EP0149787B1 - Feed controlling device for a variable hydropump - Google Patents

Feed controlling device for a variable hydropump Download PDF

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Publication number
EP0149787B1
EP0149787B1 EP84115198A EP84115198A EP0149787B1 EP 0149787 B1 EP0149787 B1 EP 0149787B1 EP 84115198 A EP84115198 A EP 84115198A EP 84115198 A EP84115198 A EP 84115198A EP 0149787 B1 EP0149787 B1 EP 0149787B1
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EP
European Patent Office
Prior art keywords
valve
control
pressure
pump
torque
Prior art date
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EP84115198A
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German (de)
French (fr)
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EP0149787B2 (en
EP0149787A2 (en
EP0149787A3 (en
Inventor
Gerhard Beutler
Heinz Berthold
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Brueninghaus Hydraulik GmbH
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Brueninghaus Hydraulik GmbH
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Classifications

    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a flow control device according to the preamble of claim 1.
  • a flow control device of this type is known for example from DE-A-15 28 550 and FR-A-22 11 054.
  • the delivery rate is set solely for the purpose of traversing a specific performance curve as a function of the pump delivery pressure or a control or operating pressure which is synchronous with it.
  • the stroke volume of the pump there is a direct functional relationship between the stroke volume of the pump and the control of the operating pressure which actuates the control valve, which results in low-loss torque control because the torque characteristic is not determined by a throttle system by lowering the operating pressure, but only by changing the Spring preload on the momentary valve, d. H. by designing the measuring spring or the measuring spring set.
  • the relationship applies that the product of the operating pressure and the stroke volume of the pump must be constant.
  • the measure of the stroke volume of a hydraulic pump is the position of the pump actuator which adjusts the pump delivery quantity and which, according to the invention, is connected to the torque valve by means of the spring / measuring spring set.
  • the torque valve is followed by the control valve, which acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • the control valve acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • DE-A-15 28 550 and from DE-A-20 38 968 per se to connect a torque valve to the pump actuator by means of a measuring spring set for the delivery rate control, but there are significant differences between these known configurations and the solution according to the invention .
  • DE-A-15 28 550 there is no torque control, but the pump pressure is set so that the max. Operating pressure does not exceed a certain value.
  • DE-A-20 38 968 discloses a power control device for two or more hydraulic pumps, and moreover the torque valve is not arranged so that it pressurizes the operating pressure control line depending on the pressure in the operating pressure control line and the preload of the measuring spring set Process connects.
  • a torque valve is known per se from FR-A-13 18 661, the spring of which is connected to the pump frame, but this known embodiment relates to a manually adjustable pump, and moreover the torque valve does not become dependent on the pressure in the operating pressure control line controlled.
  • the design and arrangement of the torque valve according to the invention in a flow rate control allows in a further embodiment of the invention that the torque valve can be attached to the hydraulic pump as a separate assembly and a driver pin of the pump actuator on the torque valve to change the bias of the measuring spring / measuring spring set depending on the flow rate setting attacks.
  • Such a torque valve can be used for pumps of different sizes and capacities, these pumps only having to match in the adjustment path for the pump actuator, that is to say, for example, in the swivel angle for adjustable inclined-axis pumps.
  • An expedient embodiment of such a torque valve is characterized in claims 4 and 5.
  • the torque characteristic is determined solely by designing the characteristic of the measuring spring or the measuring spring set
  • a particularly expedient embodiment of the invention results if the stop for the measuring spring measuring spring set can be adjusted from the outside by means of a handle in the torque valve. Due to the externally adjustable measuring spring or measuring spring set, any number of different torque characteristics can be preselected and also set or adjusted during operation, which is particularly advantageous when the pump torque is optimally adapted to the torque of the drive machine driving the pump. A quick adaptation to any application is possible.
  • the stop in the torque valve can expediently be arranged on the end of the valve housing and be detachable for the exchange of the measuring spring / measuring spring set.
  • the torque control device is also suitable as a total control for two or more hydraulic pumps mechanically coupled on the drive side if, according to the invention, the closing element of the torque valve of each pump is acted upon by the sum of the pressure in the operating pressure control line of the individual pump and the pressure in the operating pressure line of the other pump (s) and that each torque valve pressurizes the operating pressure control line of its pump as a function of the total operating pressure and the preload of its measuring spring Process connects.
  • the closing elements of the torque valves have a plurality of measuring surfaces which act in parallel and are each acted upon by the operating pressure of one of the pumps.
  • the hydraulic pump 1 is driven via the shaft 2 by a drive, not shown.
  • the pump actuator consists of a swivel element 3, the swivel angle a of which is proportional to the stroke volume of the hydraulic pump 1.
  • the servo-setting device (not shown in detail) for adjusting the swivel angle ⁇ comprises a spring 4 and a steep piston 5 which can be pressurized, the spring 4 adjusting the hydraulic pump 1 in the direction of the maximum swivel angle ⁇ , that is to say the maximum delivery volume.
  • An actuating piston 6 of the actuating device which can also be functionally combined with the piston 5, takes over the resetting function in the direction of a smaller pivot angle a.
  • the control pressure acting on the piston 6 in the line 7 is removed via a control valve 8 and the line 9 from the delivery pressure line 10 of the hydraulic pump 1.
  • a common pressure relief valve 11 is in series with the control valve 8.
  • the control valve 8 is designed as a pressure compensator and is acted upon on the one hand by the delivery pressure and on the other hand by a control pressure in the operating pressure control line 12, which controls the operating pressure of the hydraulic pump 1 behind a throttle 13 which limits the control flow the operating pressure line 14 decreases after an optionally adjustable flow restrictor 15.
  • a moment valve 16 is acted upon on the one hand by the pressure in the control line 12 and on the other hand by a measuring spring or measuring spring set 17, the pretension of which is determined by the position of the piston 6 or the pump actuator 3.
  • the torque valve 16 can connect the control line 12 to the unpressurized outlet 18.
  • the operating pressure in the control line 12 reaches the value set on the torque valve 16 so that it begins to open, a pressure drop occurs at the control slide of the control valve 8 via the throttle 13.
  • the control slide is moved into the switching position 11 and supplies the piston 6 with Control pressure, so that it strives to adjust the actuator 3 of the hydraulic pump 1 in the direction of smaller flow rates.
  • the measuring spring 17 or the measuring spring set of the torque valve 16 is biased.
  • the spring characteristics of the measuring springs or the measuring spring set are designed such that, depending on the preload, an envelope curve is created in the theoretically desired power hyperbola.
  • a defined swivel angle a corresponds to a defined operating pressure in line 10.
  • the delivery rate setting of the hydraulic pump 1 in the area in which the torque control, that is to say the torque valve 16 has not yet responded is carried out in the usual way via the delivery rate throttle 15 and requires no special explanation.
  • FIG. 2 shows an embodiment of a torque valve 16 in its assignment to the pivotable pump actuator of an inclined-axis axial piston pump.
  • the pivotable actuator has a driver pin 20 projecting into the torque valve 16.
  • the torque valve 16 is designed as a seat valve arranged in a valve housing 21 with a valve cone 22 as a closing element which is acted upon by a measuring spring set 17 formed from the springs 23 and 24.
  • the valve seat for the valve cone 22 is formed on a valve body 25 which is displaceably arranged in the valve housing 21 and on which the driver pin 20 of the pump actuator acts.
  • the valve body is acted upon by a spring 26 which is supported in the valve housing 21 and holds the valve body 25 in positive engagement with the driver pin 20.
  • the spring 23 of the measuring spring set 17 is supported on a stop 27 and the spring 24 on an adjusting screw 28 in the stop 27.
  • the stop 27 is screwed into the end of the valve housing 21. Due to the rotational position of the stop 27, the preload of the measuring spring set 17 and thus the position of the desired torque characteristics and the response point of the torque valve 16 can be adjusted.
  • the stop 27 has a handle 29. The course of the torque characteristics or the spring characteristic can be done by changing the bias of the spring 24 with the help of the adjusting screw 28.
  • the pressure in the operating pressure control line 12 acts through the channel 30 in the valve body 25 on the closing member 22 against the force of the measuring spring set 17.
  • the width of the The valve seat determines the effective measuring surface on the closing element 22 for the pressure in the line 12. If the force exerted on the measuring surface by the pressure in the line 12 exceeds the prestressing force of the measuring spring set 17, the valve cone of the closing element 22 lifts off the valve seat in the valve body 25 and opens the control line 12 to the pressureless outlet, formed by the interior 31 of the valve housing 21 which is fixedly connected to the hydraulic pump, the interior 31 being connected to the depressurized interior 32 of the hydraulic pump.
  • the driving pin 20 moves the valve body 25 in FIG. 2 to the right against the closing member 22 and thus increases the preload of the spring set 17 in accordance with the desired course of the torque characteristic.
  • FIG. 3 shows the control device according to the invention as a total torque control for two hydraulic pumps 33, 34, the drive shafts of which are driven directly or via a corresponding transfer gear 35 (only schematically indicated by a dash) by a common drive machine, not shown.
  • the control devices for the individual pumps correspond to the control device shown in FIG. The same parts are provided with the same reference numerals and are not explained again.
  • Only the torque valves denoted by 16 in FIG. 1 are designed here as total torque valves 36 and differ from the torque valve 16 in that the closing member 22 according to FIG. 4 has an additional measuring surface 37. The operating pressure of the other pump acts on this measuring surface 37 in each case via a control line 38, 39.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung bezieht sich auf eine Fördermengen-Regeleinrichtung nach dem Oberbegriff des Anspruchs 1.The invention relates to a flow control device according to the preamble of claim 1.

Eine Fördermengen-Regeleinrichtung dieser Art, ist beispielsweise aus der DE-A-15 28 550 und der FR-A-22 11 054 bekannt. Bei diesen bekannten Regeleinrichtungen erfolgt die Fördermengeneinstellung zwecks Durchfahren einer bestimmten Leistungskurve ausschließlich in Abhängigkeit des Pumpenförderdrucks bzw. eines diesem synchronen Steuer- bzw. Betriebsdrucks. Dabei handelt es sich um Maßgaben, die sich jeweils in Abhängigkeit der Belastung erst einstellen und deshalb unzureichend und außerdem verzögert wirksam sind.A flow control device of this type is known for example from DE-A-15 28 550 and FR-A-22 11 054. In the case of these known control devices, the delivery rate is set solely for the purpose of traversing a specific performance curve as a function of the pump delivery pressure or a control or operating pressure which is synchronous with it. These are stipulations that only arise depending on the load and are therefore inadequate and also have a delayed effect.

Es ist Aufgabe der Erfindung, eine Fördermengen-Regeleinrichtung der eingangs genannten Art so weiterzubilden, daß zusätzlich eine Momentenregelung geschaffen ist.It is an object of the invention to develop a flow control device of the type mentioned in the introduction so that torque control is additionally created.

Diese Aufgabe wird durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.This object is achieved by the characterizing features of claim 1.

Bei der erfindungsgemäßen Ausgestaltung besteht eine direkte Funktionsbeziehung zwischen dem Hubvolumen der Pumpe und der Steuerung des Betriebsdrucks, der das Steuerventil betätigt, wodurch eine verlustarme Momentenregeiung gegeben ist, weil die Momentenkennlinie nicht durch ein Drosselsystem durch Absenken des Betriebsdruckes festgelegt wird, sondern ausschließlich durch Veränderung der Federvorspannung am Momentventil, d. h. durch Auslegung der Meßfeder bzw. des Meßfedersatzes. Für eine Momentenregelung gilt die Beziehung, daß das Produkt aus Betriebsdruck und Hubvolumen der Pumpe konstant sein muß. Ein; Maß für das Hubvolumen einer Hydropumpe ist die Stellung des die Pumpenfördermenge einstellenden Pumpenstellgliedes, das er- findungsgemäß mittels der/dem Feder/Meßfedersatz mit dem Momentenventil verbunden ist. Außerdem ist dem Momentenventil das als Druckwaage wirkende, primär der Fördermengeneinstellung dienende Steuerventil nachgeschaltet. Dies hat den Vorteil, daß unterhalb der ansprechenden Momentenregelung am Momentenventil die Förderstromeinstellung unbeeinflußt bleibt. Ein weiterer wesentlicher Vorteil der Erfindung ist, daß kurze Ausschwenkzeiten (Einstellzeiten für die Pumpe auf maximale Fördermenge) ermöglicht sind, da der Stellkolben des Stellgerätes unmittelbar mit dem Ablauf verbunden werden kann.In the embodiment according to the invention, there is a direct functional relationship between the stroke volume of the pump and the control of the operating pressure which actuates the control valve, which results in low-loss torque control because the torque characteristic is not determined by a throttle system by lowering the operating pressure, but only by changing the Spring preload on the momentary valve, d. H. by designing the measuring spring or the measuring spring set. For a torque control, the relationship applies that the product of the operating pressure and the stroke volume of the pump must be constant. A; The measure of the stroke volume of a hydraulic pump is the position of the pump actuator which adjusts the pump delivery quantity and which, according to the invention, is connected to the torque valve by means of the spring / measuring spring set. In addition, the torque valve is followed by the control valve, which acts as a pressure compensator and primarily serves to adjust the delivery rate. This has the advantage that below the responsive torque control on the torque valve, the flow rate setting remains unaffected. Another important advantage of the invention is that short swiveling times (setting times for the pump to the maximum delivery rate) are made possible, since the actuating piston of the actuating device can be connected directly to the process.

Es ist zwar aus DE-A-15 28 550 und aus DE-A-20 38 968 ansich bekannt, zur Fördermengen-Regelung ein Momentenventil mittels eines Meßfedersatzes mit dem Pumpenstellglied zu verbinden, jedoch bestehten wesentliche Unterschiede zwischen diesen bekannten Ausgestaltungen und der erfindungsgemäßen Lösung. Bei der Ausgestaltung gemäß DE-A-15 28 550 erfolgt keine Momentenregelung, sondern es wird der Pumpendruck so eingestellt, daß er den max. Betriebsdruck um einen bestimmten Wert nicht überschreitet. DE-A-20 38 968 offenbart eine Leistungs-Regelvorrichtung für zwei oder mehrere Hydropumpen, und außerdem ist das Momentenventil nicht so angeordnet, daß es die Betriebsdruck-Steuerleitung in Abhängigkeit vom Druck in der Betriebsdruck-Steuerleitung und der Vorspannung des Meßfedersatzes mit dem drucklosen Ablauf verbindet.It is known from DE-A-15 28 550 and from DE-A-20 38 968 per se to connect a torque valve to the pump actuator by means of a measuring spring set for the delivery rate control, but there are significant differences between these known configurations and the solution according to the invention . In the embodiment according to DE-A-15 28 550, there is no torque control, but the pump pressure is set so that the max. Operating pressure does not exceed a certain value. DE-A-20 38 968 discloses a power control device for two or more hydraulic pumps, and moreover the torque valve is not arranged so that it pressurizes the operating pressure control line depending on the pressure in the operating pressure control line and the preload of the measuring spring set Process connects.

Außerdem ist aus FR-A-13 18 661 ein Momentenventil ansich bekannt, dessen Feder mit dem Pumpengestell verbunden ist, jedoch bezieht sich diese bekannte Ausgestaltung auf eine manuell verstellbare Pumpe, und außerdem wird das Momentenventil nicht in Abhängigkeit vom Druck in der Betriebsdruck-Steuerleitung gesteuert.In addition, a torque valve is known per se from FR-A-13 18 661, the spring of which is connected to the pump frame, but this known embodiment relates to a manually adjustable pump, and moreover the torque valve does not become dependent on the pressure in the operating pressure control line controlled.

Die erfindungsgemäße Ausbildung und Anordnung des Momentenventiles in einer Fördermengenregelung gestattet es in weiterer Ausbildung der Erfindung, daß das Momentenventil als gesonderte Baugruppe an der Hydropumpe befestigt werden kann und ein Mitnehmerstift des Pumpenstellgliedes am Momentenventil zur Änderung der Vorspannung der Meßfeder/Meßfedersatzes in Abhängigkeit von der Fördermengeneinstellung angreift. Ein solches Momentenventil kann für Pumpen unterschiedlicher Größe und Leistung verwendet werden, wobei diese Pumpen lediglich im Verstellweg für das Pumpenstellglied übereinstimmen müssen, also beispielsweise im Schwenkwinkel bei verstellbaren Schrägachsenpumpen. Eine zweckmäßige Ausgestaltung eines solchen Momentenventils ist in den Ansprüchen 4 und 5 gekennzeichnet.The design and arrangement of the torque valve according to the invention in a flow rate control allows in a further embodiment of the invention that the torque valve can be attached to the hydraulic pump as a separate assembly and a driver pin of the pump actuator on the torque valve to change the bias of the measuring spring / measuring spring set depending on the flow rate setting attacks. Such a torque valve can be used for pumps of different sizes and capacities, these pumps only having to match in the adjustment path for the pump actuator, that is to say, for example, in the swivel angle for adjustable inclined-axis pumps. An expedient embodiment of such a torque valve is characterized in claims 4 and 5.

Da bei dererfindungsgemäßen Einrichtung die Momentenkennlinie allein durch Auslegung der Charakteristik der Meßfeder bzw. des Meßfedersatzes bestimmt ist, ergibt sich eine besonders zweckmäßige Ausgestaltung der Erfindung, wenn im Momentenventil der Anschlag für die Meßfeder-Meßfedersatz mittels einer Handhabe von außen einstellbar ist. Durch die von außen einstellbare Meßfeder bzw. Meßfedersatz können beliebig viele unterschiedliche Momentenkennlinien vorgewählt werden und auch während des Betriebes eingestellt bzw. verstellt werden, was besonders bei der optimalen Anpassung des Pumpenmomentes an das Moment der die Pumpe antreibenden Antriebsmaschine von Vorteil ist. Eine schnelle Anpassung an beliebige Anwendungsfälle ist ermöglicht.Since in the device according to the invention the torque characteristic is determined solely by designing the characteristic of the measuring spring or the measuring spring set, a particularly expedient embodiment of the invention results if the stop for the measuring spring measuring spring set can be adjusted from the outside by means of a handle in the torque valve. Due to the externally adjustable measuring spring or measuring spring set, any number of different torque characteristics can be preselected and also set or adjusted during operation, which is particularly advantageous when the pump torque is optimally adapted to the torque of the drive machine driving the pump. A quick adaptation to any application is possible.

In weiterer Ausbildung kann zweckmäßig der Anschlag im Momentenventil stirnseitig am Ventilgehäuse angeordnet und für den Austausch der Meßfeder/Meßfedersatzes lösbar sein.In a further embodiment, the stop in the torque valve can expediently be arranged on the end of the valve housing and be detachable for the exchange of the measuring spring / measuring spring set.

In zweckmäßiger Weiterbildung der Erfindung ist die Momentenregeleinrichtung auch als Summenregelung für zwei oder mehrere antriebsseitig mechanisch gekoppelte Hydropumpen geeignet, wenn erfindungsgemäß daß das Schließglied des Momentenventils jeder Pumpe von der Summe des Druckes in der Betriebsdruck-Steuerleitung der einzelnen Pumpe und dem Druck in der Betriebsdruckleitung der anderen Pumpe/Pumpen beaufschlagt ist und daß jedes Momentenventil die Betriebsdruck-Steuerleitung seiner Pumpe in Abhängigkeit vom Summen-Betriebsdruck und der Vorspannung seiner Meßfeder mit dem drucklosen Ablauf verbindet. Dazu weisen die Schließglieder der Momentenventile mehrere Meßflächen auf, die parallel wirken und jeweils vom Betriebsdruck einer der Pumpen beaufschlagt sind.In an expedient development of the invention, the torque control device is also suitable as a total control for two or more hydraulic pumps mechanically coupled on the drive side if, according to the invention, the closing element of the torque valve of each pump is acted upon by the sum of the pressure in the operating pressure control line of the individual pump and the pressure in the operating pressure line of the other pump (s) and that each torque valve pressurizes the operating pressure control line of its pump as a function of the total operating pressure and the preload of its measuring spring Process connects. For this purpose, the closing elements of the torque valves have a plurality of measuring surfaces which act in parallel and are each acted upon by the operating pressure of one of the pumps.

Beispielsweise Ausführungsformen der Erfindung werden im folgenden anhand der beiliegenden Zeichnungen näher beschrieben. Es zeigen

  • Figur 1 schematisch eine erfindungsgemäße Regeleinrichtung für eine Hydropumpe,
  • Figur 2 schematisch im Schnitt und im Ausschnitt ein auf einer Hydropumpe angebrachtes Momentenventil gemäß der Erfindung,
  • Figur 3 schematisch die erfindungsgemäße Regeleinrichtung für zwei antriebsseitig gekoppelte Hydropumpen, und
  • Figur 4 schematisch im Ausschnitt und in vergrößerter Darstellung das Momentenventil mit einem Schließglied mit mehreren Meßflächen.
For example, embodiments of the invention are described in more detail below with reference to the accompanying drawings. Show it
  • FIG. 1 shows schematically an inventive control device for a hydraulic pump,
  • FIG. 2 schematically, in section and in detail, a torque valve according to the invention attached to a hydraulic pump,
  • Figure 3 shows schematically the control device according to the invention for two hydraulic pumps coupled on the drive side, and
  • Figure 4 shows schematically in detail and in an enlarged view the torque valve with a closing member with several measuring surfaces.

Die Hydropumpe 1 wird über die Welle 2 durch einen nichtdargestellten Antrieb angetrieben. Handelt es sich bei der Hydropumpe 1 beispielsweise um eine verstellbare Axialkolbenpumpe, besteht das Pumpenstellglied aus einem Schwenkglied 3, dessen Schwenkwinkel a dem Hubvolumen der Hydropumpe 1 proportional ist. Das nicht näher dargestellte Servostellgerät zur Einstellung des Schwenkwinkels a umfaßt eine Feder 4 und einen druckbeaufschlagbaren Steilkolben 5, wobei die Feder 4 die Hydropumpe 1 in Richtung maximalen Schwenkwinkel α, das heißt maximalen Fördervolumen einstellt. Ein Stellkolben 6 des Stellgerätes, der auch mit dem Kolben 5 funktionell vereinigt sein kann, übernimmt die Rückstellfunktion in Richtung kleinerer Schwenkwinkel a. Seine Kolbenfläche ist wesentlich größer als die des Stellkolbens 5. Der auf den Kolben 6 wirkende Steuerdruck in der Leitung 7 wird über ein Steuerventil 8 und die Leitung 9 von der Förderdruckleitung 10 der Hydropumpe 1 abgenommen. Mit dem Steuerventil 8 in Reihe liegt ein übliches Druckbegrenzungsventil 11. Das Steuerventil 8 ist als Druckwaage ausgebildet und einerseits vom Förderdruck beaufschlagt und andererseits von einem Steuerdruck in der Betriebsdruck-Steuerleitung 12, welche den Betriebsdruck der Hydropumpe 1 hinter einer den Steuerstrom begrenzenden Drossel 13 von der Betriebsdruckleitung 14 nach einer gegebenenfalls verstellbaren Förderstromdrossel 15 abnimmt.The hydraulic pump 1 is driven via the shaft 2 by a drive, not shown. If the hydraulic pump 1 is, for example, an adjustable axial piston pump, the pump actuator consists of a swivel element 3, the swivel angle a of which is proportional to the stroke volume of the hydraulic pump 1. The servo-setting device (not shown in detail) for adjusting the swivel angle α comprises a spring 4 and a steep piston 5 which can be pressurized, the spring 4 adjusting the hydraulic pump 1 in the direction of the maximum swivel angle α, that is to say the maximum delivery volume. An actuating piston 6 of the actuating device, which can also be functionally combined with the piston 5, takes over the resetting function in the direction of a smaller pivot angle a. Its piston area is significantly larger than that of the actuating piston 5. The control pressure acting on the piston 6 in the line 7 is removed via a control valve 8 and the line 9 from the delivery pressure line 10 of the hydraulic pump 1. A common pressure relief valve 11 is in series with the control valve 8. The control valve 8 is designed as a pressure compensator and is acted upon on the one hand by the delivery pressure and on the other hand by a control pressure in the operating pressure control line 12, which controls the operating pressure of the hydraulic pump 1 behind a throttle 13 which limits the control flow the operating pressure line 14 decreases after an optionally adjustable flow restrictor 15.

Ein Momentenventil 16 ist einerseits vom Druck in der Steuerleitung 12 beaufschlagt und andererseits von einer Meßfeder bzw. Meßfedersatz 17, dessen Vorspannung durch die Stellung des Kolben 6 bzw. des Pumpenstellgliedes 3 bestimmt ist. Das Momentenventil 16 kann die Steuerleitung 12 mit dem drucklosen Ablauf 18 verbinden.A moment valve 16 is acted upon on the one hand by the pressure in the control line 12 and on the other hand by a measuring spring or measuring spring set 17, the pretension of which is determined by the position of the piston 6 or the pump actuator 3. The torque valve 16 can connect the control line 12 to the unpressurized outlet 18.

Erreicht der Betriebsdruck in der Steuerleitung 12 den am Momentenventil 16 eingestellten Wert, so daß dieses beginnt zum Ablauf zu öffnen, entsteht über die Drossel 13 ein Druckgefälle am Steuerschieber des Steuerventiles 8. Der Steuerschieber wird in die Schaltposition 11 verschoben und versorgt den Kolben 6 mit Steuerdruck, so daß dieser bestrebt ist, das Stellglied 3 der Hydropumpe 1 in Richtung kleinerer Fördermengen zu verstellen. Dabei wird die Meßfeder 17 bzw. der Meßfedersatz des Momentenventiles 16 vorgespannt. Die Meßfedern bzw. der Meßfedersatz ist in ihrer Federcharakteristik so ausgebildet, daß je nach Vorspannung eine Hüllkurve in der theoretisch gewünschten Leistungshyperbel entsteht. Einem definierten Betriebsdruck in der Leitung 10 entspricht ein vorgegebener Schwenkwinkel a. Die Fördermengeneinstellung der Hydropumpe 1 in dem Bereich, in welchem die Momentenregelung, das heißt das Momentenventil 16 noch nicht angesprochen hat, erfolgt in üblicher Weise über die Fördermengendrossel 15 und bedarf keiner besonderten Erläuterung.If the operating pressure in the control line 12 reaches the value set on the torque valve 16 so that it begins to open, a pressure drop occurs at the control slide of the control valve 8 via the throttle 13. The control slide is moved into the switching position 11 and supplies the piston 6 with Control pressure, so that it strives to adjust the actuator 3 of the hydraulic pump 1 in the direction of smaller flow rates. The measuring spring 17 or the measuring spring set of the torque valve 16 is biased. The spring characteristics of the measuring springs or the measuring spring set are designed such that, depending on the preload, an envelope curve is created in the theoretically desired power hyperbola. A defined swivel angle a corresponds to a defined operating pressure in line 10. The delivery rate setting of the hydraulic pump 1 in the area in which the torque control, that is to say the torque valve 16 has not yet responded, is carried out in the usual way via the delivery rate throttle 15 and requires no special explanation.

In Figur 2 ist eine Ausführungsform eines Momentenventiles 16 in seiner Zuordnung zu dem schwenkbaren Pumpenstellglied einer Schrägachsen-Axialkolbenpumpe dargestellt. Die Pumpe ist im einzelnen nicht näher erläutert. Das Schwenkbare Stellglied weist einen in das Momentenventil 16 ragenden Mitnehmerstift 20 auf. Das Momentenventil 16 ist bei der gezeigten Ausführungsform als in einem Ventilgehäuse 21 angeordnetes Sitzventil ausgebildet mit einem Ventilkegel 22 als Schließglied, welches von einem aus den Federn 23 und 24 gebildeten Meßfedersatz 17 beaufschlagt ist. Der Ventilsitz für den Ventilkegel 22 ist an einem in dem Ventilgehäuse 21 verschiebbar angeordneten Ventilkörper 25 ausgebildet, an welchem der Mitnehmerstift 20 des Pumpenstellgliedes angreift. Der Ventilkörper ist von einer Feder 26 beaufschlagt, welche im Ventilgehäuse 21 abgestützt ist und den Ventilkörper 25 formschlüssig mit dem Mitnehmerstift 20 in Eingriff hält. Die Feder 23 des Meßfedersatzes 17 ist an einem Anschlag 27 abgestützt und die Feder 24 an einer Stellschraube 28 in dem Anschlag 27.FIG. 2 shows an embodiment of a torque valve 16 in its assignment to the pivotable pump actuator of an inclined-axis axial piston pump. The pump is not explained in detail. The pivotable actuator has a driver pin 20 projecting into the torque valve 16. In the embodiment shown, the torque valve 16 is designed as a seat valve arranged in a valve housing 21 with a valve cone 22 as a closing element which is acted upon by a measuring spring set 17 formed from the springs 23 and 24. The valve seat for the valve cone 22 is formed on a valve body 25 which is displaceably arranged in the valve housing 21 and on which the driver pin 20 of the pump actuator acts. The valve body is acted upon by a spring 26 which is supported in the valve housing 21 and holds the valve body 25 in positive engagement with the driver pin 20. The spring 23 of the measuring spring set 17 is supported on a stop 27 and the spring 24 on an adjusting screw 28 in the stop 27.

Der Anschlag 27 ist stirnseitig in das Ventilgehäuse 21 eingeschraubt. Durch die Drehstellung des Anschlages 27 ist die Vorspannung des Meßfedersatzes 17 und damit die Lage der gewünschten Momentenkennlinien sowie der Ansprechpunkt des Momentenventiles 16 einstellbar. Dazu weist der Anschlag 27 eine Handhabe 29 auf. Der Verlauf der Momentenkennlinien bzw. der Federcharakteristik kann durch Veränderung der Vorspannung der Feder 24 mit Hilfe der Stellschraube 28 erfolgen.The stop 27 is screwed into the end of the valve housing 21. Due to the rotational position of the stop 27, the preload of the measuring spring set 17 and thus the position of the desired torque characteristics and the response point of the torque valve 16 can be adjusted. For this purpose, the stop 27 has a handle 29. The course of the torque characteristics or the spring characteristic can be done by changing the bias of the spring 24 with the help of the adjusting screw 28.

Der in der Betriebsdruck-Steuerleitung 12 anstehende Druck wirkt durch den Kanal 30 in dem Ventilkörper 25 auf das Schließglied 22 gegen die Kraft des Meßfedersatzes 17. Die Weite des Ventilsitzes bestimmt dabei die für den Druck in der Leitung 12 wirksame Meßfläche am Schließglied 22. Übersteigt die durch den Druck in der Leitung 12 auf die Meßfläche ausgeübte Kraft die Vorspannkraft des Meßfedersatzes 17, hebt der Ventilkegel des Schließgliedes 22 vom Ventilsitz im Ventilkörper 25 ab und öffnet die Steuerleitung 12 zum drucklosen Ablauf, gebildet durch den Innenraum 31 des fest mit der Hydropumpe verbundenen Ventilgehäuses 21, wobei der Innenraum 31 mit dem drucklosen Innenraum 32 der Hydropumpe in Verbindung steht.The pressure in the operating pressure control line 12 acts through the channel 30 in the valve body 25 on the closing member 22 against the force of the measuring spring set 17. The width of the The valve seat determines the effective measuring surface on the closing element 22 for the pressure in the line 12. If the force exerted on the measuring surface by the pressure in the line 12 exceeds the prestressing force of the measuring spring set 17, the valve cone of the closing element 22 lifts off the valve seat in the valve body 25 and opens the control line 12 to the pressureless outlet, formed by the interior 31 of the valve housing 21 which is fixedly connected to the hydraulic pump, the interior 31 being connected to the depressurized interior 32 of the hydraulic pump.

Durch die Bewegung des Pumpenstellgliedes in Richtung kleinerer Fördermengen bewegt der Mitnehmerstift 20 den Ventilkörper 25 in Figur 2 nach rechts gegen das Schließglied 22 und erhöht damit die Vorspannung des Federsatzes 17 entsprechend dem gewünschten Verlauf der Momentenkennlinie.Due to the movement of the pump actuator in the direction of smaller delivery quantities, the driving pin 20 moves the valve body 25 in FIG. 2 to the right against the closing member 22 and thus increases the preload of the spring set 17 in accordance with the desired course of the torque characteristic.

In Figur 3 ist die erfindungsgemäße Regeleinrichtung als Summenmomemtenregelung für zwei Hydropumpen 33, 34 dargestellt, deren Antriebswellen direkt oder über ein entsprechendes Verteilergetriebe 35 (nurschematisch durch einen Strich angedeutet) von einer gemeinsamen nicht dargestellten Antriebsmaschine angetrieben werden. Die Regeleinrichtungen für die einzelnen Pumpen entsprechen der in Figur 1 dargestellten Regeleinrichtung. Gleiche Teile sind mit gleichen Bezugszeichen versehen und werden nicht nochmals erläutert. Lediglich die in Figur 1 mit 16 bezeichneten Momentenventile sind hier als Summenmomentenventile 36 ausgebildet und unterscheiden sich von dem Momentenventil 16 dadurch, daß das Schließglied 22 gemäß Figur4 eine zusätzliche Meßfläche 37 aufweist. Auf diese Meßfläche 37wirktjeweils über eine Steuerleitung 38, 39 der Betriebsdruck der anderen Pumpe. Das Ansprechen, das heißt Öffnen der Momentenventile 36 für das Steuerdruckmittel in den Leitungen 12 zum drucklosen Ablauf erfolgt somit in Abhängigkeit von der Summe der Betriebsdrücke. Solche Regelungen sind zum Beispiel erforderlich, wenn zwei Hydropumpen von einer gemeinsamen Antriebswelle oder über ein Verteilergetriebe angetrieben werden und die Summe beider Aufnahmemomente der Pumpen das Antriebsmoment nicht überschreiten darf.FIG. 3 shows the control device according to the invention as a total torque control for two hydraulic pumps 33, 34, the drive shafts of which are driven directly or via a corresponding transfer gear 35 (only schematically indicated by a dash) by a common drive machine, not shown. The control devices for the individual pumps correspond to the control device shown in FIG. The same parts are provided with the same reference numerals and are not explained again. Only the torque valves denoted by 16 in FIG. 1 are designed here as total torque valves 36 and differ from the torque valve 16 in that the closing member 22 according to FIG. 4 has an additional measuring surface 37. The operating pressure of the other pump acts on this measuring surface 37 in each case via a control line 38, 39. The response, that is to say the opening of the torque valves 36 for the control pressure medium in the lines 12 for the unpressurized discharge, thus takes place as a function of the sum of the operating pressures. Such regulations are necessary, for example, if two hydraulic pumps are driven by a common drive shaft or via a transfer case and the sum of the two absorption torques of the pumps must not exceed the drive torque.

Claims (9)

1. Output control device for an adjustable hydropump having a hydraulic servo-mechanism for continuous adjustment of the pump output, in which the output setting is determined by the output pressure of the hydropump and a pressure in a working pressure control line, and in which the adjusting mechanism includes a spring (4) urging the pump control member in the direction of maximum output and at least one piston (6) acting on the pump control member in the direction of reduction in output, the piston face being exposed to the output pressure through a hydraulically operated control valve, or with the outlet, and the control valve is operated by the pressure in the working pressure control line, characterized by the provision of a torque valve (16, 36) whose closure force is determined by a measuring spring or set of springs (17) effectively connected to the pump control member (3) and tensioned as a function of the output setting, and the working pressure control line (12) is connected to the pressureless outlet (18) depending on the pressure in the working pressure control line (12) and the tension in the measuring spring (17).
2. Control device according to claim 1, characterized in that the pressure acting on the control valve (8) and the torque valve (16) or their closure members is received in the working pressure control line (12) as the pressure beyond a throttle (13) in the control line branching off from the working pressure line (14) of the pump (1), and an output throttle (15) which may be variable, is provided upstream of the branch in the control line (12).
3. Control device according to claim 1 or claim 2, characterized in that the torque valve (16, 36) is fixed on to the hydropump (1) as a separate unit. and a follower pin (20) of the pump control member engages the torque valve (16, 36) to alter the tension in the measuring spring or set of springs (17), depending on the output setting.
4. Control device according to claim 3, characterized in that the torque valve (16) is in the form of a seat valve in which the valve coneconstituting the closure member (22) is acted upon by the measuring spring or set of springs (17), which is or are supported on the other side by an adjustable stop (27) in the valve housing (21), and wherein the valve seat is arranged in a displaceable valve body (25) which is engaged by the follower pin (20).
5. Control device according to claim 4, characterized in that the valve body (25) is loaded by a spring that holds it closely up against the follower pin (20).
6. Control device according to claim 4, characterized in that the stop (27) for the measuring spring or set of springs is adjustable from outside by means of a hand control (29).
7. Control device according to claim 4 or claim 6, characterized in that the stop (27) is arranged on the front of the valve housing (21) and can be released to exchange the measuring spring or set of springs (17).
8. Control device according to any preceding claim as a combined control for two or more hydropumps mechanically coupled on the drive side, characterized in that the closure member (22) of the torque valve of each pump (33, 34) is exposed to the sum of the pressure in the working pressure control line (12) of the individual pumps and the pressure in the working pressure line (14) of the other pump or pumps, and that each torque valve (36) connects the working pressure control line (12) of its pump with the pressureless outlet (18) depending on its combined working pressure and the tension in its measuring spring (17).
9. Control device according to claim 8, characterized in that the closure members of the torque valves has several measuring faces which act in parallel and are each exposed to the working pressure of one of the pumps.
EP84115198A 1983-12-14 1984-12-12 Feed controlling device for a variable hydropump Expired - Lifetime EP0149787B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE8335902U DE8335902U1 (en) 1983-12-14 1983-12-14 Torque control device for an adjustable hydraulic pump
DE19833345264 DE3345264A1 (en) 1983-12-14 1983-12-14 TORQUE CONTROL UNIT FOR AN ADJUSTABLE HYDROPUMP
DE3345264 1983-12-14

Publications (4)

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EP0149787A2 EP0149787A2 (en) 1985-07-31
EP0149787A3 EP0149787A3 (en) 1985-08-21
EP0149787B1 true EP0149787B1 (en) 1987-05-06
EP0149787B2 EP0149787B2 (en) 1991-10-02

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EP84115198A Expired - Lifetime EP0149787B2 (en) 1983-12-14 1984-12-12 Feed controlling device for a variable hydropump

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US (1) US4668171A (en)
EP (1) EP0149787B2 (en)
JP (1) JPS60147588A (en)
DE (2) DE8335902U1 (en)

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Also Published As

Publication number Publication date
JPH0526955B2 (en) 1993-04-19
US4668171A (en) 1987-05-26
EP0149787B2 (en) 1991-10-02
JPS60147588A (en) 1985-08-03
EP0149787A2 (en) 1985-07-31
DE8335902U1 (en) 1987-06-04
DE3345264A1 (en) 1985-06-27
EP0149787A3 (en) 1985-08-21

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