EP0855520B2 - Ventilanordnung - Google Patents
Ventilanordnung Download PDFInfo
- Publication number
- EP0855520B2 EP0855520B2 EP98100431A EP98100431A EP0855520B2 EP 0855520 B2 EP0855520 B2 EP 0855520B2 EP 98100431 A EP98100431 A EP 98100431A EP 98100431 A EP98100431 A EP 98100431A EP 0855520 B2 EP0855520 B2 EP 0855520B2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- passage
- working
- pilot
- 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
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
Definitions
- the invention relates to a valve arrangement for pneumatic operation.
- a main valve which contains a slide valve member, which depending on the switch position, one with a pressure medium source connected feed channel with one of two working channels combines.
- the actuating force to move of the valve member supplies a fluidic pilot control medium, the one with the feed channel Pressure medium is identical and via a pilot channel given on an application surface of the valve member which is branched from the feed channel.
- the application is via a in the respective input channel switched on, designed as a solenoid valve Pilot valve controlled.
- a compared to lower supply pressure prevailing in the feed channel Actuating pressure of the applied area above the pilot control medium supplied can be switched on in the pilot channel Pressure regulator can be specified.
- the pressure regulator makes it possible to operate the pilot valve operating pressure applied to the application surface reduce so far that the switching times still at an acceptable low level lie.
- Pressure level of the actuating pressure is lower Degree of filling of the pilot channel and that of the Area of exposure to a limited area of exposure of the valve arrangement, so that for volume of pressure medium required every changeover is reduced, resulting in an air saving and thus one This results in cost savings in the operation of the valve arrangement.
- the working pressure in the working channel can be influenced by operating the pilot valve.
- valve arrangement of the type mentioned create a design in a simple manner the pressure level desired in the working channel allows.
- This measure makes it possible to Working channel pending and thus the connected Working pressure on consumers via the pressure regulator switched on in the pilot channel to adjust to a desired level that is lower than the feed pressure prevailing in the feed channel.
- a pressure regulator can be used be of significantly smaller dimensions has as a pressure regulator, alternatively in the connection between the working channel and the consumer or in the connection between the pressure medium source and the feed channel is switched on.
- the pressure regulator can thus be fixed with the Valve housing of the valve assembly are connected. Becomes the consumer also vented via the valve arrangement, results there is the further advantage that the ventilation does not have the pressure regulator has to take place, which in turn is a small controller size enables.
- the pressure regulator is expediently in the upstream of the pilot valve to the pressure medium source upstream channel section of the pilot channel switched on. In this way it is in comparison lower actuation pressure to supply pressure already on the pilot valve, and the pilot valve only has pilot control medium of the reduced actuation pressure to control. Those to be applied by the pilot valve Closing forces are consequently lower that lower electrical power for actuation of the pilot valve is sufficient, resulting in a lower Power consumption results and overall the possibility is created, pilot valves of smaller design to use.
- valve arrangement For a more universal use of the valve arrangement to enable, however, it is advantageous if the pressure regulator to set different desired Operating pressures adjustable is. Depending on the application, the actuation pressure can thus in particular, steplessly on a need reduced level can be set.
- the pilot channel is preferably fed from the feed channel of the main valve, see above that short airways are achieved and only a small one Channel effort is needed.
- the pressure regulator can be placed in the valve housing be built in or integrated.
- the current position of the piston in particular Valve slide trained valve member determines the differential forces with the participation of the Actuation pressure and the working pressure on the Attack the valve member.
- the current working pressure which affects the position of the valve member Size by reducing working pressure the valve member in the opening direction and with itself increasing working pressure in the closing direction is about the flow between the feed channel and the working channel the pending in the working channel Adjust working pressure to a predetermined value.
- valve arrangements shown in the drawing 1, 1 ', 1' 'each have a general main valve designated 2 and a generally designated 3 designated pilot valve.
- the pilot valve 3 is used to operate the main valve 2.
- the common valve housing 4 includes one first housing unit 5, which is the housing of the main valve 2 and at the same time part of the housing of the Pilot valve 3 forms.
- the housing of the pilot valve 3 further comprises a second housing unit 6, which is attached to the first housing unit 5 and formed by the housing of an electromagnetic part 55 is.
- the first housing unit 5 is exemplary executed in two parts.
- the valve member 8 is a valve spool with a cylindrical basic structure executed and could therefore also be used as a spool speak to. It has in the embodiment shown two cylindrical end sections 12, 13, between which there is a section of smaller diameter is located, which is called constriction 14 be. 1 to 4 and 6 at the axial end region of one end section 12 preferably piston-like control element 15 is provided, whose diameter is larger than that of the associated end section 12.
- the control element 15 is also movable in both axial directions connected to the valve member 8.
- the opposite End section 13 ends in these embodiments free and without control link.
- the embodiment is different 5 also the axial end region of the second End section 13 with a particularly similar Control element 15 'provided.
- the receiving chamber 7 contains, for example three axially successive chamber sections 16, 17, 18, the central chamber section 17 with a Working channel 22 communicates. From the others Chamber sections one (16) communicates with one Feed channel 23 and the other (18) with a relief channel 24. Since the exemplary valve arrangements 1, 1 ', 1' 'for pneumatic applications are provided, it is the relief channel 24 around a ventilation duct.
- the three chamber sections 16, 17, 18 are by two annular sealing units 25 from each other sectioned, which coaxially enclose the valve member 8.
- the sealing units are preferably cartridge-like executed and in the press fit in the desired Axial position in the receiving chamber 7 set.
- they contain, for example, an annular one Housing 26 with a U-like cross section, so that a circumferential opening pointing radially inwards results.
- the end sections work 12, 13 alternately with the sealing elements 27 of the two sealing units 25 together.
- FIGS. 1 to 4 and 6 adjoins the one outer chamber section 16, 18 to a first control chamber 28, which is expedient from an end portion of the receiving chamber 7 is formed. It is from the adjacent chamber section 16, 18 also through a sealing unit 25 of the type described, which is constantly in sealing contact with the associated end portion 12 of the valve member 8 stands. That of the first control chamber 28 axially Adjacent chamber section 18 is in the embodiment 1 to 4 with the relief channel 24 and in the embodiment of FIG. 6 with the Feed channel 23 in connection.
- the valve arrangement 1 ' according to FIG. 5 has in addition to that connected to the relief channel 24 Chamber section 18 adjacent first Control chamber 28 via an axially opposite second control chamber 28 '. It is from the neighboring one Chamber section 16 also by a Sealing unit 25 separated with the associated End portion 12 of the valve member 8 cooperates sealingly.
- first control element 15 Located in the first control chamber 28 in each case the first control element 15.
- second control element 15 'in the second control chamber 28 ' is there in addition provided.
- the controls 15, 15 'work dynamically sealing with the peripheral surface of the respective Control chamber 28, 28 'together. To this end they are each with a in the exemplary embodiments provided annular sealing element 31.
- the main valve takes each a vent position.
- the valve member 8 is here so far axially to that having the first control element 15 Side that the constriction 14th axially positioned approximately at the level of the sealing unit 25 is the one with the working channel 22 and the Relief channel 24 connected chamber sections 17, 18 separates from each other. This makes an annular one Given space, over which the working channel 22nd in fluid communication with the relief duct 24 stands.
- the valve member can be moved axially 8 in its second end position shown in FIG. 2 be shifted in which the main valve 2 occupies maximum open position.
- the constriction 14 in the area of the sealing unit 25 the those with the working channel 22 and with the feed channel 23 connected chamber sections 16, 17 from each other divides.
- the feed channel 23 and the working channel 22 in fluid communication.
- valve assembly 1 " 6 corresponds to that previously described. conditioned by the reverse arrangement of the with the Feed channel 23 and connected to the relief channel 24 Chamber sections 16, 18 are only the vent position and the maximum open position obtained with the valve member 8 deflected in the opposite direction.
- the working channel 22, the feed channel 23 and the relief channel 24 open out according to the example the outer surface of the valve housing 4, wherein in Mouth area connection threads are provided, the releasable connection of further pressure medium lines enable.
- This is the feed channel 23 with a pressure medium source P and the working channel 22 connectable to a consumer 32.
- the Relief channel 24 is used for relief or venting and can directly with pneumatic operation to the environment or with one of the exhaust air collected draining channel can be connected. the vent is marked by the letter "R".
- a consumer 32 to which the pressure medium is supplied is a schematic in the embodiment indicated fluid-operated working cylinder 33 intended. It has a cylinder housing 34 in which a axially movable piston 35 is arranged with a Piston rod 36 is connected by the Cylinder housing 34 is guided outwards.
- the piston 35 divides the interior of the cylinder housing 34 in two cylinder spaces 37, 38, the piston rod 36 facing away from the cylinder space 37
- Pressure medium line 39 connected to the working channel 22 is.
- it is a so-called single-acting cylinder, where the cylinder space 38 assigned to the piston rod is not connected to a pressure medium line, but has restoring means, which with vented the first cylinder chamber 37 the piston 35 in the in Fig.
- Reset means can be from a mechanical return spring or, as in the exemplary embodiment, by one enclosed air volume be formed forms an air spring.
- the provision could also by own weight or in some other way from one attached to the outer end of the piston rod 36 component to be moved.
- an actuating surface 42 is assigned to the valve member 8.
- the application surface 42 is with the valve member 8 motion-linked and is located in all Embodiments of the valve member 8 opposite Front of the in the first control chamber 28 located first control element 15.
- the application area 42 is a circular area here.
- the valve member 8 takes the one shown in FIGS. 1, 5 and 6 Position in which the first control 15 in the region of the valve member 8 axially opposite End of the first control chamber 28 is located.
- the loading area 42 with one under an actuation pressure pressurized fluidic pilot control medium, that is supplied via a pilot channel 43 becomes.
- This pilot channel 43 is constantly from the Pressure medium source P fed and stands by this Purpose with its upstream end 44 always with the feed channel 23 in connection from that below pressure medium at the supply pressure is.
- the pilot channel 43 branches out an extension 45 of the feed channel 23 assigned Chamber section 16 from.
- the first control element 15 divides the assigned one first control chamber 28 axially in two from each other separate rooms, the one from the exposure surface 42 limited, on which the valve member 8th on the opposite side arranged as the application space 47 is designated.
- the pilot channel 43 stands with its opposite the upstream end 44 downstream end 46 in constant Connection with this application space 47.
- the pilot channel 43 is already from that above controls pilot valve 3 mentioned. It is in turned on the course of the pilot channel 43 and divides this into one leading to the feed channel 23 upstream channel section 48 and one to the pressurization chamber 47 leading downstream channel section 49. It includes a valve opening 52 which is surrounded by an annular valve seat 53, the a plunger-like in the embodiment, between two switching positions movable switching element 54 lies opposite.
- the switching element 54 is exemplary from the movable armature of an electromagnetic part 55 formed or at least in drive connection with a corresponding movable anchor.
- the electromagnet part 55 is known in the art also a coil arrangement surrounding the switching element 54 56 and a yoke device, not shown.
- the coil assembly 56 and the switching element 54 are in the one already mentioned above second housing unit 6, which, moreover, with electrical Connection means 57 is equipped via the those required to operate the pilot valve 3 electrical control signals can be supplied.
- the valve seat 53 is located on the first housing unit, for example 5.
- the pilot valve takes 3 in the unactuated state according to FIG. 1 Closed position.
- the switching element 54 is seated the valve seat 53 so that the valve opening 52 is closed and the passage of fluid through the pilot channel 43 is interrupted.
- the closed position will usually by a spring device, not shown of the pilot valve 3 guaranteed.
- the coil assembly 56 is energized, so that Switching element 54 is lifted off the valve seat 53 and the Fluid passage through the pilot channel 43 released becomes.
- the pilot valve is in the actuated state 3 thus in the open position.
- the pressure regulator 58 which also as Pressure control valve could be called the Actuation surface 42 when the pilot valve is actuated 3 with the full pressure level of the feed pressure be charged.
- the pressure regulator 58 enables the actuation pressure to a notable below to reduce the pressure level of the feed pressure, so that in one configuration of the main valve as a simple switching valve, the switching times are still are sufficiently short because of the lower compression however, the degree of filling of the exposure space 47 and thus the air consumption drops.
- pilot valve In the closed position of the pilot valve becomes the outflow side Channel section 49 of the pilot channel 43 vented what, for example, over one in the second Housing unit 6 extending channel arrangement 61 and one communicating with it, to the outside surface of the valve housing 4 opening pilot ventilation channel 62 takes place.
- the valve member 8 is not only simple Switching element executed, but forms a variable and in particular continuously adjustable adjusting member, that is used to create a working channel 22 lower working pressure compared to the feed pressure adjust.
- the valve member 8 is one of the application surfaces 42 related to that by double arrow 63 indicated axial direction of movement of the Valve member 8 axially oppositely directed counter-loading surface 64 assigned. It is also with the valve member 8 coupled in motion and at 1 to 4 of the valve arrangement 1 according to FIG Acting surface 42 opposite end face of the first control element 15 is provided.
- the counteracting surface 64 is ring-shaped trained, and the space of the first limited by it Control chamber 28 forms a counterpressure chamber 65th
- Einje essentialrGegenbeetzstoffsraum65 is in the valve arrangements 1, 1 'of FIGS. 1 to 5 over a back pressure channel 66 with the working channel 22 connected.
- the counter pressure channel 66 runs inside of the valve housing 4 and in particular in the the first housing unit assigned to the main valve 2 5. Above the counterpressure channel 66 is the counteracting surface 64 constantly with that in the working channel 22 prevailing working pressure.
- valve arrangement 1 of FIGS. 1 to 4 A preferred mode of operation will now be explained.
- pilot valve 3 If the pilot valve 3 is now actuated, it arrives branched off from the pressure medium of the feed channel 23 fluidic pilot control medium over the open one Pilot channel 43 in the pressurization chamber 47.
- the contact surface 42 Actuating actuation pressure of the pilot control medium less than the feed pressure. Still moved 2 to the right in the direction to the maximum open position because the area of application 42 is larger than the end face 67, so that there is a sufficiently large resulting actuating force in the opening direction. With this opening movement counteracting surface 64 acts not yet out, since, as mentioned, with ambient pressure is acted upon.
- the working channel 22 In the maximum open position according to FIG. 2 the working channel 22 is separated from the ventilation channel 24 and is connected to the feed channel 23. Pressure medium originating from the pressure medium source P. thus flows into and over the working channel 22 the first cylinder space 37. The pressure in the Working channel 22 gradually on and in the same way the Back pressure in the connected to the working channel 22 Counterpressure room 65. As well as the total the on the counteracting surface 64 and the End face 67 compressive forces acting on the loading surface 42 acting pressure forces exceeds the valve member 8 shifts back from the open position towards the starting position until it becomes the middle position sets the closed position shown in Fig. 3. In this way, there is a working pressure in the working channel 22 from the setting or default of the Pressure regulator 58 depends.
- the Pressure regulator 58 in the upstream channel section 48 of the pilot channel 43 is turned on, like this is the case in all of the exemplary embodiments. This has to Consequence that the switching element 54 only with the already reduced actuating pressure is applied so that the closing forces to be applied are lower and one correspondingly smaller electromagnet unit 55 use Can be found. On the other hand, it would be too possible to keep a stronger electromagnetic unit 55, however, the cross section of the valve opening 52 to enlarge to a larger nominal size and thereby larger flow values with correspondingly shortened Switching times and an improved response to obtain the valve member 8.
- valve arrangement 1 Fig. 4 shows a state in which the pilot valve 3 in Connection to the operating phase shown in Fig. 3 is not more excited and switched back to the closed position is.
- the first control chamber 28 via the Pilot valve and the pilot vent channel 62 vented, reducing the forces of exposure causes so that the valve member 8 in the starting position moved back to the left.
- the working channel 22 is now vented again via the relief duct 24, and in the operating phase according to FIGS. 2 and 3 Extended piston 35 of the working cylinder 33 moves back to the retracted starting position.
- valve arrangements for example the two cylinder chambers of a double-acting Working cylinders to one valve arrangement each connect to in both directions of the piston 35 to obtain controlled operation.
- the two valve arrangements as in the exemplary embodiments be designed as 3/2-way valves could, here in a common housing be accommodated. It would be possible the working pressures for both cylinder spaces 37, 38 regulate independently.
- valve arrangement 1 ' corresponds to that of the valve arrangement 1.
- Feed pressure not acting on the valve member 8 Comprises compressive forces because the valve member 8 with a constant Cross-section passed through the chamber section 16 is. It is possible here to apply the surface 42 and the counteracting surface 64 on the two control elements 15, 15 'of the same size train so that changes are made the setting of the pressure regulator 58 proportional to the Impact changes in working pressure. This makes it easier the pressure setting.
- the pressure regulator 58 for setting different desired actuation pressures and thus expediently in particular different working pressures is continuously adjustable. This enables very easy changes in working pressure also during the operation of the valve arrangement. In particular you can see the working pressure this way during the operating phase of the connected consumer 32 optimally adapt to the requirements and especially considering the pressure level the required piston speed and necessary holding forces to the lowest possible level regulate to save energy.
- the pressure regulator 58 can be a known one Have structure so that there is a detailed description unnecessary. 6 shows schematically one functional structure. Accordingly, the pressure regulator contains 58 a controller housing 72, which is separate from the valve housing 4 and formed in the receiving recess 68 is used. The function of the controller housing could alternatively also directly from the valve housing 4 be exercised.
- the controller has a primary opening 73, which leads to the upstream end 44 Part of the upstream channel section 48 connected is. It also has a secondary opening 74 which with the part of the upstream channel section 48 is connected to the valve opening 52 of the pilot valve 3 leads.
- valve member 76 In one adjoining the primary opening 73 Valve chamber 75, a valve member 76 is arranged, that faces a valve seat 77 that one between the valve chamber 75 and the secondary opening 74 assigned overflow opening 78 is.
- a plunger connected to valve member 76 81 protrudes into a control chamber 82, which by one in the direction of adjustment of the valve member 76 and the plunger 81 movable control piston 83 is limited.
- the control room 82 stands over a connecting channel 84 constantly in communication with the secondary opening 74.
- a spring 85 arranged in the valve chamber 75 is acted upon the valve member 76 in the closing direction to the valve seat 77 out, so that at the same time the plunger 81 in the direction of the control piston 83 is acted upon.
- the control piston 83 is also in the opposite direction by a Actuated spring 86, which on the other hand on a Adjusting element 87 supports that with an actuating section 88 protrudes from the controller housing 72.
- the actuating force of the regulator spring 86 is greater than that of the spring acting on the valve member 76 85. This takes the valve member 76 as the starting position the open position shown in Fig. 6. Increases the pressure in the secondary opening 74, the control piston 83 via the connecting channel 84 the control spring 86 applied with greater force and shifts to the control spring 86, which compresses it becomes. At the same time, this can be done by the spring 85 tracked valve member 86 the overflow opening 78th close more or less, so that the Flow adjustable. If the secondary side drops Pressure off, the control piston 83 is increased again the plunger 81 pressed and consequently also the Flow cross-section in the area of the overflow opening 78 enlarged again so that the secondary pressure can rise again. In this way the secondary pressure adjusted to a predetermined value, which are influenced by the actuating force of the control spring 86 can. The influence is done by adjusting of the adjusting element 87, which relates to the preload the control spring 86 affects.
- the adjusting element 87 can be omitted, so that the bias the control spring 86 cannot be changed.
- a venting device can also be provided. It includes, for example, an im Control piston 83 formed first vent channel 89, normally from the plunger 81 is closed. If the secondary pressure is too high, however the control piston 83 is lifted from the plunger 81, so that pilot control medium via the first ventilation channel 89 can escape and a pressure reduction entry. According to the example, the air escapes from the first vent channel 89 into a control spring 86 containing chamber 90 and from there via a Controller housing 72 penetrating second ventilation channel 91 to the surroundings.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Driven Valves (AREA)
- Control Of Fluid Pressure (AREA)
Description
- Fig. 1
- eine erste Bauform der erfindungsgemäßen Ventilanordnung im Längsschnitt mit schematisch angedeutetem Verbraucher und Druckregler, wobei eine bevorzugte Bauform des Druckreglers vergrößert in Fig. 7 dargestellt ist und wobei das Hauptventil in eine Entlüftungsstellung geschaltet ist,
- Fig. 2
- die Ventilanordnung aus Fig. 1 bei in der maximalen Offenstellung befindlichem Hauptventil,
- Fig. 3
- Die Ventilanordnung aus Fig. 1 bei in der Sperr-bzw. Schließstellung befindlichem Hauptventil,
- Fig. 4
- die Ventilanordnung aus Fig. 1, erneut in der Entlüftungsstellung,
- Fig. 5
- eine Ausführungsvariante der Ventilanordnung aus Fig. 1 mit modifiziertem Ventilglied,
- Fig. 6
- einen bevorzugten, bei der Ventilanordnung zum Einsatz kommenden Drückregler in schematischer Darstellung im Längsschnitt entsprechend dem markierten Ausschnitt VII aus Fig. 1.
Claims (11)
- Ventilanordnung für pneumatischen Betrieb, mit einem Hauptventil (2), das einen mit einer Druckmittelquelle verbindbaren Speisekanal (23), einen mit einem Verbraucher (32) verbindbaren Arbeitskanal (22) und ein die Fluidverbindung zwischen dem Speisekanal (23) und dem Arbeitskanal (22) steuerndes bewegbares Ventilglied (8) aufweist, wobei dem Ventilglied (8) eine einen Beaufschlagungsraum (47) begrenzende Beaufschlagungsfläche (42) zugeordnet ist, die zum Bewegen des Ventilgliedes (8) mit einem unter einem Betätigungsdruck stehenden fluidischen Vorsteuermedium beaufschlagbar ist, das über einen von der Druckmittelquelle gespeisten und von einem Vorsteuerventil (3) beherrschen Vorsteuerkanal (43) zuführbar ist, in den ein zur Vorgabe des Betätigungsdruckes dienender, fest mit dem Ventilgehäuse (4) der Ventilanordnung (1,1',1") verbundener Druckregler (58) eingeschaltet ist, wobei durch das Vorsteuerventil (3) der Fluiddurchgang durch den Vorsteuerkanal (43) wahlweise unterbrochen oder freigegeben werden kann, wobei im unterbrochenen Zustand der Beaufschlagungsraum (47) entlüftet wird, und wobei ferner dem Ventilglied (8) eine der Beaufschlagungsfläche (42) axial entgegengesetzt gerichtete Gegenbeaufschlagungsfläche (64) zugeordnet ist, die über einen im Hauptventil (2) verlaufenden Gegendruckkanal (66) mit dem im Arbeitskanal (22) herrschenden Arbeitsdruck beaufschlagt ist, wobei der Betätigungsdruck in Öffnungsrichtung und der Arbeitsdruck in Schließrichtung auf das Ventilglied (8) einwirkt, so dass das Ventilglied (8) bei sich verringerndem Arbeitsdruck in Öffnungsrichtung und bei sich erhöhendem Arbeitsdruck in Schließrichtung verlagert wird, um über den Durchfluss zwischen dem Speisekanal (23) und dem Arbeitskanal (22) den im Arbeitskanal (22) anstehenden Arbeitsdruck auf einen vorgegebenen Wert einzuregeln.
- Ventilanordnung nach Anspruch 1, dadurch gekennzeichnet, daß der Druckregler (58) in den dem Vorsteuerventil (3) zur Druckmittelquelle hin vorgeschalteten zuströmseitigen Kanalabschnitt (48) des Vorsteuerkanals (43) eingeschaltet ist.
- Ventilanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Druckregler (58) als nicht einstellbarer, lediglich einen bestimmten Betätigungsdruck vorgebender Druckregler (58) ausgeführt ist.
- Ventilanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Druckregler (58) zur Vorgabe unterschiedlicher gewünschter Betätigungsdrücke insbesondere stufenlos einstellbar ausgebildet ist.
- Ventilanordnung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Vorsteuerkanal (43) zur Speisung aus der Druckmittelquelle mit dem Speisekanal (23) des Hauptventils (2) verbunden ist.
- Ventilanordnung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Druckregler (58) in das Ventilgehäuse (4) der Ventilanordnung (1, 1', 1'') eingebaut ist.
- Ventilanordnung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Druckregler (58) an der dem Hauptventil (2) zugeordneten Gehäuseeinheit (5) des Ventilgehäuses (4) vorgesehen ist.
- Ventilanordnung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Beaufschlagungsfläche (42) und die Gegenbeaufschlagungsfläche (64) an axial entgegengesetzten Seiten eines einem axialen Endbereich des Ventilgliedes (8) zugeordneten, insbesondere kolbenartigen Steuerelementes (15) vorgesehen sind.
- Ventilanordnung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß die Beaufschlagungsfläche (42) und die Gegenbeaufschlagungsfläche (64) an axial voneinander abgewandten Seiten zweier entgegengesetzten axialen Endbereichen des Ventilgliedes (8) zugeordneter, insbesondere kolbenartiger Steuerelemente (15, 15') vorgesehen sind.
- Ventilanordnung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß das Ventilglied (8) schieberartig ausgebildet ist.
- Ventilanordnung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß das Hauptventil (2) einen Entlastungskanal (24) aufweist und der Arbeitskanal (22) durch Betätigung des Ventilgliedes (8) entweder mit dem Speisekanal (23) oder mit dem Entlastungskanal (24) verbindbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19702948 | 1997-01-28 | ||
DE19702948A DE19702948C2 (de) | 1997-01-28 | 1997-01-28 | Ventilanordnung |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0855520A1 EP0855520A1 (de) | 1998-07-29 |
EP0855520B1 EP0855520B1 (de) | 2001-05-02 |
EP0855520B2 true EP0855520B2 (de) | 2004-10-06 |
Family
ID=7818522
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98100431A Expired - Lifetime EP0855520B2 (de) | 1997-01-28 | 1998-01-13 | Ventilanordnung |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0855520B2 (de) |
DE (2) | DE19702948C2 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1092878A1 (de) * | 1999-10-12 | 2001-04-18 | Palmstiernas Instrument AB | Pneumatische Schaltung zum Steuern eines Stellglieds |
DE10347590B3 (de) | 2003-10-14 | 2005-01-13 | Festo Ag & Co. | Verteilermodul für Ventilbatterien |
DE102005060530A1 (de) | 2005-12-17 | 2007-06-21 | Zf Friedrichshafen Ag | Belüftung eines Schaltelementes |
DE102018214318B4 (de) * | 2018-08-24 | 2020-10-29 | Festo Se & Co. Kg | Fluidsystem |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2433920A1 (de) † | 1974-05-31 | 1975-12-11 | Yuken Kogyo Co Ltd | Elektromagnetisches proportionalventil zur steuerung der durchflussrichtung und drosselung |
DE3146561A1 (de) † | 1980-11-24 | 1982-06-24 | Linde Ag, 6200 Wiesbaden | Hydrostatischer antrieb mit drucksteuerung |
DE4102203A1 (de) † | 1991-01-25 | 1992-07-30 | Linde Ag | Hydraulisches antriebssystem |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2119168B1 (de) * | 1971-04-20 | 1972-10-12 | Heilmeier & Weinlein, Fabrik fur OeI Hydraulik, 8000 München | Fernbedienungseinrichtung fur eine mengengeregelte Steuerschiebervorrichtung |
US3958495A (en) * | 1972-08-31 | 1976-05-25 | Koehring Company | Air-oil amplifier |
US4180089A (en) * | 1977-09-30 | 1979-12-25 | Ingersoll-Rand Company | Thrust piston biasing means |
DE3440262A1 (de) * | 1984-11-03 | 1986-05-15 | Robert Bosch Gmbh, 7000 Stuttgart | Druckbegrenzungsanordnung |
DE4143274C2 (de) * | 1991-12-27 | 1994-03-10 | Mannesmann Ag | Ventilbaugruppe in Modulbauweise |
DE4219552C2 (de) * | 1992-06-15 | 1996-03-07 | Rexroth Mannesmann Gmbh | Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit |
-
1997
- 1997-01-28 DE DE19702948A patent/DE19702948C2/de not_active Expired - Fee Related
-
1998
- 1998-01-13 EP EP98100431A patent/EP0855520B2/de not_active Expired - Lifetime
- 1998-01-13 DE DE59800655T patent/DE59800655D1/de not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2433920A1 (de) † | 1974-05-31 | 1975-12-11 | Yuken Kogyo Co Ltd | Elektromagnetisches proportionalventil zur steuerung der durchflussrichtung und drosselung |
DE3146561A1 (de) † | 1980-11-24 | 1982-06-24 | Linde Ag, 6200 Wiesbaden | Hydrostatischer antrieb mit drucksteuerung |
DE4102203A1 (de) † | 1991-01-25 | 1992-07-30 | Linde Ag | Hydraulisches antriebssystem |
Also Published As
Publication number | Publication date |
---|---|
EP0855520A1 (de) | 1998-07-29 |
DE59800655D1 (de) | 2001-06-07 |
DE19702948A1 (de) | 1998-07-30 |
DE19702948C2 (de) | 2000-01-27 |
EP0855520B1 (de) | 2001-05-02 |
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