EP0857326B1 - Flow-control valve - Google Patents

Flow-control valve Download PDF

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Publication number
EP0857326B1
EP0857326B1 EP96929320A EP96929320A EP0857326B1 EP 0857326 B1 EP0857326 B1 EP 0857326B1 EP 96929320 A EP96929320 A EP 96929320A EP 96929320 A EP96929320 A EP 96929320A EP 0857326 B1 EP0857326 B1 EP 0857326B1
Authority
EP
European Patent Office
Prior art keywords
flow control
valve
control valve
restrictor orifice
spring
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.)
Expired - Lifetime
Application number
EP96929320A
Other languages
German (de)
French (fr)
Other versions
EP0857326A1 (en
Inventor
Jürgen ZÜGNER
Karl Cords
Hans Müller
Michael Schulte
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
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Publication date
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Publication of EP0857326A1 publication Critical patent/EP0857326A1/en
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7784—Responsive to change in rate of fluid flow
    • Y10T137/7787—Expansible chamber subject to differential pressures
    • Y10T137/7788—Pressures across fixed choke

Definitions

  • the invention relates to a flow control valve according to the Preamble of claim 1.
  • Such flow control valves are then preferred used when in a hydraulic system, for example Cylinders and engines with different and fluctuating Load pressures with a preselected, constant volume flow should be supplied. That is, the flow control valve determines the inflow of useful power for the Consumers, for example the hydraulic cylinder or the Hydraulic motor.
  • the flow control valve determines the inflow of useful power for the Consumers, for example the hydraulic cylinder or the Hydraulic motor.
  • the Arrangement in the inlet to the consumer in the Sequence of the consumer (secondary control) or in one Bypass line of the hydraulic pump (bypass control) provided can be.
  • Such a known flow control valve 1 has one Valve housing 2 with an axial bore as a valve bore 4, which opens on the one hand in an input port P and on the other hand closed by a throttle body 6 is, which is axially displaceably mounted in the valve bore is, the setting of the axial position via an adjusting device 8 takes place in the axial direction from the outside is accessible from here.
  • the throttle body 6 has a throttle bolt 10, which protrudes into a throttle bushing 12, so that by the interaction of the throttle pin 10 and Throttle bushing 12 the effective cross section of the orifice plate adjustable by axial displacement of the throttle body 6 is.
  • the throttle bushing 12 is on an end face of the Valve bore 4 supported and in the area of the throttle pin 10 provided with radial bores 14 through which one Connection of the input port P to an output termination A is done.
  • the throttle bushing 12 is supported by a control spring 16, which in turn biases a valve spool 18 which in the valve bore 4 is guided axially and over its end section distant from the spring side the opening cross-section of the output connection A or is controllable.
  • the valve spool 18 has an inner bore, so that the connection P over the inner bore of the valve spool, the throttle bushing (orifice plate) 12, the radial bores 14 are connected to the output connection A. is. With an inflow in the direction of the valve longitudinal axis the liquid flows through the inner bore of the valve spool 18 and through the adjustable annular gap the orifice towards the regulated output.
  • valve spool 18 in the 1 shifted to the left so that this is the volume flow to the regulated output connection A throttled and thus the pressure difference at the orifice is kept constant. Because of this constant pressure drop The regulated output volume flow is also above the orifice regardless of the pressure fluctuations at the inlet connection P kept constant.
  • the valve spool can control the cross-section of the outlet connection Only change when the spring force of the Rule spring 16 is overcome. So that means if the Pressure difference across the orifice plate is greater than the spring force divided by the effective valve spool area.
  • Such flow control valves can also be reversed Direction, that is from port A to port P flow through, and then act as a check valve, where in the check function the pressure loss from the Setting the orifice plate (throttle pin 10, throttle bush 12) is dependent. That is, in use as a check valve, the control spring 16 acts as a check spring.
  • a flow control valve is disclosed in DE-A1 33 43 960, with a non-return actuator on the outer circumference of the valve spool is mounted to radial bores in the check function open the valve spool so that the orifice plate is circumvented.
  • the invention is based on the object to create a flow control valve that is reversed Flow has an improved function.
  • the spring rate in an optimal manner to the pressure conditions for the reverse flow are adaptable, the functionality of the Flow control valve with a flow in reverse Direction compared to conventional solutions be improved.
  • the spring rate of the return spring can are designed to be lower than the spring rate of Control spring, so that on the one hand the function of the flow control valve in "normal flow direction" by suitable Selection of the control spring and on the other hand the function of the non-return valve with reverse flow can be optimized by suitable selection of the return spring are.
  • Valve slides forming a control orifice are constructed in the form of a bush is so that it flows through its inner bore becomes and coaxial to an orifice sleeve in the Inner bore is guided.
  • this is Non-return actuator formed by a non-return piston, which is guided axially displaceably in the valve slide and the one against the check spring against one on the orifice plate trained seat is biased so that against the preload of the non-return spring of the non-return piston can be lifted off the orifice sleeve and the bypass channel is therefore taxable.
  • the effect of the check actuator in this case is essentially determined by the pressure drop in the area of the seat on the orifice sleeve and the spring rate of the return spring.
  • control spring on an end face remote from the orifice sleeve, preferably a radial shoulder of the check piston is supported.
  • the control spring is preferably on the orifice side End section of the valve spool of the control orifice supported so that installation space can be saved and a control spring can be used with a comparatively large outside diameter is.
  • the support takes place the control spring preferably on an axial collar of the Valve spool, which is via the output connection A extends and which is penetrated by axial bores over which the spring chamber into which the measuring orifice opens is connected to the output terminal A.
  • the Bypass channel through radial holes in the orifice sleeve formed by the valve spool against the bias the check spring can be opened.
  • the valve slide inner bore is supported, that is The control spring is located inside the valve spool.
  • the valve slide acts in this embodiment also as a non-return actuator
  • control spring is advantageously supported on the valve slide by interposing one Support bushing, whose other end section on the valve housing is supported, the support bushing the return spring interspersed advantageously in the axial direction.
  • the output port of the flow control valve and the Orifice plate output can with an expanding cross section formed according to subclaims 13 and 14 become.
  • Fig. 2 shows a longitudinal section through a first embodiment a flow control valve 1, which as a built-in valve is trained.
  • the flow control valve 1 has a valve housing 2 that can be screwed into a valve block via a threaded section is.
  • the right end of the flow control valve in Fig. 2 is formed by an end screw 20, in which a through hole is formed as an input port P. is.
  • An output connection is at an axial distance from the input connection P A formed in the embodiment shown by two radial bore stars arranged in series 21 and 22 is formed, of which the radial bore 21 has a smaller diameter than that Radial bore 22. Between the two radial bores 21, 22 remains a partition, which is connected via a connecting hole 24 is bridged in the valve housing 2, this Connection bore 24 is indicated by dashed lines in FIG. 2.
  • the left end section of the valve bore 4 in FIG. 2 is formed by a reducer 26 which is in a radial extended and provided with a threaded section End portion of the valve bore 4 is screwed.
  • a radial downgrade takes place via the reducer 26 the valve bore 4, wherein an internally threaded portion the reducer 26 is in threaded engagement with one Spindle 28, the actuating sections 30 axially from the Reducer 26 protrudes outwards and thus for the Operator is accessible.
  • a throttle pin in a known manner 10 rotatably mounted so that an adjustment movement the spindle 28 in an axial movement of the throttle pin 10 is implemented.
  • the throttle pin 10 dips with his cantilevered end section in a diaphragm or throttle box 12 a, which on the adjacent end face of the Reducer 26 is supported.
  • the orifice sleeve is at least one throttle opening 32 formed, which in the embodiment shown Has a triangular window shape that extends away from the throttle bolt 10 tapered.
  • the orifice sleeve 12 is between the end face of the reducer 26 and a contact surface of the valve bore 4 clamped with a radial shoulder. At this the control spring 16 is supported so that this the orifice sleeve 12 surrounds.
  • control spring 16 is in contact a valve spool 18 through which the radial bores 21 and 22 and 24 of the output connection A can be opened or closed are.
  • the valve spool is in the basic position shown 18 with its end section removed from the control spring 16 on the end screw 20 so that the connection holes 21 and 22 are controlled.
  • the valve spool 18 is provided with an attachment collar 34 on which the control spring 16 attacks.
  • the outside circumference of the investment association 34 is slightly smaller than that in the valve bore guided part of the valve spool 18 is formed.
  • An annular groove 36 is located at an axial distance from the contact collar 34 formed, which - in the basic position shown in Fig. 2 - Arranged approximately in the region of the radial bores 21, 22 and its width is roughly equal to the total width (Representation according to FIG. 2) of the two end-to-end occupants Radial bores 21, 22 is adapted.
  • Fig. 3 shows a front view of the valve spool 18 seen from the control spring side. As can be seen from it is, there are four in the area of the investment association 34 Axial bores 38 provided on a common Pitch circle, whose diameter is about the diameter corresponds to the valve bore 4.
  • the axial bores 38 extend up to that in FIG Fig. 2 right side wall of the annular groove 36, so that about the annular groove 36 and the axial bores 38 a connection of the spring chamber 40 can be produced with the output connection A. is.
  • Valve slide 18 and output port A thus act as a control orifice via which the pressure drop across the orifice plate 32 (throttle pin 10, orifice plate sleeve 12) adjustable is.
  • the one End section protrudes into the spring chamber 40 and on a valve seat 46 of the orifice sleeve 12 in plant can be brought so that the latter and the check piston 44th are arranged coaxially to each other.
  • the non-return piston 44 is via a return spring 48 in the direction of Valve seat 46 biased.
  • the check spring 48 supports on the one hand on the outer circumference of the non-return piston 44 attached support ring and the other on the End screw 20 from.
  • the hydraulic fluid When used as a flow control valve, that is When flowing from P to A, the hydraulic fluid flows axially into the flow control valve, flows through it in its shown non-return piston 44 and enters the orifice plate. Their more effective Cross section is through an appropriate setting of the Throttle pin 10 specified so that the hydraulic fluid flows through the throttle opening 32 and into the spring chamber 40 entry. This is where the hydraulic fluid comes from Axial bore 38 of the valve spool 18 via the annular groove 36 towards the output connection A.
  • the flow control valve according to the invention corresponds 1 a conventional flow control valve, as in Fig. 1 is shown.
  • valve housing 2 of this embodiment an axially extending valve bore 4 is again formed, whose left end section in FIG. 4 has an internal thread is provided, which is in engagement with the Outer periphery of a spindle 50 on its rear End carries an operating section and over which Valve bore 4 is completed.
  • the Input port P is formed at the other end section of the valve housing 2 at the other end section of the valve housing 2 at the other end section of the valve housing 2 .
  • the output port A opens again as radial bore star of the valve housing 2 in the inner bore 4.
  • the throttle pin 10 is rotatable in the spindle 50 set so that by appropriate adjustment the spindle 50 an axial movement of the throttle pin 10 is effected. Its cantilevered end section is immersed in the orifice sleeve 12, which with radial bores 32nd is provided, which can be opened or closed by the throttle bolt is.
  • the orifice sleeve 12 is supported on a support ring, that in the valve bore 4 of the valve housing 2 is attached and also an axial stop for the Spindle 50 forms (see illustration in FIG. 4). In the The basic position shown is that acting as a throttle opening Radial bore 32 of the orifice sleeve 12 shut off or reduced to their smallest cross section.
  • FIG Orifice plate sleeve 12 dips into valve slide 18, which is axially displaceable in the valve bore 4 is.
  • a radial bore star 52 is provided which is shown in FIG Home position from the inner peripheral wall of the valve spool 18 is closed or covered.
  • valve spool 18 which is constructed in the form of a sleeve, is biased into its starting position via the control spring 16, the output port A is completely open is.
  • the left end section of the control spring in FIG. 4 16 is supported on the end face of the orifice sleeve 12, while the other end section on a support bushing 54 attacks, which is axially displaceable in a guide bush 56 is guided, which in turn on the front side of the valve housing 2 is supported in the axial direction is.
  • the in the inner bore 42 of the valve spool 18th immersed end portion of the support bush 54 is with a Radial collar provided that a contact surface for the crizfeder 16 forms and in turn with his of the contact surface of the control spring 16 distal end face can be brought into contact with an inner end face section of the valve slide 18.
  • a contact surface for the crizfeder 16 forms and in turn with his of the contact surface of the control spring 16 distal end face can be brought into contact with an inner end face section of the valve slide 18.
  • On the right in Fig. 4 The end face of the valve slide 18 engages the non-return spring 48, the other end section of the guide bush 56 and thus supported on the valve housing 2.
  • valve arrangement When using this valve arrangement as a flow control valve, that is, when flowing from P to A occurs the hydraulic fluid through the support bush 54, the valve spool 18 and the of the orifice sleeve 12 and the Throttle bolt 10 formed orifice cross section towards Throttle opening 32 and from there to the output connection A.
  • the predetermined limit value When the pressure drop rises above the orifice plate the predetermined limit value is compressed the control spring 16, so that the valve spool 18 in the illustration 4 axially shifted to the left and the output connection A is controlled.
  • This tax movement is the support bush 54 by the valve spool 18th brought along, so that this also along an axial movement the guide bush 56 performs.
  • valve spool 18 Due to the axial movement of the valve spool 18 in turn ensures that the pressure drop across the orifice remains constant.
  • Fig. 4 moves to the right so that there is a relative displacement between the valve slide 18 and the support bush 54 sets that on the end face of the valve housing 2 is supported. Due to the resulting axial movement of the valve spool 18 becomes the radial bore star 52 opened so that a bypass channel opened is that allows a circumvention of the orifice plate, so that the hydraulic fluid directly from the output port A through through the radial bore star 52, through the valve spool 18 and the support bush 54 towards the input connection P can flow.
  • valve spool 18 When the pressure builds up from P to A, the valve spool 18 again moved to the left so that the radial bore star 52 is controlled.
  • the spring rate of the non-return spring can also be used in this variant 48 in a simple way to the operating conditions be adjusted for a reverse flow, without changing the standard spring rate.

Description

Die Erfindung betrifft ein Stromregelventil gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a flow control valve according to the Preamble of claim 1.

Derartige Stromregelventile werden bevorzugt dann eingesetzt, wenn in einem Hydrauliksystem beispielsweise Zylinder und Motoren mit unterschiedlichen und schwankenden Lastdrücken mit je einem vorgewählten, konstanten Volumenstrom versorgt werden sollen. Das heißt, das Stromregelventil bestimmt den zufließenden Nutzstrom für den Verbraucher, beispielsweise den Hydrozylinder oder den Hydromotor. Prinzipiell gibt es drei Anordnungsmöglichkeiten für Stromregelventile in Hydrosystemen, wobei die Anordnung im Zulauf zum Verbraucher (Primärsteuerung) im Ablauf des Verbrauchers (Sekundärsteuerung) oder in einer Bypass-Leitung der Hydropumpe (Bypass-Steuerung) vorgesehen sein kann.Such flow control valves are then preferred used when in a hydraulic system, for example Cylinders and engines with different and fluctuating Load pressures with a preselected, constant volume flow should be supplied. That is, the flow control valve determines the inflow of useful power for the Consumers, for example the hydraulic cylinder or the Hydraulic motor. In principle there are three possible arrangements for flow control valves in hydraulic systems, the Arrangement in the inlet to the consumer (primary control) in the Sequence of the consumer (secondary control) or in one Bypass line of the hydraulic pump (bypass control) provided can be.

Bei den bekannten Stromregelventilen wird durch Hintereinanderschalten einer fest einstellbaren Verengung, das heißt einer Meßblende und einer in Abhängigkeit von den veränderlichen Druckverhältnissen ansteuerbaren Druckwaage mit einem Ventilschieber (Regelblende) erreicht, daß das Druckgefälle an der Meßblende konstant bleibt, so daß ein konstanter Durchflußstrom durch das Stromregelventil einstellbar ist.In the known flow control valves, it is connected in series a fixed constriction, that is, an orifice plate and one depending on controllable the changing pressure conditions Pressure compensator reached with a valve slide (control orifice), that the pressure drop at the orifice is constant remains so that a constant flow through the Flow control valve is adjustable.

In Fig. 1, auf die bereits hier Bezug genommen wird, ist ein Zwei-Wege-Stromregelventil gezeigt, wie es beispielsweise im Datenblatt J2A 60 "2-Wege-Stromregelventil", S. J.07, J.08 der Anmelderin beschrieben ist. 1, to which reference is already made here, a two-way flow control valve is shown, for example in data sheet J2A 60 "2-way flow control valve", S. J.07, J.08 the applicant is described.

Ein derartiges bekanntes Stromregelventil 1 hat ein Ventilgehäuse 2 mit einer Axialbohrung als Ventilbohrung 4, die einerseits in einem Eingangsanschluß P mündet und andererseits durch einen Drosselkörper 6 verschlossen ist, der in der Ventilbohrung axial verschiebbar gelagert ist, wobei die Einstellung der Axiallage über eine Stelleinrichtung 8 erfolgt, die in Axialrichtung von außen her zugänglich ist. Der Drosselkörper 6 hat einen Drosselbolzen 10, der in eine Drosselbuchse 12 hineinragt, so daß durch Zusammenwirken des Drosselbolzens 10 und der Drosselbuchse 12 der wirksame Querschnitt der Meßblende durch Axialverschiebung des Drosselkörpers 6 einstellbar ist. Die Drosselbuchse 12 ist an einer Stirnfläche der Ventilbohrung 4 abgestützt und im Bereich des Drosselbolzens 10 mit Radialbohrungen 14 versehen, über die eine Verbindung des Eingangsanschlusses P mit einem Ausgangsabschluß A erfolgt.Such a known flow control valve 1 has one Valve housing 2 with an axial bore as a valve bore 4, which opens on the one hand in an input port P and on the other hand closed by a throttle body 6 is, which is axially displaceably mounted in the valve bore is, the setting of the axial position via an adjusting device 8 takes place in the axial direction from the outside is accessible from here. The throttle body 6 has a throttle bolt 10, which protrudes into a throttle bushing 12, so that by the interaction of the throttle pin 10 and Throttle bushing 12 the effective cross section of the orifice plate adjustable by axial displacement of the throttle body 6 is. The throttle bushing 12 is on an end face of the Valve bore 4 supported and in the area of the throttle pin 10 provided with radial bores 14 through which one Connection of the input port P to an output termination A is done.

An dem vom Drosselbolzen 10 entfernten Endabschnitt der Drosselbuchse 12 ist eine Regelfeder 16 abgestützt, die wiederum einen Ventilschieber 18 vorspannt, der in der Ventilbohrung 4 axial verschiebbar geführt ist und über dessen von der Federseite entfernten Endabschnitt der Öffnungsquerschnitt des Ausgangsanschlusses A auf- oder zusteuerbar ist. Der Ventilschieber 18 hat eine Innenbohrung, so daß der Anschluß P über die Innenbohrung des Ventilschiebers, die Drosselbuchse (Meßblende) 12, die Radialbohrungen 14 mit dem Ausgangsanschluß A verbunden ist. Bei einer Anströmung in Richtung der Ventillängsachse strömt die Flüssigkeit durch die Innenbohrung des Ventilschiebers 18 und durch den einstellbaren Ringspalt der Meßblende hin zum geregelten Ausgang. Sobald zwischen dem Eingangsanschluß P und dem geregelten Ausgangsanschluß A eine der Federrate entsprechende Druckdifferenz erreicht ist, wird der Ventilschieber 18 in der Darstellung nach Fig. 1 nach links verschoben, so daß dieser den Volumenstrom zum geregelten Ausgangsanschluß A abdrosselt und somit die Druckdifferenz an der Meßblende konstant gehalten wird. Durch diesen konstanten Druckabfall über der Meßblende wird auch der geregelte Ausgangsvolumenstrom unabhängig von den Druckschwankungen am Eingangsanschluß P konstant gehalten. Wie bereits erwähnt, kann der Ventilschieber den Querschnitt des Ausgangsanschlusses erst dann verändern, wenn die Federkraft der Regelfeder 16 überwunden wird. Das heißt also, wenn die Druckdifferenz über der Meßblende größer ist als die Federkraft geteilt durch die wirksame Ventilschieberfläche.At the end portion removed from the throttle pin 10 the throttle bushing 12 is supported by a control spring 16, which in turn biases a valve spool 18 which in the valve bore 4 is guided axially and over its end section distant from the spring side the opening cross-section of the output connection A or is controllable. The valve spool 18 has an inner bore, so that the connection P over the inner bore of the valve spool, the throttle bushing (orifice plate) 12, the radial bores 14 are connected to the output connection A. is. With an inflow in the direction of the valve longitudinal axis the liquid flows through the inner bore of the valve spool 18 and through the adjustable annular gap the orifice towards the regulated output. As soon as between the input port P and the regulated output port A is a pressure difference corresponding to the spring rate is reached, the valve spool 18 in the 1 shifted to the left so that this is the volume flow to the regulated output connection A throttled and thus the pressure difference at the orifice is kept constant. Because of this constant pressure drop The regulated output volume flow is also above the orifice regardless of the pressure fluctuations at the inlet connection P kept constant. As already mentioned, the valve spool can control the cross-section of the outlet connection Only change when the spring force of the Rule spring 16 is overcome. So that means if the Pressure difference across the orifice plate is greater than the spring force divided by the effective valve spool area.

Derartige Stromregelventile können auch in umgekehrter Richtung, das heißt vom Anschluß A hin zum Anschluß P durchströmt werden, und wirken dann als Rückschlagventil, wobei in der Rückschlagfunktion der Druckverlust von der Einstellung der Meßblende (Drosselbolzen 10, Drosselbuchse 12) abhängig ist. Das heißt, bei der Verwendung als Rückschlagventil wirkt die Regelfeder 16 als Rückschlagfeder.Such flow control valves can also be reversed Direction, that is from port A to port P flow through, and then act as a check valve, where in the check function the pressure loss from the Setting the orifice plate (throttle pin 10, throttle bush 12) is dependent. That is, in use as a check valve, the control spring 16 acts as a check spring.

Bei Einsatz eines derartigen Stromregelventils als Rückschlagventil hat sich jedoch gezeigt, daß die Rückschlagfunktion aufgrund der vergleichsweise hohen Federrate der Regelfeder 16 nur in wenigen Fällen den Anforderungen genügt. Genauer gesagt erfolgte die Zusteuerung des Ausgangsanschlusses A nur bei derart hohen Druckgefällen zwischen Anschluß P und dem Ausgang der Meßblende, daß der Einsatz des Stromregelventils nur auf verhältnismäßig wenig Anwendungsfälle beschränkt war.When using such a flow control valve as Check valve has been shown, however, that the check function due to the comparatively high spring rate the control spring 16 only in a few cases the requirements enough. More specifically, the control was made the output port A only at such high pressure drops between port P and the outlet of the orifice plate, that the use of the flow control valve is only proportional few use cases was limited.

In der DE-A1 33 43 960 ist ein Stromregelventil offenbart, bei dem ein Rückschlagstellglied am Aussenumfang des Ventilschiebers gelagert ist, um in der Rückschlagfunktion Radialbohrungen des Ventilschiebers aufzusteuern, so daß die Meßblende umgangen wird.A flow control valve is disclosed in DE-A1 33 43 960, with a non-return actuator on the outer circumference of the valve spool is mounted to radial bores in the check function open the valve spool so that the orifice plate is circumvented.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, ein Stromregelventil zu schaffen, das bei umgekehrter Durchströmung eine verbesserte Funktion aufweist. In contrast, the invention is based on the object to create a flow control valve that is reversed Flow has an improved function.

Diese Aufgabe wird durch die Merkmale der Patentansprüche 1 und 7 gelöst.This object is achieved through the features of the claims 1 and 7 solved.

Durch die Maßnahme, das Stromregelventil mit einem Rückschlagstellglied zu versehen, über das ein Bypass-Kanal zur Umgehung der Meßblende aufsteuerbar ist, wobei die Bewegung des Rückschlagstellgliedes gegen eine Rückschlagfeder erfolgt, deren Federrate in optimaler Weise an die Druckverhältnisse bei der umgekehrten Durchströmung anpaßbar sind, kann die Funktionsfähigkeit des Stromregelventils bei einer Durchströmung in umgekehrter Richtung gegenüber herkömmlichen Lösungen ganz erheblich verbessert werden. Die Federrate der Rückschlagfeder kann dabei geringer ausgelegt werden, als die Federrate der Regelfeder, so daß einerseits die Funktion des Stromregelventils in "normaler Durchströmungsrichtung" durch geeignete Auswahl der Regelfeder und andererseits die Funktion des Rückschlagstellgliedes bei umgekehrter Durchströmung durch geeignete Auswahl der Rückschlagfeder optimierbar sind.By taking the flow control valve with a To provide non-return actuator via a bypass channel to bypass the orifice plate can be opened, whereby the movement of the check actuator against a check spring takes place, the spring rate in an optimal manner to the pressure conditions for the reverse flow are adaptable, the functionality of the Flow control valve with a flow in reverse Direction compared to conventional solutions be improved. The spring rate of the return spring can are designed to be lower than the spring rate of Control spring, so that on the one hand the function of the flow control valve in "normal flow direction" by suitable Selection of the control spring and on the other hand the function of the non-return valve with reverse flow can be optimized by suitable selection of the return spring are.

Im vorliegenden Fall wird es bevorzugt, wenn der die Regelblende bildende Ventilschieber buchsenförmig aufgebaut ist, so daß er entlang seiner Innenbohrung durchströmt wird und koaxial zu einer Meßblendenbüchse in der Innenbohrung geführt ist.In the present case, it is preferred if the Valve slides forming a control orifice are constructed in the form of a bush is so that it flows through its inner bore becomes and coaxial to an orifice sleeve in the Inner bore is guided.

Bei einem bevorzugten Ausführungsbeispiel ist das Rückschlagstellglied durch einen Rückschlagkolben gebildet, der axial verschiebbar im Ventilschieber geführt ist und der über die Rückschlagfeder gegen einen an der Meßblende ausgebildeten Sitz vorspannbar ist, so daß gegen die Vorspannung der Rückschlagfeder der Rückschlagkolben von der Meßblendenbüchse abhebbar und der Bypass-Kanal somit aufsteuerbar ist. Die Wirkung des Rückschlagstellgliedes ist in diesem Fall im wesentlichen bestimmt durch den Druckabfall im Bereich des Sitzes an der Meßblendenbüchse und von der Federrate der Rückschlagfeder.In a preferred embodiment, this is Non-return actuator formed by a non-return piston, which is guided axially displaceably in the valve slide and the one against the check spring against one on the orifice plate trained seat is biased so that against the preload of the non-return spring of the non-return piston can be lifted off the orifice sleeve and the bypass channel is therefore taxable. The effect of the check actuator in this case is essentially determined by the pressure drop in the area of the seat on the orifice sleeve and the spring rate of the return spring.

Bei diese Variante wird es bevorzugt, daß die Regelfeder an einer von der Meßblendenbüchse entfernten Stirnseite, vorzugsweise einer Radialschulter des Rückschlagkolbens abgestützt ist.In this variant, it is preferred that the control spring on an end face remote from the orifice sleeve, preferably a radial shoulder of the check piston is supported.

Die Regelfeder wird bevorzugterweise an dem meßblendenseitigen Endabschnitt des Ventilschiebers der Regelblende abgestützt, so daß Bauraum einsparbar und eine Regelfeder mit vergleichsweise großem Außendurchmesser einsetzbar ist.The control spring is preferably on the orifice side End section of the valve spool of the control orifice supported so that installation space can be saved and a control spring can be used with a comparatively large outside diameter is.

Bei diesem Ausführungsbeispiel erfolgt in die Abstützung der Regelfeder vorzugsweise an einem Axialbund des Ventilschiebers, der sich über den Ausgangsanschluß A hinaus erstreckt und der von Axialbohrungen durchsetzt ist, über die der Federraum, in den die Meßblende mündet mit dem Ausgangsanschluß A verbunden ist.In this embodiment, the support takes place the control spring preferably on an axial collar of the Valve spool, which is via the output connection A extends and which is penetrated by axial bores over which the spring chamber into which the measuring orifice opens is connected to the output terminal A.

Die Abstützung der Rückschlagfeder und die Relativanordnung des Rückschlagkolbens zur Meßblendenbüchse erfolgt vorteilhafterweise nach den Weiterbildungen gemäß den Unteransprüchen 6 und 7.The support of the return spring and the relative arrangement of the non-return piston to the orifice sleeve advantageously according to the further developments subclaims 6 and 7.

Gemäß einer weiteren Konstruktionsvariante wird der Bypass-Kanal durch Radialbohrungen der Meßblendenbüchse gebildet, die vom Ventilschieber gegen die Vorspannung der Rückschlagfeder aufsteuerbar ist. In diesem Ausführungsbeispiel ist die Regelfeder an einer Radialschulter der Ventilschieber-Innenbohrung abgestützt, das heißt die Regelfeder ist innerhalb des Ventilschiebers angeordnet. Der Ventilschieber wirkt bei diesem Ausführungsbeispiel auch als Rückschlagstellglied According to a further design variant, the Bypass channel through radial holes in the orifice sleeve formed by the valve spool against the bias the check spring can be opened. In this embodiment is the standard spring on a radial shoulder the valve slide inner bore is supported, that is The control spring is located inside the valve spool. The valve slide acts in this embodiment also as a non-return actuator

Vorteilhafterweise erfolgt die Abstützung der Regelfeder am Ventilschieber durch Zwischenschalten einer Stützbuchse, deren anderer Endabschnitt am Ventilgehäuse abgestützt ist, wobei die Stützbuchse die Rückschlagfeder vorteilhafterweise in Axialrichtung durchsetzt.The control spring is advantageously supported on the valve slide by interposing one Support bushing, whose other end section on the valve housing is supported, the support bushing the return spring interspersed advantageously in the axial direction.

Der Ausgangsanschluß des Stromregelventils und der Meßblendenausgang können mit sich erweiterndem Querschnitt gemäß den Unteransprüchen 13 und 14 ausgebildet werden.The output port of the flow control valve and the Orifice plate output can with an expanding cross section formed according to subclaims 13 and 14 become.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der sonstigen Unteransprüche.Further advantageous embodiments of the invention are the subject of other subclaims.

Im folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Fig. 1 ein herkömmliches Stromregelventil;
  • Fig. 2 einen Längsschnitt durch ein erstes Ausführungsbeispiel eines erfindungsgemäßen Stromregelventils;
  • Fig. 3 ein Bauelement des Stromregelventils aus Fig. 2 und
  • Fig. 4 einen Längsschnitt durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen Stromregelventils.
    • Preferred exemplary embodiments of the invention are explained in more detail below with the aid of schematic drawings. Show it:
  • 1 shows a conventional flow control valve;
  • 2 shows a longitudinal section through a first exemplary embodiment of a flow control valve according to the invention;
  • Fig. 3 shows a component of the flow control valve from Fig. 2 and
  • Fig. 4 shows a longitudinal section through a second embodiment of a flow control valve according to the invention.

    • Fig. 2 zeigt einen Längsschnitt durch ein erstes Ausführungsbeispiel eines Stromregelventils 1, das als Einbauventil ausgebildet ist.Fig. 2 shows a longitudinal section through a first embodiment a flow control valve 1, which as a built-in valve is trained.

    Der Einfachheit halber werden im folgenden für einander entsprechende Bauelemente die gleichen Bezugszeichen verwendet, wie sie bereits bei der Beschreibung des Standes der Technik in Fig. 1 zugeordnet wurden. For the sake of simplicity, the following are for each other corresponding components have the same reference numerals used as already in the description of the state were assigned to the technology in FIG. 1.

    Das Stromregelventil 1 hat ein Ventilgehäuse 2, das über einen Gewindeabschnitt in einen Ventilblock einschraubbar ist. Der in Fig. 2 rechte Abschluß des Stromregelventils ist durch eine Abschlußschraube 20 gebildet, in der eine Durchgangsbohrung als Eingangsanschluß P ausgebildet ist.The flow control valve 1 has a valve housing 2 that can be screwed into a valve block via a threaded section is. The right end of the flow control valve in Fig. 2 is formed by an end screw 20, in which a through hole is formed as an input port P. is.

    Im Axialabstand zum Eingangsanschluß P ist ein Ausgangsanschluß A ausgebildet, der beim gezeigten Ausführungsbeispiel durch zwei in Reihe angeordnete Radialbohrungssterne 21 und 22 gebildet ist, von denen die Radialbohrung 21 einen geringeren Durchmesser aufweist als die Radialbohrung 22. Zwischen den beiden Radialbohrungen 21, 22 verbleibt eine Trennwandung, die über eine Verbindungsbohrung 24 im Ventilgehäuse 2 überbrückt ist, diese Verbindungsbohrung 24 ist in Fig. 2 gestrichelt angedeutet.An output connection is at an axial distance from the input connection P A formed in the embodiment shown by two radial bore stars arranged in series 21 and 22 is formed, of which the radial bore 21 has a smaller diameter than that Radial bore 22. Between the two radial bores 21, 22 remains a partition, which is connected via a connecting hole 24 is bridged in the valve housing 2, this Connection bore 24 is indicated by dashed lines in FIG. 2.

    Der in Fig. 2 linke Endabschnitt der Ventilbohrung 4 ist durch ein Reduzierstück 26 gebildet, das in einem radial erweiterten und mit einem Gewindeabschnitt versehenen Endabschnitt der Ventilbohrung 4 eingeschraubt ist. Über das Reduzierstück 26 erfolgt eine radiale Zurückstufung der Ventilbohrung 4, wobei ein Innengewindeabschnitt des Reduzierstücks 26 in Gewindeeingriff steht mit einer Spindel 28, deren Betätigungsabschnitte 30 axial aus dem Reduzierstück 26 nach außen vorsteht und somit für die Bedienperson zugänglich ist.The left end section of the valve bore 4 in FIG. 2 is formed by a reducer 26 which is in a radial extended and provided with a threaded section End portion of the valve bore 4 is screwed. A radial downgrade takes place via the reducer 26 the valve bore 4, wherein an internally threaded portion the reducer 26 is in threaded engagement with one Spindle 28, the actuating sections 30 axially from the Reducer 26 protrudes outwards and thus for the Operator is accessible.

    In der Spindel 28 ist in bekannter Weise ein Drosselbolzen 10 drehbar gelagert, so daß eine Verstellbewegung der Spindel 28 in eine Axialbewegung des Drosselbolzens 10 umgesetzt wird. Der Drosselbolzen 10 taucht mit seinem auskragenden Endabschnitt in eine Blenden- oder Drosselbüchse 12 ein, die an der benachbarten Stirnfläche des Reduzierstücks 26 abgestützt ist. In der Umfangswandung der Meßblendenbüchse ist zumindest eine Drosselöffnung 32 ausgebildet, die beim gezeigten Ausführungsbeispiel die Form eines Dreieckfensters hat, das sich weg vom Drosselbolzen 10 verjüngt.In the spindle 28 is a throttle pin in a known manner 10 rotatably mounted so that an adjustment movement the spindle 28 in an axial movement of the throttle pin 10 is implemented. The throttle pin 10 dips with his cantilevered end section in a diaphragm or throttle box 12 a, which on the adjacent end face of the Reducer 26 is supported. In the peripheral wall the orifice sleeve is at least one throttle opening 32 formed, which in the embodiment shown Has a triangular window shape that extends away from the throttle bolt 10 tapered.

    Durch die Verstellung der Spindel 28 und die daraus resultierende Axialverschiebung läßt sich der Querschnitt der Drosselöffnung 32 und damit der wirksame Querschnitt der vom Drosselbolzen 10 und der Meßblendenbüchse 12 mit der Drosselöffnung 32 gebildeten Meßblende variieren.By adjusting the spindle 28 and the resulting resulting cross-section axial displacement the throttle opening 32 and thus the effective cross section of the throttle pin 10 and the orifice sleeve 12 with the orifice formed 32 vary.

    Die Meßblendenbüchse 12 ist zwischen der Stirnfläche des Reduzierstücks 26 und einer Anlagefläche der Ventilbohrung 4 mit einer Radialschulter eingespannt. An dieser ist die Regelfeder 16 abgestützt, so daß diese die Meßblendenbüchse 12 umgibt.The orifice sleeve 12 is between the end face of the reducer 26 and a contact surface of the valve bore 4 clamped with a radial shoulder. At this the control spring 16 is supported so that this the orifice sleeve 12 surrounds.

    Der andere Endabschnitt der Regelfeder 16 liegt an einem Ventilschieber 18 an, über den die Radialbohrungen 21 und 22 und 24 des Ausgangsanschlusses A auf- oder zusteuerbar sind.The other end section of the control spring 16 is in contact a valve spool 18 through which the radial bores 21 and 22 and 24 of the output connection A can be opened or closed are.

    In der gezeigten Grundposition liegt der Ventilschieber 18 mit seinem von der Regelfeder 16 entfernten Endabschnitt an der Abschlußschraube 20 an, so daß die Anschlußbohrungen 21 und 22 aufgesteuert sind. Der Ventilschieber 18 ist mit einem Anlagebund 34 versehen, an dem die Regelfeder 16 angreift. Der Außenumfang des Anlagebunds 34 ist geringfügig kleiner als der in der Ventilbohrung geführte Teil des Ventilschiebers 18 ausgebildet. Im Axialabstand zum Anlagebund 34 ist eine Ringnut 36 ausgebildet, die - in der in Fig. 2 gezeigten Grundstellung - etwa in dem Bereich der Radialbohrungen 21, 22 angeordnet ist und deren Breite etwa an die Gesamtbreite (Darstellung nach Fig. 2) der beiden nebeneinander Belegenden Radialbohrungen 21, 22 angepaßt ist. The valve spool is in the basic position shown 18 with its end section removed from the control spring 16 on the end screw 20 so that the connection holes 21 and 22 are controlled. The valve spool 18 is provided with an attachment collar 34 on which the control spring 16 attacks. The outside circumference of the investment association 34 is slightly smaller than that in the valve bore guided part of the valve spool 18 is formed. An annular groove 36 is located at an axial distance from the contact collar 34 formed, which - in the basic position shown in Fig. 2 - Arranged approximately in the region of the radial bores 21, 22 and its width is roughly equal to the total width (Representation according to FIG. 2) of the two end-to-end occupants Radial bores 21, 22 is adapted.

    Fig. 3 zeigt eine Vorderansicht des Ventilschiebers 18 von der Regelfederseite aus gesehen. Wie daraus entnehmbar ist, sind im Bereich des Anlagebundes 34 vier Axialbohrungen 38 vorgesehen, die auf einem gemeinsamen Teilkreis liegen, dessen Durchmesser etwa dem Durchmesser der Ventilbohrung 4 entspricht.Fig. 3 shows a front view of the valve spool 18 seen from the control spring side. As can be seen from it is, there are four in the area of the investment association 34 Axial bores 38 provided on a common Pitch circle, whose diameter is about the diameter corresponds to the valve bore 4.

    Die Axialbohrungen 38 erstrecken sich bis zu der in Fig. 2 rechten Seitenwandung der Ringnut 36, so daß über die Ringnut 36 und die Axialbohrungen 38 eine Verbindung des Federraums 40 mit dem Ausgangsanschluß A herstellbar ist.The axial bores 38 extend up to that in FIG Fig. 2 right side wall of the annular groove 36, so that about the annular groove 36 and the axial bores 38 a connection of the spring chamber 40 can be produced with the output connection A. is.

    Ventilschieber 18 und Ausgangsanschluß A wirken somit als Regelblende, über die der Druckabfall an der Meßblende 32 (Drosselbolzen 10, Meßblendenbüchse 12) regelbar ist.Valve slide 18 and output port A thus act as a control orifice via which the pressure drop across the orifice plate 32 (throttle pin 10, orifice plate sleeve 12) adjustable is.

    Der buchsenförmig aufgebaute Ventilschieber 18 hat eine Innenbohrung 42, in der ein ebenfalls buchsenförmig aufgebauter Rückschlagkolben 44 geführt ist. Der mit einem Endabschnitt in den Federraum 40 hineinragt und an einen Ventilsitz 46 der Meßblendenbüchse 12 in Anlage bringbar ist, so daß letztere und der Rückschlagkolben 44 koaxial zueinander angeordnet sind. Der Rückschlagkolben 44 wird über eine Rückschlagfeder 48 in Richtung auf den Ventilsitz 46 vorgespannt. Die Rückschlagfeder 48 stützt sich einerseits an einem am Außenumfang des Rückschlagkolbens 44 befestigten Stützring und andererseits an der Abschlußschraube 20 ab. Zum besseren Verständis sei im folgenden die Funktion des Stromregelventils kurz beschrieben.The valve spool 18, which is constructed in the form of a sleeve, has an inner bore 42 in which is also a socket built-up check piston 44 is guided. The one End section protrudes into the spring chamber 40 and on a valve seat 46 of the orifice sleeve 12 in plant can be brought so that the latter and the check piston 44th are arranged coaxially to each other. The non-return piston 44 is via a return spring 48 in the direction of Valve seat 46 biased. The check spring 48 supports on the one hand on the outer circumference of the non-return piston 44 attached support ring and the other on the End screw 20 from. For better understanding, the following briefly describes the function of the flow control valve.

    Beim Einsatz als Stromregelventil, das heißt bei der Durchströmung von P nach A tritt das Hydraulikfluid axial in das Stromregelventil ein, durchströmt den sich in seiner dargestellten Grundposition befindlichen Rückschlagkolben 44 und tritt in die Meßblende ein. Deren wirksamer Querschnitt ist durch eine entsprechende Einstellung des Drosselbolzens 10 vorgegeben, so daß das Hydraulikfluid die Drosselöffnung 32 durchströmt und in den Federraum 40 eintritt. Von hier gelangt das Hydraulikfluid von der Axialbohrung 38 des Ventilschiebers 18 über die Ringnut 36 hin zum Ausgangsanschluß A.When used as a flow control valve, that is When flowing from P to A, the hydraulic fluid flows axially into the flow control valve, flows through it in its shown non-return piston 44 and enters the orifice plate. Their more effective Cross section is through an appropriate setting of the Throttle pin 10 specified so that the hydraulic fluid flows through the throttle opening 32 and into the spring chamber 40 entry. This is where the hydraulic fluid comes from Axial bore 38 of the valve spool 18 via the annular groove 36 towards the output connection A.

    Bei dieser Durchströmung des Stromregelventils wirkt der Hydraulikfluiddruck auf die Stirnseiten des Ventilschiebers 18, so daß bei einem entsprechenden Druckabfall innerhalb des Stromregelventils 1 - genauer gesagt entlang der Meßblende (Drosselbolzen 10, Meßblendenbüchse 12 mit Drosselöffnung 32) der Ventilschieber 18 gegen die Vorspannung der Regelfeder 16 aus seiner Anlageposition an der Abschlußschraube 20 abgehoben und in Axialrichtung nach links (Ansicht nach Fig. 2) bewegt wird. Dadurch wird der wirksame Querschnitt des Ausgangsanschlusses A zugesteuert, bis sich eine Gleichgewichtlage des Ventilschiebers 18 einstellt. Durch diese Stellbewegung des Ventilschiebers 18 ist gewährleistet, daß der Druckabfall über der Meßblende konstant bleibt.With this flow through the flow control valve acts the hydraulic fluid pressure on the face of the valve spool 18, so that with a corresponding pressure drop inside the flow control valve 1 - more precisely along the orifice plate (throttle pin 10, orifice plate sleeve 12 with throttle opening 32) of the valve slide 18 against the Biasing the control spring 16 from its contact position lifted off the end screw 20 and in the axial direction is moved to the left (view according to FIG. 2). Thereby the effective cross section of the output connection A controlled until there is an equilibrium position of the valve spool 18 sets. Through this movement of the Valve spool 18 ensures that the pressure drop remains constant above the orifice plate.

    Insoweit entspricht das erfindungsgemäße Stromregelventil 1 einem herkömmlichen Stromregelventil, wie es in Fig. 1 dargestellt ist.In this respect, the flow control valve according to the invention corresponds 1 a conventional flow control valve, as in Fig. 1 is shown.

    Bei umgekehrter Durchströmung, das heißt vom Ausgangsanschluß A hin zum Eingangsanschluß P wirkt der Fluiddruck am Anschluß A auf den sitzseitigen Endabschnitt des Rückschlagkolbens 44, so daß bei entsprechendem Druckaufbau am Anschluß A der Rückschlagkolben 44 von seinem Sitz 46 abgehoben wird und das Hydraulikfluid vom Anschluß A unter Umgehung der Meßblende direkt in den Innenraum des Rückschlagkolbens 44 und somit hin zum Eingangsanschluß P strömen kann. Die Stellbewegung des Rückschlagkolbens 44 ist vorgegeben durch die wirksame Kolbenfläche und die Federrate der Rückschlagfeder 48, so daß bei entsprechender Abstimmung dieser beiden Größen eine optimale Anpassung an die Betriebsbedingungen bei umgekehrter Durchströmung erfolgen kann.With reverse flow, that is from the outlet connection A acts towards the input port P. Fluid pressure at port A on the seat end portion of the check piston 44, so that with appropriate Pressure build-up at port A of the check piston 44 from its seat 46 is lifted off and the hydraulic fluid from Connection A bypassing the measuring orifice directly into the interior of the check piston 44 and thus towards the inlet connection P can flow. The actuating movement of the check piston 44 is predetermined by the effective piston area and the spring rate of the return spring 48, so that with appropriate coordination of these two sizes an optimal adaptation to the operating conditions reverse flow can take place.

    Im normalen Betrieb, das heißt bei Durchströmung von P nach A wird der Rückschlagkolben 44 durch die Rückschlagfeder 48 und den Fluiddruck gegen seinen Sitz 46 gedrückt, so daß der Bypass-Kanal zur Umgehung der Meßblende geschlossen ist.In normal operation, that is, with a flow of P to A is the check piston 44 by the check spring 48 and the fluid pressure against its seat 46 pressed so that the bypass channel to bypass the orifice closed is.

    In Fig. 4 ist eine weitere Variante eines erfindungsgemäßen Stromregelventils 1 dargestellt, bei allerdings kein axial verschiebbarer Rückschlagkolben 44 vorgesehen ist.4 is a further variant of an inventive Flow control valve 1 shown, however no axially displaceable check piston 44 is provided is.

    In dem Ventilgehäuse 2 dieses Ausführungsbeispiels ist wieder eine axial verlaufende Ventilbohrung 4 ausgebildet, deren in Fig. 4 linker Endabschnitt mit einem Innengewinde versehen ist, das in Eingriff steht mit dem Außenumfang einer Spindel 50, die an ihrem rückwärtigen Ende einen Betätigungsabschnitt trägt und über die die Ventilbohrung 4 abgeschlossen ist.In the valve housing 2 of this embodiment an axially extending valve bore 4 is again formed, whose left end section in FIG. 4 has an internal thread is provided, which is in engagement with the Outer periphery of a spindle 50 on its rear End carries an operating section and over which Valve bore 4 is completed.

    Am anderen Endabschnitt des Ventilgehäuses 2 ist der Eingangsanschluß P ausgebildet. Der Ausgangsanschluß A mündet wieder als Radialbohrungsstern des Ventilgehäuses 2 in der Innenbohrung 4.At the other end section of the valve housing 2 is the Input port P is formed. The output port A opens again as radial bore star of the valve housing 2 in the inner bore 4.

    In der Spindel 50 ist der Drosselbolzen 10 drehbar festgelegt, so daß durch eine entsprechende Verstellung der Spindel 50 eine Axialbewegung des Drosselbolzens 10 bewirkt wird. Dessen auskragender Endabschnitt taucht in die Meßblendenbüchse 12 ein, die mit Radialbohrungen 32 versehen ist, die durch den Drosselbolzen auf- oder zusteuerbar ist.The throttle pin 10 is rotatable in the spindle 50 set so that by appropriate adjustment the spindle 50 an axial movement of the throttle pin 10 is effected. Its cantilevered end section is immersed in the orifice sleeve 12, which with radial bores 32nd is provided, which can be opened or closed by the throttle bolt is.

    Die Meßblendenbüchse 12 ist an einem Stützring abgestützt, der in der Ventilbohrung 4 des Ventilgehäuses 2 befestigt ist und der auch einen Axialanschlag für die Spindel 50 bildet (siehe Darstellung nach Fig. 4). In der gezeigten Grundstellung ist die als Drosselöffnung wirkende Radialbohrung 32 der Meßblendenbüchse 12 abgesperrt oder auf ihren geringsten Querschnitt verringert.The orifice sleeve 12 is supported on a support ring, that in the valve bore 4 of the valve housing 2 is attached and also an axial stop for the Spindle 50 forms (see illustration in FIG. 4). In the The basic position shown is that acting as a throttle opening Radial bore 32 of the orifice sleeve 12 shut off or reduced to their smallest cross section.

    Der von der Spindel 50 entfernte Endabschnitt der Meßblendenbüchse 12 taucht in den Ventilschieber 18 ein, der axial verschiebbar in der Ventilbohrung 4 geführt ist. In diesem Endabschnitt der Meßblendenbüchse 12 ist ein Radialbohrungsstern 52 vorgesehen, der in der gezeigten Grundposition von der Innenumfangswandung des Ventilschiebers 18 geschlossen oder abgedeckt ist.The end portion of FIG Orifice plate sleeve 12 dips into valve slide 18, which is axially displaceable in the valve bore 4 is. In this end section of the orifice sleeve 12 is a radial bore star 52 is provided which is shown in FIG Home position from the inner peripheral wall of the valve spool 18 is closed or covered.

    Der büchsenförmig aufgebaute Ventilschieber 18 ist über die Regelfeder 16 in seine Ausgangsposition vorgespannt, der der Ausgangsanschluß A vollständig aufgesteuert ist. Der in Fig. 4 linke Endabschnitt der Regelfeder 16 ist an der Stirnseite der Meßblendenbüchse 12 abgestützt, während der andere Endabschnitt an einer Stützbuchse 54 angreift, die axial verschiebbar in einer Führungsbuchse 56 geführt ist, die ihrerseits an der Stirnseite des Ventilgehäuses 2 in Axialrichtung abgestützt ist. Der in die Innenbohrung 42 des Ventilschiebers 18 eintauchende Endabschnitt der Stützbuchse 54 ist mit einem Radialbund versehen, der eine Anlagefläche für die Regelfeder 16 bildet und der seinerseits mit seiner von der Anlagefläche der Regelfeder 16 entfernten Stirnfläche in Anlage bringbar ist an einen Innenstirnflächenabschnitt des Ventilschiebers 18. An der in Fig. 4 rechten Stirnfläche des Ventilschiebers 18 greift die Rückschlagfeder 48 an, deren anderer Endabschnitt an der Führungsbuchse 56 und damit am Ventilgehäuse 2 abgestützt ist.The valve spool 18, which is constructed in the form of a sleeve, is biased into its starting position via the control spring 16, the output port A is completely open is. The left end section of the control spring in FIG. 4 16 is supported on the end face of the orifice sleeve 12, while the other end section on a support bushing 54 attacks, which is axially displaceable in a guide bush 56 is guided, which in turn on the front side of the valve housing 2 is supported in the axial direction is. The in the inner bore 42 of the valve spool 18th immersed end portion of the support bush 54 is with a Radial collar provided that a contact surface for the Regelfeder 16 forms and in turn with his of the contact surface of the control spring 16 distal end face can be brought into contact with an inner end face section of the valve slide 18. On the right in Fig. 4 The end face of the valve slide 18 engages the non-return spring 48, the other end section of the guide bush 56 and thus supported on the valve housing 2.

    In der Stützbuchse 54 sind ein oder mehrere Radialbohrungen 58 ausgebildet, über die der Federraum der Rückschlagfeder 48 mit dem Inneren der Stützbuchse 54 verbunden ist, so daß der Druck am Eingangsanschluß P auf die rechte Stirnfläche des Ventilschiebers 18 wirkt.There are one or more radial bores in the support bushing 54 58 formed, via which the spring chamber of the Non-return spring 48 with the interior of the support bush 54 is connected, so that the pressure at the input port P on the right end face of the valve spool 18 acts.

    Beim Einsatz dieser Ventilanordnung als Stromregelventil, das heißt bei Durchströmung von P nach A tritt das Hydraulikfluid durch die Stützbuchse 54, den Ventilschieber 18 und den von der Meßblendenbüchse 12 und dem Drosselbolzen 10 gebildeten Meßblendenquerschnitt hin zur Drosselöffnung 32 und von dort zum Ausgangsanschluß A. Beim Ansteigen des Druckabfalls über der Meßblende auf den vorgegebenen Grenzwert wird die Regelfeder 16 zusammengedrückt, so daß der Ventilschieber 18 in der Darstellung nach Fig. 4 axial nach links verschoben und der Ausgangsanschluß A zugesteuert wird. Bei dieser Steuerbewegung wird die Stützbuchse 54 durch den Ventilschieber 18 mitgenommen, so daß diese auch eine Axialbewegung entlang der Führungsbuchse 56 durchführt.When using this valve arrangement as a flow control valve, that is, when flowing from P to A occurs the hydraulic fluid through the support bush 54, the valve spool 18 and the of the orifice sleeve 12 and the Throttle bolt 10 formed orifice cross section towards Throttle opening 32 and from there to the output connection A. When the pressure drop rises above the orifice plate the predetermined limit value is compressed the control spring 16, so that the valve spool 18 in the illustration 4 axially shifted to the left and the output connection A is controlled. With this tax movement is the support bush 54 by the valve spool 18th brought along, so that this also along an axial movement the guide bush 56 performs.

    Durch die Axialbewegung des Ventilschiebers 18 ist wiederum gewährleistet, daß der Druckabfall über der Meßblende konstant bleibt.Due to the axial movement of the valve spool 18 in turn ensures that the pressure drop across the orifice remains constant.

    Bei der umgekehrten Durchströmung des Stromregelventils vom Anschluß A zum Anschluß P wirkt der am Ausgangsanschluß A wirkende Fluiddruck auf die benachbarte Stirnfläche des Ventilschiebers 18, so daß dieser mit einem Druck beaufschlagt wird, der entgegen der Federkraft der Rückschlagfeder 48 wirkt. Nach Überwinden der Federkraft 48 wird der Ventilschieber 18 in der Darstellung nach With the reverse flow through the flow control valve from port A to port P acts on the output port A fluid pressure acting on the adjacent face of the valve spool 18, so that this with a Pressure is applied against the spring force of the Non-return spring 48 acts. After overcoming the spring force 48 the valve spool 18 is shown in the illustration

    Fig. 4 nach rechts bewegt, so daß sich eine Relativ-Verschiebung zwischen dem Ventilschieber 18 und der Stützbuchse 54 einstellt, die an der Stirnfläche des Ventilgehäuses 2 abgestützt ist. Durch die resultierende Axialbewegung des Ventilschiebers 18 wird der Radialbohrungsstern 52 aufgesteuert, so daß ein Bypass-Kanal geöffnet wird, der eine Umgehung der Meßblende ermöglicht, so daß das Hydraulikfluid direkt vom Ausgangsanschluß A durch den Radialbohrungsstern 52 hindurch, durch den Ventilschieber 18 und die Stützbuchse 54 hin zum Eingangsanschluß P strömen kann.Fig. 4 moves to the right so that there is a relative displacement between the valve slide 18 and the support bush 54 sets that on the end face of the valve housing 2 is supported. Due to the resulting axial movement of the valve spool 18 becomes the radial bore star 52 opened so that a bypass channel opened is that allows a circumvention of the orifice plate, so that the hydraulic fluid directly from the output port A through through the radial bore star 52, through the valve spool 18 and the support bush 54 towards the input connection P can flow.

    Bei einem Druckaufbau von P nach A wird der Ventilschieber 18 wiederum nach links bewegt, so daß der Radialbohrungsstern 52 zugesteuert wird.When the pressure builds up from P to A, the valve spool 18 again moved to the left so that the radial bore star 52 is controlled.

    Auch bei dieser Variante kann die Federrate der Rückschlagfeder 48 auf einfache Weise an die Betriebsbedingungen bei einer umgekehrten Strömung angepaßt werden, ohne daß es eine Abänderung der Regelfederrate bedarf.The spring rate of the non-return spring can also be used in this variant 48 in a simple way to the operating conditions be adjusted for a reverse flow, without changing the standard spring rate.

    Beide Varianten zeichnen sich durch einen einfachen Aufbau bei optimaler Anpaßbarkeit an die Betriebsbedingungen aus.Both variants are characterized by a simple one Construction with optimal adaptability to the operating conditions out.

    Claims (14)

    1. A flow control valve including a restrictor orifice (32) arranged between an inlet port (P) and an outlet port (A) of the flow control valve (1), and a valve slide (18) whereby an opening cross-section (22) toward the outlet port (A) may be controlled open or closed in accordance with the pressure drop at the restrictor orifice (32) and which is biased into its opening direction by a control spring (16), and a check actuating element (44) biased toward the closed position by means of a check spring (48), wherein a bypass channel for bypassing the restrictor orifice (32) can be controlled open in the case of a reverse flow through the flow control valve (1), characterised in that the restrictor orifice (32) is formed at a restrictor orifice bush (12) which is fixed in one of the valve bores (4), separate from the valve slide (18), and has a variable opening cross-section (32), and that a bypass opening of the bypass channel may be controlled open by displacement of the check actuating element (44) relative to the restrictor orifice bush (12).
    2. The flow control valve according to claim 1, characterised in that a check piston (44) enabling a flow through it is guided in the inner bore (42) of the valve slide (18) as a check actuating element and biased against a seat (46) at the restrictor orifice entrance by means of the check spring (48), so that the bypass channel can be controlled open by raising the check piston (44) from the seat (46) in the case of a reverse flow.
    3. The flow control valve according to claim 2, characterised in that the control spring (16) is supported at a restrictor orifice-side front surface of the valve slide (18).
    4. The flow control valve according to claim 2 or 3, characterised in that the valve slide (18) includes a contact collar (34) for the control spring (16), which extends beyond the outlet port (A) and is penetrated by at least one axial bore (38) connecting the outlet port (A) to a spring cavity (40) of the valve slide (18).
    5. The flow control valve according to one of claims 2 to 4, characterised in that the seat (46) is formed at the restrictor orifice lining (12).
    6. The flow control valve according to one of claims 2 to 5, characterised in that the check spring (48) is on the one hand supported at a front surface portion of the check piston (44) which is removed from the restrictor orifice, and on the other hand at a terminal screw (20) forming the inlet port (P).
    7. A flow control valve including a restrictor orifice (32) arranged between an inlet port (P) and an outlet port (A) of the flow control valve (1), and a valve slide (18) whereby an opening cross-section toward the outlet port (A) may be controlled open or closed in accordance with the pressure drop at the restrictor orifice (32) and which is biased into its opening direction by a control spring (16), wherein a bypass channel for bypassing the restrictor orifice (32) can be controlled open in the case of a reverse flow through the flow control valve (1), characterised in that the valve slide additionally performs the function of a check actuating element for which purpose a check spring (48) biases the valve slide (18) in the closing direction of the bypass opening of the bypass channel, in that the restrictor orifice (32) is formed at a restrictor orifice bush (12) which is fixed in one of the valve bores (4), separate from the valve slide (18), and has a variable opening cross-section (32), and that at the restrictor orifice bush (12) the bypass opening of the bypass channel is formed which may be controlled open by displacement of the valve slide (18) relative to the restrictor orifice bush (12).
    8. The flow control valve according to claim 7, characterised in that the check spring (48) acts on an outlet-port side front surface of the valve slide (18), and that the control spring (16) is supported at a radial shoulder of the inner bore (42) of the valve slide (18) on the one hand, and on the other hand on a front surface of the restrictor orifice lining (12), one end portion of which plunges into the inner bore (42).
    9. The flow control valve according to claim 7 or 8, characterised in that the end portion of the restrictor orifice lining (12) is provided with at least one radial bore (52) which can be controlled open as a bypass channel through an axial displacement of the valve slide (18).
    10. The flow control valve according to one of claims 7 to 9, characterised in that the control spring (16) is supported at the front surface of the valve slide (18) by means of a support bush (54), one end portion of which is supported at the valve housing (2), and the other end portion of which plunges into the inner bore (42) and is provided with a radial shoulder which is biased against an internal shoulder of the valve slide (18) by means of the control spring (16).
    11. The flow control valve according to one of claims 7 to 10, characterised in that the check spring (48) is arranged coaxially with the support bush (54).
    12. The flow control valve according to one of the preceding claims, characterised in that the outlet port (A) is formed to have a widening sectional area, preferably by two radial bore stars spaced apart from each other.
    13. The flow control valve according to one of the preceding claims, characterised in that a throttle opening (32) of the restrictor orifice has the form of a triangular window.
    14. The flow control valve according to one of the preceding claims 2 to 13, characterised in that the inlet port (A) is connected to the restrictor orifice through the inner bore (42), and in that the valve slide (18) is guided coaxially with a restrictor orifice lining (12).
    EP96929320A 1995-10-24 1996-08-23 Flow-control valve Expired - Lifetime EP0857326B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE1995139521 DE19539521C2 (en) 1995-10-24 1995-10-24 Flow control valve
    DE19539521 1995-10-24
    PCT/EP1996/003735 WO1997015875A1 (en) 1995-10-24 1996-08-23 Flow-control valve

    Publications (2)

    Publication Number Publication Date
    EP0857326A1 EP0857326A1 (en) 1998-08-12
    EP0857326B1 true EP0857326B1 (en) 2000-06-21

    Family

    ID=7775609

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP96929320A Expired - Lifetime EP0857326B1 (en) 1995-10-24 1996-08-23 Flow-control valve

    Country Status (5)

    Country Link
    US (1) US5996615A (en)
    EP (1) EP0857326B1 (en)
    JP (1) JPH11515076A (en)
    DE (2) DE19539521C2 (en)
    WO (1) WO1997015875A1 (en)

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    DE10051492A1 (en) * 2000-10-17 2002-04-18 Aws Appbau Arnold Gmbh Flow control valve in form of co-axial valve has setting member in corm of control tube acting with valve seat
    US6688319B2 (en) 2002-04-10 2004-02-10 Flow Design, Inc. Flow regulating control valve and method for regulating fluid flow
    US6932107B2 (en) * 2003-06-24 2005-08-23 Flow Control Industries, Inc. Flow control valves
    DE10333236B4 (en) * 2003-07-21 2013-06-27 Volkswagen Ag Control valve for controlling a volume flow, in particular for controlling a coolant flow for cooling the clutch of a dual-clutch transmission of a motor vehicle
    DE102004019748A1 (en) * 2004-04-20 2005-11-17 Bosch Rexroth Ag Flow control valve
    GB2415029B (en) * 2004-06-12 2008-02-27 Demag Delaval Ind Turbomachine A hydraulic restrictor
    DE102006014446A1 (en) * 2006-03-29 2007-10-04 Schaeffler Kg Hydraulic fluid flow control valve for e.g. hydrostatic profiled rail guide, has adjusting part to adjust control characteristics of controller and with operating section accessible from outside of pipe to adjust another adjusting part
    WO2007127949A2 (en) 2006-04-27 2007-11-08 Sko Flo Industries, Inc. Flow control valve
    WO2007127986A2 (en) 2006-04-28 2007-11-08 Sko Flo Industries, Inc. Flow measuring apparatus including a piston movable in the flow barrel
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    CN109185249A (en) * 2018-09-28 2019-01-11 广东机电职业技术学院 A kind of car hydrostatic steering system automatic control flow valve

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    Also Published As

    Publication number Publication date
    JPH11515076A (en) 1999-12-21
    DE59605471D1 (en) 2000-07-27
    US5996615A (en) 1999-12-07
    WO1997015875A1 (en) 1997-05-01
    EP0857326A1 (en) 1998-08-12
    DE19539521A1 (en) 1997-04-30
    DE19539521C2 (en) 1999-01-07

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