WO1995013473A1 - Pompe pour le dosage de liquides - Google Patents

Pompe pour le dosage de liquides Download PDF

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Publication number
WO1995013473A1
WO1995013473A1 PCT/EP1993/003156 EP9303156W WO9513473A1 WO 1995013473 A1 WO1995013473 A1 WO 1995013473A1 EP 9303156 W EP9303156 W EP 9303156W WO 9513473 A1 WO9513473 A1 WO 9513473A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pump according
pressure
pump
liquid
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.)
Ceased
Application number
PCT/EP1993/003156
Other languages
German (de)
English (en)
Inventor
Michael Wally
Christian Arnold
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.)
Prominent Dosiertechnik GmbH
Original Assignee
Prominent Dosiertechnik 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
Priority to DE4219663A priority Critical patent/DE4219663C2/de
Application filed by Prominent Dosiertechnik GmbH filed Critical Prominent Dosiertechnik GmbH
Priority to PCT/EP1993/003156 priority patent/WO1995013473A1/fr
Priority to JP7513547A priority patent/JPH08506162A/ja
Publication of WO1995013473A1 publication Critical patent/WO1995013473A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/06—Venting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K24/00—Devices, e.g. valves, for venting or aerating enclosures
    • F16K24/04—Devices, e.g. valves, for venting or aerating enclosures for venting only

Definitions

  • the invention relates to a liquid metering pump with a pump chamber, the volume of which increases during a suction stroke and decreases during a pressure stroke, and a vent valve device is arranged at the upper end thereof.
  • Metering pumps of this type are designed, for example, as piston pumps, but in particular as membrane pumps. If such a pump is to pump liquid into a system under higher pressure, the performance of the pump will be reduced or it will fail completely as soon as gas enters the pump chamber. In contrast to liquids, gas is compressible. In this case, the movement of the piston or the membrane does not push liquid out of the pump chamber into the system, but rather the gas volume is reduced. The gas reaches the pen chamber, for example, when changing the storage container from which the liquid is drawn off, or in the case of outgassing liquids. In particular in the case of higher concentrated liquids which are to be metered with the metering pump,
  • a venting device for a liquid piston pump is known from DE 28 03 470 C3, in which a vent switching valve, a throttle and a check valve are arranged side by side.
  • the check valve opens into a return line to the tank.
  • the throttle should be set so that it allows gases to pass through, while practically completely throttling liquids.
  • extensive experience and appropriately qualified specialist personnel are required to set such a choke. Particularly when the pressure fluctuates, it cannot be avoided that significant quantities of liquid escape through the throttle. If, on the other hand, the throttle gap is set too small, the desired venting effect does not occur. The venting effect is sufficient in normal operation.
  • EP 0 354 484 B1 shows a further metering pump with a vent valve and a membrane acting as a piston. After a predetermined number of piston strokes, this vent valve is opened for a further predetermined number of piston strokes via a gear mechanism or an electromagnet and then closed again.
  • this has the advantage that complete venting can be carried out in the pump chamber even with large amounts of gas, without external intervention being necessary. In operation, however, such a vent is extremely unsatisfactory. enough. Since the ratio of opening times to closing times is fixed, on the one hand it can happen that liquid escapes through the vent valve when all gas has already been displaced from the pump chamber. Conversely, it can also happen that the opening times of the vent valve device are too short to allow all gas to escape.
  • the invention is therefore based on the object of specifying a liquid metering pump with an improved venting possibility.
  • vent valve device has a flow-actuated valve, the response of which is determined by the state of aggregate of the fluid flowing through.
  • the physical state of the flowing fluid can be that of a liquid or that of a gas. As long as gas flows through the valve, it remains open. Only when liquid flows through the valve does it respond and close. As a result, the pump chamber is actually vented as required. The venting only takes effect when there is gas in the pump chamber. If the pump chamber is completely filled with liquid, liquid will already flow through the valve at the beginning of the pressure stroke, which closes it immediately and prevents further liquid leakage. The reverse remains
  • Valve opened for the required time, ie the required number of pressure strokes, until all of the gas has been displaced from the pump chamber.
  • the metering pump thus vented itself in the fastest possible way, regardless of whether the pump chamber is completely filled with gas, as is the case, for example, with an initial start-up may be the case, or whether only small amounts of gas have escaped from the liquid, as can occasionally occur during operation.
  • the valve is normally open and generates a state-dependent pressure drop in the outflowing fluid which acts on the valve in the closing direction and which is only large enough in the case of liquid to close the valve.
  • a closing force is generated via the valve which is large enough to close the valve, that is to say to prevent or interrupt the flow of liquid.
  • the force necessary to close the valve is basically generated by the piston or diaphragm, which reduces the size of the pump chamber during a pressure stroke.
  • the power required to close the valve is negligibly small compared to the pump power, so that this additional load on the diaphragm or the piston is negligible.
  • the valve advantageously closes against a predetermined opening force, the pressure drop for gas producing a smaller force and for liquid a greater force than the opening force.
  • this opening force on the one hand, the state of rest of the valve is defined.
  • this creates a threshold value that allows a distinction to be made between gases and liquids. So the valve has a built-in pressure or force measurement function. Only when the opening force is exceeded, which is by definition only the case with the flow of liquids the valve closes. Otherwise it remains open for ventilation.
  • the valve in the flow path of the fluid preferably has a throttle, which forms an outlet of a pressure chamber, in which an actuating element, which is connected to a closing body and can be moved against a valve seat, and to which the pressure in the pressure chamber acts.
  • the fluid creates a pressure drop across the throttle. This pressure drop is smaller for gases than for liquids. In the case of liquids, it is large enough to increase the pressure in the pressure chamber so that it can move the closing body against the valve seat via the actuating element. In the event of a corresponding drop in pressure, which can be caused by a liquid flow, but not by a gas flow, the closing body is moved against the valve seat and prevents further leakage of liquid. Conversely, it can be achieved with such a construction that gas can easily pass through at the flow speeds for which the pump is designed.
  • the closing body forms the actuating element, the throttle between
  • a fluid flow causes a pressure drop, which in turn leads to an increase in pressure in the pressure chamber.
  • This pressure presses the closing body against the valve seat while reducing the size of the gap.
  • This creates a kind of self-increasing effect because with a narrowing gap, i.e. a more throttling throttle, the pressure drop across the valve very quickly increases and leads to a correspondingly rapid increase in pressure in the pressure chamber.
  • This rapid increase in pressure in turn leads to a very rapid closing of the valve, ie to a very rapid movement of the closing body onto the valve seat.
  • the closing body is preferably designed as a membrane made of elastic material which, when installed, has a prestress.
  • the preload serves to generate the opening force.
  • the pretension defines a rest position of the membrane.
  • the preload can be caused by the shape of the membrane. However, it can also only be generated by tensioning the membrane during installation.
  • the membrane preferably has an opening approximately in the middle, at least one outlet channel opening eccentrically into the valve seat.
  • the membrane can therefore be clamped in its entire edge area, which leads to high mechanical stability of the valve and convenient manufacturing options. Furthermore, such a configuration allows a relatively large opening of the valve. In the middle area of the membrane, in which the distance to the edge clamping is greatest, the membrane also permits the greatest deflection.
  • the opening is advantageously surrounded by an annular bead which, in the closed position, bears against an essentially flat surface of the valve seat. With such a configuration, the opening is sealed immediately.
  • the valve seat and / or the closing body advantageously has a structure on its closing surface which limits the contact between the closing body and the valve seat to relatively narrow or small surface areas. This prevents the closing body from being sticks to the seat, which could possibly be caused by suppressing it after closing. Such sticking is prevented with a high degree of reliability by the relatively narrow surface areas, which may well approximate a line contact.
  • the surface areas are preferably designed as concentric rings or knobs. These surround the opening in the middle and lead to a graduated sealing of the closing body on the valve seat to the outside.
  • outlet channels open radially offset between individual rings.
  • Several outlet channels have a corresponding flow capacity, so that ventilation can take place relatively quickly.
  • the concentric rings or knobs ensure, when a liquid flow occurs, that the valve can be closed very quickly. Any gas remaining between the membrane and the valve seat can still escape through outlet channels located further outside, while the membrane is already beginning to close from the inside to the outside.
  • the pump chamber is preferably provided with an outlet valve which only opens at a predetermined minimum pressure. This minimum pressure can then be used to ensure ventilation. Even if only small gas residues remain in the pump chamber, which due to their small volume can only be compressed to a small extent, blocking the pump chamber outlet means that these small gas residues can also be reliably removed from the pump chamber.
  • the flow-actuated valve is advantageously arranged in series with a check valve. This Check valve prevents gas from being sucked into the pump chamber via the flow-actuated valve during a suction stroke.
  • the check valve is preferably arranged in the flow direction behind the flow-actuated valve. The check valve then does not cause a pressure drop which could have a disruptive effect on the function of the flow-operated valve.
  • the membrane is advantageously formed from metal, in particular stainless steel or Hastelloy, an elastomer or a plastic, PVDF or PTFE or a composite of these materials. With such materials it can be assumed with a high degree of reliability that the fluid does not stick and leads to a malfunction of the valve function.
  • FIG. 1 shows a first embodiment of a liquid metering pump
  • FIG 3 shows a second embodiment of a liquid metering pump.
  • a liquid metering pump 1 has a pump chamber 2 which is delimited by a housing 3 and a membrane 4. Instead of the membrane 4, a piston can also be used.
  • the membrane 4 is moved back and forth via an actuating rod 5 by a drive (not shown in more detail).
  • a drive not shown in more detail.
  • the volume of the pump chamber 2 decreases.
  • the suction stroke When the diaphragm 4 moves to the right, the volume of the pump chamber 2 increases. Such a movement is referred to below as the suction stroke.
  • An inlet connection 6 opens into the pump chamber 2 and can be connected to a feed line (not shown in more detail) via a screw connection 7.
  • An inlet valve 8 which is designed as a gravity-operated check valve, is arranged between the pump chamber 2 and the inlet connection 6.
  • the valve body shown as a ball is lifted from its seat and clears the way from the inlet connection 6 into the pump chamber 2.
  • the ball is pressed onto the valve seat and prevents the fluid in the pump chamber 2 from escaping into the inlet connection 6.
  • the pump chamber is also connected to an outlet connection 9, which is not connected to a screw connection 10 by a screw connection 10 Dosing line shown in more detail can be connected.
  • An outlet valve 11 is arranged between the outlet connection 9 and the pump chamber 2 and opens against the force of a spring 12 in the outlet direction.
  • the spring 12 defines an opening pressure. The outlet valve 11 opens only when the opening pressure is exceeded. When the opening pressure falls below this in the pump chamber 2, it closes again.
  • a ventilation channel 13 leaves the pump chamber 2.
  • the ventilation channel 13 opens into a pressure chamber 14 of a ventilation valve device 15.
  • the ventilation valve device 15 consists of a series connection of a ventilation valve 16 and a check valve 17 and will be explained in more detail with reference to FIG. 2 .
  • Fig. 2a shows the vent valve 16 in the open position.
  • Fig. 2b shows it in the closed position.
  • the vent valve 16 has a spring membrane 18 made of metal, for example stainless steel, plastic, elastomer, metal-elastomer composite or plastic-elastomer composite.
  • PVDF or PTFE can be used as the material. The advantage of these materials is that nothing can adhere to them, so that even escaping liquid cannot lead to sticking or clogging of the valve.
  • valve seat 22 Approximately in the middle of the spring membrane 18 there is an opening 19 which is surrounded by an annular bead 20 which, in the closed state, lies against an essentially flat surface 21.
  • the spring membrane 18 cooperates with a valve seat 22, of which the surface 21 forms a part.
  • Several outlet channels 23 open into the valve seat 22. These can, for example, as shown, be arranged radially offset from one another.
  • a plurality of output channels 23 can also be arranged distributed in the circumferential direction.
  • the surface of the spring membrane 18 facing the valve seat 22 is structured, i.e. it has a number of annular projections 24 which concentrically surround the opening 19 and have the effect that the contact between the spring membrane 18 and the valve seat 22 is limited to relatively narrow surface areas. One can almost speak of a line contact.
  • the spring membrane 18 has a certain preload, which can be generated by installing the spring membrane in the housing 3. It is also conceivable that the spring membrane is already designed as a molded part with a certain preload.
  • a small gap 25 is formed between the spring diaphragm 18 and the valve seat 22, which forms an outflow fluid against a throttle resistance.
  • the throttle resistance leads to a pressure drop in the outflowing fluid. This pressure drop depends, among other things, on the physical state of the fluid flowing out, whether it is a gas or a liquid.
  • the throttle can also be formed through the opening 19.
  • gas that has collected in the ventilation channel 13 can easily escape through the gap 25 between the spring membrane 18 and the valve seat 22 and can reach a ventilation bore 26 in the housing 3 via the outlet channels 23 and the check valve 17 .
  • the outflowing gas is not compressed.
  • a pressure increase in the pressure chamber 14 therefore does not take place or does not take place to any appreciable extent.
  • the pump chamber 2 and also the ventilation channel 13 are completely filled with liquid, which thus also reaches the pressure chamber 14.
  • the liquid now also flows through the gap 25 between the spring membrane 18 and the valve seat 22.
  • the throttling effect of this gap 25 is different for liquids than for gases.
  • the throttle formed by the gap 25 or the opening 19 produces a greater pressure drop in the case of liquid than with gases.
  • the pressure drop leads to an increase in pressure in the pressure chamber 14.
  • the pressure drop is of course also dependent on the viscosity of the liquid and on the flow rate.
  • the gap 25 or the opening 19 can be dimensioned accordingly, that is to say that for the given or desired delivery capacity of the metering pump 1 it is correspondingly low in the case of gases, but correspondingly high in the case of liquids Pressure drop causes.
  • Amount of liquid can be dispensed into the outlet port 9.
  • the inlet valve 8 opens.
  • the check valve 17 closes, so that no gas can be drawn into the pump chamber 2 via the vent valve 16.
  • the vent valve 16 opens in order to be able to perform its venting function again on the next pump stroke for any gas that may arise or be sucked in.
  • FIG. 3 shows a further embodiment of a liquid metering pump, in which the same parts are provided with the same, corresponding parts with reference numerals increased by 100.
  • the vent valve 116 thus has a pressure chamber 114, the output of which is formed by a throttle 125 which leads to the check valve 17.
  • the pressure chamber 114 is in turn delimited by an actuating membrane 28 which can be displaced against the force of a spring 29.
  • a closure element 31 is fastened to the membrane 29 via an actuating rod, which comes into contact with a valve seat 122 when the membrane is appropriately deflected.
  • Fluid which is pressed into the pressure chamber 114 with the aid of the membrane 4, flows through the throttle 125 and the check valve 17 into the return line 27 or the venting bore 26.
  • the pressure arising in the pressure chamber 114 is then so great that it overcomes the force of the springs 29 and moves the actuating membrane 28 against the force of the spring 29.
  • the actuating membrane 28 simultaneously moves the closure element 31, which blocks the liquid path as soon as it comes into contact with the valve seat 122. Otherwise, the function is the same as for the liquid metering pump according to FIGS. 1 and 2.
  • the pump can also work with a piston instead of the membrane 4.

Landscapes

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

Abstract

L'invention décrit une pompe pour le dosage de liquides avec une chambre de pompe (2) dont le volume augmente lors de la course d'aspiration et diminue lors de la course de poussée et dont l'extrémité supérieure porte un dispositif formant soupape d'évacuation d'air (15). Dans une pompe de dosage de ce type, ledit dispositif d'évacuation d'air doit être amélioré, et en particulier conçu de façon à évacuer l'air en fonction des besoins. Le dispositif formant soupape d'évacuation d'air (15) présente à cette fin une soupape (16) actionnée par l'écoulement, dont le comportement de réponse est déterminé par l'état d'agrégation du fluide qui la parcourt.
PCT/EP1993/003156 1992-06-16 1993-11-10 Pompe pour le dosage de liquides Ceased WO1995013473A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE4219663A DE4219663C2 (de) 1992-06-16 1992-06-16 Flüssigkeits-Dosierpumpe
PCT/EP1993/003156 WO1995013473A1 (fr) 1992-06-16 1993-11-10 Pompe pour le dosage de liquides
JP7513547A JPH08506162A (ja) 1992-06-16 1993-11-10 液体配量ポンプ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4219663A DE4219663C2 (de) 1992-06-16 1992-06-16 Flüssigkeits-Dosierpumpe
PCT/EP1993/003156 WO1995013473A1 (fr) 1992-06-16 1993-11-10 Pompe pour le dosage de liquides

Publications (1)

Publication Number Publication Date
WO1995013473A1 true WO1995013473A1 (fr) 1995-05-18

Family

ID=25915732

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1993/003156 Ceased WO1995013473A1 (fr) 1992-06-16 1993-11-10 Pompe pour le dosage de liquides

Country Status (3)

Country Link
JP (1) JPH08506162A (fr)
DE (1) DE4219663C2 (fr)
WO (1) WO1995013473A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670906A1 (fr) * 2018-12-20 2020-06-24 Lutz-Jesco GmbH Pompe de dosage pourvue de soupape de décharge intégrée et insert de soupape pour une pompe de dosage

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4418314C1 (de) * 1994-05-26 1996-01-04 Prominent Dosiertechnik Gmbh Flüssigkeitsdosierpumpe
DE19538134A1 (de) * 1995-10-13 1997-04-17 Alldos Eichler Gmbh Dosierpumpe
DE19712096C1 (de) * 1997-03-22 1998-04-02 Lang Apparatebau Gmbh Dosierpumpe zum dosierten Fördern von Flüssigkeiten
EP1132616A1 (fr) * 2000-03-10 2001-09-12 BMO Treuhand und Verwaltung AG Pompe de dosage
CN105221380A (zh) * 2015-09-29 2016-01-06 苏州巧泰精密机械有限公司 计量泵
JP6726956B2 (ja) * 2015-12-07 2020-07-22 株式会社イワキ 往復動ポンプ及びガス抜き弁のバルブ構造
DE102020119502A1 (de) 2020-07-23 2022-01-27 Washtec Holding Gmbh Verfahren zum betreiben einer dosierpumpe in einem flüssigkeitsversorgungssystem
DE102021120434A1 (de) 2021-08-05 2023-02-09 Prominent Gmbh Dosierpumpe mit UV-Lichterzeuger

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE218796C (fr) *
GB583550A (en) * 1944-08-10 1946-12-20 John Daniel Eldret Venning Improvements in or relating to air or gas relief or vent valves
DE1035058B (de) * 1955-11-25 1958-07-24 Canadian Patents Dev Entlueftungsverschluss fuer Brennstoffbehaelter und Geraete, in denen feuergefaehrliche Fluessigkeiten enthalten sind
DE2310928A1 (de) * 1972-03-06 1973-10-04 Hauke Rudolf Dipl-Ing Einrichtung zur entgasung
GB2018399A (en) * 1978-04-03 1979-10-17 Dana Corp Automatic Vent Valve
US4410302A (en) * 1980-07-16 1983-10-18 Yasutsune Chiba Automatic air venting device for electromagnetic plunger pump
DE3631984C1 (de) * 1986-09-19 1987-12-17 Hans Ing Kern Dosierpumpe
EP0515215A1 (fr) * 1991-05-24 1992-11-25 Pall Corporation Purgeur automatique

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Publication number Priority date Publication date Assignee Title
US2744469A (en) * 1953-06-05 1956-05-08 Edward J Schaefer Valve structure for preventing air lock in pumps
CH390686A (de) * 1959-12-04 1965-04-15 Eckerle Otto Förderpumpenanlage
DE2803470B2 (de) * 1978-01-27 1980-06-04 Dulger, Viktor, 6900 Heidelberg Entlüftungsvorrichtung fur eine Flussigkeitskolbenpumpe, insbesondere Dosierpumpe
DE8805638U1 (de) * 1988-04-28 1988-06-16 Hella KG Hueck & Co, 4780 Lippstadt Ventil, insbesondere für Drehkolbenpumpen mit zwei Druckstutzen für Kraftfahrzeuge
DE3827489C1 (fr) * 1988-08-12 1989-10-12 Gruenbeck Wasseraufbereitung Gmbh, 8884 Hoechstaedt, De
DE3928411A1 (de) * 1989-08-28 1991-03-07 Gruenbeck Josef Wasseraufb Dosierpumpe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE218796C (fr) *
GB583550A (en) * 1944-08-10 1946-12-20 John Daniel Eldret Venning Improvements in or relating to air or gas relief or vent valves
DE1035058B (de) * 1955-11-25 1958-07-24 Canadian Patents Dev Entlueftungsverschluss fuer Brennstoffbehaelter und Geraete, in denen feuergefaehrliche Fluessigkeiten enthalten sind
DE2310928A1 (de) * 1972-03-06 1973-10-04 Hauke Rudolf Dipl-Ing Einrichtung zur entgasung
GB2018399A (en) * 1978-04-03 1979-10-17 Dana Corp Automatic Vent Valve
US4410302A (en) * 1980-07-16 1983-10-18 Yasutsune Chiba Automatic air venting device for electromagnetic plunger pump
DE3631984C1 (de) * 1986-09-19 1987-12-17 Hans Ing Kern Dosierpumpe
EP0515215A1 (fr) * 1991-05-24 1992-11-25 Pall Corporation Purgeur automatique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670906A1 (fr) * 2018-12-20 2020-06-24 Lutz-Jesco GmbH Pompe de dosage pourvue de soupape de décharge intégrée et insert de soupape pour une pompe de dosage
EP3748156A1 (fr) * 2018-12-20 2020-12-09 Lutz-Jesco GmbH Insert de soupape pour une pompe de dosage
US11365729B2 (en) 2018-12-20 2022-06-21 Lutz-Jesco Gmbh Metering pump having an integrated overflow valve, and valve insert for a metering pump
US11619223B2 (en) 2018-12-20 2023-04-04 Lutz-Jesco Gmbh Metering pump having an integrated overflow valve, and valve insert for a metering pump

Also Published As

Publication number Publication date
DE4219663C2 (de) 1996-01-18
JPH08506162A (ja) 1996-07-02
DE4219663A1 (de) 1993-12-23

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