EP0857326B1 - Stromregelventil - Google Patents
Stromregelventil Download PDFInfo
- 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
Links
Images
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
Claims (14)
- Stromregelventil mit einer Meßblende (32), die zwischen einem Eingangsanschluß (P) und einem Ausgangsanschluß (A) des Stromregelventils (1) angeordnet ist und mit einem Ventilschieber (18), über den in Abhängigkeit vom Druckabfall an der Meßblende (32) ein Öffnungsquerschnitt (22) zum Ausgangsanschluß (A) auf- oder zusteuerbar ist und der über eine Regelfeder (16) in seine Öffnungsrichtung vorgespannt ist und mit einem Rückschlagstellglied (44), das durch eine Rückschlagfeder (48) in Schließstellung vorgespannt ist, wobei bei umgekehrter Durchströmung des Stromregelventils (1) ein By-Pass-Kanal zur Umgehung der Meßblende (32) aufsteuerbar ist, dadurch gekennzeichnet, daß die Meßblende (32) an einer in einer der Ventilbohrungen (4) festgelegten, vom Ventilschieber (18) getrennten Meßblendenbuchse (12) mit veränderbarem Öffnungsquerschnitt (32) ausgebildet ist und eine By-Pass-Öffnung des By-Pass-Kanals durch eine Verschiebung des Rückschlagstellgliedes (44) mit Bezug zur Meßbiendenbuchse (12) aufsteuerbar ist.
- Stromregelventil nach Patentanspruch 1, dadurch gekennzeichnet, daß ein durchströmbarer Rückschlagkolben (44) als Rückschlagstellglied einer Innenbohrung (42) des Ventilschiebers (18) geführt ist und über die Rückschlagfeder (48) gegen einen Sitz (46) am Meßblendeneingang vorgespannt ist, so daß bei umgekehrter Durchströmung durch Abheben des Rückschlagkolbens (44) vom Sitz (46) der Bypass-Kanal aufsteuerbar ist.
- Stromregelventil nach Patentanspruch 2, dadurch gekennzeichnet, daß die Regelfeder (16) an einer meßblendenseitigen Stirnfläche des Ventilschiebers (18) abgestützt ist.
- Stromregelventil nach Patentanspruch 2 oder 3, dadurch gekennzeichnet, daß der Ventilschieber (18) eine sich über den Ausgangsanschluß (A) hinaus erstreckenden Anlagebund (34) für die Regelfeder (16) hat, der von zumindest einer Axialbohrung (38) durchsetzt ist, die den Ausgangsanschluß (A) mit einem Federraum (40) des Ventilschiebers (18) verbindet.
- Stromregelventil nach einem der Patentansprüche 2 bis 4, dadurch gekennzeichnet, daß der Sitz (46) an der Meßblendenbüchse (12) ausgebildet ist.
- Stromregelventil nach einem der Patentansprüche 2 bis 5, dadurch gekennzeichnet, daß die Rückschlagfeder (48) einerseits an einem von der Meßblende entfernten Stirnflächenabschnitt des Rückschlagkolbens (44) und andererseits an einer den Eingangsanschluß (P) bildenden Abschlußschraube (20) abgestützt ist.
- Stromregelventil mit einer Meßblende (32), die zwischen einem Eingangsanschluß (P) und einem Ausgangsanschluß (A) des Stromregelventils (1) angeordnet ist und mit einem Ventilschieber (18), über den in Abhängigkeit vom Druckabfall an der Meßblende (32) ein Öffnungsquerschnitt zum Ausgangsanschluß (A) auf- oder zusteuerbar ist und der über eine Regelfeder (16) in seine Öffnungsrichtung vorgespannt ist, wobei bei umgekehrter Durchströmung des Stromregelventils (1) ein By-Pass-Kanal zur Umgehung der Meßblende (32) aufsteuerbar ist, dadurch gekennzeichnet, daß der Ventilschieber zusätzlich die Funktion eines Rückschlagstellglieds ausführt, wozu eine Rückschlagfeder (48) den Ventilschieber (18) in Schließrichtung der By-Pass-Öffnung des By-Pass-Kanals vorspannt, daß die Meßblende (32) an einer in einer der Ventilbohrungen (4) festgelegten, vom Ventilschieber (18) getrennten Meßblendenbuchse (12) mit veränderbarem Öffnungsquerschnitt (32) ausgebildet ist und daß an der Meßblendenbuchse (12) die By-Pass-Öffnung des By-Pass-Kanals ausgebildet ist, die durch eine Verschiebung des Ventilschiebers (18) mit Bezug zur Meßblendenbuchse (12) aufsteuerbar ist.
- Stromregelventil nach Patentanspruch 7, dadurch gekennzeichnet, daß die Rückschlagfeder (48) an einer ausgangsanschlußseitigen Stirnfläche des Ventilschiebers (18) angreift, und die Regelfeder (16) einerseits an einer Radialschulter der Innenbohrung (42) des Ventilschiebers (18) und andererseits an einer Stirnfläche der Meßblendenbüchse (12) abgestützt ist, die mit einem Endabschnitt in die Innenbohrung (42) eintaucht.
- Stromregelventil nach Patentanspruch 7 oder 8, dadurch gekennzeichnet, daß der Endabschnitt der Meßblendenbüchse (12) mit zumindest einer Radialbohrung (52) versehen ist, die durch eine Axialbewegung des Ventilschiebers (18) als Bypass-Kanal aufsteuerbar ist.
- Stromregelventil nach einem der Patentansprüche 7 bis 9, dadurch gekennzeichnet, daß die Regelfeder (16) über eine Stützbuchse (54) an der Stirnfläche des Ventilschiebers (18) abgestützt ist, deren einer Endabschnitt am Ventilgehäuse (2) abgestützt ist und deren anderer Endabschnitt in die Innenbohrung (42) eintaucht und mit einer Radialschulter versehen ist, die über die Regelfeder (16) gegen eine Innenschulter des Ventilschiebers (18) vorgespannt ist.
- Stromregelventil nach einem der Patentansprüche 7 bis 10, dadurch gekennzeichnet, daß die Rückschlagfeder (48) koaxial zur Stützbuchse (54) angeordnet ist.
- Stromregelventil nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß der Ausgangsanschluß (A) mit sich erweiternder Querschnittsfläche, vorzugsweise durch zwei zueinander beabstandete Radialbohrungssterne ausgebildet ist.
- Stromregelventil nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, daß eine Drosselöffnung (32) der Meßblende als Dreiecksfenster ausgebildet ist.
- Stromregelventil nach einem der vorhergehenden Patentansprüche 2 bis 13, dadurch gekennzeichnet, daß über die Innenbohrung (42) der Eingangsanschluß (A) mit der Meßblende verbunden ist und daß der Ventilschieber (18) koaxial zu einer Meßblendenbüchse (12) geführt ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19539521 | 1995-10-24 | ||
DE1995139521 DE19539521C2 (de) | 1995-10-24 | 1995-10-24 | Stromregelventil |
PCT/EP1996/003735 WO1997015875A1 (de) | 1995-10-24 | 1996-08-23 | Stromregelventil |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0857326A1 EP0857326A1 (de) | 1998-08-12 |
EP0857326B1 true EP0857326B1 (de) | 2000-06-21 |
Family
ID=7775609
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96929320A Expired - Lifetime EP0857326B1 (de) | 1995-10-24 | 1996-08-23 | Stromregelventil |
Country Status (5)
Country | Link |
---|---|
US (1) | US5996615A (de) |
EP (1) | EP0857326B1 (de) |
JP (1) | JPH11515076A (de) |
DE (2) | DE19539521C2 (de) |
WO (1) | WO1997015875A1 (de) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6116263A (en) * | 1998-07-23 | 2000-09-12 | Hydraforce, Inc. | Proportional priority flow regulator with reverse flow control |
US6110427A (en) * | 1998-08-14 | 2000-08-29 | Becton, Dickinson And Company | Flow regulator to maintain controllable volumetric flow rate |
DE19927392A1 (de) * | 1999-06-16 | 2000-12-21 | Bosch Gmbh Robert | Stromregelventil |
DE10051492A1 (de) * | 2000-10-17 | 2002-04-18 | Aws Appbau Arnold Gmbh | Coaxialventil als Mengenregelventil |
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 (de) * | 2003-07-21 | 2013-06-27 | Volkswagen Ag | Steuerventil zur Steuerung eines Volumenstromes, insbesondere zur Steuerung eines Kühlmittelstromes zur Kühlung der Kupplung eines Doppelkupplungsgetriebes eines Kraftfahrzeuges |
DE102004019748A1 (de) * | 2004-04-20 | 2005-11-17 | Bosch Rexroth Ag | Stromregelventil |
GB2415029B (en) * | 2004-06-12 | 2008-02-27 | Demag Delaval Ind Turbomachine | A hydraulic restrictor |
DE102006014446A1 (de) * | 2006-03-29 | 2007-10-04 | Schaeffler Kg | Stromregelventil |
US7770595B2 (en) | 2006-04-27 | 2010-08-10 | Sko Flo Industries, Inc. | Flow control valve |
US7395708B2 (en) | 2006-04-28 | 2008-07-08 | Skoflo Industries, Inc. | Flow measuring apparatus including a piston movable in the flow barrel |
WO2009089838A1 (en) * | 2008-01-16 | 2009-07-23 | Welltec A/S | A sequence valve and a downhole tractor |
CN109185249A (zh) * | 2018-09-28 | 2019-01-11 | 广东机电职业技术学院 | 一种汽车液压转向系统流量自动控制阀 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3015341A (en) * | 1958-01-10 | 1962-01-02 | William Waterman | Flow regulators |
US3145730A (en) * | 1963-03-07 | 1964-08-25 | Frank G Presnell | Control valve |
US3424196A (en) * | 1966-06-01 | 1969-01-28 | Deltrol Corp | Flow regulating valve |
US4237922A (en) * | 1978-09-25 | 1980-12-09 | Snap-Tite, Inc. | In-line flow control valve |
US4234013A (en) * | 1979-06-01 | 1980-11-18 | Sotokazu Rikuta | Control valve for keeping the rate of flow at a fixed value |
DE3013084A1 (de) * | 1980-04-03 | 1981-10-08 | Robert Bosch Gmbh, 7000 Stuttgart | Stromregelventil |
DE3343960A1 (de) * | 1982-12-08 | 1984-06-20 | Beringer-Hydraulik GmbH, 6345 Neuheim, Zug | Strombegrenzungsventil |
US4655245A (en) * | 1986-06-13 | 1987-04-07 | Dowty Decoto, Inc. | Hydraulic fuse |
DE4136991C2 (de) * | 1991-11-11 | 2000-11-02 | Bosch Gmbh Robert | Hydraulisches Wegeventil |
-
1995
- 1995-10-24 DE DE1995139521 patent/DE19539521C2/de not_active Expired - Fee Related
-
1996
- 1996-08-23 DE DE59605471T patent/DE59605471D1/de not_active Expired - Lifetime
- 1996-08-23 JP JP51622197A patent/JPH11515076A/ja active Pending
- 1996-08-23 EP EP96929320A patent/EP0857326B1/de not_active Expired - Lifetime
- 1996-08-23 US US09/051,857 patent/US5996615A/en not_active Expired - Lifetime
- 1996-08-23 WO PCT/EP1996/003735 patent/WO1997015875A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
US5996615A (en) | 1999-12-07 |
DE19539521C2 (de) | 1999-01-07 |
DE19539521A1 (de) | 1997-04-30 |
WO1997015875A1 (de) | 1997-05-01 |
DE59605471D1 (de) | 2000-07-27 |
JPH11515076A (ja) | 1999-12-21 |
EP0857326A1 (de) | 1998-08-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0857326B1 (de) | Stromregelventil | |
DE102008042624A1 (de) | Schieberventil zur hydraulischen Steuerung in einem Kraftfahrzeug-Automatikgetriebe | |
DE2858210C2 (de) | Einrichtung zum Ausgleich von Viskositätsverminderungen in der Stellvorrichtung einer Hydropumpe | |
DE10247665B4 (de) | Regelvorrichtung und Ventilblock für eine Regelvorrichtung | |
DE102014017801A1 (de) | Druckbegrenzungsventil | |
DE10316532B4 (de) | Hydraulisches Verstärkersystem für Bremsanlage | |
DE102006006228A1 (de) | Hydraulische Steueranordnung | |
DE10015971A1 (de) | Steuerventil für eine Ölpumpe | |
DE4237932A1 (de) | Volumenstromsteuerung für Kraftfahrzeughydraulik, insbesondere für Lenkeinrichtungen von Kraftfahrzeugen | |
DE3919175C2 (de) | ||
EP0717817B1 (de) | Hydraulischer steuerventilblock | |
DE10342478B3 (de) | Ventilanordnung zur Steuerung von Hydraulikflüssigkeit in einer Axialkolbenmaschine | |
DE10129822A1 (de) | Druckbegrenzungsventil für Kraftstoff-Einspritzeinrichtungen | |
EP1003972B1 (de) | Drehwerksteuerung mit brems- und steuerventilen | |
DE3135098A1 (de) | Ventilaufbau, umfassend ein pumpensteuer- bzw. -regelventil und eine entlastungsanordnung | |
DE2316504C2 (de) | Hydraulisches Stromregelventil | |
EP0743460A1 (de) | Elektrohydraulisches Hubmodul | |
DE10062428A1 (de) | Vorgesteuertes Druck-Einspeiseventil | |
EP0935716B1 (de) | Rückschlagventilanordnung | |
EP1452744B1 (de) | Hydraulische Steueranordnung | |
DE3840328A1 (de) | Vorgesteuertes wegeventil | |
DE3211545A1 (de) | Hydraulikventil zur druckmittelversorgung eines verbrauchers, insbesondere mengenregelventil | |
DE4219552C2 (de) | Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit | |
EP0582859B1 (de) | Hydraulische Steuervorrichtung | |
DE19714587C1 (de) | Ventil |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 19980305 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB IT SE |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: MANNESMANN REXROTH AG |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
17Q | First examination report despatched |
Effective date: 19990922 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT SE |
|
ITF | It: translation for a ep patent filed |
Owner name: JACOBACCI & PERANI S.P.A. |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20000627 |
|
REF | Corresponds to: |
Ref document number: 59605471 Country of ref document: DE Date of ref document: 20000727 |
|
ET | Fr: translation filed | ||
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20000921 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20020323 Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20040430 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20110824 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20110825 Year of fee payment: 16 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20120823 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120823 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120823 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20131025 Year of fee payment: 18 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59605471 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59605471 Country of ref document: DE Effective date: 20150303 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150303 |