zulaufkanal 33 entweichen kann.The consumer-side pressure signal p L1 , which acts on the spring-loaded piston head 27 of the secondary pressure compensator 78, 86, keeps the two-part control piston 72, 73 on its valve set 36, as a result of which no leakage flow can escape from the pressure-carrying consumer-side channel 22 into the inlet channel 33.

Mit zunehmendem Öffnungsweg des Hauptschieberkolbens 8 öffnet mit entsprechender Phasenverschiebung auch die Zulaufdrossel 7, wodurch der sich zunächst in Höhe der Regeldruckdifferenz ΔpLS befindende Pumpendruck pP an der Wirkfläche des Kolbenbodens 37 aufbaut. Die Sitzventilsitze 36, 53 der Kolbenböden und die Kolbenköpfe 27, 44 der zweiteiligen Regelkolben der Sekundärdruckwaagen 78, 86 sowie 79, 87 sind flächenausgeglichen.As the opening travel of the main slide piston 8 increases, the inlet throttle 7 also opens with a corresponding phase shift, as a result of which the pump pressure p P , which is initially at the level of the control pressure difference Δp LS , builds up on the active surface of the piston head 37. The seat valve seats 36, 53 of the piston heads and the piston heads 27, 44 of the two-part control pistons of the secondary pressure compensators 78, 86 and 79, 87 are surface-balanced.

Über den pumpendruckführenden Kanal 24, die Einlaßdüse 21, das Rückschlagventil 34 und die Kanäle 25, 4 und 20 wird das auf den Verbraucherlastdruck pL1begrenzte Drucksignal an den Druckregler 2 der Pumpe 1 weitergeleitet.The pressure signal limited to the consumer load pressure p L1 is forwarded to the pressure regulator 2 of the pump 1 via the pump pressure-carrying channel 24, the inlet nozzle 21, the check valve 34 and the channels 25, 4 and 20.

Die Pumpe 1 liefert einen Ausgangsdruck pp, der gegenüber dem Druckeingangssignal in der Leitung 20 die vorgewählte Regeldifferenz ΔpLS aufweist.The pump 1 supplies an output pressure p p which has the preselected control difference Δp LS compared to the pressure input signal in line 20.

Erreicht das von der Pumpe 1 erzeugte Drucksignal hinter der Einlaßdüse 21, im Kanal 35, das Verbraucherdruckniveau pL1 im Ablaufkanal 22 der Sekundärdruckwaage 78, 86, dann öffnet ein weiteres Rückschlagventil 23 und gewährleistet somit, daß das Drucksignal im Kanal 35 den Wert des Verbraucherdruckes pL1 nicht übersteigt. Dadurch ist sichergestellt, daß das von der Pumpe 1 erzeugte und an den Druckregler 2 der Pumpe 1 und die Sekundärdruckwaage 79, 87 weitergeleitete Drucksignal durch das Niveau des jeweiligen Lastdruckes begrenzt wird.If the pressure signal generated by the pump 1 behind the inlet nozzle 21, in the channel 35, reaches the consumer pressure level p L1 in the outlet channel 22 of the secondary pressure compensator 78, 86, then a further check valve 23 opens and thus ensures that the pressure signal in the channel 35 corresponds to the value of the consumer pressure p does not exceed L1 . This ensures that the pressure signal generated by the pump 1 and passed on to the pressure regulator 2 of the pump 1 and the secondary pressure compensator 79, 87 is limited by the level of the respective load pressure.

Der Pumpenausgangsdruck pP in der Leitung 19, der um die vorgewählte Regeldifferenz ΔpLS über dem Druckeingangssignal des Pumpenreglers 2 und somit um ΔpLS über dem Lastdrucksignal pL1 liegt, steht bei Bewegungsbeginn unter dem Kolbenboden 37 des zweiteiligen Regelkolbens 72, 73 der Sekundärdruckwaage 78, 86 an und übertrifft somit die auf die Wirkfläche des Kolbenkopfes 27 wirkende Summe aus Lastdruck pL1 und Äquivalenzdruck der Feder pF1 um den Differenzbetrag ΔpLS - pF1.The pump outlet pressure p P in line 19, which is above the pressure input signal of the pump regulator 2 by the preselected control difference Δp LS and thus above the load pressure signal p L1 by Δp LS , is below the piston crown 37 of the two-part control piston 72, 73 of the secondary pressure compensator 78 when the movement begins , 86 and thus exceeds the sum of the load pressure p L1 and equivalent pressure of the spring p F1 acting on the effective surface of the piston head 27 by the difference Δp LS - p F1 .

Der Ventilsitz 36 des zweiteiligen Regelkolbens 72, 73 der Sekundärdruckwaage 78, 86 öffnet infolge des Drucküberschusses auf der Kolbenbodenfläche 37, wodurch ein Volumenstrom QV1 über die Zulaufdrossel 7, den geöffneten Ventilsitz 36 und eine Ablaufdrossel 9 zum Verbraucher 16 fließt. Der sich hierbei einstellende Volumenstrom QV1 ist durch den veränderbaren Öffnungsquerschnitt AD1 der Zulaufdrossel 7 und den hierüber abfallenden Differenzdruck ΔpLS - pF1 entsprechend nachstehender Gleichung bestimmt: QV1 = K ° AD1 ° √ ΔpLS - pF1 . The valve seat 36 of the two-part control piston 72, 73 of the secondary pressure compensator 78, 86 opens due to the excess pressure on the piston crown surface 37, whereby a volume flow Q V1 flows through the inlet throttle 7, the opened valve seat 36 and an outlet throttle 9 to the consumer 16. The resulting volume flow Q V1 is determined by the variable opening cross-section A D1 of the inlet throttle 7 and the differential pressure Δp LS - p F1 that drops as a result according to the following equation: Q V1 = K ° A D1 ° √ Δp LS - p F1 ,

Gleichzeitig wird das im Kanal 35 anstehende, auf Verbraucherdruckniveau pL1 begrenzte Pumpendrucksignal über das Rückschlagventil 34, den Kanal 25 und die Leitungen 4, 5 an die zweite Sekundärdruckwaage 79, 87 weitergeleitet.At the same time, the pump pressure signal present in the channel 35 and limited to the consumer pressure level p L1 is forwarded to the second secondary pressure compensator 79, 87 via the check valve 34, the channel 25 and the lines 4, 5.

Bei der Betätigung eines zweiten Verbrauchers 17 mit dem Lastdruck pL2 können die drei folgenden Fallunterscheidungen gemacht werden.

Fall I:
Der zuerst betätigte Verbraucher 16 hat einen Lastdruck pL1, der größer ist als der des nachfolgend betätigten Verbrauchers 17 mit dem Lastdruck pL2. (pL1 > pL2).
When a second consumer 17 is actuated with the load pressure p L2 , the following three case distinctions can be made.
Case I:
The consumer 16 actuated first has a load pressure p L1 which is greater than that of the consumer 17 subsequently actuated with the load pressure p L2 . (p L1 > p L2 ).

Durch die Betätigung des Verbrauchers 16 steht in der Druckmeldeleitung 5 der Sekundärdruckwaage 79, 87 das Lastdrucksignal pL1 an, das über den Kanal 42, das Wechselventil 49 sowie den Kanal 48 und die Dämpfungsdüse 47 auf der Wirkfläche 44 des zweiteiligen Regelkolbenkopfes 74, 75 wirksam wird und somit den Ventilsitz 53 des zweiteiligen Regelkolbens 74, 75 sicher verschlossen hält. Bei der Betätigung des Verbrauchers 17 wird zunächst die Ablaufdrossel 12 geöffnet, wodurch der Lastdruck pL2 durch den Kanal 46 am Wechselventil 49 wirksam wird. Der größere Lastdruck pL1 in der oberen Kammer des Wechselventiles 49 setzt sich jedoch gegenüber dem Lastdruck pL2 durch und wirkt somit weiterhin auf den Kopf 44 des zweiteiligen Regelkolbens 74, 75, wodurch über die Zulaufdrossel 10 mit der Fläche AD2 das Differenzdruckgefälle ΔpLS - pF2 wirksam wird und sich der Volumenstrom QV2 zum Verbraucher 17 wie folgt errechnet: QV2 = K ° AD2 √ ΔpLS - pF2 . When the consumer 16 is actuated, the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87 and is effective via the channel 42, the shuttle valve 49 and the channel 48 and the damping nozzle 47 on the active surface 44 of the two-part control piston head 74, 75 is and thus holds the valve seat 53 of the two-part control piston 74, 75 securely closed. When the consumer 17 is actuated, the outlet throttle 12 is first opened, as a result of which the load pressure p L2 through the channel 46 on the shuttle valve 49 becomes effective. The larger load pressure p L1 in the upper chamber of the shuttle valve 49, however, prevails over the load pressure p L2 and thus continues to act on the head 44 of the two-part control piston 74, 75, as a result of which the differential pressure drop Δp LS occurs via the inlet throttle 10 with the area A D2 p F2 takes effect and the volume flow Q V2 to consumer 17 is calculated as follows: Q V2 = K ° A D2 √ Δp LS - p F2 ,

Das Differenzdruckgefälle pL1 - pL2 zwischen dem auf den Kolbenboden 54 wirkenden Pumpendrucksignal pP = pL1 und dem im Verbraucherkanal 39 vorherrschenden Lastdruck pL2 wird an der Steuerkante 85 des zweiteiligen Regelkolbens 74, 75 abgebaut.

Fall II:
Der zuerst betätigte Verbraucher 16 hat einen Lastdruck pL1, der dem des nachfolgend betätigten Verbrauchers 17 mit dem Lastdruck pL2 entspricht. (pL1 = pL2).
The differential pressure drop p L1 - p L2 between the pump pressure signal p P = p L1 acting on the piston crown 54 and the load pressure p L2 prevailing in the consumer channel 39 is reduced at the control edge 85 of the two-part control piston 74, 75.
Case II:
The consumer 16 actuated first has a load pressure p L1 which corresponds to that of the consumer 17 actuated subsequently with the load pressure p L2 . (p L1 = p L2 ).

Durch die Betätigung des Verbrauchers 16 steht in der Druckmeldeleitung 5 der Sekundärdruckwaage 79, 87 das Lastdrucksignal pL1 an, das über den Kanal 42, das Wechselventil 49, den Kanal 48 und die Dämpfungsdüse 47 auf der Wirkfläche des Regelkolbenkopfes 44 wirksam wird und somit den Ventilsitz 53 des zweiteiligen Regelkolbens 74, 75 sicher verschlossen hält.When the consumer 16 is actuated, the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87, which becomes active via the channel 42, the shuttle valve 49, the channel 48 and the damping nozzle 47 on the active surface of the control piston head 44 and thus the Valve seat 53 of the two-part control piston 74, 75 holds securely closed.

Bei der Betätigung des Verbrauchers 17 wird zunächst die Ablaufdrossel 12 geöffnet, wodurch der Lastdruck pL2 durch den Kanal 46 in der unteren Kammer des Wechselventiles 49 wirksam wird. Da der Lastdruck pL2 dem Lastdruck pL1 entspricht, nimmt das Wechselventil 49 eine indifferente Stellung ein, wodurch der Lastdruck pL1 = pL2 über den Kanal 48 auf den Kopf 44 des zweiteiligen Regelkolbens 74, 75 wirkt. Über die Zulaufdrossel 10 wird somit auch in diesem Fall das Differenzdruckgefälle ΔpLS - pF2 wirksam, womit sich der Volumenstrom QV2 zum Verbraucher 17 wie folgt errechnet: QV2 = K ° AD2 √ ΔpLS - pF2 . When the consumer 17 is actuated, the outlet throttle 12 is first opened, as a result of which the load pressure p L2 through the channel 46 in the lower chamber of the shuttle valve 49 is effective. Since the load pressure p L2 corresponds to the load pressure p L1 , the shuttle valve 49 assumes an indifferent position, as a result of which the load pressure p L1 = p L2 acts on the head 44 of the two-part control piston 74, 75 via the channel 48. In this case, too, the differential pressure drop Δp LS - p F2 is effective via the inlet throttle 10, with the result that the volume flow Q V2 to the consumer 17 is calculated as follows: Q V2 = K ° A D2 √ Δp LS - p F2 ,

Da bei beiden Verbrauchern 16, 17 das gleiche Lastdruckniveau pL1 = pL2 vorhanden ist, wird über den Ventilsitz 53 kein Differenzdruck abgebaut.

Fall III:
Der zuerst betätigte Verbraucher 16 hat einen Lastdruck pL1, der kleiner ist als der des nachfolgend betätigten Verbrauchers 17 mit dem Lastdruck pL2 (pL1 < pL2).
Since the same load pressure level p L1 = p L2 is present in both consumers 16, 17, no differential pressure is reduced via valve seat 53.
Case III:
The consumer 16 actuated first has a load pressure p L1 which is lower than that of the consumer 17 actuated subsequently with the load pressure p L2 (p L1 <p L2 ).

Durch die Betätigung des Verbrauchers 16 steht in der Druckmeldeleitung 5 der Sekundärdruckwaage 79, 87 das Lastdrucksignal pL1 an, das über den Kanal 42, das Wechselventil 49 und den Kanal 48 auf der Wirkfläche des Regelkolbenkopfes 44 wirksam wird und somit den Ventilsitz 53 des zweiteiligen Regelkolbens 74, 75 sicher verschlossen hält.When the consumer 16 is actuated, the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87, which becomes active via the channel 42, the shuttle valve 49 and the channel 48 on the active surface of the control piston head 44 and thus the valve seat 53 of the two-part Control piston 74, 75 holds securely closed.

Bei der Betätigung des Hauptschieberkolbens 11 des Verbrauchers 17 wird zunächst die Ablaufdrossel 12 geöffnet, wodurch der Lastdruck pL2 über den Kanal 46 in der unteren Kammer des Wechselventiles 49 wirksam wird. Da voraussetzungsgemäß gilt, daß pL1 < pL2 ist, überwiegt der Lastdruck pL2 in der unteren Kammer des Wechselventiles 49 und wirkt über den Kanal 48 und die Dämpfungsdüse 47 auf den Kopf 44 des zweiteiligen Regelkolbens 74, 75. Bei weiterem Durchschalten des Hauptschieberkolbens 11 des Verbrauchers 17 wird die Zulaufdrossel 10 mit dem Querschnitt AD2 geöffnet. Dadurch wird das von der Pumpe 1 angebotene Druckpotential pL1 + ΔpLS unter dem Kolbenboden 54 des zweiteiligen Regelkolbens 74, 75 der Druckwaage 79, 87 wirksam. Da die auf den Kolbenkopf 44 wirkende Summe aus aktuellem Lastdruck pL2 und Äquivalenzdruck pF2 der Feder größer ist als das von der Pumpe 1 am Kolbenboden 54 wirksam werdende Drucksignal pL1 + ΔpLS, bleibt der Ventilsitz 53 des zweiteiligen Regelkolbens 74, 75 zunächst geschlossen.When the main slide piston 11 of the consumer 17 is actuated, the outlet throttle 12 is first opened, as a result of which the load pressure p L2 takes effect via the channel 46 in the lower chamber of the shuttle valve 49. Since it is presupposed that p L1 <p L2 , the load pressure p L2 prevails in the lower chamber of the shuttle valve 49 and acts via the channel 48 and the damping nozzle 47 on the head 44 of the two-part control piston 74, 75. When the main spool is switched on again 11 of the consumer 17, the inlet throttle 10 is opened with the cross section A D2 . As a result, the pressure potential p L1 + Δp LS offered by the pump 1 becomes effective under the piston crown 54 of the two-part control piston 74, 75 of the pressure compensator 79, 87. Since the sum of the current load pressure p L2 and equivalent pressure p F2 of the spring acting on the piston head 44 is greater than the pressure signal p L1 + Δp LS which acts on the piston head 54 from the pump 1, the valve seat 53 of the two-part control piston 74, 75 remains initially closed.

Durch Öffnen der Zulaufdrossel 10 wird das Pumpendrucksignal pL1 + ΔpLS über die Düse 38, das Rückschlagventil 51 und die Lastmeldeleitung 42 und 5 an den Pumpenregler 2 weitergeleitet, der daraufhin mit einer Druckerhöhung des Pumpenausgangsdruckes pP in der Leitung 19 reagiert.By opening the inlet throttle 10, the pump pressure signal p L1 + Δp LS is forwarded via the nozzle 38, the check valve 51 and the load signal line 42 and 5 to the pump regulator 2, which then reacts with a pressure increase in the pump outlet pressure p P in line 19.

Der Druck in der Leitung 51 und in der Lastmeldeleitung 42 kann maximal das Lastdruckniveau pL2 erreichen, da dies zum Öffnen des Rückschlagventiles 40 und damit zur Verbindung mit dem lastführenden Verbraucherkanal 46 bzw. 39 führt.The pressure in the line 51 and in the load signaling line 42 can at most reach the load pressure level p L2 , since this leads to the opening of the check valve 40 and thus to the connection to the load-carrying consumer channel 46 or 39.

Das Druckniveau am Pumpenausgang 19 erhöht sich somit auf pL2 + ΔpLS.The pressure level at the pump outlet 19 thus increases to p L2 + Δp LS .

Über die Lastmeldeleitung 5 wird das Lastdrucksignal pL2 ebenfalls an die Sekundärdruckwaage 78, 87 des Verbrauchers 16 weitergeleitet. Da voraussetzungsgemäß gilt, daß pL2 > pL1 ist, wirkt über den Kanal 25, das Wechselventil 32, den Kanal 31 und die Dämpfungsdüse 30 das Lastsignal pL2 ebenfalls auf den Kolbenkopf 27 des zweiteiligen Regelkolbens 72, 73 der Sekundärdruckwaage 78.The load pressure signal p L2 is likewise forwarded to the secondary pressure compensator 78, 87 of the consumer 16 via the load signaling line 5. Since it is presupposed that p L2 > p L1 , the load signal p L2 also acts on the piston head 27 of the two-part control piston 72, 73 of the secondary pressure compensator 78 via the channel 25, the shuttle valve 32, the channel 31 and the damping nozzle 30.

Auf der Wirkfläche des Kolbenbodens 37 der Sekundärdruckwaage 78, 86 wirkt das erhöhte Drucksignal der Pumpe 1, womit sich über die Zulaufdrossel 7 wiederum das konstante Druckgefälle ΔpLS - pF1 einstellt. Das Differenzdruckgefälle pL2 - pL1 zwischen dem auf den Kolbenboden 37 wirkenden Pumpendrucksignal pP = pL2 und dem im Verbraucherkanal 22 vorherrschenden Lastdruck pL1 wird an der Steuerkante 36 des zweiteiligen Regelkolbens 72, 73 abgebaut.The increased pressure signal of the pump 1 acts on the active surface of the piston head 37 of the secondary pressure compensator 78, 86, which in turn sets the constant pressure drop Δp LS -p F1 via the inlet throttle 7. The differential pressure gradient p L2 - p L1 between the pump pressure signal p P = p L2 acting on the piston crown 37 and the load pressure p L1 prevailing in the consumer channel 22 is reduced at the control edge 36 of the two-part control piston 72, 73.

Das dargestellte Steuerungskonzept ist somit in der Lage, unabhängig von den jeweils anliegenden Lastdrücken, die über die Zulaufdrosseln 7, 10 vorgewählten Verbrauchergeschwindigkeiten konstant zu halten.The control concept shown is thus able to regardless of the applied load pressures via the inlet throttles 7, 10 preselected consumer speeds to keep constant.

Darüber hinaus beinhalten die dargestellten Sekundärdruckwaagen 78, 86 sowie 79, 87 neben der Lasthaltefunktion sämtliche signalerzeugenden und signalvergleichenden Funktionen, wodurch keine externe Logikelemente, wie Rückschlag- oder Wechselventile, notwendig sind. In addition, the secondary pressure compensators shown include 78, 86 and 79, 87 in addition to the load holding function all signal generating and signal comparing Functions, whereby no external logic elements, such as Check or shuttle valves are necessary.

Die in die zweiteiligen Regelkolben 72, 73 bzw. 74, 75 integrierte Sitzventilfunktion realisiert die mit mobilhydraulischen Bau- und Arbeitsmaschinen oft geforderte Lasthaltefunktion ohne zusätzliche externe Bauteile.The two-part control pistons 72, 73 and 74, 75 Integrated seat valve function is implemented with mobile hydraulic Construction and work machines often required Load holding function without additional external components.

Figur 3 zeigt eine beispielhafte Ausführung einer einzelnen Sekundärdruckwaage 78, 86, die im wesentlichen folgende Bauteile beinhaltet:

  • einen zweiteiligen Regelkolben 72, 73, der einen Kolbenboden 37 und einen Kolbenkopf 27 beinhaltet, wobei im Bereich des Kolbenkopfes 27 eine Feder 28 vorgesehen ist. Über die Einlaßdüsenplatte 21, das Rückschlagventil 34 und den Kanal 25 wird das Drucksignal der nicht dargestellten Pumpe an den Druckregler der Pumpe weitergeleitet. Im Bereich des Gehäusekopfes der dargestellten Sekundärdruckwaage 78, 86 sind weitere Kanäle 26, 29, 31 vorgesehen. Erreicht das von der Pumpe erzeugte Drucksignal hinter der Einlaßdüsenplatte 21 im Kanal 35 das Verbraucherdruckniveau pL1 im Ablaufkanal 22 bzw. 29 der Sekundärdruckwaage 78, dann öffnet ein weiteres Rückschlagventil 23 und gewährleistet somit, daß das Drucksignal im Kanal 35 den Wert des Verbraucherdruckes pL1 nicht übersteigt. Mit dem Bezugszeichen 32 ist ein Wechselventil, mit 36 der Ventilsitz des zweiteiligen Regelkolbens 72, 73 und mit 84 ist die Steuerkante des Regelkolbens 72, 73 bezeichnet.
    • FIG. 3 shows an exemplary embodiment of a single secondary pressure compensator 78, 86, which essentially contains the following components:
  • a two-part control piston 72, 73, which includes a piston crown 37 and a piston head 27, a spring 28 being provided in the region of the piston head 27. The pressure signal of the pump, not shown, is passed on to the pressure regulator of the pump via the inlet nozzle plate 21, the check valve 34 and the channel 25. Further channels 26, 29, 31 are provided in the area of the housing head of the illustrated secondary pressure compensator 78, 86. If the pressure signal generated by the pump behind the inlet nozzle plate 21 in the channel 35 reaches the consumer pressure level p L1 in the outlet channel 22 or 29 of the secondary pressure compensator 78, then a further check valve 23 opens and thus ensures that the pressure signal in the channel 35 reaches the value of the consumer pressure p L1 does not exceed. The reference numeral 32 denotes a shuttle valve, 36 the valve seat of the two-part control piston 72, 73 and 84 the control edge of the control piston 72, 73.

    • Figur 4 zeigt eine beispielhafte Ausführung mit zwei Sekundärdruckwaagen 78, 86 sowie 79, 87 mit zwei Verbrauchern 16, 17.Figure 4 shows an exemplary embodiment with two secondary pressure compensators 78, 86 and 79, 87 with two consumers 16, 17.

    Figur 5 zeigt anhand eines Diagrammes die Öffnungscharakteristik der Ablaufdrossel im Verhältnis zur Zulaufdrossel, wobei auch die Phasenverschiebung in Abhängigkeit der angegebenen Parameter dargestellt ist.FIG. 5 shows the opening characteristic using a diagram the outlet throttle in relation to the inlet throttle, the phase shift also depending the specified parameters is shown.

    Claims (10)

    1. A system for the load pressure-independent control and load-holding of a plurality of rotational and/or translatory consumer loads of a construction and/or working machine having at least: one regulated pump and at least one secondary pressure regulator including a spring-loaded regulating piston, characterised in that all control elements for signal production and for signal comparison of the load-sensing signal are provided in an upper housing portion (78, 79) and the components (36, 73, 53, 75) producing the load-holding function are provided in a lower housing portion (86, 87) releasably connected to the upper housing portion (78, 79).
    2. A system according to claim 1 characterised in that the lower housing portion (86, 87) is a component part of the control valve (7, 8, 9 and 10, 11, 12).
    3. A system according to claim 1 or claim 2 characterised in that to ensure the load-holding and pressure regulating function there is provided a two-part regulating piston (72, 73 and 74, 75) whose lower piston portion (73, 75) is formed from a conical seat valve (36, 53) in conjunction with a throttle valve (84, 85) and whose upper piston portion (72, 74) guided substantially in the upper housing portion (78, 79) does not include any further elements such as for example ducts, check, change-over or throttle valves.
    4. A system according to claim 1, claim 2 or claim 3 characterised in that the pressure signal necessary for pump actuation and internal pressure comparison can be produced by the arrangement integrated into the upper housing portion (78, 79) of the secondary pressure regulators and suitable dimensioning of throttles (21 and 38 respectively), check valves (23, 34 and 40, 51 respectively), change-over valves (32 and 49 respectively) and an in particular external LS-bypass valve (3) from the pressure signal between the feed metering throttles (7 and 8 respectively) and the control edge (84 and 85 respectively) of the regulating piston (73 and 75 respectively).
    5. A system according to claim 3 or claim 4 characterised in that the conical seat valve (36, 53) which is integrated into the lower portion (73 and 75 respectively) of the two-part regulating piston (72, 73 and 74, 75) is provided for the load-holding function, being operatively closable by the load-side load-pressure signal in ducts (22 and 39 respectively), acting on the operative surface (27, 44) of the regulating piston head, under the forces of springs (28, 45) upon opening of a discharge throttle (9 and 12 respectively).
    6. A system according to one or more of claims 1 to 5 characterised in that a connecting duct (24, 41) integrated into the housing of the respective secondary pressure regulator, from the pump (1) to a load signalling line (25, 42) supplying the pump regulator (2), has a connection in the direction from the connecting duct (24, 41) to the load signalling line (25, 42), and there is provided a check valve (34, 51) for closing the opposite through-flow direction from the load signalling line (25) to the connecting duct (24).
    7. A system according to one or more of claims 1 to 6 characterised in that to limit the pressure signal which is transmitted to the load signalling line (25, 42) to the level of the respective consumer load pressure (pL1, 2) in the duct (22 and 39) there is arranged in bypass relationship to the connecting duct (24, 41) to the load signalling line (25, 42) a check valve (23, 40) which is in communication with the load-carrying consumer duct (22, 39) and there is provided an aperture means (21, 38) acting as a throttle.
    8. A system according to one or more of claims 1 to 7 characterised in that the duct (31, 48) supplying the pressure chamber of the spring-loaded regulating piston head (27, 48) includes a damping nozzle or a throttle check valve (30, 47) for influencing the opening and closing speed of the regulating piston (72, 73 and 74, 75 respectively).
    9. A system according to one or more of claims 1 to 8 characterised in that the discharge throttle (9, 12) of the main spool axis (8, 11) has a defined phase lead in relation to an associated feed throttle (7, 10) so that the discharge throttle (9, 12) opens earlier and closes later than the feed throttle (7, 10).
    10. A system according to one or more of claims 1 to 9 characterised in that the opening characteristic of the discharge throttle (9, 12) is of a predetermined configuration in relation to the feed throttle (7, 10) of a main spool axis (8, 11).
    EP98961094A 1997-10-15 1998-09-30 System for controlling, independently of load pressure, and holding the load of a plurality of rotational and/or translational users Expired - Lifetime EP1023508B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE19745489A DE19745489B4 (en) 1997-10-15 1997-10-15 System for load-pressure-independent control and load holding of several rotary and / or translatory consumers
    DE19745489 1997-10-15
    PCT/EP1998/006215 WO1999019571A1 (en) 1997-10-15 1998-09-30 System for controlling, independently of load pressure, and holding the load of a plurality of rotational and/or translational users

    Publications (2)

    Publication Number Publication Date
    EP1023508A1 EP1023508A1 (en) 2000-08-02
    EP1023508B1 true EP1023508B1 (en) 2002-05-02

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    Application Number Title Priority Date Filing Date
    EP98961094A Expired - Lifetime EP1023508B1 (en) 1997-10-15 1998-09-30 System for controlling, independently of load pressure, and holding the load of a plurality of rotational and/or translational users

    Country Status (4)

    Country Link
    EP (1) EP1023508B1 (en)
    JP (1) JP2001520335A (en)
    DE (2) DE19745489B4 (en)
    WO (1) WO1999019571A1 (en)

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    DE102016215214A1 (en) * 2016-08-16 2018-02-22 Zf Friedrichshafen Ag Transmission device with several adjustable via hydraulically actuated piston-cylinder devices shift rails and interpretable translations

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    DE102006049584A1 (en) 2006-03-13 2007-09-20 Robert Bosch Gmbh LUDV valve assembly

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    DE102016215214A1 (en) * 2016-08-16 2018-02-22 Zf Friedrichshafen Ag Transmission device with several adjustable via hydraulically actuated piston-cylinder devices shift rails and interpretable translations
    US10480642B2 (en) 2016-08-16 2019-11-19 Zf Friedrichshafen Ag Multi speed transmission device with hydraulically actuated shift rods

    Also Published As

    Publication number Publication date
    DE19745489B4 (en) 2004-07-22
    DE19745489A1 (en) 1999-04-22
    DE59804000D1 (en) 2002-06-06
    EP1023508A1 (en) 2000-08-02
    JP2001520335A (en) 2001-10-30
    WO1999019571A1 (en) 1999-04-22

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