EP1253326B1 - Soupape pneumatique - Google Patents

Soupape pneumatique Download PDF

Info

Publication number
EP1253326B1
EP1253326B1 EP02090158A EP02090158A EP1253326B1 EP 1253326 B1 EP1253326 B1 EP 1253326B1 EP 02090158 A EP02090158 A EP 02090158A EP 02090158 A EP02090158 A EP 02090158A EP 1253326 B1 EP1253326 B1 EP 1253326B1
Authority
EP
European Patent Office
Prior art keywords
pneumatic valve
control
connection line
opening
diaphragm
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
EP02090158A
Other languages
German (de)
English (en)
Other versions
EP1253326A2 (fr
EP1253326A3 (fr
Inventor
Jörg Dipl.-Ing. Führmann
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.)
Demag Cranes and Components GmbH
Original Assignee
Demag Cranes and Components GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Demag Cranes and Components GmbH filed Critical Demag Cranes and Components GmbH
Publication of EP1253326A2 publication Critical patent/EP1253326A2/fr
Publication of EP1253326A3 publication Critical patent/EP1253326A3/fr
Application granted granted Critical
Publication of EP1253326B1 publication Critical patent/EP1253326B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F15B2013/008—Throttling member profiles
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
    • F15B2211/8855—Compressible fluids, e.g. specific to pneumatics
    • 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 pneumatic valve, in particular for use in a pneumatic lifting drive, according to the preamble of claim 1.
  • the well-known pneumatic valve has the disadvantage that the pneumatic valve with the Variable restrictors must lie in the power flow, resulting in a heavier weight Construction leads, since this must correspond to the mechanical stress.
  • This version has the disadvantage that the volume flow in only one Flow direction is adjustable. In addition, the design effort is high.
  • the object of the invention is to propose a pneumatic valve, the Volume flow pressure-independent keeps approximately constant.
  • the pneumatic valve should be so be configured that it is operable in both flow directions.
  • variable throttle a through the Main connecting line extending transverse opening, in between a first and a second end position at least in the direction of the second End position against an elastic reaction force reciprocable control is arranged, which has a control opening for the working gas, whose effective Opening cross-section starting from the first end position with further movement of the Control steadily decreases that the control is moving seen on the first end position facing side of the control with the gas pressure in front of the diaphragm and on the side facing the second end position of the control is acted upon by the gas pressure after the shutter to the Opening cross-section depending on the gas pressure difference before and after the aperture too Taxes.
  • the flow direction is before and after the aperture different pressures or at the diaphragm a pressure difference.
  • These gas pressures act on both sides of the control and move it when There is a pressure difference until the elastic counterforce causes the Control experiences the total force zero.
  • the control will be so long shifted until it is in a position between the two end positions, when the total force on the control down to a small negligible friction losses disappear.
  • the opening area smaller or larger, depending on Movement.
  • There is a closed loop for the volume flow which is adjustable in proportion to the root of the pressure difference.
  • the transverse opening is a cylindrical Through hole and the control a corresponding to this cylindrical control piston made of plastic, allowing a virtually frictionless Displacement of the control piston in the through hole is made possible.
  • the elastic counterforce is a simple design elastic element, especially a coil spring.
  • control piston is in the absence of gas pressure difference at a boundary and the control opening has the largest provided Open cross-section, so that in a lifting drive at nominal load to be lifted Immediately the full lifting force is effective.
  • the main connection line has two parallel ring channels, which are connectable only via the control port.
  • the effective iris area is easy to adjust when entering through the iris Adjusting cylinder is inserted with conically tapered tip.
  • the structurally simple solution provides that the control on the first End position facing side via a first auxiliary connection line with the The part of the main link, located directly in front of the panel, is on the the second end position facing side via a second auxiliary connection line with the part of the main line immediately behind the panel connected is.
  • the connections of the two auxiliary connection lines by means a switching valve are switched such that the first auxiliary connection line with the immediately behind the panel located part of the main line and the second auxiliary connection line with the immediately before the panel located part the main connection line is connected, and that in addition the first opening from the Supply gas pressure can be switched to venting.
  • the switching of the first opening to vent causes a Switching the auxiliary connection lines, including the switching valve via a Switching line is connected to the first opening.
  • Fig. 1 shows the basic structure of a pneumatic valve in a schematic Presentation. This serves to regulate the volume flow 1 of a working gas, the from a supply device, not shown, with a supply gas pressure provided.
  • the volume flow 1 passes through an adjusting throttle 2 and a pneumatic diaphragm 3, connected in series with the volume flow 1 to go through.
  • the order of the variable throttle 2 and the diaphragm 3 is included any.
  • Fig. 1 shows a control 4, which against a helical spring 4a trained elastic counterforce 5 between two end positions back and forth is movable.
  • the coil spring can also any elastic Element generate the counterforce 5. The only important thing is that the opposing force 5 of the position of the control is constantly dependent.
  • the control 4 is seen in the direction of movement on the one Side via an auxiliary connection line 6 with the gas pressure in front of the panel 3 and over an auxiliary connection line 7 is acted upon by the gas pressure after the diaphragm 3, each seen in the flow direction. Consequently, the occurring at the diaphragm 3 acts Gas pressure difference on the control element 4 and moves this until the Counterforce 5 is so large that the sum of acting on the control 4 Forces zero.
  • the connection 5a between the control 4 and the Adjustment throttle 2 is intended to show an adjustment of the volume flow 1 schematically.
  • FIG. 2 shows the pneumatic valve of FIG. 1 additionally with a switching valve 8, that interchanges the auxiliary connection lines 6, 7, when the pneumatic valve with reverse flow direction is operated.
  • Fig. 3 shows another auxiliary connection line 9, which the changeover valve 8 with a Supply line 9a of the volume flow 1 connects, the optional gas pressure and on Vent is switchable (not shown in Fig. 3).
  • Fig. 4 shows an embodiment of the pneumatic valve of FIG. 3, which as Metal block 10 is formed of an aluminum alloy and in a first Operating mode is.
  • the metal block 10 has a first opening 11, which in the illustrated in Fig. 4 first operating mode serves as an inlet opening for the volume flow 1 of the working gas.
  • a second opening 12 as Outlet opening On the opposite side is a second opening 12 as Outlet opening, both openings 11, 12 are via a main connection line thirteenth connected with each other.
  • the opening 11 passes through a through the metal block 10 and through the Main connection line 13 extending transverse opening 14 in the form of a cylindrical Through hole.
  • Fig. 4 opens the main connection line 13 in the region of the transverse opening 14 each in two parallel adjacent ring channels 15, 16. Both annular channels 15,16 are connected via the transverse opening 14.
  • the control 4 in the form of a cylindrical control piston inserted, which is made of plastic.
  • the control 4 is almost frictionless in the transverse opening 14 displaceable and seals the Main connection line 13 airtight to the outside.
  • the control 4 is slidable between two end positions within the transverse opening 14, wherein a the two end positions by a left boundary 17 and the other by a right boundary 18 is formed.
  • the control 4 has in the area of Ring channels 15, 16 in the shell longitudinally formed depressions 19, the cooperating with a web 19a form the control opening, so that the Working gas flow through the recesses 19 from the annular channel 15 into the annular channel 16 can. From there it reaches a pneumatic diaphragm 20 and through the opening 21 through the second opening 12, where it exits the pneumatic valve.
  • the effective aperture area 21 of the aperture 20 adjust by a setting cylinder 22 with a conically tapered tip, through the Aperture 20 is passed through while leaving an annular gap.
  • the auxiliary connection line 6 begins before the panel 20 and after the transverse opening 14, is guided over the switching valve 8 and opens based on Fig. 4 on the left Side in the transverse opening 14. Behind the panel 20, the auxiliary connection line begins 7, passes through the switching valve 8 to the transverse opening 14, where in Fig. 4 on the right side opens in the transverse opening 14.
  • the transverse opening 14 is through Closing elements 23 closed gas-tight to the outside.
  • control 4 is on the first end position (limit 17) facing side on the auxiliary connection line 6 with the front of the panel 20th connected part of the main link 13, on the second End position (boundary 18) facing side over the Hauptitatisfeitung 13th with the located behind the aperture 20 part of the main connection line 13.
  • Bei lack of gas pressure difference before and behind the diaphragm 20 is the control 4 at the limit 17 and the control port has the largest provided Opening cross-section on. The control will increase with increasing pressure difference, i.e.
  • the control moves along the transverse opening 14 relative to 4 to the right, against the elastic counterforce of the coil spring 4a, which is effective in the direction of the second end position (limit 18). It reduces the opening cross-section of the control port.
  • the control port is designed to that the effective opening cross-section starting from the first end position (Limit 17) as the control element 4 advances steadily, decreasing linearly here. In this way, the opening cross-section depends on the gas pressure difference and controlled by the aperture 20.
  • the volume flow 1 results in a simple manner from the effective aperture area 21, the characteristic of the coil spring 4a and the opening cross section of Control 4.
  • Fig. 5 shows the control element 4 in the form of a cylindrical control piston in one Longitudinal and a cross section. From both sections it can be seen that the Control opening 19a means in the lateral surface of the control piston in the Is formed longitudinally in the form of V-grooves.
  • Fig. 5 are two V-grooves intended; but it can also be a variety of V-grooves 24 are used.
  • the longitudinal section in Fig. 5 shows that the depth of the V-grooves to the second end position (Limit 18) steadily increases, linearly.
  • the side surfaces of the V-grooves 24 form a right triangle here.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (14)

  1. Clapet pneumatique, destiné en particulier à être utilisé dans un entraínement de levage pneumatique, pour la régulation du flux volumique d'un gaz de travail qui est délivré par un dispositif d'alimentation à une pression de gaz d'alimentation, lequel clapet pneumatique comporte une première ouverture (19) et une deuxième ouverture (12) pour l'entrée et la sortie du gaz de travail, lesquelles ouvertures sont reliées entre elles par une conduite de liaison principale (13) dans laquelle un étrangleur de réglage (2) et un obturateur pneumatique (1) sont montés l'un derrière l'autre,
    caractérisé en ce que
       l'étrangleur de réglage (2) comporte une ouverture transversale (14) qui s'étend transversalement à travers la ligne de liaison principale (13) et dans laquelle est placé, entre une première position d'extrémité et une deuxième position d'extrémité, un élément de commande qui est apte à se déplacer alternativement au moins en direction de la deuxième position d'extrémité en s'opposant à une force antagoniste élastique (5) et qui comporte une ouverture de commande destinée au gaz de travail dont la section efficace diminue régulièrement en partant de la première position d'extrémité lorsque l'élément de commande poursuit son déplacement, et
       l'élément de commande (4) est sollicité, par référence à la direction de déplacement, du côté de l'élément de commande qui est dirigé vers la première position d'extrémité par la pression exercée par le gaz en amont de l'obturateur (3) et du côté de l'élément de commande qui est dirigée vers la deuxième position d'extrémité par la pression exercée par le gaz en aval de l'obturateur (3) pour commander la section d'ouverture en fonction de la différence de pression du gaz en amont et en aval de l'obturateur (3).
  2. Clapet pneumatique selon la revendication 1, caractérisé en ce que l'ouverture transversale (14) est un perçage traversant cylindrique et l'élément de commande (4) est un piston de commande cylindrique en matière plastique correspondant à ce perçage traversant.
  3. Clapet pneumatique selon la revendication 2, caractérisé en ce que le piston de commande peut être déplacé à peu près sans frottement dans le perçage traversant.
  4. Clapet pneumatique selon l'une des revendications 2 et 3, caractérisé en ce que la première position d'extrémité est formée par une butée de limitation (17) dans le perçage traversant.
  5. Clapet pneumatique selon l'une des revendications 1 à 4, caractérisé en ce que la force antagoniste élastique (5) est formée par un élément élastique.
  6. Clapet pneumatique selon la revendication 5, caractérisé en ce que l'élément élastique est un ressort hélicoïdal (4a).
  7. Clapet pneumatique selon l'une des revendications 2 à 6, caractérisé en ce que le piston de commande porte, en l'absence d'une différence de pression de gaz, contre la butée de limitation (17) et l'ouverture de commande présente la plus grande section d'ouverture prévue.
  8. Clapet pneumatique selon l'une des revendications 2 à 7, caractérisé en ce que la conduite de liaison principale (13) comporte deux canaux annulaires parallèles (15, 16) qui peuvent être reliés entre eux par l'ouverture de commande.
  9. Clapet pneumatique selon l'une des revendications 2 à 8, caractérisé en ce que l'ouverture est formée par des gorges en V (24) ménagées dans la surface d'enveloppe le long du piston de commande.
  10. Clapet pneumatique selon la revendication 9, caractérisé en ce que chaque face latérale des gorges en V (24) forme un triangle.
  11. Clapet pneumatique selon l'une des revendications 1 à 10, caractérisé en ce qu'un vérin (22) comportant une pointe conique est introduit dans l'obturateur (3) pour régler la surface d'obturateur efficace.
  12. Clapet pneumatique selon l'une des revendications 1 à 11, caractérisé en ce que l'élément de commande (4) est relié, du côté dirigé vers la première position d'extrémité, par une première conduite de liaison auxiliaire (6) à la partie de la conduite de liaison principale (13) qui est placée immédiatement en amont de l'obturateur et, du côté dirigé vers la deuxième position d'extrémité, par une deuxième conduite de liaison auxiliaire (7) à la partie de la conduite de liaison principale (13) qui est placée immédiatement en arrière de l'obturateur (3).
  13. Clapet pneumatique selon la revendication 12, caractérisé en ce que les raccords des deux conduits de liaison auxiliaires (6, 7) peuvent être commutés au moyen d'un clapet de commutation (8) de sorte que la première conduite de liaison auxiliaire (6) est reliée à la partie de la conduite de liaison principale (13) qui est placée immédiatement en aval de l'obturateur (3) et la deuxième conduite de liaison auxiliaire (7) est reliée à la partie de la conduite de liaison principale qui est montée immédiatement en amont de l'obturateur (3), et en ce que, en plus, la première ouverture (11) peut être commutée sur la purge par la pression de gaz d'alimentation.
  14. Clapet pneumatique selon la revendication 13, caractérisé en ce que le clapet de commutation (8) est commuté de telle sorte qu'une commutation des conduites de liaison auxiliaires (6, 7) est effectuée lors de la commutation de la première ouverture (11) sur la purge.
EP02090158A 2001-04-27 2002-04-29 Soupape pneumatique Expired - Lifetime EP1253326B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10123157A DE10123157C1 (de) 2001-04-27 2001-04-27 Pneumatikventil
DE10123157 2001-04-27

Publications (3)

Publication Number Publication Date
EP1253326A2 EP1253326A2 (fr) 2002-10-30
EP1253326A3 EP1253326A3 (fr) 2004-02-18
EP1253326B1 true EP1253326B1 (fr) 2005-08-10

Family

ID=7684560

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02090158A Expired - Lifetime EP1253326B1 (fr) 2001-04-27 2002-04-29 Soupape pneumatique

Country Status (4)

Country Link
US (1) US6729346B2 (fr)
EP (1) EP1253326B1 (fr)
JP (1) JP2003035377A (fr)
DE (2) DE10123157C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101375064B (zh) * 2006-01-30 2012-05-23 科瓦尔公司 真空发生器

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050183776A1 (en) * 2004-02-23 2005-08-25 Gerald Matranga Pressure regulator
WO2006110128A1 (fr) * 2005-04-08 2006-10-19 Twin Disc, Incorporated Regulateur de pression
DE102005055894A1 (de) * 2005-11-22 2007-05-31 Thyssenkrupp Presta Steertec Gmbh Schwingungsgedämpftes Proportionalventil
EP2021892B1 (fr) * 2006-04-27 2013-02-20 Sko Flo Industries, Inc. Soupape de regulation de debit
WO2007127986A2 (fr) * 2006-04-28 2007-11-08 Sko Flo Industries, Inc. Appareil de mesure d'écoulement
US9052715B2 (en) * 2010-10-05 2015-06-09 Sko Flo Industries, Inc. Flow rate controller for high flow rates and high pressure drops
US10914304B2 (en) * 2015-05-01 2021-02-09 Graco Minnesota Inc. Pneumatic timing valve
CN106195327B (zh) * 2016-08-17 2018-07-03 浙江利百加泵阀科技有限公司 气动截止换向阀
EP3597939B1 (fr) * 2018-07-20 2022-04-13 Hamilton Sundstrand Corporation Servovanne

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE500790C (de) * 1929-01-05 1930-06-28 Ludwig Sautter Dr Ing Membrangasdruckregler
US2495785A (en) 1945-01-11 1950-01-31 Hydraulic Equipment Company Lowering valve
GB809651A (en) * 1954-12-22 1959-02-25 Keelavite Co Ltd Fluid flow control apparatus
US2990847A (en) 1959-05-25 1961-07-04 Marquardt Corp Fluid flow regulator
DE1206610B (de) * 1962-05-26 1965-12-09 Karl Marx Stadt Ind Werke Vorrichtung zur Regelung der Durchflussmenge in entgegengesetzten Stroemungsrichtungen
GB1001407A (en) * 1963-01-04 1965-08-18 Pneumatic Components Ltd Improvements in or relating to apparatus for dispensing air or other gas
US3554222A (en) 1968-06-04 1971-01-12 Mitsubishi Heavy Ind Ltd Automatic flow control valve
US3773083A (en) * 1972-03-28 1973-11-20 Kemp Ind Inc Hydraulic control apparatus
US3770007A (en) * 1972-04-21 1973-11-06 Int Harvester Co Dual direction flow control valve
US3807443A (en) * 1972-12-08 1974-04-30 Sperry Rand Corp Power transmission
US4422470A (en) * 1982-07-01 1983-12-27 The Cessna Aircraft Company Flow limiting valve
US4694852A (en) * 1985-01-22 1987-09-22 Fsi Corporation Flow regulating valve for controlling the flow of corrosive fluids
US5027919A (en) * 1989-12-29 1991-07-02 Young & Franklin, Inc. Fluid friction controller
US5097863A (en) * 1991-06-05 1992-03-24 Mccann's Engineering And Manufacturing Co. Flow control apparatus
KR19990087371A (ko) 1996-02-28 1999-12-27 모서 다니엘 내하중 브레이크 밸브
US5913328A (en) * 1997-09-15 1999-06-22 Taube; John D. Flow control valve with one piece plug/valve tube sleeve assembly
DE29802606U1 (de) * 1998-02-16 1998-04-23 Zasche Fördertechnik GmbH, 86720 Nördlingen Handgesteuertes Hebegerät mit einem pneumatischen Hubantrieb

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101375064B (zh) * 2006-01-30 2012-05-23 科瓦尔公司 真空发生器

Also Published As

Publication number Publication date
EP1253326A2 (fr) 2002-10-30
EP1253326A3 (fr) 2004-02-18
DE10123157C1 (de) 2002-11-14
DE50203854D1 (de) 2005-09-15
US6729346B2 (en) 2004-05-04
JP2003035377A (ja) 2003-02-07
US20020157709A1 (en) 2002-10-31

Similar Documents

Publication Publication Date Title
DE3323363C2 (fr)
DE3719113C1 (de) Regelbarer Schwingungsdaempfer
DE3634728C2 (fr)
EP0760908B1 (fr) Systeme de commande pour au moins deux consommateurs hydrauliques
DE112007003035T5 (de) Mikroventilvorrichtung
EP0279315B1 (fr) Dispositif de commande hydraulique
DE1921977B2 (de) Ventileinrichtung zur Steuerung der Druckmittelwege eines doppelwirkenden Servomotors
EP1253326B1 (fr) Soupape pneumatique
EP0103250B1 (fr) Soupape de contrôle pour contrôle hydraulique
DE10019254C2 (de) Drucksteuerventil
DE3630823A1 (de) Richtungssteuerungsventil
DE3688346T2 (de) Hydraulisches steuersystem.
DE4115594A1 (de) Proportional-druckregelventil
LU84377A1 (de) Einstellbares drosselventil
EP0483585B1 (fr) Valve d'étranglement proportionelle réglable à contre-réaction
DE3919175C2 (fr)
EP1126349A2 (fr) Vanne de réduction de pression
DE3836076A1 (de) Steuerteil fuer ein steuersystem zur steuerung des inneren volumens eines rotationskompressors
WO2004104426A1 (fr) Dispositif de commande hydraulique
EP0375916B1 (fr) Distributeur pour commander un cylindre hydraulique
DE3806015A1 (de) Steueranordnung zur steuerung des inneren volumens eines rotationskompressor
EP0491155B1 (fr) Distributeur pour commande d'un moteur hydraulique
EP0331958A2 (fr) Dispositif de commande hydraulique
DE2716694A1 (de) Steuereinrichtung fuer einen hydraulischen arbeitszylinder
EP0176679A1 (fr) Dispositif de commande hydraulique

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

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

RIC1 Information provided on ipc code assigned before grant

Ipc: 7F 15B 11/05 A

Ipc: 7G 05D 7/01 B

17P Request for examination filed

Effective date: 20040712

17Q First examination report despatched

Effective date: 20040913

AKX Designation fees paid

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50203854

Country of ref document: DE

Date of ref document: 20050915

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ET Fr: translation filed
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

Effective date: 20060511

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20150420

Year of fee payment: 14

Ref country code: DE

Payment date: 20150421

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20150427

Year of fee payment: 14

Ref country code: FR

Payment date: 20150421

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50203854

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160429

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20161230

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: 20160429

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161101

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160502

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: 20160429