EP2682610B1 - Regulator system of a hydraulic variable capacity pump - Google Patents

Regulator system of a hydraulic variable capacity pump Download PDF

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Publication number
EP2682610B1
EP2682610B1 EP12174666.3A EP12174666A EP2682610B1 EP 2682610 B1 EP2682610 B1 EP 2682610B1 EP 12174666 A EP12174666 A EP 12174666A EP 2682610 B1 EP2682610 B1 EP 2682610B1
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EP
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Prior art keywords
pressure
regulating
line
actuating
actuating cylinder
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German (de)
French (fr)
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EP2682610A1 (en
Inventor
Georg Dipl.-Ing. Jemüller
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F15B11/055—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 by adjusting the pump output or bypass
    • 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

Definitions

  • the invention relates to a control system of a hydraulic variable displacement pump according to the preamble of patent claim 1.
  • the pilot valve assumes a throttling control position, so that pressure fluid is discharged from the signal pressure line in the return line, as well as the pilot valve for pressure control.
  • This means a loss which increases relative to the pump flow, the farther the pump is moved towards the minimum delivery, and may for example be about 2 to 3 l / min, so that then the pump has to work increasingly for loss compensation. This significantly degrades the volumetric efficiency.
  • variable pumps are pressure-controlled via the main stage and the pilot valve, either with adjustable pressure directly to the pump to keep the system pressure constant with varying flow requirements, for example in constant-pressure systems in which different flow rates are required, or as a low-loss pressure limitation of a hydraulic system.
  • the main stage can be operated as a load-sensing controller, for example with integrated pressure limitation of the system pressure, independent of the load pressure, wherein a load pressure signal of at least one consumer supplied by the variable displacement pump is fed into the signal pressure line and to the pilot valve.
  • a torque controller for example, to keep the product of pressure x flow constant, this torque controller is adjustable in a certain percentage of the drive torque of the variable displacement pump.
  • pilot valve a 2/2-way pressure control valve, for example with actuation by a proportional solenoid, it being possible to control the flow rate directly or indirectly proportional to the bias current of the proportional solenoid, that is, the flow rate with increasing Beaufschlagungsstrom for example, to increase linearly or to decrease linearly.
  • a proportional solenoid for example, the flow rate with increasing Beaufschlagungsstrom for example.
  • There may be more than one unilaterally acted actuator cylinder can be provided.
  • differential cylinder with double-sided pressurization, or an eccentric cradle can be used to adjust the pump.
  • the pilot valve allows pressure medium to flow out of the signal pressure line to the return line, which means a relatively increasing loss in the direction of the minimum displacement adjustment pump, which degrades the volumetric efficiency.
  • the invention has for its object to improve a control system of a hydraulic variable displacement pump, which is operated with volume control and / or torque control and a single main stage, in terms of volumetric efficiency.
  • the pressure medium discharged from the signal pressure line during the control does not flow as a loss into the return line but into the already lower pressure range of the actuating cylinder, so that Here, a pressure medium circuit is created, which is largely closed. Since there is a steadily adapting pressure level when the adjusting cylinder is pressurized, the torque and / or quantity control may possibly also be more stable than when the pressure medium is discharged into the substantially uniform, extremely low pressure level of the return line. Since thus drained pressure medium is not lost, despite the small-sized, cost-effective and lightweight Control system of the volumetric efficiency of the variable, for example, then significantly improved when the variable displacement is increasingly adjusted towards minimum funding.
  • the quantity pilot valve is adjustable by a proportional solenoid against spring force either to a passage position (the delivery increases directly proportional to the charge current of the proportional solenoid) or a blocking position (the flow rate per unit time decreases indirectly proportional to the charge current of the proportional solenoid) 2 / 2-way pressure control valve.
  • a proportional solenoid against spring force either to a passage position (the delivery increases directly proportional to the charge current of the proportional solenoid) or a blocking position (the flow rate per unit time decreases indirectly proportional to the charge current of the proportional solenoid) 2 / 2-way pressure control valve.
  • the application current of the proportional solenoid specifies the desired value of the quantity to be regulated. This setpoint specification could alternatively, e.g. on the pilot valve, hydraulically, pneumatically, by spring force, or otherwise done.
  • the torque control and / or the pressure control pilot valve is a pressure-controlled from the signal pressure line forth against spring force toward a passage position 2/2 pressure relief valve.
  • pilot valve types fulfill the control function for the pilot pressure of the main stage under spring force.
  • embodiments of the control system are possible in which e.g. in addition to the pressure regulator pilot valve only the flow control pilot valve or only the torque control pilot valve are provided.
  • the torque control is suitably adjustable by the spring-control pilot valve in the direction of a locking position acting spring force is adjustable.
  • the torque control (or power control) intervenes, for example, only from a selectable pressure level within the usable pressure range and then to the maximum pressure to reduce the flow rate after a predetermined curve.
  • the spring force of the flow control and / or torque control pilot valve is generated by a spring and by a position feedback feedback, preferably the actuating cylinder, changeable.
  • a position feedback feedback preferably the actuating cylinder, changeable.
  • the spring force can be changed with increasing adjustment of the pump in the direction of minimum delivery, for example, increased.
  • the return takes place by tapping off the position of the first actuating cylinder via a cam surface and a button that changes the set spring preload or spring force.
  • the feedback can also be done by using a displacement transducer, a pressure sensor, an angle sensor of the swash plate, etc. In this way, the control loop is simply closed via the pilot valve.
  • the pressure in the signal pressure line can be generated by means of an inlet nozzle from the pressure line leading to the main stage in the control system itself and modified if necessary.
  • the signal pressure line may be connected to a load pressure signal circuit of at least one consumer powered by the pump and separated from the pressure line.
  • a control line is connected to the actuating cylinder between the main stage and the actuating cylinder via a nozzle to the return line.
  • the consequent loss of pressure medium is negligible.
  • the 3/2-way pressure control valve of the main stage in the direction of adjustment for connecting the pressure line and the first actuating cylinder from the pressure line ssenvorteil, that is from the delivery pressure of the variable itself, and pressure controlled in the direction of the connection of the first actuating cylinder with the return line from the signal pressure line and spring loaded.
  • This spring load is conveniently adjustable, z. B. to produce a constant pressure level below the set by the system pressure relief valve pressure levels in variations of the flow rate.
  • At least one second actuating cylinder may be loaded from the pressure line and spring-biased, e.g. in such a way that the variable-speed pump starts up with maximum delivery during commissioning, for example before the control system intervenes.
  • variable displacement pump equipped with the control system is a swashplate type axial piston pump, for example with a nominal pressure of up to about 350 bar, a maximum pressure of about 400 bar, and type-dependent with a displacement volume of 60, 90 or 110 cm 3 / rev.
  • This design is robust and reliable and designed for flanging on power take-offs of commercial vehicle transmissions or for a standard connection with an SAE flange, and is universally suitable for other applications.
  • the design has a high Denansaugnaviere and a low sound pressure level.
  • the volume flow is proportional to the speed and the current displacement volume and can be infinitely adjusted.
  • Such variable displacement pumps are particularly suitable for use with proportional directional slides and can be operated with alternating direction of rotation.
  • the actuating cylinders engage e.g. together on a swash plate adjusting.
  • the actuating cylinders are arranged in pairs and connected in parallel.
  • this actuating cylinder has a larger pressurization surface than every second actuating cylinder.
  • the area ratio may be between about 2: 1 to 5: 1, or even greater, controlling the pressure fluid discharged to the actuator cylinder very precisely.
  • the pilot valves for pressure and / or torque control may e.g. Be slide valves.
  • a control system S of a hydraulic variable-displacement pump V is arranged, for example, with a control system housing 9 on or in a variable-displacement pump housing 1.
  • the variable displacement pump V is, for example, a swashplate axial piston pump 2, whose volumetric flow is steplessly adjustable in the direction of a double arrow between maximum delivery and minimum delivery by means of a swash plate adjusting element 3.
  • At least one actuating cylinder Z1 (and optionally a second actuating cylinder Z2) engages on the adjusting element 3.
  • FIG Fig. 1 is a parallel-connected pair of first actuating cylinder Z1, Z1 'and a parallel pair of second actuating cylinder Z2, Z2' provided.
  • sensors 35 transducers, angle sensors, pressure sensors, or the like
  • sensors 35 could be used for reporting, e.g.
  • at least one double-acting differential adjusting cylinder could be used to adjust the pump, or an eccentric cradle (not shown).
  • Each actuating cylinder Z1, Z1 ' is connected at its pressurization side to a control line 7.
  • the second actuating cylinders Z2, Z2 'further comprise springs 34, that is, are spring-biased to the variable displacement pump V as by the pressurization from the pressure line 8, for. in the direction of maximum promotion.
  • a pressurization of the actuating cylinder Z1, Z1 'then takes an adjustment in the direction of minimum funding.
  • a pressure port 10 is indicated (X, LS) on which a signal pressure in a signal pressure line 21 can either be measured or fed, for example, from a load pressure signal circuit LS of the consumer M, comes ( Fig. 2 ).
  • a signal pressure in a signal pressure line 21 can either be measured or fed, for example, from a load pressure signal circuit LS of the consumer M, comes ( Fig. 2 ).
  • the pressure in the signal pressure line 21 from the control system S itself adjustable.
  • the control system S includes a single main stage 11, which is designed as a 3/2-way control valve and connected to the pressure line 8 and a return line 19 on the one hand and to the control line 7 on the other.
  • the 3/2-way pressure control valve 12 is pressure-controlled from the pressure line 8 via a pilot line 16 and from the signal pressure line 21 via a pilot line 13, wherein on the side of the pilot line 13, a spring force 15 is effective, which is, suitably, adjustable ,
  • the 3/2-way pressure control valve 12 is switched after startup of the variable V in the setting for maximum promotion from the switching position shown in another switching position in which the pressure line 8 is connected to the control line 7 and the return line 19 is shut off , so that the adjusting cylinders Z1, Z1 'are pressurized and adjust the variable displacement pump V in the direction of minimum promotion, against the force of the pressurization of the second actuating cylinder Z2, Z2 'from the pressure line 8 and the biasing springs 34.
  • the pressurization surface of each first actuating cylinder Z1, Z1' is expediently larger than the pressurization surface of the second actuating cylinder Z2, Z2 '(area ratio eg between 2: 1 to 5: 1 or greater).
  • the line 22 leads to a pressure control pilot valve 34 (with suitably adjustable spring force), from the drain side, a line 31 via a node 32 to a node 33 of the control line 7 leads.
  • a line 23 branching off from the line 22 leads to an inlet side of a quantity control pilot valve 24.
  • the line 22 ' leads to the inlet side of a torque control pilot valve 25, which is pressure-controlled from the line 22' against a spring force 22 and 2/2 Way drain valve may be formed.
  • the flow control pilot valve 24 is a 2/2-way pressure control valve, which is actuated by a proportional solenoid 26 against spring force 28, and, preferably, even a proportional pressure pilot 27 may have.
  • the proportional solenoid 26 actuates the valve 24 in the direction of a passage position against the spring force 28 which adjusts a shut-off position.
  • the energization of the proportional magnet 26 is a desired value specification for the quantity control. This set point specification could also be made hydraulically, mechanically, pneumatically or otherwise (not shown).
  • the pilot valves 25, 24, 34 are each connected at the outlet side to the node 32 and thus via the line 31 to the node 33 in the control line 7 and the respective actuating cylinder Z1, Z1 'connected to feed according to the invention pressure medium there, so that this pressure medium from the signal pressure line 21 is not lost.
  • the pilot valves 24, 25, 34 (or only 24 or 25 and 34) are associated with the main stage 11 and in the embodiment shown in FIG Fig. 1 the pressure difference generated by the inlet nozzle 14 for the main stage 11th
  • the pilot valve 24 is, as long as the proportional solenoid 26 is not energized, in the shut-off position, and has no influence on the pressure in the signal pressure line 21. If the proportional solenoid 26 is energized, then the pilot valve 24 reduces the pressure in the signal pressure line 21, with increasing Adjustment of the actuating cylinder Z1, Z1 'eg in the direction of the minimum promotion of the variable V increases the spring force 28 and thus the pressure in the signal pressure line 21 is increased again with constant energization of the proportional magnet 26.
  • FIG. 2 shown detail variant ends the pressure line 8 to the main stage 11 and the pressure in the signal pressure line 21, for example, from the load pressure signal circuit LS used to adjust the main stage 11 against the pressure in the pilot line 16 from the pressure line 8.
  • Fig. 3 In the detail variant in Fig. 3 is the pilot valve 24 'connected inversely to flow control as in Fig. 1 that is, the spring force 28 holds the control valve 24 'in the passage position shown, while the proportional solenoid 26 causes an adjustment in the direction or to the shut-off when energized against the spring force 28.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Description

Die Erfindung betrifft ein Regelsystem einer Hydraulik-Verstellpumpe gemäß Oberbegriff des Patentanspruchs 1.The invention relates to a control system of a hydraulic variable displacement pump according to the preamble of patent claim 1.

Aus der technischen Informationsschrift D 7960 N, der Firma HAWE Hydraulik SE, Streitfeldstraße 25, 81673 München, Ausgabe Juli 2011-03, Seiten 2 und 3, sowie Seite 19, Kennzeichen ZL; LLSN; LN, sind solche Regelsysteme für Hydraulik-Verstellpumpen z. B. eines Axialkolben-Schrägscheiben-Typs, bekannt, bei denen für eine Leistungs- bzw. DrehmomentRegelung der für die Druckregelung verantwortlichen Hauptstufe ein an die Signaldruckleitung angeschlossenes Vorsteuerventil zugeordnet ist. Dieses Vorsteuerventil ist ein z. B. 2/2-Wege-Ablassventil mit Federbelastung und Druckvorsteuerung aus der Signaldruckleitung und ist ablaufseitig mit einer Rücklaufleitung verbunden. Sobald die Pumpe durch den Stellzylinder z.B. aus der Stellung für Maximalförderung in Richtung zur Minimalförderung verstellt wird, nimmt das Vorsteuerventil eine drosselnde Regelstellung ein, so dass Druckmittel aus der Signaldruckleitung in die Rücklaufleitung abgelassen wird, wie auch vom Vorsteuerventil zur Druckregelung. Dies bedeutet einen Verlust, der relativ zum Pumpen-Förderstrom zunimmt, je weiter die Pumpe in Richtung zur Minimalförderung verstellt wird, und kann beispielsweise etwa 2 bis 3 l/min betragen, so dass dann die Pumpe zunehmend zur Verlustkompensation arbeiten muss. Dies verschlechtert den volumetrischen Wirkungsgrad erheblich. Diese Regelsysteme bieten als Ausstattung von Verstellpumpen den wichtigen Vorteil kostengünstiger kleiner Vorsteuerventile, kleiner Abmessungen und geringen Gewichts, was z.B. bei Einsatz an oder in Fahrzeugen sehr bedeutsam ist. Solche Verstellpumpen werden über die Hauptstufe und deren Vorsteuerventil druckgeregelt, entweder mit direkt an der Pumpe einstellbarem Druck, um bei variierendem Förderstrombedarf den Systemdruck konstant zu halten, beispielsweise in Konstant-Drucksystemen, in denen unterschiedliche Förderströme gefragt sind, oder als verlustarme Druckbegrenzung eines Hydrauliksystems. Alternativ kann die Hauptstufe als Load-Sensing-Regler, beispielsweise mit integrierter Druckbegrenzung des Systemdrucks, lastdruckunabhängig betrieben werden, wobei ein Lastdrucksignal wenigstens eines von der Verstellpumpe gespeisten Verbrauchers in die Signaldruckleitung und zum Vorsteuerventil eingespeist wird. Diese beiden Regelprinzipien können kombiniert werden mit einem Drehmoment-Regler, beispielsweise um das Produkt aus Druck x Förderstrom konstant zu halten, wobei dieser Drehmoment-Regler in einem einen bestimmten Prozentanteil des Antriebsmoments der Verstellpumpe verstellbar ist. Aus der Praxis ist es ferner bekannt, in ein solches Regelsystem alternativ oder additiv zum Drehmoment-Regler einen Mengenregler zu integrieren. Hierfür wird ebenfalls ein Vorsteuerventil der einzigen Hauptstufe zugeordnet und an die Signaldruckleitung angeschlossen, das ablaufseitig an die Rücklaufleitung angeschlossen ist. Der Mengenregler greift z. B. über den gesamten nutzbaren Druckbereich ein, ehe die Verstellpumpe mechanisch auf Anschlag kommt, um über den gesamten Druckbereich beispielsweise eine gleichbleibende, oder zunehmende oder abnehmende Menge einzuregeln. Hierzu ist es bekannt, als Vorsteuerventil ein 2/2-Wege-Druckregelventil z.B. mit Betätigung durch einen Proportionalmagneten zu verwenden, wobei es möglich ist, die Fördermenge direkt oder indirekt proportional zum Beaufschlagungsstrom des Proportionalmagneten zu regeln, das heißt, die Fördermenge mit zunehmendem Beaufschlagungsstrom beispielsweise linear ansteigen oder linear abfallen zu lassen.
Es können mehr als ein einseitig beaufschlagbarer Stellzylinder vorgesehen sein. Auch Differentialzylinder mit doppelseitiger Druckbeaufschlagung, oder eine exzentrische Wiege können zum Verstellen der Pumpe verwendet werden. Sobald die Verstellpumpe z.B. in Richtung zur Minimalförderung verstellt wird, lässt das Vorsteuerventil Druckmittel aus der Signaldruckleitung zur Rücklaufleitung abströmen, was einen bei in Richtung zur Minimalförderung verstellter Verstellpumpe relativ zunehmenden Verlust bedeutet, der den volumetrischen Wirkungsgrad verschlechtert.From the technical information document D 7960 N, the company HAWE Hydraulik SE, Streitfeldstraße 25, 81673 Munich, July 2011-03 issue, pages 2 and 3, and page 19, license plate ZL; LLSN; LN, such control systems for hydraulic variable displacement pumps z. B. an axial piston swashplate type, known, in which for a power or torque control of the main stage responsible for the pressure control is associated with a connected to the signal pressure line pilot valve. This pilot valve is a z. B. 2/2-way drain valve with spring load and pressure feedforward from the signal pressure line and is connected to the drain side with a return line. Once the pump is adjusted by the actuator cylinder, for example, from the position for maximum delivery in the direction of minimum funding, the pilot valve assumes a throttling control position, so that pressure fluid is discharged from the signal pressure line in the return line, as well as the pilot valve for pressure control. This means a loss, which increases relative to the pump flow, the farther the pump is moved towards the minimum delivery, and may for example be about 2 to 3 l / min, so that then the pump has to work increasingly for loss compensation. This significantly degrades the volumetric efficiency. These control systems offer as equipment of variable displacement pumps the important advantage of inexpensive small pilot valves, small dimensions and low weight, which is very important for use on or in vehicles. Such variable pumps are pressure-controlled via the main stage and the pilot valve, either with adjustable pressure directly to the pump to keep the system pressure constant with varying flow requirements, for example in constant-pressure systems in which different flow rates are required, or as a low-loss pressure limitation of a hydraulic system. Alternatively, the main stage can be operated as a load-sensing controller, for example with integrated pressure limitation of the system pressure, independent of the load pressure, wherein a load pressure signal of at least one consumer supplied by the variable displacement pump is fed into the signal pressure line and to the pilot valve. These two control principles can be combined with a torque controller, for example, to keep the product of pressure x flow constant, this torque controller is adjustable in a certain percentage of the drive torque of the variable displacement pump. From practice, it is also known to integrate into such a control system alternatively or in addition to the torque controller a flow regulator. This is also for this a pilot valve assigned to the single main stage and connected to the signal pressure line, which is connected to the drain side of the return line. The flow regulator uses z. B. over the entire usable pressure range before the variable pump mechanically comes to a stop to regulate over the entire pressure range, for example, a constant, or increasing or decreasing amount. For this purpose, it is known to use as pilot valve, a 2/2-way pressure control valve, for example with actuation by a proportional solenoid, it being possible to control the flow rate directly or indirectly proportional to the bias current of the proportional solenoid, that is, the flow rate with increasing Beaufschlagungsstrom for example, to increase linearly or to decrease linearly.
There may be more than one unilaterally acted actuator cylinder can be provided. Also differential cylinder with double-sided pressurization, or an eccentric cradle can be used to adjust the pump. As soon as the variable-displacement pump is adjusted, for example, in the direction of minimum delivery, the pilot valve allows pressure medium to flow out of the signal pressure line to the return line, which means a relatively increasing loss in the direction of the minimum displacement adjustment pump, which degrades the volumetric efficiency.

Es sind ferner Regelsysteme bekannt, die mehrere Hauptstufen ohne Vorsteuerventile enthalten. Diese Bauweise bedingt jedoch deutlich höhere Kosten, große Abmessungen und höheres Gewicht.There are also known control systems that contain several main stages without pilot valves. However, this design requires significantly higher costs, large dimensions and higher weight.

Weiterer Stand der Technik ist zu finden in CH 431 221A .Further prior art can be found in CH 431 221A ,

Der Erfindung liegt die Aufgabe zugrunde, ein Regelsystem einer Hydraulik-Verstellpumpe, die mit Mengenregelung und/oder Drehmoment-Regelung und einer einzigen Hauptstufe betrieben wird, hinsichtlich des volumetrischen Wirkungsgrades zu verbessern.The invention has for its object to improve a control system of a hydraulic variable displacement pump, which is operated with volume control and / or torque control and a single main stage, in terms of volumetric efficiency.

Die gestellte Aufgabe wird mit den Merkmalen des Patentanspruchs 1 gelöst.The stated object is achieved with the features of claim 1.

In dem das jeweilige Vorsteuerventil zumindest des Mengen- und/oder Drehmoment-Reglers ablaufseitig an den Stellzylinder angeschlossen ist, strömt das bei der Regelung aus der Signaldruckleitung abgelassene Druckmittel nicht als Verlust in die Rücklaufleitung, sondern in den ohnedies niedrigeren Druckbereich des Stellzylinders, so dass hier ein Druckmittelkreislauf geschaffen ist, der weitestgehend geschlossen ist. Da bei Druckbeaufschlagung des Stellzylinders ein sich stetig anpassendes Druckniveau vorliegt, kann gegebenenfalls auch die Drehmoment- und/oder Mengen-Regelung stabiler ablaufen, als bei Ablassen des Druckmittels in das im Wesentlichen gleichförmige, extrem niedrige Druckniveau der Rücklaufleitung. Da somit abgelassenes Druckmittel nicht verloren geht, wird trotz des kleinbauenden, kostengünstigen und leichten Regelsystems der volumetrische Wirkungsgrad der Verstellpumpe z.B. dann erheblich verbessert, wenn die Verstellpumpe zunehmend in Richtung zur Minimalförderung verstellt wird.In that the respective pilot valve at least of the flow and / or torque controller is connected to the actuating cylinder on the outlet side, the pressure medium discharged from the signal pressure line during the control does not flow as a loss into the return line but into the already lower pressure range of the actuating cylinder, so that Here, a pressure medium circuit is created, which is largely closed. Since there is a steadily adapting pressure level when the adjusting cylinder is pressurized, the torque and / or quantity control may possibly also be more stable than when the pressure medium is discharged into the substantially uniform, extremely low pressure level of the return line. Since thus drained pressure medium is not lost, despite the small-sized, cost-effective and lightweight Control system of the volumetric efficiency of the variable, for example, then significantly improved when the variable displacement is increasingly adjusted towards minimum funding.

Wenn auch das Vorsteuerventil zur Druckregelung ablaufseitig an den Stellzylinder angeschlossen ist, werden Verluste noch mehr minimiert.If the pilot valve for pressure control is connected to the actuating cylinder on the outlet side, losses are minimized even more.

In einer zweckmäßigen Ausführungsform ist das Mengen-Vorsteuerventil ein durch einen Proportionalmagneten gegen Federkraft entweder zu einer Durchgangsstellung (die Fördermenge nimmt direkt proportional zum Beaufschlagungsstrom des Proportionalmagneten zu) oder einer Sperrstellung (die Fördermenge pro Zeiteinheit nimmt indirekt proportional zum Beaufschlagungsstrom des Proportionalmagneten ab) verstellbares 2/2-Wege-Druckregelventil. Um mit einem kleinbauenden und leichten Proportionalmagneten auskommen zu können, kann es sogar zweckmäßig sein, das Vorsteuerventil mit einer Proportional-Druckvorsteuerung durch den Proportionalmagneten auszustatten. Der Beaufschlagungsstrom des Proportionalmagneten gibt den Sollwert der zu regelnden Menge vor. Diese Sollwertvorgabe könnte alternativ, z.B. am Vorsteuerventil, hydraulisch, pneumatisch, durch Federkraft, oder auf andere Weise erfolgen.In an expedient embodiment, the quantity pilot valve is adjustable by a proportional solenoid against spring force either to a passage position (the delivery increases directly proportional to the charge current of the proportional solenoid) or a blocking position (the flow rate per unit time decreases indirectly proportional to the charge current of the proportional solenoid) 2 / 2-way pressure control valve. To be able to manage with a small-sized and lightweight proportional magnet, it may even be appropriate to equip the pilot valve with a proportional pressure pilot by the proportional solenoid. The application current of the proportional solenoid specifies the desired value of the quantity to be regulated. This setpoint specification could alternatively, e.g. on the pilot valve, hydraulically, pneumatically, by spring force, or otherwise done.

Bei einer anderen zweckmäßigen Ausführungsform ist das Drehmoment-Regel- und/oder das Druckregel-Vorsteuerventil ein von der Signaldruckleitung her gegen Federkraft in Richtung zu einer Durchgangsstellung druckvorgesteuertes 2/2-Druckentlastungsventil.In another advantageous embodiment, the torque control and / or the pressure control pilot valve is a pressure-controlled from the signal pressure line forth against spring force toward a passage position 2/2 pressure relief valve.

Beide Vorsteuerventilarten erfüllen die Regelfunktion für den Vorsteuerdruck der Hauptstufe unter Federkraft. Dabei sind Ausführungsformen des Regelsystems möglich, bei denen z.B. zusätzlich zum Druckregler-Vorsteuerventil nur das Mengenregel-Vorsteuerventil oder nur das Drehmoment-Regel-Vorsteuerventil, vorgesehen sind.Both pilot valve types fulfill the control function for the pilot pressure of the main stage under spring force. In this case, embodiments of the control system are possible in which e.g. in addition to the pressure regulator pilot valve only the flow control pilot valve or only the torque control pilot valve are provided.

Die Drehmoment-Regelung ist zweckmäßig einstellbar, indem die das Drehmoment-Regel-Vorsteuerventil in Richtung zu einer Sperrstellung beaufschlagende Federkraft einstellbar ist. Die Drehmomentregelung (oder Leistungsregelung) greift beispielsweise erst ab einem wählbaren Druckniveau innerhalb des nutzbaren Druckbereichs und dann bis zum Maximaldruck ein, um den Förderstrom nach einer vorgegebenen Kurve zu verringern.The torque control is suitably adjustable by the spring-control pilot valve in the direction of a locking position acting spring force is adjustable. The torque control (or power control) intervenes, for example, only from a selectable pressure level within the usable pressure range and then to the maximum pressure to reduce the flow rate after a predetermined curve.

Bei einer zweckmäßigen Ausführungsform ist die Federkraft des Mengenregel- und/oder Drehmomentregel-Vorsteuerventils von einer Stellfeder generiert und durch eine Stellungs-Istwert-Rückführung, vorzugsweise des Stellzylinders, veränderbar. Durch Rückführung des Stellungs-Istwerts der Verstellpumpe kann die Federkraft mit zunehmender Verstellung der Pumpe in Richtung zur Minimalförderung geändert, z.B. erhöht, werden. Auf baulich einfache Weise erfolgt die Rückführung durch den Abgriff der Position des ersten Stellzylinders über eine Nockenfläche und einen Taster, der die eingestellte Federvorspannung bzw. Federkraft verändert. Alternativ kann die Rückführung auch durch Benutzen eines Wegaufnehmers, eines Drucksensors, eines Winkelsensors der Schrägscheibe, etc. erfolgen. Auf diese Weise wird der Regelkreis einfach über das Vorsteuerventil geschlossen.In an advantageous embodiment, the spring force of the flow control and / or torque control pilot valve is generated by a spring and by a position feedback feedback, preferably the actuating cylinder, changeable. By returning the actual position value of the variable displacement pump, the spring force can be changed with increasing adjustment of the pump in the direction of minimum delivery, for example, increased. In a structurally simple manner, the return takes place by tapping off the position of the first actuating cylinder via a cam surface and a button that changes the set spring preload or spring force. Alternatively, the feedback can also be done by using a displacement transducer, a pressure sensor, an angle sensor of the swash plate, etc. In this way, the control loop is simply closed via the pilot valve.

Um die Hauptstufe zu betätigen, sind unterschiedliche Verschaltungen der Signaldruckleitung möglich. Es kann der Druck in der Signaldruckleitung über eine Zulaufdüse aus der zur Hauptstufe führenden Druckleitung im Regelsystem selbst erzeugt und gegebenenfalls verändert werden. Als Alternative kann die Signaldruckleitung an einen Lastdrucksignalkreis wenigstens eines von der Pumpe gespeisten Verbrauchers angeschlossen und von der Druckleitung separiert sein.To operate the main stage, different interconnections of the signal pressure line are possible. The pressure in the signal pressure line can be generated by means of an inlet nozzle from the pressure line leading to the main stage in the control system itself and modified if necessary. Alternatively, the signal pressure line may be connected to a load pressure signal circuit of at least one consumer powered by the pump and separated from the pressure line.

Ferner ist es zweckmäßig, wenn eine Stellleitung zum Stellzylinder zwischen der Hauptstufe und dem Stellzylinder über eine Düse an die Rücklaufleitung angeschlossen ist. Der dadurch bedingte Druckmittelverlust ist vernachlässigbar.Furthermore, it is expedient if a control line is connected to the actuating cylinder between the main stage and the actuating cylinder via a nozzle to the return line. The consequent loss of pressure medium is negligible.

Zweckmäßig ist das 3/2-Wege-Druckregelventil der Hauptstufe in Stellrichtung zur Verbindung der Druckleitung und des ersten Stellzylinders aus der Druckleitung druckvorgesteuert, das heißt vom Förderdruck der Verstellpumpe selbst, und in Stellrichtung zur Verbindung des ersten Stellzylinders mit der Rücklaufleitung aus der Signaldruckleitung druckvorgesteuert und federbelastet. Diese Federbelastung ist zweckmäßigerweise einstellbar, z. B. um bei Variationen der Fördermenge ein gleichbleibendes Druckniveau unterhalb des vom Systemdruckbegrenzungsventil festgesetzten Druckniveaus zu erzeugen.Conveniently, the 3/2-way pressure control valve of the main stage in the direction of adjustment for connecting the pressure line and the first actuating cylinder from the pressure line druckvorgesteuert, that is from the delivery pressure of the variable itself, and pressure controlled in the direction of the connection of the first actuating cylinder with the return line from the signal pressure line and spring loaded. This spring load is conveniently adjustable, z. B. to produce a constant pressure level below the set by the system pressure relief valve pressure levels in variations of the flow rate.

Wenigstens ein zweiter Stellzylinder kann aus der Druckleitung beaufschlagt und federvorgespannt sein, z.B. so, dass die Verstellpumpe bei Inbetriebnahme mit Maximalförderung anläuft, beispielsweise ehe das Regelsystem eingreift.At least one second actuating cylinder may be loaded from the pressure line and spring-biased, e.g. in such a way that the variable-speed pump starts up with maximum delivery during commissioning, for example before the control system intervenes.

In einer zweckmäßigen Ausführungsform ist die mit dem Regelsystem ausgestattete Verstellpumpe eine Axialkolbenpumpe in Schrägscheibenbauart, beispielsweise mit einem Nenndruck bis zu etwa 350 bar, einem Maximaldruck von etwa 400 bar, und typabhängig mit einem Verdrängervolumen von 60, 90 oder 110 cm3/U. Diese Bauart ist robust und zuverlässig und zum Anflanschen an Nebenabtriebe von Nutzfahrzeuggetrieben oder für eine standardgemäße Verbindung mit einem SAE-Flansch konzipiert, und ist universell auch für andere Einsatzzwecke geeignet. Die Bauweise hat eine hohe Selbstansaugdrehzahl und einen geringen Schalldruckpegel. Der Volumenstrom ist proportional zur Drehzahl und dem aktuellen Verdrängungsvolumen und kann stufenlos verstellt werden. Solche Verstellpumpen sind besonders geeignet für einen Einsatz mit Proportional-Wegeschiebern und können mit wechselnder Drehrichtung betrieben werden.In an expedient embodiment, the variable displacement pump equipped with the control system is a swashplate type axial piston pump, for example with a nominal pressure of up to about 350 bar, a maximum pressure of about 400 bar, and type-dependent with a displacement volume of 60, 90 or 110 cm 3 / rev. This design is robust and reliable and designed for flanging on power take-offs of commercial vehicle transmissions or for a standard connection with an SAE flange, and is universally suitable for other applications. The design has a high Selbstansaugdrehzahl and a low sound pressure level. The volume flow is proportional to the speed and the current displacement volume and can be infinitely adjusted. Such variable displacement pumps are particularly suitable for use with proportional directional slides and can be operated with alternating direction of rotation.

Die Stellzylinder greifen z.B. gemeinsam an einem Schrägscheibenverstellglied an. Zweckmäßig sind die Stellzylinder jeweils paarweise angeordnet und parallel geschaltet.The actuating cylinders engage e.g. together on a swash plate adjusting. Suitably, the actuating cylinders are arranged in pairs and connected in parallel.

Im Hinblick auf ein moderates Druckniveau bei Beaufschlagen des Stellzylinders aus dem Regelsystem ist es zweckmäßig, wenn dieser Stellzylinder eine größere Druckbeaufschlagungsfläche aufweist, als jeder zweite Stellzylinder. Das Flächenverhältnis kann zwischen etwa 2 : 1 bis 5 : 1 liegen, oder sogar noch größer sein, die zum Stellzylinder abgelassenes Druckmittel sehr präzise steuern.With regard to a moderate pressure level when acting on the actuating cylinder from the control system, it is expedient if this actuating cylinder has a larger pressurization surface than every second actuating cylinder. The area ratio may be between about 2: 1 to 5: 1, or even greater, controlling the pressure fluid discharged to the actuator cylinder very precisely.

Die Vorsteuerventile zur Druck- und/oder Drehmomentregelung können z.B. Schieberventile sein.The pilot valves for pressure and / or torque control may e.g. Be slide valves.

Ausführungsformen des Erfindungsgegenstandes werden anhand der Zeichnung erläutert. Es zeigen:

Fig. 1
ein Blockschaltbild eines Regelsystems einer Hydraulik-Verstellpumpe, in drucklosem Zustand,
Fig. 2
eine Detailvariante,
Fig. 3
eine weitere Detailvariante, und
Fig. 4
eine weitere Detailvariante.
Embodiments of the subject invention will be explained with reference to the drawing. Show it:
Fig. 1
a block diagram of a control system of a hydraulic variable displacement pump, in a pressureless state,
Fig. 2
a detail variant,
Fig. 3
another detail variant, and
Fig. 4
another detail variant.

Ein Regelsystem S einer Hydraulik-Verstellpumpe V ist beispielsweise mit einem Regelsystem-Gehäuse 9 an oder in einem Verstellpumpen-Gehäuse 1 angeordnet. Die Verstellpumpe V ist beispielsweise eine Schrägscheiben-Axialkolbenpumpe 2, deren Volumenstrom stufenlos in Richtung eines Doppelpfeils zwischen Maximalförderung und Minimalförderung mittels eines Schrägscheiben-Verstellgliedes 3 verstellbar ist. An dem Verstellglied 3 greift wenigstens ein Stellzylinder Z1 (und optional ein zweiter Stellzylinder Z2) an. In der gezeigten Ausführungsform in Fig. 1 ist ein parallel geschaltetes Paar erster Stellzylinder Z1, Z1' und ein parallel geschaltetes Paar zweiter Stellzylinder Z2, Z2' vorgesehen. Der Stellzylinder Z1, Z1' enthält einen Kolben 4, an dem beispielsweise als Positions-Istwert-Rückführung F der Verstellpumpe V eine Nockenfläche 5 angeordnet ist, die über einen mechanischen Taster 6 die Kolbenstellung abgreift, und somit indirekt die Verstellposition der Verstellpumpe V meldet. Der Stellzylinder Z1, Z1' wird einseitig aus dem Regelsystem S druckbeaufschlagt.A control system S of a hydraulic variable-displacement pump V is arranged, for example, with a control system housing 9 on or in a variable-displacement pump housing 1. The variable displacement pump V is, for example, a swashplate axial piston pump 2, whose volumetric flow is steplessly adjustable in the direction of a double arrow between maximum delivery and minimum delivery by means of a swash plate adjusting element 3. At least one actuating cylinder Z1 (and optionally a second actuating cylinder Z2) engages on the adjusting element 3. In the embodiment shown in FIG Fig. 1 is a parallel-connected pair of first actuating cylinder Z1, Z1 'and a parallel pair of second actuating cylinder Z2, Z2' provided. The actuating cylinder Z1, Z1 'contains a piston 4, on which, for example, a cam surface 5 is arranged as a position-actual feedback F of the variable V, which picks up the piston position via a mechanical button 6, and thus indirectly reports the adjustment of the variable V. The actuating cylinder Z1, Z1 'is pressurized on one side from the control system S.

Alternativ könnten Sensoren 35 (Wegaufnehmer, Winkelsensoren, Drucksensoren, oder Ähnliche) zum Melden verwendet werden, z. B. am Stellzylinder Z1' oder am Verstellglied 3. Alternativ könnte wenigstens ein doppelseitig beaufschlagter Differential-Stellzylinder zur Pumpenverstellung verwendet werden, oder eine exzentrische Wiege (nicht gezeigt).Alternatively, sensors 35 (transducers, angle sensors, pressure sensors, or the like) could be used for reporting, e.g. Alternatively, at least one double-acting differential adjusting cylinder could be used to adjust the pump, or an eccentric cradle (not shown).

Jeder Stellzylinder Z1, Z1' ist an seiner Druckbeaufschlagungsseite an eine Stellleitung 7 angeschlossen. Die zweiten Stellzylinder Z2, Z2' sind an ihren Druckbeaufschlagungsseiten an eine von der Verstellpumpe gespeiste Druckleitung 8 angeschlossen sind, aus der ein nur schematisch angedeuteter Verbraucher M, beispielsweise über nicht gezeigte Steuerventile, gespeist wird. Die zweiten Stellzylinder Z2, Z2' enthalten ferner Federn 34, das heißt, sind federvorgespannt, um wie auch durch die Druckbeaufschlagung aus der Druckleitung 8 die Verstellpumpe V z.B. in Richtung zur Maximalförderung zu verstellen. Eine Druckbeaufschlagung der Stellzylinder Z1, Z1' nimmt dann eine Verstellung in Richtung zur Minimalförderung vor.Each actuating cylinder Z1, Z1 'is connected at its pressurization side to a control line 7. The second actuating cylinder Z2, Z2 'are connected at their Druckbeaufschlagungsseiten to one of the variable displacement pumped pressure line 8, from which an only schematically indicated consumer M, for example, via control valves, not shown, is fed. The second actuating cylinders Z2, Z2 'further comprise springs 34, that is, are spring-biased to the variable displacement pump V as by the pressurization from the pressure line 8, for. in the direction of maximum promotion. A pressurization of the actuating cylinder Z1, Z1 'then takes an adjustment in the direction of minimum funding.

Am Gehäuse 9 des Regelsystems S ist ein Druckanschluss 10 angedeutet (X, LS) an dem ein Signaldruck in einer Signaldruckleitung 21 entweder gemessen oder eingespeist werden kann, der beispielsweise aus einem Lastdrucksignalkreis LS des Verbrauchers M, stammt (Fig. 2). In der in Fig. 1 gezeigten Ausführungsform ist beispielsweise der Druck in der Signaldruckleitung 21 vom Regelsystem S selbst einstellbar.On the housing 9 of the control system S, a pressure port 10 is indicated (X, LS) on which a signal pressure in a signal pressure line 21 can either be measured or fed, for example, from a load pressure signal circuit LS of the consumer M, comes ( Fig. 2 ). In the in Fig. 1 shown embodiment, for example, the pressure in the signal pressure line 21 from the control system S itself adjustable.

Zur Druckregelung enthält das Regelsystem S eine einzige Hauptstufe 11, die als 3/2-Wege-Regelventil ausgebildet und an die Druckleitung 8 sowie eine Rücklaufleitung 19 einerseits und an die Stellleitung 7 andererseits angeschlossen ist. Das 3/2-Wege-Druckregelventil 12 wird aus der Druckleitung 8 über eine Vorsteuerleitung 16 und aus der Signaldruckleitung 21 über eine Vorsteuerleitung 13 jeweils druckvorgesteuert, wobei an der Seite der Vorsteuerleitung 13 auch eine Federkraft 15 wirksam ist, die, zweckmäßig, einstellbar ist.For pressure control, the control system S includes a single main stage 11, which is designed as a 3/2-way control valve and connected to the pressure line 8 and a return line 19 on the one hand and to the control line 7 on the other. The 3/2-way pressure control valve 12 is pressure-controlled from the pressure line 8 via a pilot line 16 and from the signal pressure line 21 via a pilot line 13, wherein on the side of the pilot line 13, a spring force 15 is effective, which is, suitably, adjustable ,

In der gezeigten Stellung (druckloses System) verbindet das 3/2-Wege-Druckregelventil 12 die Stellleitung 17 mit der Rücklaufleitung 19, während die Druckleitung 8 abgesperrt ist. Die Druckleitung 8 führt über eine Zulaufdüse 14 zur Signaldruckleitung 21. Über die Zulaufdüse 14 wird im Betrieb eine Druckdifferenz erzeugt, welche die Hauptstufe 11 mit Einflussnahme der Federkraft 15 zur Druckregelung umsetzt. Über die Vorsteuerleitung 16 wird das 3/2-Wege-Druckregelventil 12 nach Anlaufen der Verstellpumpe V in der Einstellung für Maximalförderung aus der gezeigten Schaltstellung in eine andere Schaltstellung umgeschaltet, in der die Druckleitung 8 mit der Stellleitung 7 verbunden und die Rücklaufleitung 19 abgesperrt ist, so dass die Stellzylinder Z1, Z1' druckbeaufschlagt werden und die Verstellpumpe V in Richtung zur Minimalförderung verstellen, und zwar gegen die Kraft der Druckbeaufschlagung der zweiten Stellzylinder Z2, Z2' aus der Druckleitung 8 und den Vorspannfedern 34. Die Druckbeaufschlagungsfläche jedes ersten Stellzylinders Z1, Z1' ist zweckmäßig größer als die Druckbeaufschlagungsfläche der zweiten Stellzylinder Z2, Z2' (Flächenverhältnis z.B. zwischen 2 : 1 bis 5 : 1 oder größer). Beim Regeln bewegt sich das 3/2-Wege-Druckregelventil 12 stufenlos zwischen den beiden vorerwähnten Schaltstellungen.In the position shown (non-pressurized system) connects the 3/2-way pressure control valve 12, the control line 17 with the return line 19, while the pressure line 8 is shut off. The pressure line 8 leads via an inlet nozzle 14 to the signal pressure line 21. About the inlet nozzle 14, a pressure difference is generated during operation, which converts the main stage 11 with the influence of the spring force 15 for pressure control. About the pilot control line 16, the 3/2-way pressure control valve 12 is switched after startup of the variable V in the setting for maximum promotion from the switching position shown in another switching position in which the pressure line 8 is connected to the control line 7 and the return line 19 is shut off , so that the adjusting cylinders Z1, Z1 'are pressurized and adjust the variable displacement pump V in the direction of minimum promotion, against the force of the pressurization of the second actuating cylinder Z2, Z2 'from the pressure line 8 and the biasing springs 34. The pressurization surface of each first actuating cylinder Z1, Z1' is expediently larger than the pressurization surface of the second actuating cylinder Z2, Z2 '(area ratio eg between 2: 1 to 5: 1 or greater). When controlling the 3/2-way pressure control valve 12 moves continuously between the two aforementioned switch positions.

An einem Knoten 17 der Stellleitung 7 zwischen den ersten Stellzylindern Z1, Z' und der Hauptstufe 11 zweigt eine Leckageleitung 30, in der eine Düse 18 enthalten ist, zur Rücklaufleitung 19 ab. Ferner können die Rückführungen F der Stellzylinder Z1, Z1' an eine Leckageleitung 20 angeschlossen sein.At a node 17 of the control line 7 between the first actuating cylinders Z1, Z 'and the main stage 11 branches off a leakage line 30, in which a nozzle 18 is included, to the return line 19 from. Furthermore, the feedbacks F of the adjusting cylinders Z1, Z1 'can be connected to a leakage line 20.

Von der Signaldruckleitung 21 zweigen Leitungen 22 bzw. 22' ab. Die Leitung 22 führt zu einem Druckregel-Vorsteuerventil 34 (mit zweckmäßigerweise einstellbarer Federkraft), von dem ablaufseitig eine Leitung 31 über einen Knoten 32 zu einem Knoten 33 der Stellleitung 7 führt. Eine von der Leitung 22 abzweigende Leitung 23 führt zu einer Zulaufseite eines Mengenregel-Vorsteuerventils 24. Die Leitung 22' führt zur Zulaufseite eines Drehmoment-Regel-Vorsteuerventils 25, das aus der Leitung 22' gegen eine Federkraft 22 druckvorgesteuert und als 2/2-Wege-Ablassventil ausgebildet sein kann.From the signal pressure line 21 branch lines 22 and 22 'from. The line 22 leads to a pressure control pilot valve 34 (with suitably adjustable spring force), from the drain side, a line 31 via a node 32 to a node 33 of the control line 7 leads. A line 23 branching off from the line 22 leads to an inlet side of a quantity control pilot valve 24. The line 22 'leads to the inlet side of a torque control pilot valve 25, which is pressure-controlled from the line 22' against a spring force 22 and 2/2 Way drain valve may be formed.

Das Mengenregel-Vorsteuerventil 24 ist ein 2/2-Wege-Druckregelventil, das durch einen Proportionalmagneten 26 gegen Federkraft 28 betätigbar ist, und, vorzugsweise, sogar eine proportionale Druckvorsteuerung 27 aufweisen kann. In der in Fig. 1 gezeigten Ausführungsform betätigt der Proportionalmagnet 26 das Ventil 24 in Richtung zu einer Durchgangsstellung gegen die eine Absperrstellung einstellende Federkraft 28. Die Bestromung des Proportionalmagneten 26 ist eine Sollwertvorgabe für die Mengenregelung. Diese Sollwertvorgabe könnte auch auf hydraulischem, mechanischem, pneumatischem oder anderem Weg erfolgen (nicht gezeigt). Die Vorsteuerventile 25, 24, 34 sind ablaufseitig jeweils an den Knoten 32 angeschlossen und somit über die Leitung 31 mit dem Knoten 33 in der Stellleitung 7 bzw. dem jeweiligen Stellzylinder Z1, Z1' verbunden, um entsprechend der Erfindung abgelassenes Druckmittel dort einzuspeisen, so dass dieses Druckmittel aus der Signaldruckleitung 21 nicht verloren geht. Die Vorsteuerventile 24, 25, 34 (oder nur 24 oder 25 und 34) sind der Hauptstufe 11 zugeordnet und regeln in der gezeigten Ausführungsform in Fig. 1 die über die Zulaufdüse 14 erzeugte Druckdifferenz für die Hauptstufe 11.The flow control pilot valve 24 is a 2/2-way pressure control valve, which is actuated by a proportional solenoid 26 against spring force 28, and, preferably, even a proportional pressure pilot 27 may have. In the in Fig. 1 In the embodiment shown, the proportional solenoid 26 actuates the valve 24 in the direction of a passage position against the spring force 28 which adjusts a shut-off position. The energization of the proportional magnet 26 is a desired value specification for the quantity control. This set point specification could also be made hydraulically, mechanically, pneumatically or otherwise (not shown). The pilot valves 25, 24, 34 are each connected at the outlet side to the node 32 and thus via the line 31 to the node 33 in the control line 7 and the respective actuating cylinder Z1, Z1 'connected to feed according to the invention pressure medium there, so that this pressure medium from the signal pressure line 21 is not lost. The pilot valves 24, 25, 34 (or only 24 or 25 and 34) are associated with the main stage 11 and in the embodiment shown in FIG Fig. 1 the pressure difference generated by the inlet nozzle 14 for the main stage 11th

Bei Ansprechen (Öffnen) des Vorsteuerventils 25 wird der Druck in der Signaldruckleitung 21 vermindert, wobei mit zunehmender Verstellung der ersten Stellzylinder Z1, Z1' über die Rückführung F die Federkraft 29 erhöht und somit der Druck in der Signaldruckleitung 21 wieder gesteigert wird. Das Vorsteuerventil 34 arbeitet nur gegen die Federkraft.Upon response (opening) of the pilot valve 25, the pressure in the signal pressure line 21 is reduced, with increasing adjustment of the first actuating cylinder Z1, Z1 'via the feedback F increases the spring force 29 and thus the pressure in the signal pressure line 21 is increased again. The pilot valve 34 only works against the spring force.

Das Vorsteuerventil 24 ist, solange der Proportionalmagnet 26 nicht bestromt ist, in der Absperrstellung, und nimmt keinen Einfluss auf den Druck in der Signaldruckleitung 21. Wird der Proportionalmagnet 26 bestromt, dann vermindert das Vorsteuerventil 24 den Druck in der Signaldruckleitung 21, wobei mit zunehmender Verstellung der Stellzylinder Z1, Z1' z.B. in Richtung zur Minimalförderung der Verstellpumpe V die Federkraft 28 erhöht und somit bei gleichbleibender Bestromung des Proportional-Magneten 26 der Druck in der Signaldruckleitung 21 wieder gesteigert wird.The pilot valve 24 is, as long as the proportional solenoid 26 is not energized, in the shut-off position, and has no influence on the pressure in the signal pressure line 21. If the proportional solenoid 26 is energized, then the pilot valve 24 reduces the pressure in the signal pressure line 21, with increasing Adjustment of the actuating cylinder Z1, Z1 'eg in the direction of the minimum promotion of the variable V increases the spring force 28 and thus the pressure in the signal pressure line 21 is increased again with constant energization of the proportional magnet 26.

In der in Fig. 2 gezeigten Detailvariante endet die Druckleitung 8 an der Hauptstufe 11 und wird der Druck in der Signaldruckleitung 21 beispielsweise aus dem Lastdrucksignalkreis LS verwendet, um die Hauptstufe 11 gegen den Druck in der Vorsteuerleitung 16 aus der Druckleitung 8 zu verstellen.In the in Fig. 2 shown detail variant ends the pressure line 8 to the main stage 11 and the pressure in the signal pressure line 21, for example, from the load pressure signal circuit LS used to adjust the main stage 11 against the pressure in the pilot line 16 from the pressure line 8.

In der Detailvariante in Fig. 3 ist das Vorsteuerventil 24' zur Mengenregelung umgekehrt verschaltet wie in Fig. 1, das heißt, die Federkraft 28 hält das Steuerventil 24' in der gezeigten Durchgangsstellung, während der Proportionalmagnet 26 bei Bestromen gegen die Federkraft 28 eine Verstellung in die oder in Richtung zur Absperrstellung bewirkt.In the detail variant in Fig. 3 is the pilot valve 24 'connected inversely to flow control as in Fig. 1 that is, the spring force 28 holds the control valve 24 'in the passage position shown, while the proportional solenoid 26 causes an adjustment in the direction or to the shut-off when energized against the spring force 28.

In der Detailvariante in Fig. 4 ist das Druckregel-Vorsteuerventil 34 abströmseitig nicht an den Knoten 32 wie in Fig. 1, sondern über eine Leitung 31' direkt an die Rücklaufleitung 19 angeschlossen. In the detail variant in Fig. 4 is the pressure control pilot valve 34 downstream not at the node 32 as in Fig. 1 but connected via a line 31 'directly to the return line 19.

Claims (15)

  1. Regulating system of a hydraulic variable capacity pump (V), comprising at least one actuating cylinder (Z1, Z1') which is to be actuated by pressure of the regulating system in an actuating direction of the pump either to a minimal capacity or a maximal capacity, a main stage (11) connected with a pressure line (8) and a return line (19) for regulating a control pressure actuating the actuating cylinder (Z1, Z1'), wherein the main stage (9) is a pilot pressure controlled 3/2-multiway pressure regulating valve (12), at least one pilot pressure control valve (24, 25, 24', 34) associated with the main stage (11) for regulating pressure and/or torque and/or quantity, wherein the respective pilot pressure control valve is connected at a supply side to a signal pressure line (21) extending to a pilot pressure control of the 3/2-multiway pressure regulating valve (12) and at an outlet side to a low pressure region, characterized in that at least the respective pilot pressure control valve (24, 25, 24') is connected at the outlet side to the actuating cylinder (Z1, Z1') for regulating the quantity and/or the torque.
  2. Regulating system according to claim 1, characterized in that also the pilot pressure control valve (34) provided for the pressure regulation is connected at the outlet side to the actuating cylinder (Z1, Z1').
  3. Regulating system according to claim 1, characterized in that the pilot pressure control valve (24, 24') for regulating the quantity is a 2/2-multiways-pressure regulating valve, preferably including a proportional pilot pressure control (27) which is to be actuated by a proportional solenoid (26) counter to a spring force (28) either in a direction to a through-flow position or to a blocking position.
  4. Regulating system according to claim 1, characterized in that the pilot pressure control valve (25) for regulating the torque and/or the pilot control valve (34) for regulating the pressure is a pilot pressure-controlled 2/2-ways pressure relief valve which is actuated by pressure of the signal pressure line (21) counter to a spring force (29) and in a direction to a through-flow position.
  5. Regulating system according to claim 3, characterized in that the spring force (29) actuating the pilot pressure control valve (25) for regulating the torque and/or the pilot pressure control valve (34) for regulating the pressure in a direction to a blocking position is adjustable.
  6. Regulating system according to claim 2 or claim 3, characterized in that the spring force (28, 29) of the pilot pressure control valve (24, 24') for regulating the quantity and/or of the pilot pressure control valve (28) for regulating the torque is generated by an actuating spring, and that the adjusted spring force is variable, preferably by the actuating cylinder (Z1, Z1'), in operation of the regulating system (S) by feedback (F) of the actual value of the position the feedback (F) of the actual value preferably transmitting the respective capacity position of the pump to the pilot pressure control valve (24, 25, 24').
  7. Regulating system according to claim 1, characterized in that the signal pressure line (20) is connected with the pressure line (8) via a supply nozzle (14) and that the pressure line (8) extends to the main stage (11).
  8. Regulating system according to claim 1, characterized in that the signal pressure line (21) is connected with a load pressure signal circuit (LS) of at least one consumer (M) supplied with hydraulic medium by the pump, and that the signal pressure line (21) is separated from the pressure line (8).
  9. Regulating system according to claim 1, characterized in that actuating line (7) extending between the main stage (11) and the first actuating cylinder (Z1, Z1') is additionally connected via a nozzle (18) to the return line (18).
  10. Regulating system according to claim 1, characterized in that the 3/2-multiways pressure regulating valve (12) of the main stage (11) is pilot pressure controlled from the pressure line (8) in actuating direction for connecting the pressure line (8) and the first actuating cylinder (Z1, Z1') and is pilot pressure controlled from the signal pressure line (21) and spring loaded (15) in actuating direction for connecting the first actuating cylinder (Z1, Z1') and the return line (19).
  11. Regulating system according to claim 10, characterized in that the force of the spring load (15) is adjustable.
  12. Regulating system according to claim 1, characterized in that the actuating cylinder (Z1, Z1') is to be actuated in actuating direction of the pump towards minimal capacity, and that at least a second actuating cylinder (Z2, Z2') is provided, which is actuated by pressure of the pressure line (8) in actuating direction of the pump towards maximal capacity and comprises a spring feed load (34).
  13. Regulating system according to at least one of the preceding claims, characterized in that the variable capacity pump (V) is an axial piston pump (2) with a swash plate design, and that the actuating cylinders (Z1, Z1', Z2, Z2') engage at an adjustment member (3) of the swash plate, wherein, preferably, respectively, two first and two second actuating cylinders are provided, respectively switched in parallel.
  14. Regulating system according to claim 13, characterized in that the first actuating cylinder (Z1, Z1') has a larger pressure receiving surface than the second actuating cylinder (Z2, Z2'), preferably with a ratio between the surfaces between about 2:1 to 5:1.
  15. Regulating system according to at least one of the preceding claims, characterized in that the pilot pressure control valve (25, 34), the outlet side of which is connected with the actuating cylinder (Z1, Z1') for regulating the pressure and/or the torque is a slider valve.
EP12174666.3A 2012-07-02 2012-07-02 Regulator system of a hydraulic variable capacity pump Active EP2682610B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12174666.3A EP2682610B1 (en) 2012-07-02 2012-07-02 Regulator system of a hydraulic variable capacity pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12174666.3A EP2682610B1 (en) 2012-07-02 2012-07-02 Regulator system of a hydraulic variable capacity pump

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EP2682610A1 EP2682610A1 (en) 2014-01-08
EP2682610B1 true EP2682610B1 (en) 2015-12-09

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018200825B3 (en) 2018-01-18 2019-01-24 Hawe Hydraulik Se Control system for a hydraulic variable pump, pump set and vehicle with a pump set

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104179734B (en) * 2014-08-27 2016-06-29 浙江德泰机电工程有限公司 A kind of constant-pressure control device for hydraulic pump and control method
DE102017202899B4 (en) 2017-02-22 2022-01-05 Hawe Hydraulik Se Control system for a hydraulic variable displacement pump, pump unit and hydraulic system with one pump unit
DE102022202279A1 (en) 2022-03-07 2023-09-07 Hawe Hydraulik Se Electro-hydraulic control device and adjustable hydraulic pump system

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH431221A (en) * 1964-10-02 1967-02-28 Buehler Ag Geb Hydrostatic drive

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018200825B3 (en) 2018-01-18 2019-01-24 Hawe Hydraulik Se Control system for a hydraulic variable pump, pump set and vehicle with a pump set

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