EP0191936B1 - Pompe à diaphragme à balayage circulant - Google Patents

Pompe à diaphragme à balayage circulant Download PDF

Info

Publication number
EP0191936B1
EP0191936B1 EP85116076A EP85116076A EP0191936B1 EP 0191936 B1 EP0191936 B1 EP 0191936B1 EP 85116076 A EP85116076 A EP 85116076A EP 85116076 A EP85116076 A EP 85116076A EP 0191936 B1 EP0191936 B1 EP 0191936B1
Authority
EP
European Patent Office
Prior art keywords
diaphragm pump
flow
pump according
conduit
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
EP85116076A
Other languages
German (de)
English (en)
Other versions
EP0191936A2 (fr
EP0191936A3 (en
Inventor
Eberhard Schlücker
Adolf Müller
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.)
Lewa Herbert Ott GmbH and Co KG
Original Assignee
Lewa Herbert Ott GmbH and Co KG
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 Lewa Herbert Ott GmbH and Co KG filed Critical Lewa Herbert Ott GmbH and Co KG
Publication of EP0191936A2 publication Critical patent/EP0191936A2/fr
Publication of EP0191936A3 publication Critical patent/EP0191936A3/de
Application granted granted Critical
Publication of EP0191936B1 publication Critical patent/EP0191936B1/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
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • the invention relates to a diaphragm pump according to the preamble of claim 1.
  • the invention is therefore based on the object of providing the diaphragm pump of the generic type with a circulating flush, which can be implemented with extremely little design effort and is independent of the number (over 1) of the connecting channels provided, so that, in particular in the case of small diaphragm pumps, the setting is prevented by gas bubbles and at the same time it is achieved that the gas bubbles are automatically transported to a point at which they are removed from the piston chamber or from the membrane working space.
  • the mean flow velocity is understood here to mean the difference between the flow velocity during the suction stroke and that during the pressure stroke.
  • gas bubbles which may settle in the connecting channels, are practically transported in the manner of a pilgrim step method in a certain desired direction, with a movement of the gas bubbles in the direction of the suction stroke in all those channels in which the flow resistance has not been changed.
  • the gas bubbles are transported in the direction of the pressure stroke, i. H. in the direction of the membrane.
  • the diaphragm pump according to the invention is characterized in that only a single channel has to be so modified that the flow resistance prevailing here for the hydraulic medium moved by the displacement piston during the pressure stroke as well as during the suction stroke is different in one flow direction from that in the other flow direction , so that a transport flow for gas bubbles contained in the hydraulic medium acting in the manner of the vocational method is thus formed in all channels.
  • a special constructive embodiment of the invention can be seen in the fact that the modified channel has a resistance body which can be moved between two positions under the action of the flow of the hydraulic medium and which in one position has no influence on the flow rate of the hydraulic medium, but in the other position generates an increased flow resistance and thus reduces the flow rate of the hydraulic medium.
  • this resistance body is formed by a pin which is arranged in an approximately perpendicular bore section of the modified channel and, in its position which exerts the increased flow resistance, rests on a shoulder of the bore section under the action of gravity.
  • the pin serving as a resistance body is to be designed according to the invention in such a way that the flow resistance of the channel having this pin is very high in the suction stroke.
  • Such a pin does not necessarily have to sit sealingly on the shoulder of the bore section, but only has to produce a flow resistance during the suction stroke in the channel in question, which is very high compared to that during the pressure stroke.
  • the pin serving as a resistance body is expediently provided with chamfered edges at least at its lower end, so that it is thereby possible to influence the extent of the increase in the flow resistance in the suction stroke by a corresponding design of the pin.
  • the invention provides the essential advantage that it can be used with all pump sizes, since only a small amount of construction and cost is required to achieve the flushing or circulating flushing provided according to the invention.
  • the special type of flushing is also possible with all pump sizes because only a part of the hydraulic medium has to flow past the resistance body.
  • the application of the invention is independent of the number of connection channels provided, which provides a further significant advantage.
  • the invention therefore fulfills two basic requirements, namely that the flow or connection channels can be as small as possible in cross section in order to avoid damage to the membrane in its rear contact.
  • the pressure loss in the connecting channels should also be as small as possible.
  • several, that is at least two, flow channels must be provided for the connection between the piston chamber and the membrane working chamber, although it should be advantageous to provide, for example, five or six flow channels.
  • the mean flow velocity i.e. H. the temporal mean value of the flow velocity, is different from zero and that there is therefore no purely pulsating flow. This is important according to the invention because experience has shown that gas bubbles which are located in the respective connecting channel in the case of a purely pulsating flow are never transported out of this channel.
  • the mean flow velocity which is designed differently from zero according to the invention, is always directed in the direction of the degassing space.
  • this valve is arranged in the modified channel in such a way that it opens during the suction stroke and closes during the pressure stroke.
  • the other channel is expediently designed such that it has a high flow resistance.
  • the channel having the high flow resistance is designed as a thin bore.
  • a particularly advantageous embodiment is present when the high flow resistance, ie. H.
  • the channel having the throttle cross section is arranged geodetically higher than the channel which has the valve opening in the suction stroke, since in this channel provided with the throttle cross section, H. both during the suction stroke and during the pressure stroke, a gas bubble transport takes place and therefore this channel should be located at the geodetic point that the gas bubbles always strive for due to their buoyancy in the hydraulic medium.
  • a diaphragm 1 is provided in the diaphragm pump shown, which separates a delivery space 2 which receives the pumped medium from a diaphragm working space 3.
  • the membrane working space 3 is arranged in the end face of a pump housing 4, which in turn is closed by a housing cover 5 which contains the delivery chamber 2.
  • a housing cover 5 which contains the delivery chamber 2.
  • a piston chamber 10 is also provided in the manner shown, in which a displacement piston 11 can be moved back and forth for the oscillating actuation of the membrane 1.
  • the piston chamber 10 is connected to the diaphragm working chamber 3 via two essentially horizontal connecting channels 12, 13.
  • the entirety of membrane working space 3, connecting channels 12, 13 and piston space 10, which is acted upon by the displacement piston 11, represents a pressure space which is filled with hydraulic medium as a whole.
  • a vertical bore section 14 is formed within the upper connecting channel 13, which has a shoulder 15 at its lower end and reciprocally receives a pin 16 serving as a resistance body.
  • This pin 16 is provided at both ends with chamfered edges 17 and is only under the action of gravity, so that it during the suction stroke, i. H.
  • the middle channel 13 results in an average flow velocity - and thus a migration of any gas bubbles - in the direction of the membrane 1, while this average flow velocity in the lower channel 12 in the sense of the required forced compensation in the direction of the piston chamber 10 or the pressure stroke and thus the gas bubbles located in this channel 12 are also transported in the direction of the piston chamber 10.
  • Ventilation channels 18, 19 in the usual way, which originate from the geodetically highest point of the membrane work chamber 3 or the piston chamber 10 and via a gas discharge valve 20 or sniffer valve 21 open into the open or into a suitable container.
  • the modified embodiment according to FIG. 2 differs from that according to FIG. 1 in that the horizontal section of the upper connecting channel 13, which in the embodiment according to FIG. 1 runs between the piston chamber 10 and the vertical bore section 14, in the embodiment according to FIG Fig. 2 is omitted, so that this vertical bore section 14 opens directly into the piston chamber 10.
  • one of the two connecting channels 12 and 13, namely the upper channel 13, is provided with an extension 13a which connects to the piston chamber 10.
  • the geodetically lower channel 12 is provided with a vertical channel section 12 ', which connects directly to the piston working space 10 and has a valve 22.
  • This valve 22 is arranged such that, as can be seen from FIG. 4, it opens during the suction stroke of the displacer 11 and closes during the pressure stroke.
  • this channel 13 has a high flow resistance.
  • this channel 13 is a thin hole, i.e. H. formed such that its passage cross section is significantly smaller than that of the geodetically lower channel 12.
  • the channel 13 does not directly adjoin the piston chamber 10 at one end, but is connected to this piston chamber 10 via the vertical bore section 14, which connects the piston chamber 10 to the gas discharge valve 20.
  • the arrangement and design of the channels 12, 13 is such that their total flow resistance during the suction stroke is small, since the valve 22 located in the lower channel 12 opens during the suction stroke and thus that from the individual cross sections of the Channels 12, 13 formed total cross-section for return transport of the hydraulic medium is available during the suction stroke. This causes the gas bubbles to be transported in such a way that they move both in the lower channel 12 and in the upper channel 13 from the membrane working chamber 3 in the direction of the piston chamber 10.
  • the total flow resistance of the channels 12, 13 during the pressure stroke of the displacer 11 is large, since in such a case no transport of hydraulic medium takes place through the lower channel 12 due to the then closed valve 22 and the entire transport of the hydraulic medium from the piston chamber 10 to the diaphragm working chamber 3 is effected through the channel 13. Accordingly, during the pressure stroke, the gas bubbles approximately formed in the hydraulic medium move in the direction of the diaphragm working space 3 in the direction of the membrane working space 3, namely at a flow velocity that is greater than that of the gas bubbles during the suction stroke of the displacer 11. Thus, overall there is a transport flow which the gas bubbles ultimately transported via the vertical bore section 14 to the gas discharge valve 20. The desired rinsing effect is thus achieved overall.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (13)

1. Pompe à diaphragme avec un diaphragme qui sépare une chambre de refoulement d'une chambre de travail entièrement remplie d'un fluide hydraulique, et une chambre de piston, qui est reliée par deux conduits au moins à une chambre de travail à diaphragme dans laquelle un piston de refoulement peut être déplacé d'un mouvement de va-et-vient pour la commande des oscillations du diaphragme, dont les conduits d'expulsion des bulles de gaz sont conçus de manière telle que la vitesse moyenne d'écoulement est orientée suivant une direction de course, caractérisée en ce que la disposition et le mode de réalisation des conduits (12, 13) mettant en rotation la chambre de travail (3) et la chambre de piston (10) sont prévus de telle sorte que la résistance à l'écoulement d'une partie seulement des conduits (12, 13) est différente dans un sens d'écoulement de la résistance dans l'autre sens d'écoulement, ce qui procure ainsi dans l'ensemble un courant de transport dans tous les conduits (12, 13) pour les bulles de gaz contenues dans le fluide hydraulique.
2. Pompe à diaphragme selon la revendication 1, caractérisée en ce que la disposition et le mode de réalisation des conduits (12, 13) sont tels que la résistance totale à l'écoulement de tous les conduits (12, 13) est moindre pour la course d'aspiration que pour la course de refoulement.
3. Pompe à diaphragme selon la revendication 1 ou 2, caractéisée en ce qu'un seul conduit (12 ou 13) est réalisé modifié de telle sorte que sa résistance à l'écoulement dans l'un des sens d'écoulement est différente de sa résistance dans l'autre sens d'écoulement.
4. Pompe à diaphragme selon la revendication 3, caractérisée en ce que le conduit (13) modifié dans son exécution présente, en raison de l'écoulement du fluide hydraulique, un corps de résistance mobile entre deux positions, qui, dans l'une des positions, n'a pas d'influence sur la vitesse d'écoulement du fluide hydraulique, mais qui, dans l'autre position, produit une résistance à l'écoulement accrue et réduit ainsi la vitesse d'écoulement du fluide hydraulique.
5. Pompe à diaphragme selon la revendication 4, caractérisée en ce que le corps de résistance est constitué par une cheville (16) qui est disposée dans une partie de l'alésage (14) s'étendant de manière sensiblement verticale du conduit modifié dans sa réalisation.
6. Pompe à diaphragme selon la revendication 5, caractérisée en ce que la cheville (16) dans sa position exerçant une résistance à l'écoulement accrue repose, sous l'effet de la gravité, sur un épaulement (15) de la partie d'alésage (14).
7. Pompe à diaphragme selon la revendication 5 ou 6, caractérisée en ce que la cheville (16) servant de corps de résistance est pourvue, au moins à une de ses extrémités, de bords chanfreinés (17), notamment à son extrémité inférieure.
8. Pompe à diaphragme selon la revendication 3, caractérisée en ce que le conduit (13) modifié dans son exécution présente un élargissement de sa section.
9. Pompe à diaphragme selon l'une des revendications 1 à 4, caractérisée en ce que le conduit (12) modifié dans son exécution présente une soupage (22).
10. Pompe à diaphragme selon la revendication 9, caractérisée en ce que la soupage (22) est disposée dans le conduit (12) modifié dans son exécution de manière telle qu'elle s'ouvre pour la course d'aspiration et se ferme pour la course de refoulement.
11. Pompe à diaphragme selon la revendication 9, caractérisée en ce que l'autre conduit (13) est constitué de manière à présenter une résistance à l'écoulement élevée.
12. Pompe à diaphragme selon la revendication 11, caractérisée en ce que le conduit (13) présentant la résistance à l'écoulement élevée est constitué avec un alésage étroit.
13. Pompe à diaphragme selon l'une des revendications 1 à 12, caractérisée en ce que la chambre de piston (10) et/ou la chambre de travail à diaphragme (3) présente un canal d'aération (18 ou 19) séparé.
EP85116076A 1984-12-21 1985-12-17 Pompe à diaphragme à balayage circulant Expired - Lifetime EP0191936B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843446952 DE3446952A1 (de) 1984-12-21 1984-12-21 Membranpumpe mit umlaufspuelung
DE3446952 1984-12-21

Publications (3)

Publication Number Publication Date
EP0191936A2 EP0191936A2 (fr) 1986-08-27
EP0191936A3 EP0191936A3 (en) 1987-02-25
EP0191936B1 true EP0191936B1 (fr) 1990-03-07

Family

ID=6253582

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85116076A Expired - Lifetime EP0191936B1 (fr) 1984-12-21 1985-12-17 Pompe à diaphragme à balayage circulant

Country Status (4)

Country Link
US (1) US4832581A (fr)
EP (1) EP0191936B1 (fr)
JP (1) JPS61197778A (fr)
DE (2) DE3446952A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01203672A (ja) * 1988-02-03 1989-08-16 Karl Eickmann 高圧ポンプ又はコンプレッサ装置
US5262068A (en) * 1991-05-17 1993-11-16 Millipore Corporation Integrated system for filtering and dispensing fluid having fill, dispense and bubble purge strokes
DE19840365A1 (de) * 1998-09-04 2000-03-09 Bran & Luebbe Membrankolbenpumpe
ATE367527T1 (de) * 2001-04-27 2007-08-15 Hydrocision Inc Hochdruckeinwegpumpenkassette zur anwendung auf medizinischem gebiet
DE10209758B4 (de) * 2002-03-05 2004-11-18 Horst Kleibrink Verfahren zur Optimierung der Gasströmung innerhalb eines Membrankompressors
JP2003343469A (ja) * 2002-03-20 2003-12-03 Toyota Industries Corp 真空ポンプ
US7021909B1 (en) * 2003-07-16 2006-04-04 Trebor International, Inc. Oscillator for pneumatic pump having single valve
JP4526350B2 (ja) * 2004-10-29 2010-08-18 シーケーディ株式会社 薬液供給用ポンプ
FR2941749A1 (fr) * 2009-02-03 2010-08-06 Milton Roy Europe Pompe a membrane elastique a commande hydraulique
EP2362101B1 (fr) * 2010-02-18 2013-07-03 Grundfos Management A/S Pompe de dosage
DE102010039829A1 (de) * 2010-08-26 2012-03-01 Prominent Dosiertechnik Gmbh Membranpumpe mit trägheitsgesteuertem Leckergänzungsventil
CN103352833B (zh) * 2013-08-01 2015-10-28 山东荣利中石油机械有限公司 一种能在运行中调节流量的隔膜泵液力端
MX2016008049A (es) * 2013-12-20 2018-01-23 Tetra Laval Holdings & Finance Sensor de la conductividad, y bomba que comprende tal sensor.
FR3021713B1 (fr) * 2014-05-27 2019-04-05 Milton Roy Europe Pompe a membrane a commande hydraulique comprenant un chemin de degazage dedie

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US29055A (en) * 1860-07-10 Island
US2578746A (en) * 1946-12-12 1951-12-18 Mills Ind Inc Fluid pump
DE1053316B (de) * 1957-05-23 1959-03-19 Sigma Lutin Entlueftungsvorrichtung fuer hydraulisch durch Plunger betaetigte Membranpumpen
DE2216215A1 (de) * 1972-04-04 1973-10-18 Ott Kg Lewa Membranpumpe
US3767326A (en) * 1972-08-04 1973-10-23 Yarway Corp Volumetric flow control system for pumps
DE2421487A1 (de) * 1973-05-24 1975-01-30 Milton Roy Co Membranpumpe
DE2923284A1 (de) * 1979-06-08 1980-12-11 Wagner Gmbh J Verfahren und vorrichtung zur leistungsregelung von membranpumpen
DE2930765C2 (de) * 1979-07-28 1983-01-05 BURDOSA Ing. Herwig Burgert, 6305 Buseck Gelochte Stützscheibe für die Membran einer hydraulisch betätigten Membranpumpe
ATE10670T1 (de) * 1980-12-29 1984-12-15 Lewa Herbert Ott Gmbh + Co. Membranpumpe mit druckentlastet eingespannter membran.
EP0085725B1 (fr) * 1982-02-05 1984-11-28 Bran & Lübbe GmbH Pompe à membrane entraînée par un piston

Also Published As

Publication number Publication date
DE3576387D1 (de) 1990-04-12
EP0191936A2 (fr) 1986-08-27
EP0191936A3 (en) 1987-02-25
JPS61197778A (ja) 1986-09-02
JPH0415400B2 (fr) 1992-03-17
US4832581A (en) 1989-05-23
DE3446952A1 (de) 1986-07-10

Similar Documents

Publication Publication Date Title
EP0191936B1 (fr) Pompe à diaphragme à balayage circulant
DE2530212C2 (de) Verfahren und Vorrichtung zum Saugkraftausgleich einer Flüssigkeitskolbenpumpe
DE2840445A1 (de) Hydraulische einrichtung zum betaetigen von gaswechselventilen
DE2028603A1 (fr)
DE1188886B (de) Steuerung fuer einen doppeltwirkenden Druckmittelmotor mit einem Steuerschieber
EP0427165A1 (fr) Système hydraulique, en particulier arrangement de valves pour un vérin alimenté par une pompe
DE3115088A1 (de) Mehrabschnitts-steuerventilbank
DE3013381C2 (de) Arbeitskolben-Zylinder-Einheit
DE2705585A1 (de) Druckbegrenzungsventil
EP0283026B1 (fr) Méthode et dispositif de démarrage d'une pompe à membrane chargée
DE3048776A1 (de) Druckwandlergeraet
DE69222861T2 (de) Hydraulische schaltung mit druckausgleichventil
DE3219730C2 (fr)
DE1130657B (de) Steuerschieber
DE19514244A1 (de) Hydraulische Zahnstangenlenkung
DE8437633U1 (de) Membranpumpe mit Umlaufspülung
DE3810490C2 (fr)
DE2940235C2 (de) Einrichtung zum selbsttätigen Ergänzen des Schmieröls in der Kurbelwanne einer Brennkraftmaschine
DE19512143C1 (de) Druckabschneidungsventil mit Wechselventilkolben
DE4118600C2 (de) Dosierpumpeneinrichtung mit einem Entlüftungsventil
DE2216215A1 (de) Membranpumpe
DE68916946T2 (de) Steuerungsventil.
DE2240012B2 (de) Steuereinrichtung für hydrostatische Lenkungen u.dgl
DE2733523A1 (de) Hydrauliksystem, insbesondere fuer landwirtschaftlich oder bauwirtschaftlich nutzbare zug- oder arbeitsmaschinen
DE101662C (fr)

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): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19870514

17Q First examination report despatched

Effective date: 19880714

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

ITF It: translation for a ep patent filed
REF Corresponds to:

Ref document number: 3576387

Country of ref document: DE

Date of ref document: 19900412

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19901213

Year of fee payment: 6

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

ITTA It: last paid annual fee
26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19910226

Year of fee payment: 6

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

Ref country code: GB

Payment date: 19911202

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19920831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19920901

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19921217

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

Effective date: 19921217