EP0402871A2 - Control device for variable displacement pump - Google Patents

Control device for variable displacement pump Download PDF

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Publication number
EP0402871A2
EP0402871A2 EP90111124A EP90111124A EP0402871A2 EP 0402871 A2 EP0402871 A2 EP 0402871A2 EP 90111124 A EP90111124 A EP 90111124A EP 90111124 A EP90111124 A EP 90111124A EP 0402871 A2 EP0402871 A2 EP 0402871A2
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EP
European Patent Office
Prior art keywords
bearing
cradle
axial piston
piston machine
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP90111124A
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German (de)
French (fr)
Other versions
EP0402871B1 (en
EP0402871A3 (en
Inventor
Werner Dipl.-Ing. Hörmann
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Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Hydromatik GmbH
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Application filed by Brueninghaus Hydromatik GmbH, Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0402871A2 publication Critical patent/EP0402871A2/en
Publication of EP0402871A3 publication Critical patent/EP0402871A3/en
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Publication of EP0402871B1 publication Critical patent/EP0402871B1/en
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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
    • 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 control device according to the preamble of claim 1.
  • Such a control device with a control valve, in which a power regulator and a pressure regulator are integrated, is known, for example, from DE-OS 19 11 695 and described below with reference to the exemplary basic circuit shown in FIG. 1, the power and pressure regulators being simplified Representation are drawn separately from each other.
  • the control device generally designated 1, comprises a control valve 10 with a power controller 2 and a pressure controller 3 superimposed by the latter, both of which control the hydraulic loading of an adjusting cylinder 4, which is part of an adjusting device 5 for a pump 6 used in an open circuit.
  • the pump 6 driven by a drive shaft 7 sucks through a suction line 8 from a tank 9 and delivers into a working line 11.
  • a leak line 12 leading from the pump 6 to the tank 9 is shown with broken lines.
  • the power valve 13 of the power regulator 2 and the pressure limiting valve 14 of the pressure regulator 3 are arranged in a parallel arrangement in a line connecting the working line 11 to the adjusting cylinder 4.
  • the working spaces 16, 21 present on both sides of the piston 15 of the adjusting cylinder 4 can be acted upon.
  • the piston annulus 16 is connected to the working line 11 by a hydraulic line 17. Extends from the piston annulus 16 Line section 18 to the power valve 13.
  • the line extension 19 which follows behind the power valve 13 extends to the piston chamber 21 of the adjusting cylinder 4.
  • a branch line 23 leading to the tank 9 branches off from the line extension 19 and contains a throttle 24, the function of which is still described becomes.
  • the pressure limiting valve 14 is located in a parallel line 25 branching off from the line section 18.
  • the valve slide 26 of the pressure limiting valve 14 can be acted upon by the working pressure through a line section 27 and is adjustable against a spring 28 of variable spring force.
  • the line section 27 branches off from the parallel line 25 or the line section 18
  • the valve slide 29 of the power valve 13 is adjustable depending on the delivery rate setting of the pump 6 and depending on the working pressure against springs 31 and 31.1, possibly variable spring force.
  • an angle lever 32 mounted at its apex, one lever arm adjusts the valve slide 29 and the other lever arm is adjusted by a hydraulic piston 33, which is displaceably mounted in the transverse arrangement in the piston rod 34 of the adjusting cylinder 4 and by a connecting line 35 extending in the piston rod 34 from the piston ring space 16 to the piston 33 can be acted upon by the working pressure.
  • control device 1 The function of the control device 1 is as follows. The arrangement shown shows the depressurized state. If a consumer in the working line 11 causes an increasing working pressure A, the valve spool 29 of the power valve 13 is displaced to the left by the piston 33 and the angle lever 32 in FIG. 1, the valve spool 29 at the first passage denoted by 41 a control pressure R im Line extension 19 adjusts with increasing Working pressure A increases and displaces the piston 15 for the purpose of reducing the setting of the delivery volume of the pump 6, in the present exemplary embodiment pushes out.
  • the pressure regulator 3 comes into operation, which adjusts a control pressure R 1 at the second passage designated 42 in the pressure relief valve 14, which adjusts itself in a line section 36 connecting the pressure relief valve 14 to the power valve 13 and over reproduces a third passage 43 in the power valve 13 in the line extension 19 and thus in the piston chamber 21 and adjusts the pump 6 so that the working pressure A does not increase any further.
  • the piston 15 is pushed back, here pushed in, the amount of liquid displaced from the piston chamber 21 through the second passage 43 and a fourth passage 45 in the pressure limiting valve 14 connecting the line section 36 to a drain line 44 leading to the tank 9 can flow to the tank 9.
  • the power valve 13 and the pressure relief valve 14 are each formed by a 3/2-way proportional valve.
  • the invention has for its object to design a control device of the type mentioned in such a way that the flow loss required for dynamic stability can be reduced.
  • the throttled drain line ensuring the dynamic stability of the pressure regulator is controlled as a function of the function of the pressure regulator, wherein it is opened or comes into operation when the pressure regulator responds.
  • the leakage flow is thus limited to the control range of the pressure regulator, whereby a significant increase in performance is achieved because in the control range of the power regulator, the throttled drain line is inoperative and thus the power loss caused by the loss flow is eliminated.
  • the control device uses a throttled drain line arranged in its control valve 51, which is designed in the form of a bypass 92, 89, 93 with a throttle 47.
  • the throttled bypass 92, 89, 93 of the control valve 51 according to the invention is in the latter Capacity control area closed and only functional in its pressure control area.
  • the control valve 51 comprises a valve spool 52 and a control spool 73.
  • the former corresponds to the valve spool 29 and the latter to the valve spool 26 of the known control valve 10.
  • the valve spool 52 is sleeve-shaped and is axially displaceably mounted in a housing wall 53 of the pump housing 54 and is accessible from the outside in the narrower section 55 of a stepped bore 56, the larger step of which is designated 57 and has an internal thread, into which a closure cap 58 is screwed with an adjusting device 59 for the basic adjustment of the control valve 51.
  • the narrower section 55 of the stepped bore 56 cuts 53 channels in the housing wall, of which the channel labeled 61 corresponds to the line 18 according to FIG. 1 and thus contains the working pressure A.
  • the middle channel 62 corresponds to the line 19 in FIG. 1, which contains the regulating pressure R with which the piston chamber 21 of the adjusting cylinder 4 is acted upon.
  • the channel 63 arranged to the right of the channel 62 in FIGS. 2 and 3 corresponds to the drain line 44 leading to the tank according to FIG. 1.
  • the channel 61 is connected to a circumferential groove 65 on the valve slide 52, the right boundary edge of which forms a control edge 66 which interacts with a counter-control edge 67 formed by the wall of the channel 62.
  • the control edge 66 is at the same time the left boundary edge of a circumferential web 68 formed on the valve slide 52, the right boundary edge of which forms a further control edge 69 which is the left shoulder of a second initial groove 71 of the valve slide 52, which is connected to the channel 63.
  • the control edges 66, 69 interact with the mutually opposite circumferential sections 67 of the channel 62.
  • the valve spool 52 has an axial guide bore 72 in which the control spool 73 is axially displaceably mounted.
  • the control slide 73 has an axial blind bore from which a pressure pin 74 protrudes and is connected to the one lever arm 75 of the angle lever 76, which is pivotably mounted about an axis of rotation 77 extending transversely to the valve slide 52 .
  • the other rebel arm 78 of the angle lever 76 is acted upon by an adjustable compression spring 79 against an actuator in the form of a hydraulic piston 81, which corresponds to the piston 33 according to FIG.
  • the circumferential groove 65 is connected by a radial channel 82 to a circumferential groove 84 in the control slide 73, which is delimited on its right side by an annular shoulder 85 of the control slide 73.
  • a hydraulic working chamber 86 which is delimited on the right side by a guide section 87 which guides a narrowed guide part 88 of the control slide 73 in a sliding guide.
  • a circumferential groove 89 is formed, the left shoulder of which forms a control edge 91 which can close or open one or more ring and / or radial channels 92 in the valve slide 52 in the region of the circumferential web 68, in which throttles can be arranged, and which communicate with the circumferential groove 89 in the open position.
  • the radial channel 93 with the throttle 47 is arranged, which connects the circumferential groove 71 with the circumferential groove 89 of the valve slide 52.
  • the annular shoulder 85 is a circumferential groove 84 with the Throttle point 80 connecting working chamber 86 is provided, which is formed here by a flattening.
  • a delivery rate control is implemented in which the control or regulating pressure R is increased as the working pressure A increases.
  • the size of the working surface of the working annular chamber 86 is dimensioned or matched to the existing arrangement so that in the power control range of the control valve 51 the angle lever 76 and the set force of the compression spring 79 are the hydraulic thrust force which moves the control slide 73 relative to the valve slide 52 to the left tries to push, press over, so that the control slide 73 assumes the right end position or rest position shown in FIG. 2, in which the control slide 73 rests against the bottom 72.1 of the guide bore 72.
  • the control slide 73 presses the angle lever 76, the control slide 73 being displaced relative to the valve slide 52 to the left into the control position shown in FIG. 3, in which the control edge 91 the radial channels 92 opens at least partially and the bypass 46 formed by the radial channels 92, the circumferential groove 89 and the radial channel 93 and the throttle 47 is opened and thus a small amount of the hydraulic medium can flow away, whereby the desired dynamic stability of the control valve 51 is achieved.
  • the adjusting device 59 and also an adjusting device, generally designated 94, for the force of the compression spring 79 is designed in a manner known per se with adjusting screws which act against spring plates and adjust different spring forces by longitudinal adjustment.

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

Abstract

The invention relates to a control device for an adjustable pump (6), with a hydraulic adjusting device (5) having an adjusting cylinder (4) and with a regulating valve (51), incorporating an output regulator (52) for adjusting the delivery and a pressure regulator (73) for limiting the working pressure (A) to a specific upper limit, a restricted outlet pipe which leads to the return (9) branching off with the pipe (19, 62) acting hydraulically on the adjusting cylinder (4). It is the object of the invention to reduce the flow loss necessary for dynamic stability. This is achieved in that the flow passing through the restricted outlet pipe (92, 89, 93, 47) is opened as the pressure regulator (73) increasingly responds. <IMAGE>

Description

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

Eine derartige Regeleinrichtung mit einem Regelventil, in dem ein Leistungsregler und ein Druckregler integriert sind, ist beispielsweise aus der DE-OS 19 11 695 bekannt und nachstehend anhand der in Fig. 1 dargestellten exemplarischen Prinzipschaltung beschrieben, wobei der Leistungs- und der Druckregler der vereinfachten Darstellung wegen getrennt voneinander gezeichnet sind.Such a control device with a control valve, in which a power regulator and a pressure regulator are integrated, is known, for example, from DE-OS 19 11 695 and described below with reference to the exemplary basic circuit shown in FIG. 1, the power and pressure regulators being simplified Representation are drawn separately from each other.

Die allgemein mit 1 bezeichnete Regeleinrichtung umfaßt ein Regelventil 10 mit einem Leistungsregler 2 und einem von letzterem überlagerten Druckregler 3, die beide die hydraulische Beaufschlagung eines Verstellzylinders 4 regeln, der Teil einer Verstelleinrichtung 5 für eine im offenen Kreislauf eingesetzte Pumpe 6 ist. Die durch eine Antriebswelle 7 angetriebene Pumpe 6 saugt durch eine Saugleitung 8 aus einem Tank 9 und fördert in eine Arbeitsleitung 11. Mit gestrichelten Linien ist eine von der Pumpe 6 zum Tank 9 führende Leckleitung 12 dargestellt.The control device, generally designated 1, comprises a control valve 10 with a power controller 2 and a pressure controller 3 superimposed by the latter, both of which control the hydraulic loading of an adjusting cylinder 4, which is part of an adjusting device 5 for a pump 6 used in an open circuit. The pump 6 driven by a drive shaft 7 sucks through a suction line 8 from a tank 9 and delivers into a working line 11. A leak line 12 leading from the pump 6 to the tank 9 is shown with broken lines.

Das Leistungsventil 13 des Leistungsreglers 2 und das Druckbegrenzungsventil 14 des Druckreglers 3 sind in Parallelanordnung in einer die Arbeitsleitung 11 mit dem Verstellzylinder 4 verbindenden Leitung angeordnet. Beim vorliegenden Ausführungsbeispiel sind die beidseitig des Kolbens 15 des Verstellzylinders 4 vorhandenen Arbeitsräume 16,21 beaufschlagbar. Der Kolbenringraum 16 ist durch eine hydraulische Leitung 17 mit der Arbeitsleitung 11 verbunden. Vom Kolbenringraum 16 erstreckt sich ein Leitungsabschnitt 18 bis zum Leistungsventil 13. Der sich hinter dem Leistungsventil 13 anschließende Leitungsfortsatz 19 erstreckt sich zum Kolbenraum 21 des Verstellzylinder 4. Vom Leitungsfortsatz 19 zweigt eine zum Tank 9 führende Ablaufleitung 23 ab, in der eine Drossel 24 angeordnet ist, deren Funktion noch beschrieben wird. Das Druckbegrenzungsventil 14 befindet sich in einer vom Leitungsabschnitt 18 abzweigenden Parallelleitung 25. Der Ventilschieber 26 des Druckbegrenzungsventils 14 ist durch einen Leitungsabschnitt 27 mit dem Arbeitsdruck beaufschlagbar und gegen eine Feder 28 veränderlicher Federkraft verstellbar. Der Leitungsabschnitt 27 zweigt von der Parallelleitung 25 oder dem Leitungsabschnitt 18 ab und weist eine Drossel 20 auf.The power valve 13 of the power regulator 2 and the pressure limiting valve 14 of the pressure regulator 3 are arranged in a parallel arrangement in a line connecting the working line 11 to the adjusting cylinder 4. In the present exemplary embodiment, the working spaces 16, 21 present on both sides of the piston 15 of the adjusting cylinder 4 can be acted upon. The piston annulus 16 is connected to the working line 11 by a hydraulic line 17. Extends from the piston annulus 16 Line section 18 to the power valve 13. The line extension 19 which follows behind the power valve 13 extends to the piston chamber 21 of the adjusting cylinder 4. A branch line 23 leading to the tank 9 branches off from the line extension 19 and contains a throttle 24, the function of which is still described becomes. The pressure limiting valve 14 is located in a parallel line 25 branching off from the line section 18. The valve slide 26 of the pressure limiting valve 14 can be acted upon by the working pressure through a line section 27 and is adjustable against a spring 28 of variable spring force. The line section 27 branches off from the parallel line 25 or the line section 18 and has a throttle 20.

Der Ventilschieber 29 des Leistungsventils 13 wird in Abhängigkeit von der Fördermengeneinstellung der Pumpe 6 und in Abhängigkeit vom Arbeitsdruck gegen Federn 31 und 31.1 gegebenenfalls veränderlicher Federkraft verstellbar. Hierzu dient in an sich bekannter Weise ein an seinem Scheitel gelagerter Winkelhebel 32, dessen einer Hebelarm den Ventilschieber 29 verstellt und dessen anderer Hebelarm von einem hydraulischen Kolben 33 verstellt wird, der in Queranordnung in der Kolbenstange 34 des Verstellzylinders 4 verschiebbar gelagert ist und durch eine sich in der Kolbenstange 34 vom Kolbenringraum 16 zum Kolben 33 erstreckende Verbindungsleitung 35 mit dem Arbeitsdruck beaufschlagbar ist.The valve slide 29 of the power valve 13 is adjustable depending on the delivery rate setting of the pump 6 and depending on the working pressure against springs 31 and 31.1, possibly variable spring force. For this purpose, in a manner known per se, an angle lever 32 mounted at its apex, one lever arm adjusts the valve slide 29 and the other lever arm is adjusted by a hydraulic piston 33, which is displaceably mounted in the transverse arrangement in the piston rod 34 of the adjusting cylinder 4 and by a connecting line 35 extending in the piston rod 34 from the piston ring space 16 to the piston 33 can be acted upon by the working pressure.

Die Funktion der Regeleinrichtung 1 ist folgende. Die dargestellte Anordnung zeigt den drucklosen Zustand. Wenn ein Verbraucher in der Arbeitsleitung 11 einen ansteigenden Arbeitsdruck A verursacht, wird der Ventilschieber 29 des Leistungsventils 13 durch den Kolben 33 und den Winkelhebel 32 in Fig. 1 nach links verschoben, wobei der Ventilschieber 29 am mit 41 bezeichneten ersten Durchgang einen Regeldruck R im Leitungsfortsatz 19 einstellt, der mit zunehmendem Arbeitsdruck A zunimmt und den Kolben 15 zwecks verringerter Einstellung des Fördervolumens der Pumpe 6 verschiebt, beim vorliegenden Ausführungsbeispiel ausschiebt.The function of the control device 1 is as follows. The arrangement shown shows the depressurized state. If a consumer in the working line 11 causes an increasing working pressure A, the valve spool 29 of the power valve 13 is displaced to the left by the piston 33 and the angle lever 32 in FIG. 1, the valve spool 29 at the first passage denoted by 41 a control pressure R im Line extension 19 adjusts with increasing Working pressure A increases and displaces the piston 15 for the purpose of reducing the setting of the delivery volume of the pump 6, in the present exemplary embodiment pushes out.

Wenn der Arbeitsdruck A einen vorbestimmten maximalen Wert erreicht, tritt der Druckregler 3 in Funktion, der am mit 42 bezeichneten zweiten Durchgang im Druckbegrenzungsventil 14 einen Regeldruck R₁ einstellt, der sich in einem das Druckbegrenzungsventil 14 mit dem Leistungsventil 13 verbindenen Leitungsabschnitt 36 einstellt und sich über einen dritten Durchgang 43 im Leistungsventil 13 in den Leitungsfortsatz 19 und somit in den Kolbenraum 21 fortpflanzt und die Pumpe 6 so verstellt, daß der Arbeitsdruck A nicht weiter ansteigt. Wenn der Arbeitsdruck A im Regelbereich sinkt, wird der Kolben 15 zurückgeschoben, hier eingeschoben, wobei die aus dem Kolbenraum 21 verdrängte Flüssigkeitsmenge durch den zweiten Durchgang 43 und einen den Leitungsabschnitt 36 mit einer zum Tank 9 führenden Ablaufleitung 44 verbindenen vierten Durchgang 45 im Druckbegrenzungsventil 14 zum Tank 9 abfließen kann.When the working pressure A reaches a predetermined maximum value, the pressure regulator 3 comes into operation, which adjusts a control pressure R 1 at the second passage designated 42 in the pressure relief valve 14, which adjusts itself in a line section 36 connecting the pressure relief valve 14 to the power valve 13 and over reproduces a third passage 43 in the power valve 13 in the line extension 19 and thus in the piston chamber 21 and adjusts the pump 6 so that the working pressure A does not increase any further. When the working pressure A falls in the control range, the piston 15 is pushed back, here pushed in, the amount of liquid displaced from the piston chamber 21 through the second passage 43 and a fourth passage 45 in the pressure limiting valve 14 connecting the line section 36 to a drain line 44 leading to the tank 9 can flow to the tank 9.

Das Leistungsventil 13 und das Druckbegrenzungsventil 14 sind jeweils durch ein 3/2-Proportionalwegeventil gebildet.The power valve 13 and the pressure relief valve 14 are each formed by a 3/2-way proportional valve.

Es ist der Zweck der mittels der Drossel 24 gedrosselten Ablaufleitung 23, eine geringe Strömung und somit die dynamische Stabilität des Druckreglers 3 zu gewährleisten. Diesem Vorteil steht jedoch ein Leistungsverlust aufgrund der Verlustströmung an der Drossel 24 entgegen. Dieser Strömungs- bzw. Leistungsverlust ist beträchtlich, da er im gesamten Regelbereich der Regeleinrichtung 1 stattfindet.The purpose of the outlet line 23 throttled by means of the throttle 24 is to ensure a low flow and thus the dynamic stability of the pressure regulator 3. However, this advantage is countered by a loss of power due to the loss of flow at the throttle 24. This flow or power loss is considerable since it takes place in the entire control range of the control device 1.

Der Erfindung liegt die Aufgabe zugrunde, eine Regeleinrichtung der eingangs bezeichneten Art so auszugestalten, daß der für eine dynamische Stabilität erforderliche Strömungsverlust verringert werden kann.The invention has for its object to design a control device of the type mentioned in such a way that the flow loss required for dynamic stability can be reduced.

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 ist die die dynamische Stabilität des Druckreglers gewährleistende gedrosselte Ablaufleitung in Abhängigkeit von der Funktion des Druckreglers gesteuert, wobei sie geöffnet wird oder in Funktion tritt, wenn der Druckregler anspricht. Die Verlustströmung ist somit auf den Regelbereich des Druckreglers begrenzt, wodurch eine erhebliche Leistungssteigerung erzielt wird, weil im Regelbereich des Leistungsreglers die gedrosselte Ablauf leitung außer Funktion ist und somit der durch die Verlustströmung hervorgerufene Leistungsverlust entfällt.In the embodiment according to the invention, the throttled drain line ensuring the dynamic stability of the pressure regulator is controlled as a function of the function of the pressure regulator, wherein it is opened or comes into operation when the pressure regulator responds. The leakage flow is thus limited to the control range of the pressure regulator, whereby a significant increase in performance is achieved because in the control range of the power regulator, the throttled drain line is inoperative and thus the power loss caused by the loss flow is eliminated.

Nachfolgend ist die Erfindung anhand eines in der Zeichnung dargestellten bevorzugten Ausführungsbeispiels näher erläutert. Es zeigen

  • Fig. 2 einen Längsschnitt des Regelventils des Ausführungsbeispiels der erfindungsgemäßen Regeleinrichtung in der Funktionsstellung Leistungsregelung und
  • Fig. 3 einen Längsschnitt des Regelventils nach Fig. 2 in der Funktionsstellung Druckregelung.
The invention is explained in more detail below on the basis of a preferred exemplary embodiment shown in the drawing. Show it
  • Fig. 2 shows a longitudinal section of the control valve of the embodiment of the control device according to the invention in the power control function position and
  • Fig. 3 shows a longitudinal section of the control valve of FIG. 2 in the pressure control functional position.

Statt der dem Regelventil 10 der bekannten Regeleinrichtung nachgeschalteten gedrosselten Ablaufleitung 23 verwendet die erfindungsgemäße Regeleinrichtung eine in ihrem Regelventil 51 angeordnete gedrosselte Ablaufleitung, die in Form eines Beipasses 92,89,93 mit einer Drossel 47 ausgebildet ist. Im Gegensatz zu der im gesamten Funktionsbereich des bekannten Regelventils in Funktion befindlichen Ablaufleitung 23 ist der gedrosselte Beipass 92,89,93 des erfindungsgemäßen Regelventils 51 in dessen Leistungsregelungsbereich geschlossen und lediglich in dessen Druckregelungsbereich funktionsfähig.Instead of the throttled drain line 23 downstream of the control valve 10 of the known control device, the control device according to the invention uses a throttled drain line arranged in its control valve 51, which is designed in the form of a bypass 92, 89, 93 with a throttle 47. In contrast to the drain line 23, which is in operation in the entire functional range of the known control valve, the throttled bypass 92, 89, 93 of the control valve 51 according to the invention is in the latter Capacity control area closed and only functional in its pressure control area.

Das Regelventil 51 umfaßt einen Ventilschieber 52 und einen Steuerschieber 73. Ersterer entspricht dem Ventilschieber 29 und letzterer dem Ventilschieber 26 des bekannten Regelventils 10. Der Ventilschieber 52 ist hülsenförmig ausgebildet und axial verschiebbar in einer Gehäusewand 53 des Pumpengehäuses 54 gelagert ist und zwar von außen zugänglich in dem engeren Abschnitt 55 einer Stufenbohrung 56, deren größere Stufe mit 57 bezeichnet ist und ein Innengewinde aufweist, in das eine Verschlußkappe 58 mit einer Einstellvorrichtung 59 für die Basis-Einstellung des Regelventils 51 eingeschraubt ist.The control valve 51 comprises a valve spool 52 and a control spool 73. The former corresponds to the valve spool 29 and the latter to the valve spool 26 of the known control valve 10. The valve spool 52 is sleeve-shaped and is axially displaceably mounted in a housing wall 53 of the pump housing 54 and is accessible from the outside in the narrower section 55 of a stepped bore 56, the larger step of which is designated 57 and has an internal thread, into which a closure cap 58 is screwed with an adjusting device 59 for the basic adjustment of the control valve 51.

Der engere Abschnitt 55 der Stufenbohrung 56 schneidet in der Gehäusewand 53 Kanäle, von denen der mit 61 bezeichnete Kanal der Leitung 18 gemäß Fig. 1 entspricht und somit den Arbeitsdruck A enthält. Der mittlere Kanal 62 entspricht der Leitung 19 in Fig. 1, die den Regeldruck R enthält, mit dem der Kolbenraum 21 des Verstellzylinders 4 beaufschlagt ist. Der in Fig. 2 und 3 rechts vom Kanal 62 angeordnete Kanal 63 entspricht der zum Tank führenden Ablaufleitung 44 gemäß Fig. 1. Außerdem ist noch ein Kanal 64 rechts von den vorgenannten Kanälen vorhanden, der im wesentlichen drucklos ist und ebenfalls zum Tank führt. Der Kanal 61 steht in Verbindung mit einer Umfangsnut 65 am Ventilschieber 52, deren rechte Begrenzungskante eine Steuerkante 66 bildet, die mit einer durch die Wandung des Kanals 62 gebildete Gegensteuerkante 67 zusammenwirkt. Die Steuerkante 66 ist zugleich linke Begrenzungskante eines am Ventilschieber 52 ausgebildeten Umfangssteges 68, dessen rechte Begrenzungskante eine weitere Steuerkante 69 bildet, die die linke Schulter einer zweiten amfangsnut 71 des Ventilschiebers 52 ist, die mit dem Kanal 63 in Verbindung steht. Die Steuerkanten 66, 69 wirken mit den einander gegenüberliegenden Umfangsabschnitten 67 des Kanals 62 zusammen.The narrower section 55 of the stepped bore 56 cuts 53 channels in the housing wall, of which the channel labeled 61 corresponds to the line 18 according to FIG. 1 and thus contains the working pressure A. The middle channel 62 corresponds to the line 19 in FIG. 1, which contains the regulating pressure R with which the piston chamber 21 of the adjusting cylinder 4 is acted upon. The channel 63 arranged to the right of the channel 62 in FIGS. 2 and 3 corresponds to the drain line 44 leading to the tank according to FIG. 1. In addition, there is also a channel 64 to the right of the aforementioned channels, which is essentially depressurized and also leads to the tank. The channel 61 is connected to a circumferential groove 65 on the valve slide 52, the right boundary edge of which forms a control edge 66 which interacts with a counter-control edge 67 formed by the wall of the channel 62. The control edge 66 is at the same time the left boundary edge of a circumferential web 68 formed on the valve slide 52, the right boundary edge of which forms a further control edge 69 which is the left shoulder of a second initial groove 71 of the valve slide 52, which is connected to the channel 63. The control edges 66, 69 interact with the mutually opposite circumferential sections 67 of the channel 62.

Der Ventilschieber 52 weist eine axiale Führungsbohrung 72 auf, in der der Steuerschieber 73 axial verschiebbar gelagert ist. An seinem in Fig. 2 und 3 linken Ende weist der Steuerschieber 73 eine axiale Sackbohrung aufs aus der ein Druckstift 74 herausragt und mit dem einem Hebelarm 75 des Winkelhebels 76 in Verbindung steht, der um eine quer zum Ventilschieber 52 verlaufende Drehachse 77 schwenkbar gelagert ist. Der andere Rebelarm 78 des Winkelhebels 76 wird durch eine einstellbare Druckfeder 79 gegen ein Stellglied in Form eines hydraulischen Kolbens 81 beaufschlagt, der dem Kolben 33 gemäß Fig. 1 entspricht und in der Kolbenstange 34 des Verstellzylinders 4 quer verschiebbar gelagert ist, so daß sich sein Abstand a bezüglich der Drehachse 77 mit steigendem Arbeitsdruck verringert und mit fallendem Arbeitsdruck vergrößert. Die Funktion einer solchen Leistungsregeleinrichtung ist an sich bekannt, so daß es keiner Beschreibung im einzelnen bedarf.The valve spool 52 has an axial guide bore 72 in which the control spool 73 is axially displaceably mounted. At its left end in FIGS. 2 and 3, the control slide 73 has an axial blind bore from which a pressure pin 74 protrudes and is connected to the one lever arm 75 of the angle lever 76, which is pivotably mounted about an axis of rotation 77 extending transversely to the valve slide 52 . The other rebel arm 78 of the angle lever 76 is acted upon by an adjustable compression spring 79 against an actuator in the form of a hydraulic piston 81, which corresponds to the piston 33 according to FIG. 1 and is mounted in the piston rod 34 of the adjusting cylinder 4 so that it can be displaced transversely Distance a with respect to the axis of rotation 77 is reduced with increasing working pressure and increased with falling working pressure. The function of such a power control device is known per se, so that no detailed description is required.

Die Umfangsnut 65 steht durch einen Radialkanal 82 mit einer Umfangsnut 84 im Steuerschieber 73 in Verbindung, die an ihrer rechten Seite durch einen Ringansatz 85 des Steuerschiebers 73 begrenzt ist. Rechts vom Ringansatz 85 befindet sich eine hydraulische Arbeitskammer 86, die rechtsseitig durch einen Führungsabschnitt 87 begrenzt ist, der einen verengten Führungsteil 88 des Steuerschiebers 73 in einer Gleitführung führt. Im Führungsteil 88 ist eine Umfangsnut 89 ausgebildet, deren linke Schulter eine Steuerkante 91 bildet, die einen oder mehrere Ring- und/oder Radialkanäle 92 im Ventilschieber 52 im Bereich des Umfangssteges 68 durch Schließen oder zu öffnen vermag, in denen Drosseln angeordnet sein können, und die in der geöffneten Stellung mit der Umfangsnut 89 in Verbindung stehen. Im Ventilschieber 52 ist rechts neben den Radialkanälen 92 der Radialkanal 93 mit der Drossel 47 angeordnet, der die Umfangsnut 71 mit der Umfangsnut 89 des Ventilschiebers 52 verbindet. Im Ringansatz 85 ist eine die Umfangsnut 84 mit der Arbeitskammer 86 verbindende Drosselstelle 80 vorgesehen, die hier durch eine Abflachung gebildet ist.The circumferential groove 65 is connected by a radial channel 82 to a circumferential groove 84 in the control slide 73, which is delimited on its right side by an annular shoulder 85 of the control slide 73. To the right of the ring extension 85 is a hydraulic working chamber 86 which is delimited on the right side by a guide section 87 which guides a narrowed guide part 88 of the control slide 73 in a sliding guide. In the guide part 88, a circumferential groove 89 is formed, the left shoulder of which forms a control edge 91 which can close or open one or more ring and / or radial channels 92 in the valve slide 52 in the region of the circumferential web 68, in which throttles can be arranged, and which communicate with the circumferential groove 89 in the open position. In the valve slide 52 to the right of the radial channels 92, the radial channel 93 with the throttle 47 is arranged, which connects the circumferential groove 71 with the circumferential groove 89 of the valve slide 52. In the annular shoulder 85 is a circumferential groove 84 with the Throttle point 80 connecting working chamber 86 is provided, which is formed here by a flattening.

Beim vorliegenden Ausführungsbeispiel wird eine Fördermengensteuerung verwirklicht, bei der mit zunehmendem Arbeitsdruck A der Steuer- bzw. Regeldruck R vergrößert wird. Die Größe der Arbeitsfläche der Arbeits-Ringkammer 86 ist so bemessen bzw. auf die vorhandene Anordnung abgestimmt, daß im Leistungsregelbereich des Regelventils 51 der Winkelhebel 76 und die eingestellte Kraft der Druckfeder 79 die hydraulische Schubkraft, die den Steuerschieber 73 relativ zum Ventilschieber 52 nach links zu schieben sucht, überdrücken, so daß der Steuerschieber 73 die in Fig. 2 dargestellte rechte Endposition oder Ruhestellung einnimmt, in der der Steuerschieber 73 am Grund 72.1 der Führungsbohrung 72 anliegt. Wenn der Arbeitsdruck A beim Übergang vom Leistungsregelbereich zum Druckregelbereich seinen Maximaldruck erreicht, überdrückt der Steuerschieber 73 den Winkelhebel 76, wobei der Steuerschieber 73 relativ zum Ventilschieber 52 nach links in die in Fig. 3 dargestellte Regelstellung verschoben wird, in der die Steuerkante 91 die Radialkanäle 92 wenigstens teilweise öffnet und der durch die Radialkanäle 92, die Umfangsnut 89 und den Radialkanal 93 sowie die Drossel 47 gebildete Beipaß 46 geöffnet wird und somit eine geringe Menge des hydraulischen Mediums abfließen kann, wodurch die angestrebte dynamische Stabilit des Regelventils 51 erreicht wird.In the present exemplary embodiment, a delivery rate control is implemented in which the control or regulating pressure R is increased as the working pressure A increases. The size of the working surface of the working annular chamber 86 is dimensioned or matched to the existing arrangement so that in the power control range of the control valve 51 the angle lever 76 and the set force of the compression spring 79 are the hydraulic thrust force which moves the control slide 73 relative to the valve slide 52 to the left tries to push, press over, so that the control slide 73 assumes the right end position or rest position shown in FIG. 2, in which the control slide 73 rests against the bottom 72.1 of the guide bore 72. When the working pressure A reaches its maximum pressure during the transition from the power control range to the pressure control range, the control slide 73 presses the angle lever 76, the control slide 73 being displaced relative to the valve slide 52 to the left into the control position shown in FIG. 3, in which the control edge 91 the radial channels 92 opens at least partially and the bypass 46 formed by the radial channels 92, the circumferential groove 89 and the radial channel 93 and the throttle 47 is opened and thus a small amount of the hydraulic medium can flow away, whereby the desired dynamic stability of the control valve 51 is achieved.

Die Einstellvorrichtung 59 und auch eine allgemein mit 94 bezeichnete Einstellvorrichtung für die Kraft der Druckfeder 79 ist in an sich bekannter Art mit Stellschrauben ausgebildet, die gegen Federteller wirken und durch Längsverstellung unterschiedliche Federkräfte einstellen.The adjusting device 59 and also an adjusting device, generally designated 94, for the force of the compression spring 79 is designed in a manner known per se with adjusting screws which act against spring plates and adjust different spring forces by longitudinal adjustment.

Claims (11)

1. Hydraulische Axialkolbenmaschine (1) in Schiefscheibenbauart, deren Schiefscheibe (9) an einer in einem Segmentwälzlager (24) schwenkbar gelagerten Wiege (5) angeordnet ist, mit einer Nachführeinrichtung (21) für den Käfig (19) des Schwenklagers (24), die ein stangenförmiges Führungselement (22) aufweist, das in einem ersten Lager (25) in der Wiege (5) parallel zur Schwenkebene (SE) schwenkbar mit der Wiege (5) verbunden ist, in einem zweiten Lager (26) parallel zur Schwenkebene (SE) schwenkbar und in seiner Längsrichtung (23) verschiebbar mit dem Käfig (19) verbunden ist, und in einem dritten Lager (27) parallel zur Schwenkebene (SE) schwenkbar gelagert ist,
dadurch gekennzeichnet,
daß die Wiege (5) durch ein quer zur Mittelachse (3) der Axialkolbenmaschine (1) verschiebbar gelagertes Stellglied (17) verstellbar ist und das dritte Lager (25) an einem Führungsteil (33) angeordnet ist, das beweglich mit dem Stellglied (17) und der Wiege (5) verbunden ist.1. Hydraulic axial piston machine (1) of swash plate type, the swash plate (9) of which is arranged on a cradle (5) pivotably mounted in a segment roller bearing (24), with a tracking device (21) for the cage (19) of the swivel bearing (24), which has a rod-shaped guide element (22) which is pivotally connected to the cradle (5) in a first bearing (25) in the cradle (5) parallel to the pivot plane (SE), in a second bearing (26) parallel to the pivot plane ( SE) is pivotably connected to the cage (19) in its longitudinal direction (23) and is pivotably mounted in a third bearing (27) parallel to the pivoting plane (SE),
characterized by
that the cradle (5) is adjustable by an actuator (17) which is displaceably mounted transversely to the central axis (3) of the axial piston machine (1) and the third bearing (25) is arranged on a guide part (33) which is movable with the actuator (17 ) and the cradle (5) is connected. 2. Axialkolbenmaschine nach Anspruch 1,
dadurch gekennzeichnet,
daß das Führungsteil (33) in der Schwenkebene (SE) schwenkbar mit der Wiege (5) und parallel zur Mittelachse (3) verstellbar mit dem Stellglied (17) verbunden ist.2. axial piston machine according to claim 1,
characterized by
that the guide part (33) is pivotally connected to the cradle (5) in the pivot plane (SE) and adjustable to the actuator (17) parallel to the central axis (3). 3. Axialkolbenmaschine nach Anspruch 2,
dadurch gekennzeichnet,
daß das Führungsteil durch einen Gleitstein (33) gebildet ist, der mit der Wiege (5) durch einen sich rechtwinklig zur Schwenkebene (SE) erstreckenden, vorzugsweise an der Wiege (5) angeordneten sowie in eine vorzugsweise am Gleitstein ausgebildete Lagerbohrung (35) einfassenden Schwenkzapfen (34) verbunden, in einer Umfangsnut (36) des Stellgliedes (17) längs der Mittelachse (3) verschiebbar geführt und im dritten Lager (27) parallel zur Schwenkebene (SE) des Schwenklagers (24) schwenkbar mit dem Führungselement (22) verbunden ist.3. axial piston machine according to claim 2,
characterized by
that the guide part is formed by a sliding block (33) which is arranged with the cradle (5) by a perpendicular to the pivot plane (SE), preferably on the cradle (5) and preferably in a Bearing pin (34) enclosing a sliding block formed in the sliding block, guided in a circumferential groove (36) of the actuator (17) so as to be displaceable along the central axis (3) and in the third bearing (27) parallel to the pivoting plane (SE) of the pivot bearing (24) is pivotally connected to the guide element (22). 4. Axialkolbenmaschine nach wenigstens einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet,
daß das Führungselement (22) im ersten Lager (25) in seiner Längsrichtung (23) unverschieblich an der Wiege (5) gelagert und im dritten Lager (27) in seiner Längsrichtung (23) verschiebbar mit dem Gleitstein (33) verbunden ist.4. axial piston machine according to at least one of claims 1 to 3,
characterized by
that the guide element (22) in the first bearing (25) in its longitudinal direction (23) is immovably mounted on the cradle (5) and in the third bearing (27) in its longitudinal direction (23) is slidably connected to the sliding block (33). 5. Axialkolbenmaschine nach wenigstens einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet,
daß das Stellglied (17) ein hydraulischer Kolben ist.5. axial piston machine according to at least one of claims 1 to 4,
characterized by
that the actuator (17) is a hydraulic piston. 6. Axialkolbenmaschine nach wenigstens einem der Ansprüche 3 bis 5,
dadurch gekennzeichnet,
daß das Führungselement (22) zwischen der Wiege (5) und dem Gleitstein (33) angeordnet ist und einen sich rechtwinklig zur Schwenkebene (SE) erstreckenden, aus dem Gleitstein (33) herausragenden Gelenkbolzen (37) diametral mit Bewegungsspiel durchfaßt.6. axial piston machine according to at least one of claims 3 to 5,
characterized by
that the guide element (22) is arranged between the cradle (5) and the sliding block (33) and extends through a joint pin (37) which extends at right angles to the swivel plane (SE) and protrudes from the sliding block (33) diametrically with play. 7. Axialkolbenmaschine nach wenigstens einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet,
daß das erste Lager (25) und das dritte Lager (27) auf der dem zweiten Lager (26) abgewandten Seite des Schwenkzapfens (34) angeordnet sind.7. axial piston machine according to at least one of claims 1 to 6,
characterized by
that the first bearing (25) and the third bearing (27) are arranged on the side of the pivot pin (34) facing away from the second bearing (26). 8. Axialkolbenmaschine nach wenigstens einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet,
daß das erste Lager (25) und das dritte Lager (27) zwischen dem zweiten Lager (26) und dem Schwenkzapfen (34) angeordnet sind.8. axial piston machine according to at least one of claims 1 to 6,
characterized by
that the first bearing (25) and the third bearing (27) between the second bearing (26) and the pivot pin (34) are arranged. 9. Axialkolbenmaschine nach wenigstens einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet,
daß das Führungselement (22) durch einen C-förmig gebogenen runden Draht gebildet ist, von dessen aufeinanderzu gewandten freien Enden das eine freie Ende (42) sich bis in den Bereich des zweiten Lagers (26) und das andere freie Ende (43) sich durch das dritte Lager (27) hindurch bis zum ersten Lager (25) erstreckt.9. axial piston machine according to at least one of claims 1 to 8,
characterized by
that the guide element (22) is formed by a C-shaped round wire, from the free ends of which face one another, one free end (42) extends into the region of the second bearing (26) and the other free end (43) extends through the third bearing (27) to the first bearing (25). 10. Axialkolbenmaschine nach Anspruch 9,
dadurch gekennzeichnet,
daß das erste Lager (25) durch eine sich rechtwinklig zur Schwenkebene (SE) erstreckende Sackbohrung (29) in der Schwenkwiege (5) und einen rechtwinklig abgebogenen Schenkel (28) des sich zum dritten und ersten Lager (25, 27) erstreckenden freien Endes (43) gebildet ist.10. axial piston machine according to claim 9,
characterized by
that the first bearing (25) through a blind hole (29) extending at right angles to the swivel plane (SE) in the swivel cradle (5) and a right-angled leg (28) of the free end extending to the third and first bearings (25, 27) (43) is formed. 11. Axialkolbenmaschine nach Anspruch 9 oder 10,
dadurch gekennzeichnet,
daß der Draht aus Federstahl besteht.11. axial piston machine according to claim 9 or 10,
characterized by
that the wire is made of spring steel.
EP90111124A 1989-06-12 1990-06-12 Control device for variable displacement pump Expired - Lifetime EP0402871B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3919175 1989-06-12
DE3919175A DE3919175A1 (en) 1989-06-12 1989-06-12 CONTROL DEVICE FOR AN ADJUSTABLE PUMP

Publications (3)

Publication Number Publication Date
EP0402871A2 true EP0402871A2 (en) 1990-12-19
EP0402871A3 EP0402871A3 (en) 1992-09-02
EP0402871B1 EP0402871B1 (en) 1996-04-17

Family

ID=6382606

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90111124A Expired - Lifetime EP0402871B1 (en) 1989-06-12 1990-06-12 Control device for variable displacement pump

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EP (1) EP0402871B1 (en)
DE (2) DE3919175A1 (en)

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CN103261706B (en) * 2010-12-22 2016-11-30 罗伯特·博世有限公司 Fluid pressure drive device
CN114135458A (en) * 2021-11-30 2022-03-04 力源液压（苏州）有限公司 Constant power control structure of plunger pump

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DE19756600C1 (en) * 1997-12-18 1999-08-26 Brueninghaus Hydromatik Gmbh Capacity control valve
DE10358727B3 (en) * 2003-12-15 2005-08-25 Brueninghaus Hydromatik Gmbh Total power controller
WO2019112554A1 (en) * 2017-12-04 2019-06-13 Halliburton Energy Services, Inc. Safety pressure limiting system and method for positive displacement pumps with optional automatic restart
DE102018216831A1 (en) 2018-10-01 2020-04-02 Robert Bosch Gmbh Control device for pump pressure and volume flow with concentric control spools

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CN103261706A (en) * 2010-12-22 2013-08-21 罗伯特·博世有限公司 Hydraulic driver
CN103261706B (en) * 2010-12-22 2016-11-30 罗伯特·博世有限公司 Fluid pressure drive device
CN114135458A (en) * 2021-11-30 2022-03-04 力源液压（苏州）有限公司 Constant power control structure of plunger pump

Also Published As

Publication number Publication date
DE3919175C2 (en) 1993-01-07
DE59010287D1 (en) 1996-05-23
EP0402871B1 (en) 1996-04-17
DE3919175A1 (en) 1990-12-13
EP0402871A3 (en) 1992-09-02

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