EP0733802A1 - Pompe à membrane façonnée - Google Patents

Pompe à membrane façonnée Download PDF

Info

Publication number
EP0733802A1
EP0733802A1 EP96101648A EP96101648A EP0733802A1 EP 0733802 A1 EP0733802 A1 EP 0733802A1 EP 96101648 A EP96101648 A EP 96101648A EP 96101648 A EP96101648 A EP 96101648A EP 0733802 A1 EP0733802 A1 EP 0733802A1
Authority
EP
European Patent Office
Prior art keywords
membrane
ribs
stabilizing
radial
underside
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.)
Granted
Application number
EP96101648A
Other languages
German (de)
English (en)
Other versions
EP0733802B1 (fr
Inventor
Heinz Riedlinger
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.)
KNF Neuberger GmbH
Original Assignee
KNF Neuberger 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 KNF Neuberger GmbH filed Critical KNF Neuberger GmbH
Publication of EP0733802A1 publication Critical patent/EP0733802A1/fr
Application granted granted Critical
Publication of EP0733802B1 publication Critical patent/EP0733802B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members

Definitions

  • the invention relates to a diaphragm pump with a shaped membrane made of elastic material, which is reinforced in its central area in the stroke direction and has a flexible ring area around it, which is held on the outside with a clamping edge on the pump housing, which shaped membrane by means of a connecting rod acting on its central area or the like lifting device can be deflected from an upper to a lower dead center position and vice versa, the membrane top facing the pump chamber in the central region and the adjacent wall of the pump chamber in particular being geometrically adapted to one another and radial ribs for stabilization being provided on the membrane underside facing away from the pump chamber, at least in the ring region.
  • Such a diaphragm pump is already known from DE 40 07 932 C2, in which the wall of the pump chamber facing the molded membrane is approximately spherical in its central region and the upper side of the molded membrane is geometrically geometrically attached to this spherical pump chamber region with respect to its upper side is adapted so that the upper side of the shaped membrane, at least in its central region, at least almost completely conforms to the wall of the pump chamber with its top dead center position.
  • the ring area of the forming membrane is designed to be comparatively thin and flexible, while the central area is reinforced in the direction of the stroke in order to prevent the lifting movement Type of piston effect.
  • the known diaphragm pump In order to reduce the risk of the molded membrane bulging in the direction of the adjacent pump chamber wall when the diaphragm pumps are used, preferably used as a vacuum pump, during operation of the pump - particularly during the suction stroke - the known diaphragm pump has radial ribs on the underside of the ring area. that should stabilize it.
  • radial ribs on the underside of the ring area.
  • the radial ribs are arranged so far apart that the diaphragm has sufficient flexibility in the ring area, the ring area bulges too much, so that at low suction pressures the volumetric efficiency and the pumping speed of the pump accordingly is reduced.
  • vibrations can occur in the membrane, which on the one hand lead to heating of the molded membrane and on the other hand can also cause the molded membrane to collide with the adjacent pump chamber wall. Abutment of the molded membrane on the pump chamber wall is particularly undesirable because it leads to premature wear of the molded membrane in addition to increased noise. Particles removed from the molded membrane can also impair the function of the inlet and outlet valves, which further reduces the quality of the vacuum that can be achieved with the membrane pump.
  • the stabilizing ribs are either aligned in the circumferential direction, that is to say arranged concentrically to the longitudinal axis of the membrane, or that they are aligned tangentially to the circumferential direction or somewhat obliquely to the circumferential direction, for example spirally.
  • the ring area of the shaped membrane is supported both by the radial ribs and by the stabilizing ribs running transversely to it.
  • the radial ribs can therefore be arranged at a sufficiently large distance from one another, so that there is a particularly flexible ring area which causes only comparatively little flexing work when the pump is in operation. Nevertheless, arching of the ring area and the associated vibrations, in particular also during the suction movement of the membrane and with large negative pressures, are effectively avoided.
  • the membrane areas lying between the radial ribs are thus arranged in a targeted manner so that the ring area of the shaped membrane is flexible around a circumferential line, but has a comparatively great bending stiffness in a direction running transversely thereto.
  • This results in a smoothly actuated molded membrane which converts only a very small proportion of the lifting energy applied into flexing work, and which nevertheless prevents vibrations and an impact on the molded membrane at top dead center on the adjacent pump chamber wall.
  • the molded membrane has a longer service life and, on the other hand, the action of the valves of the membrane pump is not so quickly impaired by membrane particles rubbed off the molded membrane.
  • the diaphragm pump according to the invention is therefore particularly suitable for use as a vacuum pump.
  • the stabilizing ribs enable a significant reduction in the deformation of the membrane, especially in the area of the inlet and outlet openings of the pump chamber.
  • An advantageous embodiment provides that a plurality of radially offset stabilizing ribs are arranged between adjacent radial ribs. The forces acting on the ring area under vacuum can then be absorbed even more evenly by the stabilizing ribs and via the radial ribs be introduced into the pump housing or the central region of the molded membrane.
  • a further development of the invention provides that the bending moment of the radial ribs around a circumferential line of the shaped membrane is greater than that of an individual stabilizing rib around a radius of the shaped membrane crossing it.
  • the radial ribs are thus designed to be more rigid than the stabilizing ribs, with several stabilizing ribs each interacting with and being supported on a common radial rib.
  • the number of radial ribs can thus be reduced, so that there is a ring region which is flexible about a circumferential line but is nevertheless comparatively rigid about a diameter line and which despite low flexing work losses also enables good pumping speed even at working pressures in the displacement of just a few millibars.
  • the greater bending moment of the radial ribs in comparison to the stabilizing ribs can be achieved particularly simply in that the height of the radial ribs oriented in the direction of the longitudinal axis of the membrane is greater than the height of at least one, in particular the stabilizing rib arranged on the outside in the radial direction.
  • the stabilizing ribs are applied in the circumferential direction run around the underside of the membrane and cross or penetrate the radial ribs.
  • At least the stabilizing rib of the ring region arranged on the inside in the radial direction points in the axial direction the molded membrane has a greater height than at least one stabilizing rib which is arranged further out in comparison to this.
  • This also allows the stretching of the elastic membrane material to be reduced, which is particularly advantageous in the case of Teflon-coated molded membranes, since Teflon tends to crack easily due to its low elasticity.
  • One embodiment provides that the underside of the stabilizing rib arranged on the inside in the radial direction connects approximately flush with the underside of the radial ribs.
  • the rubber material used for the molded membrane can then flow better into the corner areas between the stabilizing and radial ribs during the vulcanization process.
  • the thickness of the inner stabilizing rib oriented in the axial direction of the shaped membrane is approximately as large or somewhat smaller than the thickness of the outer edge region of the central region adjacent to this stabilizing rib. This results in a particularly smooth transition between the central area and the ring area, by means of which the mechanical stresses which occur in the molded membrane during operation of the membrane pump are reduced.
  • the central area has a shoulder on the underside of the membrane, which forms a preferably stepped transition area to the ring area.
  • a particularly smooth and favorable for the power flow transition between the central area and the ring area can be achieved in that the underside of the radial ribs connects flush with the underside of the shoulder and that the height of the radial ribs decreases radially outwards at least between the shoulder and the radial stabilizing rib .
  • the stabilizing ribs which are preferably arranged at equal intervals radially offset from one another, form an approximately wavy profile in the radial direction with rounded transitions between the individual stabilizing ribs.
  • a rectangular cross section viewed in the circumferential direction of the molding membrane is preferred in order to achieve greater flexural rigidity.
  • a particularly advantageous embodiment provides that the central region narrows downward on its underside and is preferably approximately frustoconical in shape, that the central region has essentially radially-axially arranged stabilizing projections on its underside and that these protrude outward into the stabilizing ribs continue the ring area.
  • the supporting forces transmitted from the stabilizing ribs to the radial ribs can then be better introduced into the central area, so that bending or arching of the ring area in the direction of the pumping space is counteracted even more effectively when the molding membrane is subjected to a vacuum.
  • a diaphragm pump designated as a whole by 1 has a shaped diaphragm 2 made of elastic material, which is reinforced in its central region 3 in the stroke direction 4 and has a flexible ring region 5 around this central region 3. This is clamped on its outer circumference with a clamping edge 6 on the pump housing between the crankcase 7 and the pump head 8.
  • a molded core 9 designed as a driver core is vulcanized into the molded membrane 2, and a connecting rod 11 engages the threaded connector 10, with which the molded membrane 2 can be deflected from an upper to a lower dead center position and vice versa.
  • the pump head 8 has an inlet channel 12 and an outlet channel 13 for the medium to be pumped or suctioned, which each open into the pump chamber 16 delimited by the pump wall 14 of the pump head 8 and the membrane top 15.
  • the inlet and outlet channels 12, 13 are provided in a known manner with inclusion or outlet valves, which are not shown in FIG. 1 for reasons of clarity.
  • the membrane top 15 facing the pump chamber 16 in the central region 3 and the adjacent pump chamber wall 14 are geometrically adapted to one another. Both the pump chamber wall 14 and the molded membrane 2 are each spherical in their central area.
  • the shaped membrane 2 has on its underside 17 facing away from the pump chamber 16 in the ring area 5 a total of 18 evenly over the Circumferential ribs 18 distributed around the circumference of the ring area 5, which are combined with four stabilizing ribs 19 that run concentrically and at equal intervals from one another on the underside 17 of the ring area 5.
  • the support ribs 19 allow through the recesses between them, on which the shaped membrane 2 only one has a comparatively small wall thickness, a particularly flexible shaped membrane 2 around a circumferential line in the ring area 5, which converts only a very small proportion of the lifting energy applied into flexing work during the lifting movement.
  • the stabilization ribs 19 have a comparatively high bending stiffness, so that the deflection or curvature of the ring region 5 in the direction of the pump chamber 16 is reduced under vacuum.
  • the radial ribs 18 prevent the ring region 5 from bending excessively around a circumferential line of the shaped membrane 2 when subjected to negative pressure or vacuum in the pump chamber 16.
  • the diaphragm pump 1 Due to the combination of the radial ribs 18 with the supporting ribs 19 running in the circumferential direction, the diaphragm pump 1 has an improved volumetric efficiency, particularly at low suction pressures, which results in a greater pumping speed.
  • FIG. 5 shows the pumping speed curve 24 of the diaphragm pump 1 according to the invention in comparison to the pumping speed curve 25 of the diaphragm pump previously known from DE-PS 40 07 932 C2, which, although radial ribs 18, but has no stabilizing ribs 19 oriented in the circumferential direction.
  • the pumping speed in liters per hour is plotted as a function of the suction pressure of the diaphragm pump 1, which is given in absolute terms in millibars.
  • FIG. 5 shows that the diaphragm pump 1, which is equipped with radial and stabilizing ribs, has a significantly improved pumping speed compared to the diaphragm pump which has only radial ribs 18, especially at suction pressures below 10 mbar.
  • the minimum negative pressure against which the diaphragm pump 1 can still draw is reduced by about a third compared to the previously known diaphragm pump.
  • the diaphragm pump 1 according to the invention is therefore even more suitable as a vacuum pump and can in particular also be used as a backing pump for a turbo-molecular pump.
  • the stabilizing ribs 19 combined with the radial ribs 18 also reduce vibrations in the molded membrane 2, which can lead to the molded membrane 2 bumping against the adjacent pump chamber wall 14. This results on the one hand in a longer service life of the membrane, which is particularly advantageous in the case of relatively expensive, Teflon-coated molded membranes, and on the other hand also an impairment of the function of the inlet and outlet valves due to the wear of the molded membrane 2 when it hits the pump chamber wall 14 Particles largely avoided.
  • a total of four concentric stabilizing ribs 19 are arranged on the underside 17 of the ring area 5.
  • the stabilizing ribs 19 run closed on the underside of the membrane 17 and cross the radial ribs 18. The membrane forces can thereby be transmitted particularly well from the stabilizing ribs 19 to the radial ribs 18. Because everyone Radial rib 18 supports a plurality of stabilizing ribs 19, the bending moment of the radial ribs 18 around a circumferential line of the shaped membrane 2 is greater than that of the individual stabilizing ribs 19 around a diameter line of the shaped membrane 2. For this purpose, the radial ribs 18 have a greater height a than the height b three outer stabilizing ribs 19.
  • the inner stabilizing rib 19 has a greater height c than the height b of the outer stabilizing ribs 19. This results in the lifting movement of the molded membrane 2 in the transition region between Ring and central area a more uniform load on the elastic membrane material. If necessary, additional gradations can be provided for the height of the individual stabilizing ribs 19, this height becoming smaller and smaller as the distance from the central region 3 increases.
  • the height c of the inner stabilization ribs 19 is preferably chosen to be somewhat smaller than the thickness d of the outer edge of the central region 3 adjacent to these stabilization ribs 19.
  • a shoulder 20 is provided on the outer edge of the central area 3, which forms the transition to the ring area 5.
  • the thickness d of this shoulder 20 corresponds approximately to four times the height b of the outer stabilizing ribs 19.
  • the thickness of the ring region at the highest point of the inner stabilizing rib 19 is somewhat smaller than the thickness d of the shoulder 20.
  • the radial ribs 18 go along their inner, the longitudinal central axis 21 facing the molding membrane 2 directly into the shoulder 20 and extend with its outer end region into the thickened clamping edge 6.
  • the radial ribs 18 between the inner stabilizing rib 19 and the shoulder 20 are chamfered on their underside, so that in this area the height of the radial ribs 18 radially outwards decreases.
  • the radial ribs 18 have a constant rib height between the inner stabilizing rib 19 and the clamping edge 6.
  • the stabilizing ribs 19, which are offset with respect to one another, have an approximately wavy profile in the radial direction with rounded transitions.
  • the flow of force in the form membrane 2 is thereby to be distributed particularly uniformly over the available material cross section.
  • a rectangular cross section is provided for the radial ribs 18, since these are practically only subjected to bending in the longitudinal direction.
  • radially-axially arranged stabilizing projections 22 are provided on its underside, which extend from the flange 23 for the connecting rod 11 to the shoulder 20 and continue outward in the radial ribs 18 (FIG 1).
  • this increases the rigidity of the central region 3 and, on the other hand, the supporting forces absorbed by the radial ribs 18 can be transmitted even better to the central region.
  • annular intermediate membrane region 27 Radially inward from the shoulder 20 is an annular intermediate membrane region 27 which is arranged concentrically to the longitudinal axis 21 of the membrane and which has an approximately constant thickness both in the circumferential direction and along its radial extent.
  • the radial width of this intermediate region 27 corresponds approximately to its thickness.
  • Recesses 26 adjoin the intermediate region 27 radially inwards and between the Stabilizing projections 22 are arranged. In the area of these recesses 26, the shaped membrane 2 - viewed in the direction of the longitudinal central axis 21 - has an approximately 10% smaller thickness than in the intermediate area 27.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP96101648A 1995-03-24 1996-02-06 Pompe à membrane façonnée Expired - Lifetime EP0733802B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19510828A DE19510828C2 (de) 1995-03-24 1995-03-24 Membranpumpe mit einer Formmembran
DE19510828 1995-03-24

Publications (2)

Publication Number Publication Date
EP0733802A1 true EP0733802A1 (fr) 1996-09-25
EP0733802B1 EP0733802B1 (fr) 1998-08-26

Family

ID=7757644

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96101648A Expired - Lifetime EP0733802B1 (fr) 1995-03-24 1996-02-06 Pompe à membrane façonnée

Country Status (4)

Country Link
US (1) US5699717A (fr)
EP (1) EP0733802B1 (fr)
JP (1) JPH08261156A (fr)
DE (2) DE19510828C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024115010A1 (fr) * 2022-12-01 2024-06-06 Robert Bosch Gmbh Pompe à diaphragme

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29612117U1 (de) * 1996-07-11 1996-09-12 ASF THOMAS Industries GmbH, 82178 Puchheim Membrane für eine Membranpumpe
DE19647882A1 (de) * 1996-11-20 1998-05-28 Knf Neuberger Gmbh Membranpumpe
US6067893A (en) * 1998-03-10 2000-05-30 Westinghouse Air Brake Company Ribbed diaphragm
DE19906317C1 (de) * 1999-02-16 2000-10-19 Knf Flodos Ag Sursee Membranpumpe
US6295918B1 (en) * 1999-10-15 2001-10-02 John M. Simmons Suspended diaphragm
ATE368181T1 (de) * 2001-01-02 2007-08-15 Medela Holding Ag Membranpumpe
DE10227192B4 (de) * 2002-06-18 2009-08-06 Ulman Dichtungstechnik Gmbh Verbundmembran für Membranpumpen
DE10227193B4 (de) * 2002-06-18 2007-05-10 Ulman Dichtungstechnik Gmbh Verbundmembran für Membranpumpen
US6748848B1 (en) * 2002-12-11 2004-06-15 Gits Manufacturing Company, Llc Waste gate valve actuator
DE10312899A1 (de) * 2003-03-22 2004-10-07 Knf Neuberger Gmbh Membranpumpe
DE20307457U1 (de) * 2003-05-13 2003-07-31 GEMÜ Gebr. Müller Apparatebau GmbH & Co. KG, 74653 Ingelfingen Druckstück für ein Membranventil
ITTO20070440A1 (it) 2007-06-20 2007-09-19 Giorgio Tosini Coperchio flessibile a tenuta contro gli agenti atmosferici.
US20090001638A1 (en) * 2007-06-28 2009-01-01 Semaan Gilbert A Bellows structure
CA2722592C (fr) * 2008-05-16 2016-05-03 Joe Santa & Associates Pty Limited Soupape et diaphragme pour une pompe
DE202008007700U1 (de) * 2008-06-10 2009-10-22 Mann+Hummel Gmbh Handpumpe zum Pumpen von Kraftstoff
CN104791226A (zh) * 2014-01-16 2015-07-22 蔡应麟 隔膜增压泵的减震构造
CN104791235B (zh) * 2014-01-16 2018-10-26 蔡应麟 隔膜增压泵的减震方法
US20150198154A1 (en) * 2014-01-16 2015-07-16 Ying Lin Cai Vibration-reducing structure for compressing diaphragm pump
JP6080080B2 (ja) * 2014-05-20 2017-02-15 蔡応麟 ４圧縮チャンバダイアフラムポンプの振動低減構造
US10173183B2 (en) 2014-09-11 2019-01-08 Flowserve Management Company Diaphragm pump with improved tank recirculation
US9896829B2 (en) 2014-09-12 2018-02-20 Zurn Industries, Llc Flush valve diaphragm
JP6412460B2 (ja) 2015-04-14 2018-10-24 株式会社Ｓｏｋｅｎ 走行路推定装置
TWI659719B (zh) * 2017-02-09 2019-05-21 瑞士商耐斯泰克公司 用於飲料製備模組之薄膜泵
KR102734939B1 (ko) * 2017-02-17 2024-11-28 한온시스템 주식회사 사판식 압축기의 리어 헤드
US10677238B2 (en) * 2017-11-08 2020-06-09 Ingersoll-Rand Industrial U.S., Inc. Filled resin layer separated pump housing
US10859540B2 (en) * 2018-08-03 2020-12-08 Chromatography Research Supplies, Inc. Duckbill septum
DE102020126241B4 (de) * 2020-10-07 2026-03-19 Alfmeier Präzision SE Membrananordnung mit um den Membrankörper umlaufendem Ring sowie Sitzanordnung und Pumpenanordnung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0010943A1 (fr) * 1978-10-30 1980-05-14 Jr. Alan Dean Tuck Pompe à diaphragme actionnée par un fluide sous pression
FR2482674A1 (fr) * 1980-05-16 1981-11-20 Wagner Gmbh J Diaphragme pour pompes foulantes a haute pression, compresseurs ou analogues
DE4007932A1 (de) * 1990-03-13 1991-09-19 Knf Neuberger Gmbh Membranpumpe mit einer formmembrane

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2840339A (en) * 1953-05-13 1958-06-24 Saunders Valve Co Ltd Diaphragm valves and diaphragms therefor
US3135173A (en) * 1961-10-26 1964-06-02 Midland Ross Corp Diaphragm
GB950678A (en) * 1961-11-16 1964-02-26 Nat Res Dev Improvements in and relating to diaphragms and diaphragm-operated machines
US3911796A (en) * 1973-02-12 1975-10-14 Gates Rubber Co Diaphragm
US3872777A (en) * 1973-05-30 1975-03-25 Berg Manufacturing Co Diaphragm
US4270441A (en) * 1978-10-30 1981-06-02 Wilden Pump & Engineering Co. Pump diaphragm
JPS59577B2 (ja) * 1979-08-13 1984-01-07 新日本製鐵株式会社 冷延鋼帯の短時間連続焼鈍方法
JPS60211052A (ja) * 1984-04-03 1985-10-23 Hitachi Ltd プラスチック成型用型材およびその製造方法
US5335584A (en) * 1993-03-30 1994-08-09 Baird Dayne E Improved diaphragm
US5349896A (en) * 1993-06-14 1994-09-27 W. L. Gore & Associates, Inc. Pump diaphragm
DE4328559C5 (de) * 1993-08-25 2004-11-25 Knf-Neuberger Gmbh Membranpumpe mit wenigstens zwei Membranen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0010943A1 (fr) * 1978-10-30 1980-05-14 Jr. Alan Dean Tuck Pompe à diaphragme actionnée par un fluide sous pression
FR2482674A1 (fr) * 1980-05-16 1981-11-20 Wagner Gmbh J Diaphragme pour pompes foulantes a haute pression, compresseurs ou analogues
DE4007932A1 (de) * 1990-03-13 1991-09-19 Knf Neuberger Gmbh Membranpumpe mit einer formmembrane

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024115010A1 (fr) * 2022-12-01 2024-06-06 Robert Bosch Gmbh Pompe à diaphragme

Also Published As

Publication number Publication date
US5699717A (en) 1997-12-23
DE19510828A1 (de) 1996-09-26
DE59600466D1 (de) 1998-10-01
DE19510828C2 (de) 1998-12-24
EP0733802B1 (fr) 1998-08-26
JPH08261156A (ja) 1996-10-08

Similar Documents

Publication Publication Date Title
EP0733802B1 (fr) Pompe à membrane façonnée
DE4328559C2 (de) Membranpumpe mit wenigstens zwei Membranen
EP1153218B1 (fr) Pompe a membrane
DE4007932C2 (fr)
DE2713599C2 (fr)
DE19634922C2 (de) Membranpumpe
DE3405351C2 (de) Hochdruckdichtung
EP0604740A1 (fr) Pompe à membrane
EP3978751A1 (fr) Membrane composite pour pompes à membrane
EP1525399B1 (fr) Pompe a diaphragme
DE60315785T2 (de) Pumpe
EP0731273A2 (fr) Piston avec tige de piston
EP1532366B1 (fr) Pompe pour appareil de nettoyage haute pression
DE29505021U1 (de) Membranpumpe mit einer Formmembran
DE9406216U1 (de) Membranpumpe mit einer Formmembran
EP0112404B1 (fr) Pompe à deux cylindres pour liquides visqueux, de préférence pompe à béton
EP0017789B1 (fr) Arrangement piston et cylindre
WO1998022713A1 (fr) Pompe a membrane
CH704934B1 (de) Vakuumventil.
DE1085642B (de) Kolbenkompressor zum Foerdern von gasfoermigem Medium
DE102015006126A1 (de) Exzenterscheibenstruktur für Verdichtungsmembranpumpe mit Mehrfachwirkungen
EP0929743A1 (fr) Pompe a piston radial
EP0263199B2 (fr) Compresseur à membrane
DE102023115951A1 (de) Statorauskleidung, Stator sowie Verfahren zum Herstellen einer Statorauskleidung
DE10312898A1 (de) Hubkolbenmaschine

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: A1

Designated state(s): DE FR GB

17P Request for examination filed

Effective date: 19960831

17Q First examination report despatched

Effective date: 19971014

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

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

REF Corresponds to:

Ref document number: 59600466

Country of ref document: DE

Date of ref document: 19981001

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

Effective date: 19981215

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

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20150309

Year of fee payment: 20

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

Ref country code: GB

Payment date: 20150219

Year of fee payment: 20

Ref country code: FR

Payment date: 20150115

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59600466

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20160205

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 EXPIRATION OF PROTECTION

Effective date: 20160205