EP1504191B1 - Regulating device for hydrostatic piston machines - Google Patents

Regulating device for hydrostatic piston machines Download PDF

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Publication number
EP1504191B1
EP1504191B1 EP03727295A EP03727295A EP1504191B1 EP 1504191 B1 EP1504191 B1 EP 1504191B1 EP 03727295 A EP03727295 A EP 03727295A EP 03727295 A EP03727295 A EP 03727295A EP 1504191 B1 EP1504191 B1 EP 1504191B1
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EP
European Patent Office
Prior art keywords
piston
leg
adjusting device
control
setting
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Expired - Lifetime
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EP03727295A
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German (de)
French (fr)
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EP1504191A1 (en
Inventor
Winfried Lilla
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Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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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
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to an adjusting device for hydrostatic piston engines, in particular hydraulic motors of traction drives.
  • An adjusting device in which can be adjusted by a control piston movement, a pivot angle of a hydrostatic piston engine, wherein the actuating movement of the actuating piston is fed back to a control valve is from the DE 195 40 654 C1 known.
  • On the two oppositely oriented piston surfaces of the actuating piston acts in the control pressure chamber in each case a control pressure which is adjusted by a control valve.
  • the two control pressure chambers are acted upon by a corresponding control pressure.
  • the control piston is acted upon for deflection from its central position at its two end faces in each case with a control pressure.
  • the adjusting piston in a certain end position, while the control piston of the control valve is in its neutral position.
  • the control piston In this rest position, the control piston is free of forces. Since a deflection of the actuating piston from its end position is possible only in one direction, only a control force is generated on the control piston over the entire travel path up to its second end position, which is oriented in one direction. Due to the omitted change of direction of the control force on the control piston, the inharmonic pivot angle adjustment is prevented in the region of the central position.
  • the return force may not be equal to zero.
  • the control piston in the central rest position of the adjusting device, the return force may not be equal to zero.
  • a first embodiment of an adjusting device 1 is shown.
  • a control piston 2 is acted upon in a control pressure chamber 3 and a second control pressure chamber 4 with a control pressure.
  • the actuating pressures acting in the first and second actuating pressure chambers 3 and 4 act on the oppositely oriented piston surfaces of the actuating piston 2, at which a resultant force acts on a pressure difference.
  • a control pressure control valve 5 is provided.
  • the control pressure control valve 5 has a control piston 6 which is arranged axially displaceably in a bore of a housing 7.
  • a first feed pressure bore 8 and a second feed pressure bore 9 are introduced into the housing 7.
  • the first feed pressure bore 8 and second feed pressure bore 9 are connected to a feed pressure line 14, which may be connected, for example, to an auxiliary pressure source.
  • the feed pressure line 14 and the first feed pressure bore 8 or the second feed pressure bore 9 with a first actuating pressure line 12 or a second actuating pressure line 13 connectable.
  • the first actuating pressure line 12 is connected to a first actuating pressure channel 10, which opens on the part of the control piston 6 in a first groove 15.
  • the second actuating pressure line 13 is connected via a second actuating pressure channel 11 with a second groove 16.
  • the control piston 6 has a first control piston section 17 and a second control piston section 18, respectively.
  • the two control piston sections 17 and 18 respectively have a first control pressure control edge 19 and a second control pressure control edge 20, which are arranged at the oppositely oriented ends of the respective control piston section 17 or 18.
  • the first control pressure control edge 19 and the second control pressure control edge 20 form with the respective first groove 15 and second groove 16 a variable depending on the axial position of the control piston 6 throttle point.
  • the first actuating pressure channel 10 is connected via the first groove 15 with a first feed pressure 21 and thus the first actuating pressure chamber 3 is depressed with the pressure from the feed pressure line 14.
  • the second actuating pressure channel 11 is connected via the second groove 16 with a second feed pressure groove 22 when the control piston 6 is deflected in the opposite direction.
  • a first expansion control edge 23 is arranged on the side remote from the first control pressure control edge 19 side of the first control piston portion 17.
  • a second expansion control edge 24 is arranged at the second control piston portion 18 .
  • the respective control pressure chamber 3 or 4 is expanded via the two expansion control edges 23 and 24 via the first groove 15 and the second groove 16 into a tank volume 25.
  • the rear control piston chambers 27 and 27' are Also connected to the tank volume 25 via the volume equalization channels 26 and 26 ', the rear control piston chambers 27 and 27'.
  • the slight volume fluctuations that arise in the rear control piston chambers 27 and 27 'by an axial movement of the control piston 6 are thus compensated.
  • a proportional solenoid 28 is provided, which is arranged on the housing 7 of the control valve 5.
  • the proportional magnet 28 has a plunger 29, wherein the plunger 29 acts on an end face 30 of the control piston 6.
  • a control force can be transmitted to the control piston 6 in the axial direction, which is generated by the proportional magnet 28 in response to a control signal which is supplied to the proportional magnet 28 via an electrical connection 41. If the proportional magnet 28 is supplied with such a control signal via the electrical connection 41, it generates a force which displaces the control piston 6. In this case, a flow-through gap is generated by the axial movement of the control piston 6 at the first control pressure control edge 19.
  • the pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first setting pressure chamber 3 via the first setting pressure passage 10.
  • the thus increased pressure in the first actuating pressure chamber 3 causes an adjustment of the actuating piston 2 against the force of a return spring 40 in the direction of its second end position.
  • the throttle point of the second discharge control edge 24 is opened in the second control piston section 18.
  • the second control pressure chamber 4 is expanded via the second control pressure line 13 and the second control pressure channel 11 in the tank volume 25.
  • a Mit supportiveausnaturalung 33 is provided in the adjusting piston 2, in which a driving head 32 is arranged, which is connected to the adjusting lever 31.
  • the adjusting lever 31 is rotatably mounted on a bearing pin 34, so that the adjusting movement of the actuating piston 2 leads to a rotation of the actuating lever 31.
  • Also rotatably mounted on the bearing pin 34 are a first leg 35 and a second leg 36.
  • the first leg 35 and the second leg 36 are connected via a tension spring 37 with each other, so that a deflection of one of the two legs relative to the other to a voltage the tension spring 37 leads.
  • a driving pin 38 is arranged at the opposite end to the driving head 32 of the actuating lever 31 end of the actuating lever 31.
  • the driving pin 38 moves in opposite directions to the actuating piston movement.
  • the driving pin 38 abuts against the second leg 36, so that the second leg 36 is deflected relative to the first leg 35 by the rotational movement of the actuating lever 31 and the spring 37 is tensioned.
  • Fig. 2 the adjusting piston 2 is shown in its second end position, wherein, as described, the second leg 36 is deflected relative to the first leg 35, so that the tension spring 37 is maximally tensioned. Due to the tension of the tension spring is on the first leg 35 a Force generated with which the first leg 35 of the movement of the second leg 36 tries to follow. However, the first leg 35 is in abutment with a contact pin 39, which is arranged on the control piston 6. Thereby, the force of the tension spring 37 is transmitted from the first leg 35 to the abutment pin 39 and the control piston 6 experiences a return force, which is opposite to the control force of the proportional magnet 28.
  • This return force is the greater, the further the actuating piston 2 is deflected in the direction of its second end position.
  • the return force transmitted from the first leg 35 to the control piston 6 by means of the abutment pin 39 moves the control piston 6 counter to the control force generated by the proportional magnet 28 until an equilibrium of forces from the return force and the control force is achieved.
  • the control piston 6 is again in its neutral position, in which the throttles formed on the control pressure control edges 19 and 20 are closed.
  • the deflecting control signal which is supplied via the electrical connection 41 to the proportional magnet 28, withdrawn.
  • the control piston 6 is no longer in the balance of power and is characterized by the overwhelming return force in the representation of Fig. 2 deflected to the right.
  • a flow-through gap is now generated at the second control pressure control edge 20 and correspondingly at the first expansion control edge 23 of the first control piston section 17, a gap also through which can flow.
  • the second control pressure chamber 4 is depressed with the pressure medium from the feed pressure line 14, the first control pressure chamber 3, however, relaxed.
  • the adjusting piston 2 follows the changed pressure ratio and moves in the direction of its first end position.
  • a control force is generated on the control piston 6, which acts in one direction. Free of a control force is the control piston 6 only when the actuator piston 2 is in its first end position. A transfer and an associated change of direction of the force between the two legs 35 and 36 is not required, so that the control characteristic is harmonious.
  • the control force proportional to the deflection of the actuating piston 2 likewise generates an actuating piston movement 2, which is proportional to the control signal applied to the proportional magnet 28.
  • a second embodiment of the adjusting device according to the invention is shown.
  • an exercise with a compression spring 42 wherein the compression spring 42 between a first spring bearing 43 and a second spring bearing 44 is supported.
  • the second spring bearing 44 is part of a sleeve which is arranged displaceably on a sliding cylinder 45.
  • the spring bearing 44 is rotatably connected to the second leg 36 in an eye 48 of the leg 36.
  • the first spring bearing 43 is connected to the sliding cylinder 45 via a Retaining pin 46 connected.
  • a control pressure port 47 is provided. Via the control pressure port 47, a control force is applied to the end face 30 of the control piston 6, wherein the control force is generated in a known manner, for example from an auxiliary pressure source.
  • Fig. 4 is a partial section along the line AA the Fig. 1 shown.
  • the adjusting lever 31, the leg 35 and the second leg 36 are rotatably mounted on a common bearing pin 34.
  • the bearing pin 34 is designed in multiple stages, and fixed in the housing 7 in a first and a second bore 48 and 49, respectively.
  • the driving pin 38 is arranged in a bore.
  • the investment pin 39 is also arranged in a bore.
  • the driving pin 38 and the contact pin 39 are fixed with a press fit in their holes. As already described, the driving pin 38 acts on the second leg 36, the contact pin 39, however, on the first leg 35, which in the Fig.
  • Fig. 5 is an enlarged view in the section V of Fig. 1 shown.
  • the section shows a part of the first leg 35 and of the control piston 6 with the abutment pin 39 arranged therein.
  • the first leg 35 has a flattening 50.
  • the flattening 50 is oriented so that the longitudinal axis of the control piston 6 with the flattened point 50 encloses a right angle. This prevents that the introduction of the return force to the control piston 6 deviates from the central axis and thus its direction of movement.
  • the return force in the then central rest position of the adjusting device 1 also be non-zero, even if the feed pressure p sp is equal to zero.
  • the central rest position is then by two arranged on each side of the control piston 2 compression springs 40 as in the DE 195 40 654 C1 guaranteed. In this case, the control piston 6 will not located in the central rest position to its neutral position when no control power is transmitted to the regulating piston 6 from the proportional solenoid 28 or by the control pressure p tax.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft eine Verstellvorrichtung für hydrostatische Kolbenmaschinen, insbesondere Hydromotoren von Fahrantrieben.The invention relates to an adjusting device for hydrostatic piston engines, in particular hydraulic motors of traction drives.

Eine Verstellvorrichtung, bei der sich durch eine Stellkolbenbewegung ein Schwenkwinkel einer hydrostatischen Kolbenmaschine einstellen läßt, wobei die Stellbewegung des Stellkolbens auf ein Regelventil rückgekoppelt ist, ist aus der DE 195 40 654 C1 bekannt. Durch die Rückkopplung der Stellbewegung des Stellkolbens wird dabei eine Einstellung eines Schwenkwinkels, der proportional zu einer Steuergröße ist, ermöglicht. Auf die beiden entgegengesetzt orientierten Kolbenflächen des Stellkolbens wirkt in der Stelldruckkammer jeweils ein Stelldruck, der durch ein Regelventil eingestellt wird. In Abhängigkeit von einer axialen Position eines Regelkolbens werden die beiden Stelldruckkammern mit einem entsprechenden Stelldruck beaufschlagt. Der Regelkolben ist zur Auslenkung aus seiner Mittellage an seinen beiden Stirnseiten jeweils mit einem Steuerdruck beaufschlagbar.An adjusting device in which can be adjusted by a control piston movement, a pivot angle of a hydrostatic piston engine, wherein the actuating movement of the actuating piston is fed back to a control valve, is from the DE 195 40 654 C1 known. By the feedback of the adjusting movement of the adjusting piston while an adjustment of a pivot angle, which is proportional to a control variable allows. On the two oppositely oriented piston surfaces of the actuating piston acts in the control pressure chamber in each case a control pressure which is adjusted by a control valve. Depending on an axial position of a control piston, the two control pressure chambers are acted upon by a corresponding control pressure. The control piston is acted upon for deflection from its central position at its two end faces in each case with a control pressure.

Über einen Stellhebel und zwei mit einer Feder gekoppelten Schenkeln ist eine der Auslenkungen des Stellkolbens aus seiner Mittellage proportionale Kraft auf den Regelkolben rückkoppelbar. Die Rückkopplung erfolgt dabei so, daß auf den Regelkolben eine Kraft ausgeübt wird, welche dem an jeweils einem Ende des Regelkolbens anliegenden Steuerdruck entgegengerichtet ist.About a lever and two coupled with a spring legs one of the deflections of the actuating piston from its central position proportional force can be fed back to the control piston. The feedback takes place so that a force is exerted on the control piston, which is directed opposite to the voltage applied to one end of the control piston control pressure.

Bei der beschriebenen Stellvorrichtung ist von Nachteil, daß bei einem Verfahrweg des Stellkolbens von einer Endposition zur anderen Endposition die Mittelposition überfahren werden muß, wobei in diesem Fall eine Übergabe der Rückkopplung von einem Schenkel auf den anderen Schenkel erfolgt. Da eine spielfreie Ausführung des Stellhebels, der beiden Schenkel sowie der entsprechenden Mitnehmer nicht möglich ist, führt dies zwangsläufig zu einer unharmonischen Schwenkwinkelverstellung.In the described adjusting device has the disadvantage that in a travel of the actuating piston from one end position to the other end position, the center position must be crossed over, in which case a transfer of the feedback from one leg to the other leg. Because a backlash-free execution of Adjusting lever, the two legs and the corresponding driver is not possible, this inevitably leads to a disarmed swing angle adjustment.

Es ist die Aufgabe der Erfindung, eine Verstellvorrichtung mit einer harmonischen Verstellung des Schwenkwinkels über den gesamten Schwenkwinkelbereich zu schaffen.It is the object of the invention to provide an adjusting device with a harmonic adjustment of the swivel angle over the entire swivel angle range.

Die Aufgabe wird durch die erfindungsgemäße Verstellvorrichtung mit den Merkmalen des Anspruchs 1 oder des Anspruchs 3 gelöst.The object is achieved by the adjusting device according to the invention with the features of claim 1 or claim 3.

Erfindungsgemäß befindet sich in der Ruheposition der Verstellvorrichtung gemäß Anspruch 1 der Stellkolben in einer bestimmten Endposition, während sich der Regelkolben des Regelventils in seiner Neutralstellung befindet. In dieser Ruheposition ist der Regelkolben frei von Kräften. Da eine Auslenkung des Stellkolbens aus seiner Endposition nur in einer Richtung möglich ist, wird auch über den gesamten Verfahrweg bis hin zu seiner zweiten Endposition nur eine Regelkraft auf den Regelkolben erzeugt, welche in einer Richtung orientiert ist. Durch den entfallenden Richtungswechsel der Regelkraft auf den Regelkolben wird die unharmonische Schwenkwinkelverstellung im Bereich der Mittellage verhindert.According to the invention is in the rest position of the adjusting device according to claim 1, the adjusting piston in a certain end position, while the control piston of the control valve is in its neutral position. In this rest position, the control piston is free of forces. Since a deflection of the actuating piston from its end position is possible only in one direction, only a control force is generated on the control piston over the entire travel path up to its second end position, which is oriented in one direction. Due to the omitted change of direction of the control force on the control piston, the inharmonic pivot angle adjustment is prevented in the region of the central position.

Alternativ kann gemäß Anspruch 3 auch in der mittigen Ruheposition der Verstellvorrichtung die Rückführungskraft ungleich Null sein. Dabei befindet sich der Regelkolben in der mittigen Ruheposition nicht in seiner Neutralstellung, wenn auf den Regelkolben keine Steuerkraft übertragen wird.Alternatively, according to claim 3, in the central rest position of the adjusting device, the return force may not be equal to zero. In this case, the control piston is not in its neutral position in the central rest position when no control force is transmitted to the control piston.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der Erfindung möglich.The measures listed in the dependent claims advantageous developments of the invention are possible.

In den Zeichnungen sind Ausführungsbeispiele der Erfindung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
eine schematische Darstellung eines ersten Ausführungsbeispiels der erfindungsgemäßen Verstellvorrichtung in Ruheposition;
Fig. 2
eine schematische Darstellung des ersten Ausführungsbeispiels der erfindungsgemäßen Verstellvorrichtung in seiner zweiten Endposition;
Fig. 3
ein zweites Ausführungsbeispiel der erfindungsgemäßen Verstellvorrichtung in Ruheposition;
Fig. 4
ein Teilschnitt entlang der Linie A-A der Fig. 1; und
Fig. 5
eine vergrößerte Darstellung im Ausschnitt V der Fig. 2.
In the drawings, embodiments of the invention are illustrated and explained in more detail in the following description. Show it:
Fig. 1
a schematic representation of a first embodiment of the adjusting device according to the invention in the rest position;
Fig. 2
a schematic representation of the first embodiment of the adjusting device according to the invention in its second end position;
Fig. 3
a second embodiment of the adjusting device according to the invention in the rest position;
Fig. 4
a partial section along the line AA the Fig. 1 ; and
Fig. 5
an enlarged view in the section V of Fig. 2 ,

In Fig. 1 ist ein erstes Ausführungsbeispiel einer erfindungsgemäßen Verstellvorrichtung 1 dargestellt. Zum Regeln eines Schwenkwinkels einer nicht dargestellten hydrostatischen Kolbenmaschine wird ein Stellkolben 2 in einer Stelldruckkammer 3 sowie einer zweiten Stelldruckkammer 4 mit einem Stelldruck beaufschlagt. Die in der ersten und zweiten Stelldruckkammer 3 und 4 wirkenden Stelldrücke wirken auf die entgegengesetzt orientierten Kolbenflächen des Stellkolbens 2, an dem bei einer Druckdifferenz eine resultierende Kraft angreift. Zur Einstellung der Druckdifferenz in den beiden Stelldruckkammern 3 und 4 ist ein Stelldruckregelventil 5 vorgesehen. Das Stelldruckregelventil 5 weist einen Regelkolben 6 auf, der in einer Bohrung eines Gehäuses 7 axial verschieblich angeordnet ist. Weiterhin sind in dem Gehäuse 7 eine erste Speisedruckbohrung 8 sowie eine zweite Speisedruckbohrung 9 eingebracht. Die erste Speisedruckbohrung 8 und zweite Speisedruckbohrung 9 sind mit einer Speisedruckleitung 14 verbunden, die beispielsweise an einer Hilfsdruckquelle angeschlossen sein kann.In Fig. 1 a first embodiment of an adjusting device 1 according to the invention is shown. To control a swivel angle of a hydrostatic piston machine, not shown, a control piston 2 is acted upon in a control pressure chamber 3 and a second control pressure chamber 4 with a control pressure. The actuating pressures acting in the first and second actuating pressure chambers 3 and 4 act on the oppositely oriented piston surfaces of the actuating piston 2, at which a resultant force acts on a pressure difference. To set the pressure difference in the two control pressure chambers 3 and 4, a control pressure control valve 5 is provided. The control pressure control valve 5 has a control piston 6 which is arranged axially displaceably in a bore of a housing 7. Furthermore, a first feed pressure bore 8 and a second feed pressure bore 9 are introduced into the housing 7. The first feed pressure bore 8 and second feed pressure bore 9 are connected to a feed pressure line 14, which may be connected, for example, to an auxiliary pressure source.

Zum Einstellen der Stelldrücke in der ersten Stelldruckkammer 3 und der zweiten Stelldruckkammer 4 ist die Speisedruckleitung 14 bzw. die erste Speisedruckbohrung 8 oder die zweite Speisedruckbohrung 9 mit einer ersten Stelldruckleitung 12 oder einen zweiten Stelldruckleitung 13 verbindbar. Hierzu ist die erste Stelldruckleitung 12 an einem ersten Stelldruckkanal 10 angeschlossen, der seitens des Regelkolbens 6 in eine erste Nut 15 mündet. Ebenso ist die zweite Stelldruckleitung 13 über einen zweiten Stelldruckkanal 11 mit einer zweiten Nut 16 verbunden. Im Bereich der ersten bzw. zweiten Nut 15 bzw. 16 weist der Regelkolben 6 einen ersten Regelkolbenabschnitt 17 bzw. einen zweiten Regelkolbenabschnitt 18 auf. Die beiden Regelkolbenabschnitte 17 bzw. 18 weisen eine erste Stelldrucksteuerkante 19 bzw. eine zweite Stelldrucksteuerkante 20 auf, die an den entgegengesetzt orientierten Enden des jeweiligen Regelkolbenabschnitts 17 bzw. 18 angeordnet sind. Die erste Stelldrucksteuerkante 19 und die zweite Stelldrucksteuerkante 20 bilden mit der jeweiligen ersten Nut 15 bzw. zweiten Nut 16 eine in Abhängigkeit von der axialen Position des Regelkolbens 6 variable Drosselstelle aus. Durch die gemeinsame Bewegung der beiden Steuerkanten 19 bzw. 20 wird dabei jeweils eine Drossel geöffnet und gleichzeitig die andere Drossel geschlossen.To set the control pressures in the first control pressure chamber 3 and the second control pressure chamber 4, the feed pressure line 14 and the first feed pressure bore 8 or the second feed pressure bore 9 with a first actuating pressure line 12 or a second actuating pressure line 13 connectable. For this purpose, the first actuating pressure line 12 is connected to a first actuating pressure channel 10, which opens on the part of the control piston 6 in a first groove 15. Likewise, the second actuating pressure line 13 is connected via a second actuating pressure channel 11 with a second groove 16. In the region of the first and second groove 15 and 16, the control piston 6 has a first control piston section 17 and a second control piston section 18, respectively. The two control piston sections 17 and 18 respectively have a first control pressure control edge 19 and a second control pressure control edge 20, which are arranged at the oppositely oriented ends of the respective control piston section 17 or 18. The first control pressure control edge 19 and the second control pressure control edge 20 form with the respective first groove 15 and second groove 16 a variable depending on the axial position of the control piston 6 throttle point. By the common movement of the two control edges 19 and 20, one throttle is opened while the other throttle is closed.

Je nach Bewegungsrichtung der Regelkolbens 6 wird damit der erste Stelldruckkanal 10 über die erste Nut 15 mit einer ersten Speisedrucknut 21 verbunden und damit die erste Stelldruckkammer 3 mit dem Druck aus der Speisedruckleitung 14 bedrückt. Analog wird der zweite Stelldruckkanal 11 über die zweite Nut 16 mit einer zweiten Speisedrucknut 22 verbunden, wenn der Regelkolben 6 in die entgegengesetzte Richtung ausgelenkt wird.Depending on the direction of movement of the control piston 6 so that the first actuating pressure channel 10 is connected via the first groove 15 with a first feed pressure 21 and thus the first actuating pressure chamber 3 is depressed with the pressure from the feed pressure line 14. Similarly, the second actuating pressure channel 11 is connected via the second groove 16 with a second feed pressure groove 22 when the control piston 6 is deflected in the opposite direction.

Auf der von der ersten Stelldrucksteuerkante 19 abgewandten Seite des ersten Regelkolbenabschnitts 17 ist eine erste Entspannungssteuerkante 23 angeordnet. Ebenso ist an dem zweiten Regelkolbenabschnitt 18 eine zweite Entspannungssteuerkante 24 angeordnet. In Abhängigkeit von der axial Position des Regelkolbens 6 wird über die beiden Entspannungssteuerkanten 23 bzw. 24 die jeweilige Stelldruckkammer 3 bzw. 4 über die erste Nut 15 bzw. die zweite Nut 16 in ein Tankvolumen 25 entspannt.On the side remote from the first control pressure control edge 19 side of the first control piston portion 17, a first expansion control edge 23 is arranged. Likewise is at the second control piston portion 18 a second expansion control edge 24 is arranged. Depending on the axial position of the control piston 6, the respective control pressure chamber 3 or 4 is expanded via the two expansion control edges 23 and 24 via the first groove 15 and the second groove 16 into a tank volume 25.

Ebenfalls mit dem Tankvolumen 25 verbunden sind über die Volumenausgleichskanäle 26 und 26' die rückwärtigen Regelkolbenräume 27 und 27'. Die geringfügigen Volumenschwankungen, die in den rückwärtigen Regelkolbenräumen 27 und 27' durch eine axiale Bewegung des Regelkolbens 6 entstehen, werden damit ausgeglichen. Außerdem wird ein Teil der Regelkolbenleckage über die Volumenausgleichskanäle 26 und 26' ins Tankvolumen 25 abgeführt.Also connected to the tank volume 25 via the volume equalization channels 26 and 26 ', the rear control piston chambers 27 and 27'. The slight volume fluctuations that arise in the rear control piston chambers 27 and 27 'by an axial movement of the control piston 6 are thus compensated. In addition, a part of the control piston leakage via the volume equalization channels 26 and 26 'discharged into the tank volume 25.

Um den Stellkolben 2 in seine in der Fig. 2 dargestellte zweite Endposition zu verstellen, ist ein Proportionalmagnet 28 vorgesehen, welcher an dem Gehäuse 7 des Regelventils 5 angeordnet ist. Der Proportionalmagnet 28 weist einen Stößel 29 auf, wobei der Stößel 29 auf eine Stirnfläche 30 des Regelkolbens 6 wirkt. Damit ist auf den Regelkolben 6 in axialer Richtung eine Steuerkraft übertragbar, welche durch den Proportionalmagneten 28 in Abhängigkeit von einem Steuersignal erzeugt wird, das dem Proportionalmagneten 28 über einen elektrischen Anschluß 41 zugeführt wird. Wird dem Proportionalmagneten 28 über den elektrischen Anschluß 41 ein solches Steuersignal zugeführt, so erzeugt er eine Kraft, die den Regelkolben 6 verschiebt. Dabei wird durch die axiale Bewegung des Regelkolbens 6 an der ersten Stelldrucksteuerkante 19 ein durchströmbarer Spalt erzeugt. Das über die Speisedruckleitung 14 und die erste Speisedruckbohrung 8 zugeführte Druckmittel kann über den ersten Stelldruckkanal 10 in die erste Stelldruckkammer 3 gelangen. Der somit in der ersten Stelldruckkammer 3 erhöhte Druck bewirkt eine Verstellung des Stellkolbens 2 entgegen der Kraft einer Rückstellfeder 40 in Richtung seiner zweiten Endposition.To the actuator piston 2 in his in the Fig. 2 Adjusted shown second end position, a proportional solenoid 28 is provided, which is arranged on the housing 7 of the control valve 5. The proportional magnet 28 has a plunger 29, wherein the plunger 29 acts on an end face 30 of the control piston 6. Thus, a control force can be transmitted to the control piston 6 in the axial direction, which is generated by the proportional magnet 28 in response to a control signal which is supplied to the proportional magnet 28 via an electrical connection 41. If the proportional magnet 28 is supplied with such a control signal via the electrical connection 41, it generates a force which displaces the control piston 6. In this case, a flow-through gap is generated by the axial movement of the control piston 6 at the first control pressure control edge 19. The pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first setting pressure chamber 3 via the first setting pressure passage 10. The thus increased pressure in the first actuating pressure chamber 3 causes an adjustment of the actuating piston 2 against the force of a return spring 40 in the direction of its second end position.

Gleichzeitig mit dem Öffnen der Drosselstelle an der ersten Stelldrucksteuerkante 19 wird im zweiten Regelkolbenabschnitt 18 die Drosselstelle der zweiten Entlastungssteuerkante 24 geöffnet. Der zweite Stelldruckraum 4 wird über die zweite Stelldruckleitung 13 sowie den zweiten Stelldruckkanal 11 in das Tankvolumen 25 entspannt.Simultaneously with the opening of the throttle point at the first control pressure control edge 19, the throttle point of the second discharge control edge 24 is opened in the second control piston section 18. The second control pressure chamber 4 is expanded via the second control pressure line 13 and the second control pressure channel 11 in the tank volume 25.

Zur Rückkopplung der Stellbewegung des Stellkolbens 2 ist in dem Stellkolben 2 eine Mitnehmerausnehmung 33 vorgesehen, in welcher ein Mitnehmerkopf 32 angeordnet ist, der mit dem Stellhebel 31 verbunden ist. Der Stellhebel 31 ist auf einem Lagerbolzen 34 drehbar gelagert, so daß die Stellbewegung des Stellkolbens 2 zu einer Drehung des Stellhebels 31 führt. Ebenfalls auf dem Lagerbolzen 34 drehbar gelagert sind ein erster Schenkel 35 sowie ein zweiter Schenkel 36. Der erste Schenkel 35 sowie der zweite Schenkel 36 sind über eine Zugfeder 37 miteinander verbunden, so daß eine Auslenkung eines der beiden Schenkel relativ zu dem anderen zu einer Spannung der Zugfeder 37 führt.For the feedback of the adjusting movement of the adjusting piston 2, a Mitnehmerausnehmung 33 is provided in the adjusting piston 2, in which a driving head 32 is arranged, which is connected to the adjusting lever 31. The adjusting lever 31 is rotatably mounted on a bearing pin 34, so that the adjusting movement of the actuating piston 2 leads to a rotation of the actuating lever 31. Also rotatably mounted on the bearing pin 34 are a first leg 35 and a second leg 36. The first leg 35 and the second leg 36 are connected via a tension spring 37 with each other, so that a deflection of one of the two legs relative to the other to a voltage the tension spring 37 leads.

An dem zu dem Mitnehmerkopf 32 des Stellhebels 31 entgegengesetzten Ende des Stellhebels 31 ist ein Mitnahmestift 38 angeordnet. Bei einer Bewegung des Stellkolbens 2 und einer damit verbundenen Drehbewegung des Stellhebels 31 bewegt sich der Mitnahmestift 38 gegenläufig zu der Stellkolbenbewegung. Der Mitnahmestift 38 liegt an dem zweiten Schenkel 36 an, so daß durch die Drehbewegung des Stellhebels 31 der zweite Schenkel 36 relativ zu dem ersten Schenkel 35 ausgelenkt wird und die Feder 37 gespannt wird.At the opposite end to the driving head 32 of the actuating lever 31 end of the actuating lever 31, a driving pin 38 is arranged. During a movement of the actuating piston 2 and an associated rotational movement of the adjusting lever 31, the driving pin 38 moves in opposite directions to the actuating piston movement. The driving pin 38 abuts against the second leg 36, so that the second leg 36 is deflected relative to the first leg 35 by the rotational movement of the actuating lever 31 and the spring 37 is tensioned.

In Fig. 2 ist der Stellkolben 2 in seiner zweiten Endposition gezeigt, wobei, wie beschrieben, der zweite Schenkel 36 gegenüber dem ersten Schenkel 35 ausgelenkt ist, so daß die Zugfeder 37 maximal gespannt ist. Durch die Spannung der Zugfeder wird auf den ersten Schenkel 35 eine Kraft erzeugt, mit welcher der erste Schenkel 35 der Bewegung des zweiten Schenkels 36 zu folgen versucht. Der erste Schenkel 35 befindet sich jedoch in Anlage mit einem Anlagestift 39, der an dem Regelkolben 6 angeordnet ist. Dadurch wird die Kraft der Zugfeder 37 von dem ersten Schenkel 35 auf den Anlagestift 39 übertragen und der Regelkolben 6 erfährt eine Rückführungskraft, die der Steuerkraft des Proportionalmagneten 28 entgegengerichtet ist.In Fig. 2 the adjusting piston 2 is shown in its second end position, wherein, as described, the second leg 36 is deflected relative to the first leg 35, so that the tension spring 37 is maximally tensioned. Due to the tension of the tension spring is on the first leg 35 a Force generated with which the first leg 35 of the movement of the second leg 36 tries to follow. However, the first leg 35 is in abutment with a contact pin 39, which is arranged on the control piston 6. Thereby, the force of the tension spring 37 is transmitted from the first leg 35 to the abutment pin 39 and the control piston 6 experiences a return force, which is opposite to the control force of the proportional magnet 28.

Diese Rückführungskraft ist um so größer, je weiter der Stellkolben 2 in Richtung seiner zweiten Endposition ausgelenkt ist. Die von dem ersten Schenkel 35 mittels des Anlagestifts 39 auf den Regelkolben 6 übertragene Rückführungskraft bewegt den Regelkolben 6 so lange entgegen der durch den Proportionalmagneten 28 erzeugten Steuerkraft, bis ein Kräftegleichgewicht aus der Rückführungskraft und der Steuerkraft erreicht ist. Bei eingestelltem Kräftegleichgewicht an dem Regelkolben 6 befindet sich der Regelkolben 6 wieder in seiner Neutralposition, in der die an den Stelldrucksteuerkanten 19 bzw. 20 ausgebildeten Drosseln geschlossen sind.This return force is the greater, the further the actuating piston 2 is deflected in the direction of its second end position. The return force transmitted from the first leg 35 to the control piston 6 by means of the abutment pin 39 moves the control piston 6 counter to the control force generated by the proportional magnet 28 until an equilibrium of forces from the return force and the control force is achieved. When the balance of power is set on the control piston 6, the control piston 6 is again in its neutral position, in which the throttles formed on the control pressure control edges 19 and 20 are closed.

Um eine Rückstellbewegung des Stellkolbens 2 in Richtung seiner ersten Endposition zu erzeugen, wird das auslenkende Steuersignal, welches über den elektrischen Anschluß 41 dem Proportionalmagneten 28 zugeführt ist, zurückgenommen. Der Regelkolben 6 befindet sich nicht mehr im Kräftegleichgewicht und wird durch die überwiegende Rückführungskraft in der Darstellung der Fig. 2 nach rechts ausgelenkt. Umgekehrt zu dem vorher beschriebenen Stellvorgang des Stellkolbens 2 in Richtung seiner zweiten Endposition wird nunmehr an der zweiten Stelldrucksteuerkante 20 ein durchströmbarer Spalt erzeugt und entsprechend an der ersten Entspannungsteuerkante 23 des ersten Regelkolbenabschnitts 17 ein ebenfalls durchströmbarer Spalt. Damit wird im umgekehrten Fall zur Stellbewegung nunmehr die zweite Steuerdruckkammer 4 mit dem Druckmittel aus der Speisedruckleitung 14 bedrückt, die erste Steuerdruckkammer 3 hingegen entspannt. Der Stellkolben 2 folgt dem veränderten Druckverhältnis und bewegt sich in Richtung seiner ersten Endposition.In order to generate a return movement of the actuating piston 2 in the direction of its first end position, the deflecting control signal, which is supplied via the electrical connection 41 to the proportional magnet 28, withdrawn. The control piston 6 is no longer in the balance of power and is characterized by the overwhelming return force in the representation of Fig. 2 deflected to the right. Conversely to the previously described adjusting operation of the actuating piston 2 in the direction of its second end position, a flow-through gap is now generated at the second control pressure control edge 20 and correspondingly at the first expansion control edge 23 of the first control piston section 17, a gap also through which can flow. Thus, in the opposite case to the adjusting movement now the second control pressure chamber 4 is depressed with the pressure medium from the feed pressure line 14, the first control pressure chamber 3, however, relaxed. The adjusting piston 2 follows the changed pressure ratio and moves in the direction of its first end position.

Durch die Auswahl der Ruheposition des Stellkolbens 2 in seiner ersten Endposition bei Verschwinden der Steuerkraft wird über den gesamten Regelbereich bzw. den Stellbereich des Stellkolbens 2 eine Regelkraft auf den Regelkolben 6 erzeugt, die in eine Richtung wirkt. Frei von einer Regelkraft ist der Regelkolben 6 nur, wenn der Stellkolben 2 sich in seiner ersten Endposition befindet. Eine Übergabe und ein damit verbundener Richtungswechsel der Kraft zwischen den beiden Schenkeln 35 und 36 ist nicht erforderlich, so daß die Regelkennlinie harmonisch ist. Die der Auslenkung des Stellkolbens 2 proportionale Regelkraft erzeugt dabei gleichermaßen eine Stellkolbenbewegung 2, die proportional zu der an dem Proportionalmagneten 28 angelegten Steuersignal ist.By selecting the rest position of the actuating piston 2 in its first end position upon disappearance of the control force over the entire control range or the control range of the actuating piston 2, a control force is generated on the control piston 6, which acts in one direction. Free of a control force is the control piston 6 only when the actuator piston 2 is in its first end position. A transfer and an associated change of direction of the force between the two legs 35 and 36 is not required, so that the control characteristic is harmonious. The control force proportional to the deflection of the actuating piston 2 likewise generates an actuating piston movement 2, which is proportional to the control signal applied to the proportional magnet 28.

Durch die asymmetrische Auslegung ist es weiterhin möglich, den Proportionalmagneten 28 in seinem proportionalen Regelbereich über den gesamten Verstellweg des Stellkolbens 2 zu betreiben. Die bei Verwendung zweier auf die entgegengesetzten Enden des Regelkolbens 6 wirkenden Proportionalmagnete verursachen Unregelmäßigkeiten in der Kennlinie durch die Rampe, auf der der Proportionalmagnet aus seiner stromlosen Ausgangslage in seinem proportionalen Regelbereich gebracht werden muß.Due to the asymmetrical design, it is also possible to operate the proportional magnet 28 in its proportional control range over the entire displacement of the actuating piston 2. The use of two acting on the opposite ends of the control piston 6 proportional solenoids cause irregularities in the characteristic by the ramp on which the proportional solenoid must be brought from its currentless starting position in its proportional control range.

In Fig. 3 ist ein zweites Ausführungsbeispiel der erfindungsgemäßen Verstellvorrichtung dargestellt. Anstelle der Zugfeder 37 ist hier eine Ausübung mit einer Druckfeder 42 dargestellt, wobei sich die Druckfeder 42 zwischen einem ersten Federlager 43 und einem zweiten Federlager 44 abstützt. Das zweite Federlager 44 ist Teil einer Hülse, welche auf einem Gleitzylinder 45 verschiebbar angeordnet ist. Das Federlager 44 ist mit dem zweiten Schenkel 36 in einem Auge 48 des Schenkels 36 drehbar verbunden. Das erste Federlager 43 ist mit dem Gleitzylinder 45 über einen Haltestift 46 verbunden. In dem Hülsenbereich des zweiten Federlagers 44 sind nicht dargestellte Schlitze angebracht, in denen der Haltesplint 46 eine Längsverschiebung ausführen kann, so daß das erste Federlager 44 außen auf der Hülse längsverschiebbar ist. Der Gleitzylinder 45 ist in einem Auge 49 des ersten Schenkels 35 ebenfalls drehbar gelagert. Eine relative Auslenkung des zweiten Schenkels 36 zu dem ersten Schenkel 35 führt damit zu einer Kompression der Druckfeder 42. Die Funktion einer solchen Anordnung unterscheidet sich von den zu Fig. 2 erläuterten Arbeitsweise nur dadurch, daß die Rückführungskraft über eine Kompression der Druckfeder 42 erzeugt wird.In Fig. 3 a second embodiment of the adjusting device according to the invention is shown. Instead of the tension spring 37 is here shown an exercise with a compression spring 42, wherein the compression spring 42 between a first spring bearing 43 and a second spring bearing 44 is supported. The second spring bearing 44 is part of a sleeve which is arranged displaceably on a sliding cylinder 45. The spring bearing 44 is rotatably connected to the second leg 36 in an eye 48 of the leg 36. The first spring bearing 43 is connected to the sliding cylinder 45 via a Retaining pin 46 connected. In the sleeve portion of the second spring bearing 44 slots not shown are attached, in which the retaining pin 46 can perform a longitudinal displacement, so that the first spring bearing 44 is longitudinally displaceable on the outside of the sleeve. The sliding cylinder 45 is also rotatably mounted in an eye 49 of the first leg 35. A relative deflection of the second leg 36 to the first leg 35 thus leads to a compression of the compression spring 42. The function of such an arrangement differs from that Fig. 2 explained operation only in that the return force is generated by compression of the compression spring 42.

Weiterhin ist in dem in Fig. 3 gezeigten Ausführungsbeispiel anstelle des Proportionalmagneten 28 ein Steuerdruckanschluß 47 vorgesehen. Über den Steuerdruckanschluß 47 wird auf die Stirnfläche 30 des Regelkolbens 6 eine Steuerkraft gegeben, wobei die Steuerkraft auf bekannte Weise erzeugt wird, beispielsweise aus einer Hilfsdruckquelle.Furthermore, in the in Fig. 3 embodiment shown instead of the proportional solenoid 28, a control pressure port 47 is provided. Via the control pressure port 47, a control force is applied to the end face 30 of the control piston 6, wherein the control force is generated in a known manner, for example from an auxiliary pressure source.

In Fig. 4 ist ein Teilschnitt entlang der Linie A-A der Fig. 1 dargestellt. Der Stellhebel 31, der Schenkel 35 sowie der zweite Schenkel 36 sind auf einem gemeinsamen Lagerbolzen 34 drehbar gelagert. Der Lagerbolzen 34 ist mehrstufig ausgeführt, und in dem Gehäuse 7 in einer ersten sowie einer zweiten Bohrung 48 bzw. 49 fixiert. An dem von dem Mitnehmerkopf 32 abgewandten Ende des Stellhebels 31 ist in einer Bohrung der Mitnahmestift 38 angeordnet. In dem Regelkolben 6 ist ebenfalls in einer Bohrung der Anlagestift 39 angeordnet. Der Mitnahmestift 38 und der Anlagestift 39 sind mit einer Preßpassung in ihren Bohrungen fixiert. Wie bereits beschrieben, wirkt der Mitnahmestift 38 auf den zweiten Schenkel 36, der Anlagestift 39 dagegen auf den ersten Schenkel 35, der in der Fig. 4 aufgrund der Lage der Schnittlinie nur im Bereich des Lagerbolzens 34 dargestellt ist. Wie in der Fig. 4 durch die Darstellung des ersten Schenkels 35 und des zweiten Schenkels 36 im Bereich des Lagerbolzens 34 zu erkennen, sind die Schenkel 35 und 36 im Bereich der Lagerung auf dem Lagerbolzen 34 in axialer Richtung abgeflacht.In Fig. 4 is a partial section along the line AA the Fig. 1 shown. The adjusting lever 31, the leg 35 and the second leg 36 are rotatably mounted on a common bearing pin 34. The bearing pin 34 is designed in multiple stages, and fixed in the housing 7 in a first and a second bore 48 and 49, respectively. At the end remote from the driver head 32 of the actuating lever 31, the driving pin 38 is arranged in a bore. In the control piston 6, the investment pin 39 is also arranged in a bore. The driving pin 38 and the contact pin 39 are fixed with a press fit in their holes. As already described, the driving pin 38 acts on the second leg 36, the contact pin 39, however, on the first leg 35, which in the Fig. 4 is shown only in the region of the bearing pin 34 due to the position of the cutting line. Like in the Fig. 4 by the representation of the first leg 35 and the second leg 36 in the region of the bearing pin 34 recognize the legs 35 and 36 are flattened in the storage area on the bearing pin 34 in the axial direction.

In Fig. 5 ist eine vergrößerte Ansicht im Ausschnitt V der Fig. 1 dargestellt. Der Ausschnitt zeigt einen Teil des ersten Schenkels 35 sowie des Regelkolbens 6 mit dem darin angeordneten Anlagestift 39. Im Bereich des Anlagestifts 39 weist der erste Schenkel 35 eine Abflachung 50 auf. Die Abflachung 50 ist dabei so orientiert, daß die Längsachse des Regelkolbens 6 mit der abgeflachten Stelle 50 einen rechten Winkel einschließt. Damit wird verhindert, daß die Einleitung der Rückführungskraft auf den Regelkolben 6 von dessen Mittelachse und damit seiner Bewegungsrichtung abweicht. Die dargestellte rechtwinklige Anordnung zwischen der abgeflachten Stelle 50 und der Achse des Regelkolbens 6 gilt exakt nur in der Ruheposition der Verstellvorrichtung 1, in der der Regelkolben in seiner Neutralstellung ist und der Stellkolben 2 sich in seiner ersten Endposition befindet. Die Verstellwege des Regelkolbens 6 sind jedoch klein, so daß näherungsweise der rechte Winkel erhalten bleibt.In Fig. 5 is an enlarged view in the section V of Fig. 1 shown. The section shows a part of the first leg 35 and of the control piston 6 with the abutment pin 39 arranged therein. In the area of the abutment pin 39, the first leg 35 has a flattening 50. The flattening 50 is oriented so that the longitudinal axis of the control piston 6 with the flattened point 50 encloses a right angle. This prevents that the introduction of the return force to the control piston 6 deviates from the central axis and thus its direction of movement. The illustrated right-angled arrangement between the flattened point 50 and the axis of the control piston 6 applies exactly only in the rest position of the adjusting device 1, in which the control piston is in its neutral position and the actuating piston 2 is in its first end position. The adjustment of the control piston 6, however, are small, so that approximately the right angle is maintained.

Alternativ kann die Rückführungskraft in der dann mittigen Ruheposition der Verstellvorrichtung 1 auch ungleich Null sein, selbst wenn der Speisedruck psp gleich Null ist. Die mittige Ruheposition wird dann durch zwei auf jeweils einer Seite des Regelkolbens 2 angeordnete Druckfedern 40 wie bei der DE 195 40 654 C1 gewährleistet. Dabei befindet sich in der mittigen Ruheposition der Regelkolben 6 dann nicht in seiner Neutralstellung, wenn von dem Proportionalmagneten 28 oder durch den Steuerdruck psteuer keine Steuerkraft auf den Regelkolben 6 übertragen wird.Alternatively, the return force in the then central rest position of the adjusting device 1 also be non-zero, even if the feed pressure p sp is equal to zero. The central rest position is then by two arranged on each side of the control piston 2 compression springs 40 as in the DE 195 40 654 C1 guaranteed. In this case, the control piston 6 will not located in the central rest position to its neutral position when no control power is transmitted to the regulating piston 6 from the proportional solenoid 28 or by the control pressure p tax.

Claims (14)

  1. Adjusting device for hydrostatic piston machines having a setting piston (2), which is movable between two end positions and which can be subjected to setting pressures acting oppositely on it, and a setting pressure regulating valve (5), by which the setting pressures can be regulated, the setting pressure regulating valve (5) having a regulating piston (6), which can be displaced from a neutral position and is subjected to a return force dependent on the position of the setting piston (2) and directed opposite a control force acting on the regulating piston (6), the return force being zero in a rest position of the adjusting device (1),
    characterised
    in that in the rest position the regulating piston (6) is in its neutral position and the setting piston (2) is in a given end position.
  2. Adjusting device according to Claim 1,
    characterised
    in that the regulating piston (6) can be subjected to a control force on one side.
  3. Adjusting device for hydrostatic piston machines having a setting piston (2), which is movable between two end positions and which can be subjected to setting pressures acting oppositely on it, and a setting pressure regulating valve (5), by which the setting pressures can be regulated, the setting pressure regulating valve (5) having a regulating piston (6), which can be displaced from a neutral position and is subjected to a return force dependent on the position of the setting piston (2) and directed opposite a control force acting on the regulating piston (6), the return force being non-zero in a central rest position of the adjusting device (1),
    characterised
    in that in the central rest position the regulating piston (6) is not in its neutral position if there is no control force transmitted to the regulating piston (6).
  4. Adjusting device according to Claim 2 or 3,
    characterised
    in that a proportional magnet (28) is provided to produce the control force.
  5. Adjusting device according to Claim 3,
    characterised
    in that an end face (30) of the regulating piston (6) can be subjected to a control pressure (pcontrol) to produce the control force.
  6. Adjusting device according to one of Claims 1 to 5,
    characterised
    in that the return force can be transmitted to the regulating piston (6) by a first leg (35) via a bearing pin (39).
  7. Adjusting device according to Claim 6,
    characterised
    in that the return force is proportional to the tension of a spring (37, 42) arranged between the first leg (35) and a second leg (36) operatively connected to the first leg (35) via the spring (37, 42).
  8. Adjusting device according to Claim 7,
    characterised
    in that the second leg (36) is displaceable relative to the first leg (35) and the displacement is dependent on the position of the setting piston (2).
  9. Adjusting device according to Claim 8,
    characterised
    in that the second leg (36) is displaceable by a driving pin (38) arranged on a setting lever (31), and the setting lever (31) is coupled to the setting piston (2) for feedback of the position.
  10. Adjusting device according to Claim 9,
    characterised
    in that the first leg (35), the second leg (36) and the setting lever (31) have a common pivot (34).
  11. Adjusting device according to one of Claims 7 to 10,
    characterised
    in that the spring arranged between the first and the second leg (35, 36) is a tension spring (37).
  12. Adjusting device according to one of Claims 7 to 10,
    characterised
    in that the spring arranged between the first and the second leg (35, 36) is a compression spring (42) supported on two spring bearings (43, 44), in each case one spring bearing (43, 44) being connected to the first and the second leg (35, 36), respectively, and
    in that, on displacement of the second leg (36) relative to the first leg (35), the compression spring (42) counteracts the displacement.
  13. Adjusting device according to one of Claims 6 to 12,
    characterised
    in that the first leg (35) has a bearing surface (50) for the bearing pin (39), the surface normal of which bearing surface is oriented parallel to the direction of movement of the bearing pin (39) in the rest position of the adjusting device (1).
  14. Adjusting device according to one of Claims 1 to 13,
    characterised
    in that the regulating piston (2) has, for each setting pressure chamber (3, 4), a regulating piston section (17, 18) with in each case two control edges (19, 23, 20, 24), via which the respective setting pressure chamber (3, 4) can be connected to a feed pressure source or a tank volume (25).
EP03727295A 2002-05-10 2003-04-11 Regulating device for hydrostatic piston machines Expired - Lifetime EP1504191B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10220889 2002-05-10
DE10220889A DE10220889C5 (en) 2002-05-10 2002-05-10 Adjustment device for hydrostatic piston machines
PCT/EP2003/003793 WO2003095831A1 (en) 2002-05-10 2003-04-11 Regulating device for hydrostatic piston machines

Publications (2)

Publication Number Publication Date
EP1504191A1 EP1504191A1 (en) 2005-02-09
EP1504191B1 true EP1504191B1 (en) 2009-06-24

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Country Status (4)

Country Link
US (1) US7171887B2 (en)
EP (1) EP1504191B1 (en)
DE (2) DE10220889C5 (en)
WO (1) WO2003095831A1 (en)

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DE10220889C5 (en) 2009-05-28
US20050252369A1 (en) 2005-11-17
WO2003095831A9 (en) 2004-10-21
EP1504191A1 (en) 2005-02-09
DE10220889B3 (en) 2004-02-12
US7171887B2 (en) 2007-02-06
DE50311633D1 (en) 2009-08-06
WO2003095831A1 (en) 2003-11-20

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