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WO1998005870A1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
WO1998005870A1
WO1998005870A1 PCT/EP1997/003031 EP9703031W WO9805870A1 WO 1998005870 A1 WO1998005870 A1 WO 1998005870A1 EP 9703031 W EP9703031 W EP 9703031W WO 9805870 A1 WO9805870 A1 WO 9805870A1
Authority
WO
WIPO (PCT)
Prior art keywords
control
piston
pressure
control piston
consumer
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.)
Ceased
Application number
PCT/EP1997/003031
Other languages
German (de)
French (fr)
Inventor
Armin Stellwagen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of WO1998005870A1 publication Critical patent/WO1998005870A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool

Definitions

  • the invention relates to a hydraulic control device according to the preamble of claim 1.
  • control piston has sleeve-shaped extensions at its ends, which protrude into the control spaces for the control liquid and each have an axial and radial bore in the control piston with the closest one connected to the consumer connection
  • Volumetric pistons are guided in the sleeve-shaped extensions, which are supported on fixed housing stops when acted upon by the load pressure occurring in the controlled consumer.
  • the force resulting from this pressurization counteracts the force acting on the control piston from the control pressure for displacing the control piston into an opening position which determines the amount of working fluid from the pressure medium source to the consumer.
  • the cross-sectional area of the measuring piston acted upon by the load pressure must be of such a size that the resulting pressure force, in addition to the spring force of the springs returning the control piston to its initial position, is not greater than the maximum adjusting force by the control pressure of the control piston.
  • the load pressure is passed on to the control chamber of a pressure compensator assigned to the control piston or to the outside for connection to the adjusting device of a variable displacement pump via housing channels which branch off from the consumer connections.
  • the object of the invention is to simplify the housing of the control device by largely dispensing with the housing channels carrying the load pressure and, when using control pistons with two measuring pistons, two measuring pistons a common space loaded by the load pressure can be assigned.
  • 1 denotes the housing of a hydraulic control device.
  • a control piston 3 In a through bore 2, a control piston 3 is arranged, which consists of five sections 4, 5, 6, 7 and 8, which are interconnected by four webs 9, 10, 11 and 12.
  • the webs form control spaces 13, 14, 15 and 16 together with circumferential housing recesses.
  • the control space 15 is connected via a channel 17 and a pressure compensator 18 to the connection channel 19 for a variable displacement pump P and the control spaces 14 and 16 with connection channels (not shown) for the
  • a circumferential housing recess 20 is provided between the control rooms 14 and 15 and a circumferential housing recess 21 is provided between the control rooms 15 and 16.
  • the housing recess 20 is connected via a channel 22 to the working line connection A and the housing recess 21 via a channel 23 to the working line connection B, which in turn are connected via working lines AI, Bl to the working spaces ZI, Z2 of a consumer V designed as a differential cylinder .
  • the housing recesses 20, 21 are from control edges 24, 25, 26 and 27 limited, which cooperate with a corresponding axial displacement of the control piston with its fine control grooves 28, 29, 30, 31 and its circumferential control edges 32, 33, 34, 35.
  • the control piston 3 is traversed with an axial bore 36 which at its ends for receiving guide inserts 37, 38 for
  • volumetric flasks 39, 40 are expanded and provided with thread 41.
  • the control piston also has radial bores 42, 43 in the area of the fine control grooves 29, 30, which are connected to the axial bore 36.
  • a further radial bore 55 which rotates in connection with the axial bore 36 is provided in the web 9, so that the same pressure prevails in the control chamber 13 delimited by the control piston sections 4 and 5 as in the axial bore 36.
  • the control chamber 13 is connected via a housing channel 56 to the Control room 57 of the pressure compensator 18 in connection.
  • compression springs 45, 46 are supported by spring plates, which are housed in the end caps 47, 48 and hold the control piston 3 in its shown starting position or middle position.
  • the spaces 49, 50 enclosed by the end caps 47, 48 can be acted upon with control fluid for displacing the control piston against the force of the compression springs 45, 46 in one direction or the other.
  • Axially adjustable stops 51, 52 for the measuring pistons 39, 40 are arranged on the end face of the end cap 47, 48.
  • the measuring pistons have collars 53, 54 on the axial bore side, which are supported on the guide inserts 37, 38 to limit the stroke of the measuring pistons on the stop side. For example, if the space 50 delimited by the end cover 48 is subjected to control pressure, the control piston 3 moves against the force of the compression spring 45 in the direction of the space 49 delimited by the end cover 47.
  • This displacement of the control piston connects the radial bores 42 to the housing recess 20, so that the same pressure prevails in the axial bore 36 of the control piston as in the housing space 20 connected to the consumer connection A via the channel 22.
  • the housing space 20 is connected to the control space 15 via the fine control grooves 29 and with a correspondingly large displacement of the control piston via the control edge 33.
  • the housing seraum 21 communicates with the control chamber 16 connected to the tank via the fine control grooves 31 or the control edge 35.
  • connection channel 1 9 which in this case the counter to the force of the control spring 58 opening pressure compensator 18 and the channel 17 in Control chamber 15 and from there further via the control piston 3 in the open position to the housing recess 20 and further via the channel 22 to the consumer connection A.
  • the working fluid flows via the working line AI to the working chamber Z of the working cylinder V and there displaces the piston K with piston rod St in the direction of the work area Z2.
  • the measuring piston 40 moves so far in the direction of the stop 52 until its collar 54 abuts the annular surface of the guide insert 38.
  • the opposite measuring piston 39 is supported with its end face on the stop 51.
  • This results in a reaction force acting on the control piston 3 in the direction of the control chamber 50, that is to say in the closing direction of the control piston, the size of which is determined by the load or consumer pressure and the active surface of the measuring piston acted on by the load or consumer pressure.
  • the spring force of the compression spring 45 acting on the control piston 3 also acts in the closing direction of the control piston 3.
  • the opening position of the control piston is given control pressure from the prevailing load or consumer pressure.
  • the dimensioning of the cross-sectional area of the volumetric pistons acted upon by the load or consumer pressure must be carried out in such a way that the maximum load or consumer pressure that occurs and the resulting reaction force acting on the control piston additionally the maximum spring force of the compression springs 45 returning the control piston in its central position , 46 is smaller than the control force that can be set on a control unit and acts on the control piston 3 in the opening direction and the cross-sectional area of the control piston on the control pressure.
  • the compression spring loading the control piston in the closing direction also having to be taken into account.
  • the control piston is displaced in the opposite direction by acting on the space 49 delimited by the end cover 47 with control pressure by a control device (not shown), the radial bores 43 connect the axial bore 36 to the housing recess 21, which in this control position of the control piston via the fine control grooves 30 or control edge 34 communicates with the control chamber 15 connected to the pump.
  • the radial bores 42 are kept closed by the guide bore 2 for the control piston 3.
  • the housing recess 20 connected to the working line connection A is connected via the fine control grooves 28 or control edge 32 to the control chamber 14 connected to the tank.
  • the measuring piston 40 In this control position of the control piston, the measuring piston 40 is supported with its end face on the stop 52, while the measuring piston 39 is supported with its collar 53 on the guide insert 37, so that a reaction force resulting from the load or consumer pressure in the closing direction of the control piston, thus occurs in the direction of space 49.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A hydraulic control device has at least one control piston for driving at least one consumer and a hydraulic medium source formed by a pump. The load pressure at the consumers is used as control signal for controlling the amount of working liquid to be supplied to the consumers and determined by the position of the control piston. A control chamber to which the load pressure is applied is provided at least at one end of the control piston and receives an outwardly extending measurement piston whose outer end can be supported on a housing stop. The force which results from the load pressure applied on the measurement piston is oriented against the driving force for moving the control piston into an opening position which determines the amount of working liquid to be supplied by the hydraulic medium source to the consumer. The hydraulic control device is characterised in that the control piston (3) has a section (9) which forms a control chamber (13) with the control piston-receiving housing bore (2). The control chamber (13) communicates through a transverse bore (55) with the axial bore (36) receiving the measure piston (39, 40) through which the load or consumer pressure is transmitted and which forms a control chamber. A channel (56) extends outwards from the control chamber (13) through the housing to retransmit the load or consumer pressure to the adjustment device of a variable displacement pump (P) or to the control chamber (57) of a pressure balance (18) associated to the control piston (3).

Description

Beschreibung description

Hydraulische SteuervorrichtungHydraulic control device

Die Erfindung betrifft eine hydraulische Steuervorrichtung nach dem Oberbegriff des Anspruches 1.The invention relates to a hydraulic control device according to the preamble of claim 1.

Eine solche Steuervorrichtung ist durch das US-Patent 4,407,122 bekannt. Bei dieser bekannten Steuervorrichtung weist der Steuerkolben an seinen Enden hülsenföπnige Verlängerungen auf, die in die Steuerräume für die Steuerflüssigkeit ragen und über je eine Axial- und Radialbohrung im Steuerkolben mit dem nächstge- legenen mit dem Verbraucheranschluß in Verbindung stehendenSuch a control device is known from US Patent 4,407,122. In this known control device, the control piston has sleeve-shaped extensions at its ends, which protrude into the control spaces for the control liquid and each have an axial and radial bore in the control piston with the closest one connected to the consumer connection

Steuerraum in Verbindung stehen. In den hülsenförmigen Verlängerungen sind Meßkolben geführt, die sich bei Beaufschlagung durch den in dem angesteuerten Verbraucher auftretenden Lastdruck an festen Gehäuseanschlägen abstützen. Die aus dieser Druckbeauf- schlagung resultierende Kraft wirkt der auf den Steuerkolben wirkenden aus dem Ansteuerdruck resultierenden Kraft zum Verschieben des Steuerkolbens in eine die Arbeitsflussigkeitsmenge von der Druckmittelquelle zum Verbraucher bestimmende Öffnungslage entgegen. Die vom Lastdruck beaufschlagte Querschnittsflä- ehe des Meßkolbens muß eine solche Größe aufweisen, daß die daraus resultierende Druckkraft zusätzlich der Federkraft der den Steuerkolben in seine Ausgangslage zurückführenden Federn nicht größer ist als die maximale Verstellkraft durch den Ansteuerdruck des Steuerkolbens . Die Weiterleitung des Lastdrucks in den Steuerraum einer dem Steuerkolben zugeordneten Druckwaage oder nach außen zur Verbindung mit der Versteileinrichtung einer Verstellpumpe erfolgt über Gehäusekanäle, die von den Verbraucheranschlüssen abgezweigt sind.Control room communicating. Volumetric pistons are guided in the sleeve-shaped extensions, which are supported on fixed housing stops when acted upon by the load pressure occurring in the controlled consumer. The force resulting from this pressurization counteracts the force acting on the control piston from the control pressure for displacing the control piston into an opening position which determines the amount of working fluid from the pressure medium source to the consumer. The cross-sectional area of the measuring piston acted upon by the load pressure must be of such a size that the resulting pressure force, in addition to the spring force of the springs returning the control piston to its initial position, is not greater than the maximum adjusting force by the control pressure of the control piston. The load pressure is passed on to the control chamber of a pressure compensator assigned to the control piston or to the outside for connection to the adjusting device of a variable displacement pump via housing channels which branch off from the consumer connections.

Die Aufgabe der Erfindung besteht in der Vereinfachung des Ge- häuses der Steuervorrichtung, indem auf die den Lastdruck führenden Gehäusekanäle weitgehend verzichtet werden kann und bei Verwendung von Steuerkolben mit zwei Meßkolben beiden Meßkolben ein gemeinsamer vom Lastdruck beaufschlagter Raum zugeordnet werden kann.The object of the invention is to simplify the housing of the control device by largely dispensing with the housing channels carrying the load pressure and, when using control pistons with two measuring pistons, two measuring pistons a common space loaded by the load pressure can be assigned.

Dies wird mit den kennzeichnenden Merkmalen des Anspruches 1 erreicht. Dadurch, daß der Lastdruck für die Versteileinrichtung einer Verstellpumpe oder dem Steuerraum einer dem Steuerkolben zugeordneten Druckwaage über den Steuerkolben geleitet wird, lassen sich besondere Abzweigkanäle von den Verbraucheranschlußkanälen einsparen, so daß sich insbesondere die gießtechnische Herstellung des Gehäuses für die Steuervorrichtung wesentlich vereinfachen läßt und zusätzlich das Gehäuse kompakter gestaltet werden kann. Außerdem läßt sich der Steuerkolben mit zwei Meßkolben durch eine Durchgangsbohrung in seiner Herstellung vereinfachen.This is achieved with the characterizing features of claim 1. Because the load pressure for the adjusting device of a variable displacement pump or the control chamber of a pressure compensator assigned to the control piston is passed over the control piston, special branch ducts can be saved from the consumer connection ducts, so that in particular the casting production of the housing for the control device can be considerably simplified and additionally the housing can be made more compact. In addition, the control piston with two measuring pistons can be simplified in its manufacture by means of a through hole.

Weitere Merkmale der Erfindung ergeben sich aus den Unteransprü- chen und der nachfolgenden Beschreibung eines Ausführungsbei- spiels.Further features of the invention result from the subclaims and the following description of an exemplary embodiment.

In der einzigen Figur bezeichnet 1 das Gehäuse einer hydraulischen Steuervorrichtung. In einer Durchgangsbohrung 2 ist ein Steuerkolben 3 angeordnet , der aus fünf Abschnitten 4 , 5 , 6 , 7 und 8 besteht, die untereinander durch vier Stege 9, 10, 11 und 12 verbunden sind. Die Stege bilden gemeinsam mit umlaufenden Gehäuseausnehmungen Steuerräume 13, 14, 15 und 16. Der Steuerraum 15 steht über einen Kanal 17 und einer Druckwaage 18 mit dem Anschlußkanal 19 für eine Verstellpumpe P und die Steuerräu- me 14 und 16 mit nicht dargestellten Anschlußkanälen für denIn the single figure, 1 denotes the housing of a hydraulic control device. In a through bore 2, a control piston 3 is arranged, which consists of five sections 4, 5, 6, 7 and 8, which are interconnected by four webs 9, 10, 11 and 12. The webs form control spaces 13, 14, 15 and 16 together with circumferential housing recesses. The control space 15 is connected via a channel 17 and a pressure compensator 18 to the connection channel 19 for a variable displacement pump P and the control spaces 14 and 16 with connection channels (not shown) for the

Tank in Verbindung. Zwischen den Steuerräumen 14 und 15 ist eine umlaufende Gehäuseausnehmung 20 und zwischen den Steuerräumen 15 und 16 eine umlaufende Gehäuseausnehmung 21 vorgesehen. Die Gehäuseausnehmung 20 ist über einen Kanal 22 mit dem Arbeitslei- tungsanschluß A und die Gehäuseausnehmung 21 über einen Kanal 23 mit dem Arbeitsleitungsanschluß B verbunden, die ihrerseits über Arbeitsleitungen AI, Bl mit den Arbeitsräumen ZI, Z2 eines als Differentialzylinder ausgebildeten Verbrauchers V in Verbindung stehen. Die Gehäuseausnehmungen 20, 21 sind von Steuerkanten 24, 25, 26 und 27 begrenzt, die bei entsprechender Axialverschiebung des Steuerkolbens mit dessen Feinsteuernuten 28, 29, 30, 31 und dessen umlaufenden Steuerkanten 32, 33, 34, 35 zusammenarbeiten.Tank in connection. A circumferential housing recess 20 is provided between the control rooms 14 and 15 and a circumferential housing recess 21 is provided between the control rooms 15 and 16. The housing recess 20 is connected via a channel 22 to the working line connection A and the housing recess 21 via a channel 23 to the working line connection B, which in turn are connected via working lines AI, Bl to the working spaces ZI, Z2 of a consumer V designed as a differential cylinder . The housing recesses 20, 21 are from control edges 24, 25, 26 and 27 limited, which cooperate with a corresponding axial displacement of the control piston with its fine control grooves 28, 29, 30, 31 and its circumferential control edges 32, 33, 34, 35.

Der Steuerkolben 3 ist mit einer Axialbohrung 36 durchzogen, die an ihren Enden zur Aufnahme von Führungseinsätzen 37, 38 fürThe control piston 3 is traversed with an axial bore 36 which at its ends for receiving guide inserts 37, 38 for

Meßkolben 39, 40 erweitert und mit Gewinde 41 versehen sind. Der Steuerkolben weist ferner im Bereich der Feinsteuernuten 29, 30 Radialbohrungen 42, 43 auf, die mit der Axialbohrung 36 in Verbindung stehen. Eine weitere mit der Axialbohrung 36 in Verbin- düng srehende Radialbohrung 55 ist im Steg 9 vorgesehen, so daß im von dem Steuerkolbenabschnitten 4 und 5 begrenzten Steuerraum 13 derselbe Druck herrscht wie in der Axialbohrung 36. Der Steuerraum 13 steht über einen Gehäusekanal 56 mit dem Steuerraum 57 der Druckwaage 18 in Verbindung. An den Enden des Steuerkolbens stützen sich über Federteller 44 Druckfedern 45, 46 ab, die in den Abschlußdeckeln 47, 48 untergebracht sind und den Steuerkolben 3 in seiner gezeigten Ausgangslage oder Mittelstellung halten. Die von den Abschlußdeckeln 47, 48 eingeschlossenen Räume 49, 50 sind mit Steuerflüssigkeit zum Verschieben des Steuerkol- bens gegen die Kraft der Druckfedern 45, 46 in die eine oder andere Richtung beaufschlagbar. An der Stirnseite der Abschlußdek- kel 47, 48 sind axial verstellbare Anschläge 51, 52 für die Meßkolben 39, 40 angeordnet. Die Meßkolben weisen axialbohrungssei- tig Bunde 53, 54 auf, die sich zur Begrenzung des anschlagseiti- gen Hubes der Meßkolben an den Führungseinsätzen 37, 38 abstützen. Wird beispielsweise der vom Abschlußdeckel 48 begrenzte Raum 50 mit Steuerdruck beaufschlagt, verschiebt sich der Steuerkolben 3 gegen die Kraft der Druckfeder 45 in Richtung des vom Abschlußdeckel 47 begrenzten Raumes 49. Durch diese Verschiebung des Steuerkolbens werden die Radialbohrungen 42 mit der Gehäuseausnehmung 20 verbunden, so daß in der Axialbohrung 36 des Steuerkolbens derselbe Druck herrscht wie im mit dem Verbraucheranschluß A über den Kanal 22 verbundenen Gehäuseraum 20. Gleichzeitig wird über die Feinsteuernuten 29 und bei entsprechend großer Verschiebung des Steuerkolbens über die Steuerkante 33 der Gehäuseraum 20 mit dem Steuerraum 15 verbunden. Der Gehäu- seraum 21 steht über die Feinsteuernuten 31 bzw. der Steuerkante 35 mit dem mit dem Tank verbundenen Steuerraum 16 in Verbindung. Bei Betrieb der nicht dargestellten Pumpe P strömt bei dieser Steuerlage des Steuerkolbens 3 die von der Pumpe geförderte Ar- beitsflüssigkeit über die Pumpenleitung Pl, den Anschlußkanal 19 und die sich hierbei gegen die Kraft der Regelfeder 58 öffnende Druckwaage 18 und den Kanal 17 in den Steuerraum 15 und von dort weiter über den in Offenstellung befindlichen Steuerkolben 3 zur Gehäuseausnehmung 20 und weiter über den Kanal 22 zum Verbrau- cheranschluß A. Von dort strömt die Arbeitsflüssigkeit über die Arbeitsleitung AI zu dem Arbeitsraum Z des ArbeitsZylinders V und verschiebt dort den Kolben K mit Kolbenstange St in Richtung des Arbeitsraumes Z2. Die aus dem Zylinderraum Z2 verdrängte Ar¬ beitsflüssigkeit wird über die Arbeitsleitung Bl, über den Ge- häusekanal 23, über die Gehäuseausnehmung 21, den Feinsteuernuten 31 bzw. der Steuerkante 35 über den Steuerraum 16 zum Tank abgeführt. Der hierbei im Gehäuseraum 20 auftretende Lastdruck ist über die geöffneten Radialbohrungen 42 auch in der Axialbohrung 36 des Steuerkolbens wirksam und beaufschlagt dort die Meß- kolben 39, 40 in Richtung der Anschläge 51, 52. Die Radialbohrungen 43 bleiben bei dieser Steuerlage des Steuerkolbens verschlossen.Volumetric flasks 39, 40 are expanded and provided with thread 41. The control piston also has radial bores 42, 43 in the area of the fine control grooves 29, 30, which are connected to the axial bore 36. A further radial bore 55 which rotates in connection with the axial bore 36 is provided in the web 9, so that the same pressure prevails in the control chamber 13 delimited by the control piston sections 4 and 5 as in the axial bore 36. The control chamber 13 is connected via a housing channel 56 to the Control room 57 of the pressure compensator 18 in connection. At the ends of the control piston 44 compression springs 45, 46 are supported by spring plates, which are housed in the end caps 47, 48 and hold the control piston 3 in its shown starting position or middle position. The spaces 49, 50 enclosed by the end caps 47, 48 can be acted upon with control fluid for displacing the control piston against the force of the compression springs 45, 46 in one direction or the other. Axially adjustable stops 51, 52 for the measuring pistons 39, 40 are arranged on the end face of the end cap 47, 48. The measuring pistons have collars 53, 54 on the axial bore side, which are supported on the guide inserts 37, 38 to limit the stroke of the measuring pistons on the stop side. For example, if the space 50 delimited by the end cover 48 is subjected to control pressure, the control piston 3 moves against the force of the compression spring 45 in the direction of the space 49 delimited by the end cover 47. This displacement of the control piston connects the radial bores 42 to the housing recess 20, so that the same pressure prevails in the axial bore 36 of the control piston as in the housing space 20 connected to the consumer connection A via the channel 22. At the same time, the housing space 20 is connected to the control space 15 via the fine control grooves 29 and with a correspondingly large displacement of the control piston via the control edge 33. The housing seraum 21 communicates with the control chamber 16 connected to the tank via the fine control grooves 31 or the control edge 35. When the pump P not shown in this control position of the control piston 3 passes the delivered by the pump working beitsflüssigkeit via the pump line Pl, the connection channel 1 9 and which in this case the counter to the force of the control spring 58 opening pressure compensator 18 and the channel 17 in Control chamber 15 and from there further via the control piston 3 in the open position to the housing recess 20 and further via the channel 22 to the consumer connection A. From there the working fluid flows via the working line AI to the working chamber Z of the working cylinder V and there displaces the piston K with piston rod St in the direction of the work area Z2. The displaced from the cylinder space Z2 A r ¬ beitsflüssigkeit is removed via the working line Bl, over the overall häusekanal 23, via the housing recess 21, the fine control 31 and the control edge 35 on the control chamber 16 to tank. The load pressure occurring here in the housing space 20 is also effective in the axial bore 36 of the control piston via the opened radial bores 42 and acts there on the measuring pistons 39, 40 in the direction of the stops 51, 52. The radial bores 43 remain closed in this control position of the control piston.

In der angenommenen Steuerlage des Steuerkolbens 3 verschiebt sich der Meßkolben 40 soweit in Richtung des Anschlages 52 bis dessen Bund 54 an der Ringfläche des Führungseinsatzes 38 anliegt. Der gegenüberliegende Meßkolben 39 stützt sich hingegen mit seiner Stirnfläche an dem Anschlag 51 ab. Daraus ergibt sich eine am Steuerkolben 3 in Richtung des Steuerraumes 50, also in Schließrichtung des Steuerkolbens, wirkende Reaktionskraft, de- ren Größe vom Last- bzw. Verbraucherdruck und der vom Last- bzw. Verbraucherdruck beaufschlagten Wirkfläche des Meßkolbens bestimmt wird. Neben dieser vom Last- bzw. Verbraucherdruck abhängigen Reaktionskraft wirkt noch die am Steuerkolben 3 angreifende Federkraft der Druckfeder 45 in Schließrichtung des Steuer- kolbens 3. Da die Kraftkennlinie der Druckfeder als feste Größe vorliegt, wird die Öffnungslage des Steuerkolbens bei einem vor- gegebenen Steuerdruck vom jeweils vorherrschenden Last- bzw. Verbraucherdruck festgelegt. Die Bemessung der vom Last- bzw. Verbraucherdruck beaufschlagten Querschnittsfläche der Meßkolben muß so vorgenommen werden, daß der maximal auftretende Last- bzw. Verbraucherdruck und die daraus resultierende auf den Steuerkolben wirkende Reaktionskraft zusätzlich der maximal auftretenden Federkraft der den Steuerkolben in seiner Mittellage zurückführenden Druckfedern 45, 46 kleiner ist als die aus der maximal an einem Steuergerät einstellbaren, den Steuerkolben 3 in Öffnungsrichtung beaufschlagenden Steuerdruck und der vom Steuerdruck beaufschlagten Querschnittsfläche des Steuerkolbens sich ergebende Anstellkraft. Beträgt beispielsweise der maximale Steuerdruck 30 bar und der maximale Lastdruck 300 bar, ergibt sich zwischen Meßkolben und Steuerkolben ein Flächenverhältnis von 1:10, wobei noch die den Steuerkolben in Schließrichtung belastende Druckfeder berücksichtigt werden muß. Wird der Steuerkolben in die entgegengesetzte Richtung durch Beaufschlagung des vom Abschlußdeckel 47 begrenzten Raumes 49 mit Steuerdruck durch ein nicht dargestelltes Steuergerät verschoben, verbinden die Radialbohrungen 43 die Axialbohrung 36 mit der Gehäuseausnehmung 21, die in dieser Steuerläge des Steuerkolbens über die Feinsteuernuten 30 bzw. Steuerkante 34 mit dem mit der Pumpe in Verbindung stehenden Steuerraum 15 in Verbindung steht. Die Radialbohrungen 42 werden von der Führungsbohrung 2 für den Steuerkol- ben 3 verschlossen gehalten. Die mit dem Arbeitsleitungsanschluß A in Verbindung stehende Gehäuseausnehmung 20 steht über die Feinsteuernuten 28 bzw. Steuerkante 32 mit dem mit dem Tank in Verbindung stehenden Steuerraum 14 in Verbindung. In dieser Steuerlage des Steuerkolbens stützt sich der Meßkolben 40 mit seiner Stirnfläche an dem Anschlag 52 ab, während sich der Meßkolben 39 mit seinem Bund 53 am Führungseinsatz 37 abstützt, so daß eine aus dem Last- bzw. Verbraucherdruck resultierende Reaktionskraft in Schließrichtung des Steuerkolbens, also in Richtung des Raumes 49 auftritt. In the assumed control position of the control piston 3, the measuring piston 40 moves so far in the direction of the stop 52 until its collar 54 abuts the annular surface of the guide insert 38. The opposite measuring piston 39, however, is supported with its end face on the stop 51. This results in a reaction force acting on the control piston 3 in the direction of the control chamber 50, that is to say in the closing direction of the control piston, the size of which is determined by the load or consumer pressure and the active surface of the measuring piston acted on by the load or consumer pressure. In addition to this reaction force, which is dependent on the load or consumer pressure, the spring force of the compression spring 45 acting on the control piston 3 also acts in the closing direction of the control piston 3. Since the force characteristic of the compression spring is a fixed variable, the opening position of the control piston is given control pressure from the prevailing load or consumer pressure. The dimensioning of the cross-sectional area of the volumetric pistons acted upon by the load or consumer pressure must be carried out in such a way that the maximum load or consumer pressure that occurs and the resulting reaction force acting on the control piston additionally the maximum spring force of the compression springs 45 returning the control piston in its central position , 46 is smaller than the control force that can be set on a control unit and acts on the control piston 3 in the opening direction and the cross-sectional area of the control piston on the control pressure. If, for example, the maximum control pressure is 30 bar and the maximum load pressure is 300 bar, there is an area ratio of 1:10 between the volumetric piston and the control piston, the compression spring loading the control piston in the closing direction also having to be taken into account. If the control piston is displaced in the opposite direction by acting on the space 49 delimited by the end cover 47 with control pressure by a control device (not shown), the radial bores 43 connect the axial bore 36 to the housing recess 21, which in this control position of the control piston via the fine control grooves 30 or control edge 34 communicates with the control chamber 15 connected to the pump. The radial bores 42 are kept closed by the guide bore 2 for the control piston 3. The housing recess 20 connected to the working line connection A is connected via the fine control grooves 28 or control edge 32 to the control chamber 14 connected to the tank. In this control position of the control piston, the measuring piston 40 is supported with its end face on the stop 52, while the measuring piston 39 is supported with its collar 53 on the guide insert 37, so that a reaction force resulting from the load or consumer pressure in the closing direction of the control piston, thus occurs in the direction of space 49.

Claims

Patentansprüche claims 1. Hydraulische Steuervorrichtung mit mindestens einem Steuerkolben zur Ansteuerung zumindest eines Verbrauchers und mit einer von einer Pumpe gebildeten Druckmittelquelle, wobei der an den Verbrauchern auftretende Lastdruck als Steuersignal zur Steuerung der den Verbrauchern zuzuführenden durch die Stel¬ lung des Steuerkolbens festgelegten Arbeitsflussigkeitsmenge dient und zumindest an einem Ende des Steuerkolbens ein vom Lastdruck beaufschlagter Steuerraum vorgesehen ist, der einen nach außen geführten Meßkolben aufnimmt, dessen äußeres Ende an einem Gehäuseanschlag abstützbar ist, und die aus der Lastdruckbeaufschlagung des Meßkolbens resultierende Kraft gegen die Ansteuerkraft zum Verschieben des Steuerkolbens in eine die Arbeitsflussigkeitsmenge von der Druckmittelquelle zum Verbraucher bestimmende Offnungslage gerichtet ist, dadurch gekennzeichnet, daß der Steuerkolben ( 3 ) einen Abschnitt ( 9 ) aufweist, der mit der den Steuerkolben aufnehmenden Gehäusebohrung (2) einen Steuerraum (13) bildet, daß der Steuerraum (13) über eine Querbohrung (55) mit der den Last- bzw. Verbraucherdruck führenden, den Meßkolben (39, 40) aufnehmenden, einen Steuerraum bildenden1. Hydraulic control device with at least one control piston for controlling at least one consumer and with a pressure medium source formed by a pump, the load pressure occurring at the consumers serving as a control signal for controlling the amount of working fluid to be supplied to the consumers by the position of the control piston, and at least on One end of the control piston is provided with a control chamber acted upon by the load pressure, which receives an outwardly directed volumetric piston, the outer end of which can be supported on a housing stop, and the force resulting from the load pressure of the volumetric piston against the control force for displacing the control piston into a working fluid quantity of the pressure medium source is directed towards the consumer-determining opening position, characterized in that the control piston (3) has a section (9) which is in contact with the housing bore (2) receiving the control piston. A control chamber (13) forms that the control chamber (13) forms a control chamber via a transverse bore (55) with the control chamber that carries the load or consumer pressure and accommodates the measuring piston (39, 40) Axialbohrung (36) im Steuerkolben verbunden ist und daß von dem Steueraum (13) ein Gehäusekanal (56) nach außen zur Weiterlei- tung des Last- bzw. Verbraucherdruckes zu der Versteileinrichtung einer Verstellpumpe (P) oder zum Steuerraum (57) einer dem Steuerkolben (3) zugeordneten Druckwaage (18) führt.Axial bore (36) is connected in the control piston and that from the control chamber (13) a housing channel (56) to the outside for forwarding the load or consumer pressure to the adjusting device of a variable displacement pump (P) or to the control chamber (57) of the control piston (3) assigned pressure compensator (18) leads. 2. Hydraulische Steuervorrichtung nach Anspruch 1 mit an beiden Ende des Steuerkolbens angeordneten Meßkolben, dadurch gekennzeichnet, daß den Meßkolben (39, 40) eine gemeinsame Axialbohrung (36) im Steuerkolben (3) zugeordnet ist, die nach außen von Führungseinsätzen (37, 38) für die Meßkolben (39, 40) abgeschlossen ist und die Meßkolben steuerraumseitig (36) einen Bund (53, 54) zum Abstützen an den Führungseinsätzen aufweisen.2. Hydraulic control device according to claim 1 with arranged at both ends of the control piston measuring piston, characterized in that the measuring piston (39, 40) is associated with a common axial bore (36) in the control piston (3), which outwardly from guide inserts (37, 38th ) for the volumetric flask (39, 40) is complete and the volumetric flask on the control chamber side (36) has a collar (53, 54) for support on the guide inserts. 3. Hydraulische Steuerrvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Axialbohrung (36) für den oder die Meßkolben (39, 40) über Radialbohrungen (42, 43) im Steuerkolben (3) mit dem bzw. den mit den Arbeitsleitungsanschlüssen (A, B) verbundenen Gehäuseausnehmungen (20, 21) in der die Druckmittelquelle mit dem Verbraucher verbindenden Steuerlage des Steuerkolbens (3) verbunden sind.3. Hydraulic Steuerrvorrichtung according to claim 1 or 2, characterized in that the axial bore (36) for the or the measuring pistons (39, 40) via radial bores (42, 43) in the control piston (3) with the housing recesses (20, 21) connected to the working line connections (A, B) in the control position of the control piston connecting the pressure medium source with the consumer (3) are connected. 4. Hydraulische Steuervorrichtung nach einem der vorherge¬ henden Ansprüche, dadurch gekennzeichent, daß die gehäusefesten Anschläge (51, 52) für die Meßkolben (39, 40) einstellbar sind. 4. A hydraulic control device, characterized gekennzeichent according to one of claims vorherge ¬ Henden that the housing-fixed stops (51, 52) are adjustable for the volumetric flask (39, 40).
PCT/EP1997/003031 1996-08-07 1997-06-11 Hydraulic control device Ceased WO1998005870A1 (en)

Applications Claiming Priority (2)

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DE19631803.3 1996-08-07
DE19631803A DE19631803B4 (en) 1996-08-07 1996-08-07 Hydraulic control device

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DE102009021103A1 (en) * 2009-05-13 2010-11-18 Hydac Filtertechnik Gmbh Hydraulic valve device
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