EP0283026B1 - Method and device for starting an hydraulic membrane pump against a load - Google Patents

Method and device for starting an hydraulic membrane pump against a load Download PDF

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Publication number
EP0283026B1
EP0283026B1 EP88104287A EP88104287A EP0283026B1 EP 0283026 B1 EP0283026 B1 EP 0283026B1 EP 88104287 A EP88104287 A EP 88104287A EP 88104287 A EP88104287 A EP 88104287A EP 0283026 B1 EP0283026 B1 EP 0283026B1
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EP
European Patent Office
Prior art keywords
chamber
pump
pressure chamber
connection channel
pressure
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EP88104287A
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German (de)
French (fr)
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EP0283026A3 (en
EP0283026A2 (en
Inventor
Horst Fritsch
Josef Dr. Jarosch
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Lewa Herbert Ott GmbH and Co KG
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Lewa Herbert Ott GmbH and Co KG
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Priority to AT88104287T priority Critical patent/ATE86363T1/en
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Publication of EP0283026A3 publication Critical patent/EP0283026A3/en
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    • 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 method for starting a hydraulic diaphragm pump against load according to the preamble of claim 1 and a device provided for carrying out this method according to the preamble of claim 4.
  • a start-up circuit is already known (FR-A-1 069 107) which is on the oil side, that is to say on the drive side the diaphragm pump, is arranged and designed such that it works automatically. This makes it possible to achieve a smooth start of the diaphragm pump under load without the drive having to be designed for the high breakaway torque.
  • an automatic start-up circuit has some shortcomings. These are not only the fact that such an automatic start-up circuit is subject to the influence of manufacturing tolerances, stroke frequencies of the displacer piston and viscosity of the hydraulic fluid, without it being possible to eliminate such adverse influences by appropriate countermeasures.
  • the pump once the known automatic start-up circuit has been set up and set, the pump also has a very specific start-up characteristic which cannot be changed later or only with considerable effort.
  • Diaphragm pumps are also already known (US Pat. Nos. 3,767,326 and 3,374,750), in which a connecting line is provided between the pressure chamber and the storage chamber, the opening or interruption of which is valve-controlled (batch control).
  • the two solenoid valves provided for this purpose are controlled as pure open-close valves, in opposite directions, so that it is not possible with such a device to achieve a smooth coupling of the pump to the pressure network.
  • the invention has for its object to develop the method and the device of the generic type in such a way that they work reliably with little design effort and make it possible to implement different start-up characteristics of the pump.
  • the interruption of the connection between the pressure chamber and the storage chamber is controlled externally, specifically at the minimum speed of the pump, which corresponds to a fraction of the nominal speed.
  • the invention is based on the essential idea of moving the starting device from the product side to the oil side, that is to say from the delivery side to the drive side, and for this purpose to provide a connecting channel between the pressure chamber and the storage chamber, which is basically open, but after the commissioning of the Pump is closed slowly or quickly, whereby the pressure in the pressure chamber then increases up to the delivery pressure.
  • the required breakaway torque is therefore only a fraction of that without a starting device, so that there is the decisive advantage that the pump drive in essentially only for the nominal torque, but not for the breakaway torque.
  • This has the further advantage that the drive motor designed for the nominal torque works with a significantly better efficiency than the otherwise required drive motor which is matched to the breakaway torque and is therefore much larger in size.
  • the closing device by means of which the connecting channel can be gradually closed, has a movable closing body.
  • this can have different structural configurations, namely in the form of a valve, a control slide, a control piston or the like.
  • the closing body is preferably arranged in a connection hole accessible from the outside, which is expediently provided at a kink of the connecting channel in such a way that two partial sections of the connecting channel, namely a channel section on the pressure chamber side and a channel section on the storage chamber side, are formed, which are connected by the connection hole.
  • the closing body of the closing device is actuated from the outside via an actuator, be it electrically, magnetically or pneumatically.
  • the actuator can work depending on the number or frequency of the strokes of the displacement piston, in such a way that after the pump is switched on, the passage cross-section of the connecting channel available for the displaced hydraulic fluid is reduced with each additional pressure stroke.
  • the mode of operation of the diaphragm pump provided with a starting device according to the invention is accordingly such that the diaphragm pump is switched on and raised to a minimum speed, it not yet delivering in this state.
  • the hydraulic fluid (displacement volume) displaced by the displacement piston pulsates back and forth as an oil flow in the still open connecting channel to a greater or lesser extent without the membrane moving.
  • the membrane which cannot move to the product delivery chamber due to the system pressure in the system, migrates to the rear pressure chamber-side limitation cap or is already there. This ensures that the membrane is not overstretched when starting.
  • the diaphragm pump head in question is then gently connected to the pressure network of the system, so that overall there is a gentle start-up under load without the usual high breakaway torque being overcome and the pump drive accordingly being too strong must be oversized.
  • the locking device is actuated from the outside by means of a suitably controlled actuator.
  • the start-up characteristic of the diaphragm pump can be easily adapted to the characteristics of the pump drive by appropriate design of the closing body and the flow resistance of the individual sections of the connecting channel.
  • the closing body is actuated from the outside via electrically, hydraulically or pneumatically operating actuators, independently of the pressure change processes in the pump. In this way, different start-up characteristics can be realized, and the influence of manufacturing tolerances, stroke frequencies of the displacer piston and viscosity of the hydraulic fluid is eliminated.
  • the typical torque-speed characteristic curve for a three-cylinder pump, for example, which has no starting device is designed such that it has a high starting torque, the so-called. Breakaway torque, which is almost twice the nominal torque.
  • the dashed line shows the considerably reduced breakaway torque in a diaphragm pump provided with the starting device according to the invention, so that the pump drive must at best be designed for the nominal torque or full load torque.
  • the starting device is provided in a hydraulic diaphragm pump which has a conventional diaphragm 1. This is clamped at its edge between a pump body 2 and a pump cover 3 which is detachably attached to the end thereof and separates a delivery chamber 4 from a pressure chamber 5 filled with hydraulic fluid.
  • the diaphragm pump shown has a hydraulic diaphragm drive in the form of an oscillating displacement piston 6, which is located in the pump body 2 sealed between the pressure chamber 5 and a storage space 7 for the hydraulic fluid is displaceable.
  • the piston-side pressure chamber 5 is connected via a plurality of axial bores 8 arranged in the pump body 2 to a membrane-side pressure chamber 9, which is delimited on the one hand by the membrane 1 and on the other hand by a rear (piston-side) dome 10.
  • the membrane 1 lies against this rear limiting cap 10 at the end of the suction stroke, as shown in dashed lines in FIG. 2, while it comes to bear against a front limiting cap 11 at the end of the pressure stroke.
  • the front limiting cap 11 is formed in the pump cover 3, which has a spring-loaded inlet valve 12 and a spring-loaded outlet valve 13 in the usual manner. These two valves 12, 13 are connected via an inlet duct 14 and an outlet duct 15 to the delivery chamber 4 in such a way that the delivery medium during the suction stroke of the displacement piston to the right according to FIG. 2 6 and thus the membrane 1 is sucked into the delivery chamber 4 in the direction of the arrow via the inlet valve 12 and the inlet channel 14. During the pressure stroke of the diaphragm 1 to the left according to FIG. 2, the pumped medium is then pressed out of the pumping chamber 4 in a metered manner via the outlet channel 15 and the outlet valve 13.
  • a customary spring-loaded sniffer valve 16 is provided in the pump body 2, which connects to the pressure chamber 5 or 9 and the storage chamber 7 via channels 17, 18, 19 stands.
  • the starting device A provided in the diaphragm pump described has a connecting channel 20 which runs between the pressure chamber 5 and the storage chamber 7 and can be closed by a closing body to be explained in more detail after the pump has been started up.
  • the closing body is displaceable in a connection bore 22 which is accessible from the outside and is closed by a plug 21 and which is arranged at a kink of the connection channel 20 such that the section of the connection channel 20 on the pressure chamber side into the bottom of the connection hole 22 and the section of the connection channel 20 on the storage chamber side the side wall of the connection bore 22 opens.
  • the Starting device as a closing body on a control slide 23 which is displaceable in the connection bore 22, specifically within a sleeve 24 inserted therein.
  • the sleeve 24 is provided with a transverse through bore 25 and a longitudinal channel 26 in such a way that the flow connection between the section of the connecting channel 20 on the pressure chamber side and its section on the supply side is maintained.
  • the control slide 23 has a circumferential groove 27 such that the connecting channel 20 is open when the control slide 23 is in the starting position according to FIG. 3, but is closed when the control slide 23 is in the dashed operating position.
  • the control slide 23 which establishes the connection between the pressure chamber 5 and the storage chamber 7 via the connecting channel 20 and the channels 25, 26, 27 interacting therewith, is in the starting position according to FIG. 3 when the pump is switched on. Then when the pump is slowly started up from the minimum speed, the control slide 23 is also moved downward, so that the circumferential groove 27 provided in the control slide 23 also moves away from the connection channel 20 on the storage space side. As a result, the passage cross section of the connecting channel 20 is reduced until the control slide 23 has shifted completely downward into the operating position according to FIG. 3, in which the connecting channel 20 is completely closed. In this position, the pump has reached the delivery pressure, so that the diaphragm pump head is switched on to the system pressure network.
  • the control slide 23 is actuated via an actuator 33, which in turn can be actuated electrically, magnetically or pneumatically.
  • the actuator 33 attached to the outside of the plug 21 of the connecting bore 22 is connected to the control slide 23 via an actuating plunger 34, so that the control slide 23 according to the stroke rhythm of the displacer 6 from its starting position, in which the connecting channel 20 is open, after can be shifted below into its operating position shown in dashed lines, in which the connecting channel 20 is closed.
  • valve tappet 35 connected to the actuating tappet 34 is provided, which cooperates with a valve seat 36.
  • This valve seat 36 is formed in the connection bore 22 by a shoulder formed there on the bottom side of the section of the connecting channel 20 on the pressure chamber side. Accordingly, this valve 35, 36 - analogous to the control slide 23 - can be moved by means of the actuator 33 between a starting position in which the connecting channel 20 is open and an operating position in which the connecting channel 20 is closed.

Abstract

In a diaphragm pump, which is provided with at least one diaphragm (1), which separates a delivery chamber (4) from a pressure chamber (5) filled with an hydraulic fluid and is clmaped at its edge between the pump body (2) and a pump cover (3), and with an hydraulic diaphragm drive in the form of an oscillating displacement piston (6), which is displaceable in the pump body (2) between the pressure chamber (5) and a storage chamber (7) for the hydraulic fluid, a method as well as an arrangement for starting under load is provided. For this purpose on the pump drive side between the pressure chamber (5) and the storage chamber (7) a connection channel (20) is provided. This connection channel (20) during start-up of the pump leads the hydraulic fluid displaced by the displacement piston (6) in the pressure chamber (5) back into the storage chamber (7) and in the course of the further strokes of the displacement piston (6) is closable by a controlled closing device (A), so that the pressure in the pressure chamber (5) rises up to the level of the discharge pressure.

Description

Die Erfindung betrifft ein Verfahren zum Anfahren einer hydraulischen Membranpumpe gegen Last gemäß dem Oberbegriff des Anspruchs 1 sowie eine zur Durchführung dieses Verfahrens vorgesehene Vorrichtung gemäß dem Oberbegriff des Anspruchs 4.The invention relates to a method for starting a hydraulic diaphragm pump against load according to the preamble of claim 1 and a device provided for carrying out this method according to the preamble of claim 4.

Wenn eine hydraulische Membranpumpe, d.h. eine oszillierende Verdrängerpumpe, unter Last, also bei vollem Systemdruck angefahren werden muß, ist zunächst das sog. Losbrechmoment zu überwinden. Dieses liegt in der Größenordnung des doppelten Nennmomentes, was zur Folge hat, daß der Pumpenantrieb entsprechend auszulegen ist. Damit jedoch der Antrieb nicht zu stark überdimensioniert werden muß, hilft man sich in solchen Fällen, insbesondere bei großen 3-Plunger-Pumpen, mittels Installation einer sog. Anfahrschaltung auf der Produktseite, d.h. Förderseite der Pumpe. Dies bedingt jedoch den Einsatz mehrerer Stellventile in Verbindung mit einer speziellen Steuerungseinrichtung. Es sind daher für hohe Förderdrücke derartige Anfahrschaltungen sehr aufwendig und nicht ohne Probleme, vor allem wenn es sich um schwierigere Förderfluide, z.B. Suspensionen, handelt.If a hydraulic diaphragm pump, i.e. An oscillating displacement pump, which must be started up under load, i.e. at full system pressure, must first overcome the so-called breakaway torque. This is of the order of twice the nominal torque, which means that the pump drive must be designed accordingly. However, so that the drive does not have to be oversized, in such cases, especially with large 3-plunger pumps, you can help by installing a so-called start-up circuit on the product side, i.e. Delivery side of the pump. However, this requires the use of several control valves in connection with a special control device. Starting circuits of this type are therefore very complex for high delivery pressures and are not without problems, especially if the delivery fluids are more difficult, e.g. Suspensions.

Es ist auch schon eine Anfahrschaltung bekannt (FR-A-1 069 107), die auf der Ölseite, d.h. also auf der Antriebsseite der Membranpumpe, angeordnet ist und derart ausgestaltet ist, daß sie automatisch arbeitet. Hierdurch ist es zwar möglich, ein sanftes Anfahren der Membranpumpe unter Last zu erreichen, ohne daß der Antrieb für das hohe Losbrechmoment ausgelegt werden muß. Jedoch weist eine derartige automatische Anfahrschaltung einige Unzulänglichkeiten auf. Diese liegen nicht nur darin, daß eine solche automatische Anfahrschaltung dem Einfluß von Fertigungstoleranzen, Hubfrequenzen des Verdrängerkolbens und Viskosität der Hydraulikflüssigkeit unterliegt, ohne daß es möglich ist, durch entsprechende Gegensteuerung derartige nachteilige Einflüsse auszuschalten. Hinzu kommt außerdem, daß dann, wenn die bekannte automatische Anfahrschaltung einmal eingerichtet und eingestellt ist, die Pumpe auch eine ganz bestimmte Anfahrcharakteristik aufweist, die später nicht mehr oder nur mit erheblichem Aufwand verändert werden kann.A start-up circuit is already known (FR-A-1 069 107) which is on the oil side, that is to say on the drive side the diaphragm pump, is arranged and designed such that it works automatically. This makes it possible to achieve a smooth start of the diaphragm pump under load without the drive having to be designed for the high breakaway torque. However, such an automatic start-up circuit has some shortcomings. These are not only the fact that such an automatic start-up circuit is subject to the influence of manufacturing tolerances, stroke frequencies of the displacer piston and viscosity of the hydraulic fluid, without it being possible to eliminate such adverse influences by appropriate countermeasures. In addition, once the known automatic start-up circuit has been set up and set, the pump also has a very specific start-up characteristic which cannot be changed later or only with considerable effort.

Es sind auch schon Membranpumpen bekannt (US-A 3 767 326 und US-A-3 374 750), bei denen zwischen Druckraum und Vorratsraum eine Verbindungsleitung vorgesehen ist, deren Öffnung bzw. Unterbrechung ventilgesteuert ist (Chargensteuerung). Die zu diesem Zweck vorgesehenen beiden Magnetventile werden als reine Auf-Zu-Ventile gesteuert, und zwar gegensinnig, so daß es mit einer derartigen Vorrichtung nicht möglich ist, ein sanftes Ankoppeln der Pumpe an das Drucknetz zu erreichen.Diaphragm pumps are also already known (US Pat. Nos. 3,767,326 and 3,374,750), in which a connecting line is provided between the pressure chamber and the storage chamber, the opening or interruption of which is valve-controlled (batch control). The two solenoid valves provided for this purpose are controlled as pure open-close valves, in opposite directions, so that it is not possible with such a device to achieve a smooth coupling of the pump to the pressure network.

Der Erfindung liegt die Aufgabe zugrunde, das Verfahren sowie die Vorrichtung der gattungsgemäßen Art derart weiterzubilden, daß sie mit geringem konstruktivem Aufwand zuverlässig arbeiten und es ermöglichen, unterschiedliche Anfahrcharakeristiken der Pumpe zu verwirklichen.The invention has for its object to develop the method and the device of the generic type in such a way that they work reliably with little design effort and make it possible to implement different start-up characteristics of the pump.

Diese Aufgabe wird mit dem erfindungsgemäßen Verfahren durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Ausgestaltungen sind in den Ansprüchen 2 und 3 beschrieben. Die Merkmale der in Form einer Anfahreinrichtung ausgestalteten Vorrichtung gemäß der Erfindung ergeben sich aus Anspruch 4. Zweckmäßige Weiterbildungen hiervon sind in den weiteren Ansprüchen erläutert.This object is achieved with the method according to the invention by the features of claim 1. Beneficial Refinements are described in claims 2 and 3. The features of the device designed in the form of a starting device according to the invention result from claim 4. Practical developments of this are explained in the further claims.

Bei dem erfindungsgemäßen Verfahren erfolgt die Unterbrechung der Verbindung zwischen Druckraum und Vorratsraum von außen gesteuert, und zwar bei der Minimaldrehzahl der Pumpe, die einem Bruchteil der Nenndrehzahl entspricht.In the method according to the invention, the interruption of the connection between the pressure chamber and the storage chamber is controlled externally, specifically at the minimum speed of the pump, which corresponds to a fraction of the nominal speed.

Der Erfindung liegt der wesentliche Gedanke zugrunde, die Anfahreinrichtung von der Produktseite auf die Ölseite, d.h. also von der Förderseite auf die Antriebsseite zu verlegen und zu diesem Zweck zwischen dem Druckraum und dem Vorratsraum einen Verbindungskanal vorzusehen, der grundsätzlich offen ist, jedoch nach Inbetriebsetzen der Pumpe langsam oder auch schnell verschlossen wird, wodurch der Druck im Druckraum dann bis zum Förderdruck ansteigt. Das erforderliche Losbrechmoment beträgt somit nur einen Bruchteil desjenigen ohne Anfahreinrichtung, so daß sich der entscheidene Vorteil ergibt, daß der Pumpenantrieb im wesentlichen nur für das Nennmoment, nicht aber für das Losbrechmoment ausgelegt werden muß. Dies hat den weiteren Vorteil zur Folge, daß der auf das Nennmoment ausgelegte Antriebsmotor mit einem deutlich besseren Wirkungsgrad arbeitet als der ansonsten erforderliche, auf das Losbrechmoment abgestimmte und somit viel größer zu dimensionierende Antriebsmotor.The invention is based on the essential idea of moving the starting device from the product side to the oil side, that is to say from the delivery side to the drive side, and for this purpose to provide a connecting channel between the pressure chamber and the storage chamber, which is basically open, but after the commissioning of the Pump is closed slowly or quickly, whereby the pressure in the pressure chamber then increases up to the delivery pressure. The required breakaway torque is therefore only a fraction of that without a starting device, so that there is the decisive advantage that the pump drive in essentially only for the nominal torque, but not for the breakaway torque. This has the further advantage that the drive motor designed for the nominal torque works with a significantly better efficiency than the otherwise required drive motor which is matched to the breakaway torque and is therefore much larger in size.

Die Schließeinrichtung, mittels welcher der Verbindungskanal allmählich verschließbar ist, weist erfindungsgemäß einen beweglichen Schließkörper auf. Dieser kann im Rahmen der Erfindung unterschiedliche konstruktive Ausgestaltungen besitzen, nämlich in Form eines Ventils, eines Steuerschiebers, eines Steuerkolbens oder dgl..According to the invention, the closing device, by means of which the connecting channel can be gradually closed, has a movable closing body. Within the scope of the invention, this can have different structural configurations, namely in the form of a valve, a control slide, a control piston or the like.

Der Schließkörper ist vorzugsweise in einer von außen zugänglichen Anschlußbohrung angeordnet, die zweckmäßigerweise derart an einem Knick des Verbindungskanals vorgesehen ist, daß hierdurch zwei Teilabschnitte des Verbindungskanals, nämlich ein druckraumseitiger sowie ein vorratsraumseitiger Kanalabschnitt, gebildet werden, die durch die Anschlußbohrung verbunden sind.The closing body is preferably arranged in a connection hole accessible from the outside, which is expediently provided at a kink of the connecting channel in such a way that two partial sections of the connecting channel, namely a channel section on the pressure chamber side and a channel section on the storage chamber side, are formed, which are connected by the connection hole.

Erfindungsgemäß wird der Schließkörper der Schließeinrichtung von außen über einen Stellantrieb, sei es elektrisch, magnetisch oder pneumatisch, betätigt. Der Stellantrieb kann in Abhängigkeit von der Anzahl bzw. Frequenz der Hübe des Verdrängerkolbens arbeiten, und zwar derart, daß nach dem Einschalten der Pumpe der für die verdrängte Hydraulikflüssigkeit zur Verfügung stehende Durchtrittsquerschnitt des Verbindungskanals bei jedem weiteren Druckhub verkleinert wird.According to the invention, the closing body of the closing device is actuated from the outside via an actuator, be it electrically, magnetically or pneumatically. The actuator can work depending on the number or frequency of the strokes of the displacement piston, in such a way that after the pump is switched on, the passage cross-section of the connecting channel available for the displaced hydraulic fluid is reduced with each additional pressure stroke.

Die Funktionsweise der mit einer Anfahreinrichtung gemaß der Erfindung versehenen Membranpumpe stellt sich demgemäß derart dar, daß die Membranpumpe eingeschaltet und auf Minimaldrehzahl hochgefahren wird, wobei sie in diesem Zustand noch nicht fördert. Hierbei pulsiert die vom Verdrängerkolben verdrängte Hydraulikflüssigkeit (Hubvolumen) in dem noch offenen Verbindungskanal als Ölstrom mehr oder weniger drucklos hin und her, ohne daß sich die Membran bewegt. Die Membran, die sich aufgrund des in der Anlage herrschenden Systemdrucks zum Produktförderraum nicht bewegen kann, wandert zur hinteren druckraumseitigen Begrenzungskalotte bzw. liegt dieser schon an. Dadurch wird sichergestellt, daß die Membran beim Anfahren nicht überdehnt wird. Durch langsames oder auch plötzliches Schließen des Verbindungskanals mittels der per Stellantrieb gesteuerten Schließeinrichtung wird der betreffende Membranpumpenkopf dann sanft dem Drucknetz der Anlage zugeschaltet, so daß sich insgesamt ein sanftes Anfahren unter Last ergibt, ohne daß das übliche hohe Losbrechmoment überwunden und demgemäß der Pumpenantrieb zu stark überdimensioniert werden muß.The mode of operation of the diaphragm pump provided with a starting device according to the invention is accordingly such that the diaphragm pump is switched on and raised to a minimum speed, it not yet delivering in this state. Here, the hydraulic fluid (displacement volume) displaced by the displacement piston pulsates back and forth as an oil flow in the still open connecting channel to a greater or lesser extent without the membrane moving. The membrane, which cannot move to the product delivery chamber due to the system pressure in the system, migrates to the rear pressure chamber-side limitation cap or is already there. This ensures that the membrane is not overstretched when starting. By slowly or suddenly closing the connecting channel by means of the closing device controlled by an actuator, the diaphragm pump head in question is then gently connected to the pressure network of the system, so that overall there is a gentle start-up under load without the usual high breakaway torque being overcome and the pump drive accordingly being too strong must be oversized.

Wie schon dargelegt, wird die Schließeinrichtung von außen mittels eines geeignet gesteuerten Stellantriebes betätigt.As already explained, the locking device is actuated from the outside by means of a suitably controlled actuator.

Durch entsprechende Gestaltung des Schließkörpers sowie der Strömungswiderstände der einzelnen Abschnitte des Verbindungskanals läßt sich die Anfahrcharakteristik der Membranpumpe leicht an die Eigenarten des Pumpenantriebes anpassen.The start-up characteristic of the diaphragm pump can be easily adapted to the characteristics of the pump drive by appropriate design of the closing body and the flow resistance of the individual sections of the connecting channel.

Hierbei wird die Betätigung des Schließkörpers über elektrisch, hydraulisch oder pneumatisch arbeitende Stellglieder von außen durchgeführt, und zwar unabhängig von den Druckwechselvorgängen in der Pumpe. Auf diese Weise können unterschiedliche Anfahrcharakteristiken verwirklicht werden, und es wird der Einfluß von Fertigungstoleranzen, Hubfrequenzen des Verdrängerkolbens und Viskosität der Hydraulikflüssigkeit ausgeschaltet.In this case, the closing body is actuated from the outside via electrically, hydraulically or pneumatically operating actuators, independently of the pressure change processes in the pump. In this way, different start-up characteristics can be realized, and the influence of manufacturing tolerances, stroke frequencies of the displacer piston and viscosity of the hydraulic fluid is eliminated.

Insgesamt sind damit die Vorteile der Erfindung darin zu sehen,

  • daß aufwendige und geräuschintensive Anfahrschaltungen auf der Förderseite der Pumpe entfallen können,
  • daß Bedienungsfehler in jedem Fall ausgeschlossen sind,
  • daß der Pumpenantrieb für die Betriebsbedingungen, wie Nenndrehmoment, Nennstrom usw., ausgelegt werden kann, wobei sich vor allen Dingen bei einem drehzahlverstellbaren Pumpenantrieb erhebliche Einsparungen in der Anschaffung sowie beim Betrieb der Pumpe ergeben,
  • daß Kupplungen, Getriebe und Pumpe ohne lebensdauermindernde Anfahrstöße betrieben werden können,
  • daß hydrodynamische Gleitlager erst belastet werden, wenn sich bei der Mindestdrehzahl ein tragfähiger Schmierfilm aufgebaut hat, und
  • daß aufgrund der Flexibilität der Anfahreinrichtung das Anlaufverhalten der Pumpe auf die Eigenarten des Antriebes abgestimmt werden kann.
Overall, the advantages of the invention can be seen in
  • that complex and noise-intensive start-up circuits on the delivery side of the pump can be omitted,
  • that operating errors are excluded in any case,
  • that the pump drive can be designed for the operating conditions, such as nominal torque, nominal current, etc., with considerable savings in the acquisition and operation of the pump, especially with a speed-adjustable pump drive,
  • that clutches, gears and pumps can be operated without lifelong start-ups,
  • that hydrodynamic plain bearings are only loaded when a stable lubricating film has built up at the minimum speed, and
  • that due to the flexibility of the starting device, the start-up behavior of the pump can be matched to the characteristics of the drive.

Die Erfindung wird im folgenden in Form mehrerer Ausführungsbeispiele anhand der Zeichnung näher erläutert. Hierbei zeigen:

Fig. 1
schematisch im Diagramm den typischen Verlauf einer Drehmomentkennlinie über der Drehzahl für eine Dreizylinderpumpe - sowohl ohne als auch mit Anfahreinrichtung;
Fig. 2
im Längsschnitt eine mit der Anfahreinrichtung gemäß der Erfindung versehene Membranpumpe;
Fig. 3
vergrößert im Schnitt das Detail A gemäß Fig. 2, wobei die Betätigung der Schließeinrichtung über einen Stellantrieb erfolgt, mit einem Steuerschieber als Schließkörper, und
Fig. 4
eine abgewandelte Ausführungsform mit einem Ventil als Schließkörper.
The invention is explained in more detail below in the form of several exemplary embodiments with reference to the drawing. Here show:
Fig. 1
schematically in the diagram the typical course of a torque characteristic versus the speed for a three-cylinder pump - both without and with a starting device;
Fig. 2
in longitudinal section a membrane pump provided with the starting device according to the invention;
Fig. 3
2 enlarges on average detail A according to FIG. 2, the actuation of the closing device being effected via an actuator, with a control slide as closing body, and
Fig. 4
a modified embodiment with a valve as a closing body.

Wie aus Fig. 1 ersichtlich, ist die typische Drehmoment-Drehzahlkennlinie für beispielsweise eine Dreizylinderpumpe, die keine Anfahreinrichtung aufweist, derart ausgebildet, daß diese ein hohes Anfahrmoment, das sog. Losbrechmoment, aufweist, welches fast beim doppelten Nennmoment liegt. Demgegenüber Zeigt die gestrichelt dargestellte Linie das beträchtlich verringerte Losbrechmoment bei einer mit der erfindungsgemäßen Anfahreinrichtung versehenen Membranpumpe, so daß demgemäß der Pumpenantrieb allenfalls für das Nennmoment bzw. Volllastmoment ausgelegt werden muß.As can be seen from FIG. 1, the typical torque-speed characteristic curve for a three-cylinder pump, for example, which has no starting device, is designed such that it has a high starting torque, the so-called. Breakaway torque, which is almost twice the nominal torque. In contrast, the dashed line shows the considerably reduced breakaway torque in a diaphragm pump provided with the starting device according to the invention, so that the pump drive must at best be designed for the nominal torque or full load torque.

Wie aus Fig. 2 ersichtlich, ist die Anfahreinrichtung bei einer hydraulischen Membranpumpe vorgesehen, die eine übliche Membran 1 aufweist. Diese ist an ihrem Rand zwischen einem Pumpenkörper 2 sowie einem hieran stirnseitig lösbar festgelegten Pumpendeckel 3 eingespannt und trennt einen Förderraum 4 von einem mit Hydraulikflüssigkeit gefüllten Druckraum 5. Die dargestellte Membranpumpe weist einen hydraulischen Membranantrieb in Form eines oszillierenden Verdrängerkolbens 6 auf, der im Pumpenkörper 2 abgedichtet zwischem dem Druckraum 5 und einem Vorratsraum 7 für die Hydraulikflüssigkeit verschiebbar ist. Der kolbenseitige Druckraum 5 steht über mehrere im Pumpenkörper 2 angeordnete axiale Bohrungen 8 mit einem membranseitigen Druckraum 9 in Verbindung, der einerseits durch die Membran 1 sowie andererseits durch eine hintere (kolbenseitige) Kalotte 10 begrenzt ist. Die Membran 1 liegt dieser hinteren Begrenzungskalotte 10 am Ende des Saughubes an, wie gestrichelt in Fig. 2 dargestellt, während sie am Ende des Druckhubes zur Anlage an eine vordere Begrenzungskalotte 11 kommt.As can be seen from FIG. 2, the starting device is provided in a hydraulic diaphragm pump which has a conventional diaphragm 1. This is clamped at its edge between a pump body 2 and a pump cover 3 which is detachably attached to the end thereof and separates a delivery chamber 4 from a pressure chamber 5 filled with hydraulic fluid. The diaphragm pump shown has a hydraulic diaphragm drive in the form of an oscillating displacement piston 6, which is located in the pump body 2 sealed between the pressure chamber 5 and a storage space 7 for the hydraulic fluid is displaceable. The piston-side pressure chamber 5 is connected via a plurality of axial bores 8 arranged in the pump body 2 to a membrane-side pressure chamber 9, which is delimited on the one hand by the membrane 1 and on the other hand by a rear (piston-side) dome 10. The membrane 1 lies against this rear limiting cap 10 at the end of the suction stroke, as shown in dashed lines in FIG. 2, while it comes to bear against a front limiting cap 11 at the end of the pressure stroke.

Die vordere Begrenzungskalotte 11 ist im Pumpendeckel 3 gebildet, der in der üblichen Weise ein federbelastetes Einlaßventil 12 sowie ein federbelastetes Auslaßventil 13 aufweist. Diese beiden Ventile 12, 13 stehen über einen Einlaßkanal 14 sowie einen Auslaßkanal 15 derart mit dem Förderraum 4 in Verbindung, daß das Fördermedium bei dem nach rechts gemäß Fig. 2 erfolgenden Saughub des Verdrängerkolbens 6 und damit der Membran 1 in Pfeilrichtung über das Einlaßventil 12 und den Einlaßkanal 14 in den Förderraum 4 angesaugt wird. Bei dem nach links gemäß Fig. 2 erfolgenden Druckhub der Membran 1 wird dann das Fördermedium über den Auslaßkanal 15 und das Auslaßventil 13 in Pfeilrichtung dosiert aus dem Förderraum 4 herausgedrückt.The front limiting cap 11 is formed in the pump cover 3, which has a spring-loaded inlet valve 12 and a spring-loaded outlet valve 13 in the usual manner. These two valves 12, 13 are connected via an inlet duct 14 and an outlet duct 15 to the delivery chamber 4 in such a way that the delivery medium during the suction stroke of the displacement piston to the right according to FIG. 2 6 and thus the membrane 1 is sucked into the delivery chamber 4 in the direction of the arrow via the inlet valve 12 and the inlet channel 14. During the pressure stroke of the diaphragm 1 to the left according to FIG. 2, the pumped medium is then pressed out of the pumping chamber 4 in a metered manner via the outlet channel 15 and the outlet valve 13.

Um am Ende des Saughubes eine Überlastung der Membran 1 sowie das Auftreten von Kavitation zu verhindern, ist im Pumpenkörper 2 ein übliches federbelastetes Schnüffelventil 16 vorgesehen, das über Kanäle 17, 18, 19 mit dem Druckraum 5 bzw. 9 und dem Vorratsraum 7 in Verbindung steht.In order to prevent overloading of the diaphragm 1 and the occurrence of cavitation at the end of the suction stroke, a customary spring-loaded sniffer valve 16 is provided in the pump body 2, which connects to the pressure chamber 5 or 9 and the storage chamber 7 via channels 17, 18, 19 stands.

Die bei der beschriebenen Membranpumpe vorgesehene Anfahreinrichtung A weist einen Verbindungskanal 20 auf, der zwischen Druckraum 5 sowie Vorratsraum 7 verläuft und durch einen nachstehend näher zu erläuternden Schließkörper nach Inbetriebsetzen der Pumpe verschließbar ist. Der Schließkörper ist in einer von außen zugänglichen, durch einen Stopfen 21 verschlossenen Anschlußbohrung 22 verschiebbar, die derart an einem Knick des Verbindungskanals 20 angeordnet ist, daß der druckraumseitige Abschnitt des Verbindungskanals 20 in den Boden der Anschlußbohrung 22 und der vorratsraumseitige Abschnitt des Verbindungskanals 20 in die Seitenwand der Anschlußbohrung 22 mündet.The starting device A provided in the diaphragm pump described has a connecting channel 20 which runs between the pressure chamber 5 and the storage chamber 7 and can be closed by a closing body to be explained in more detail after the pump has been started up. The closing body is displaceable in a connection bore 22 which is accessible from the outside and is closed by a plug 21 and which is arranged at a kink of the connection channel 20 such that the section of the connection channel 20 on the pressure chamber side into the bottom of the connection hole 22 and the section of the connection channel 20 on the storage chamber side the side wall of the connection bore 22 opens.

Verschiedene konstruktive Ausführungsbeispiele der im wesentlichen aus dem Verbindungskanal 20 und dem hiermit zusammenwirkenden Schließkörper bestehenden Anfahreinrichtung A werden nachstehend anhand der Fig. 3 und 4 im einzelnen erläutert.Various constructive exemplary embodiments of the starting device A essentially consisting of the connecting channel 20 and the closing body interacting therewith are explained in detail below with reference to FIGS. 3 and 4.

Bei dem Ausführungsbeispiel gemäß Fig. 3 weist die Anfahreinrichtung als Schließkörper einen Steuerschieber 23 auf, der in der Anschlußbohrung 22, und zwar speziell innerhalb einer hierin eingesetzten Hülse 24,verschiebbar ist. Die Hülse 24 ist derart mit einer querverlaufenden Durchgangsbohrung 25 und einem Längskanal 26 versehen, daß die Strömungsverbindung zwischen dem druckraumseitigen Abschnitt des Verbindungskanals 20 und dessen vorratsseitigem Abschnitt aufrechterhalten ist. An einer bestimmten Stelle seines Umfangs weist der Steuerschieber 23 eine Umfangsnut 27 auf, derart daß der Verbindungskanal 20 bei in Startstellung gemäß Fig. 3 befindlichem Steuerschieber 23 offen, jedoch verschlossen ist, wenn sich der Steuerschieber 23 in der gestrichelten Betriebsstellung befindet.3 has the Starting device as a closing body on a control slide 23 which is displaceable in the connection bore 22, specifically within a sleeve 24 inserted therein. The sleeve 24 is provided with a transverse through bore 25 and a longitudinal channel 26 in such a way that the flow connection between the section of the connecting channel 20 on the pressure chamber side and its section on the supply side is maintained. At a certain point on its circumference, the control slide 23 has a circumferential groove 27 such that the connecting channel 20 is open when the control slide 23 is in the starting position according to FIG. 3, but is closed when the control slide 23 is in the dashed operating position.

Wie schon eingangs dargelegt, befindet sich der Steuerschieber 23, der über den Verbindungskanal 20 und die hiermit zusammenwirkenden Kanäle 25, 26, 27 die Verbindung zwischen dem Druckraum 5 und dem Vorratsraum 7 herstellt, beim Einschalten der Pumpe in der Startstellung gemäß Fig. 3. Wenn dann die Pumpe langsam von Minimaldrehzahl hochgefahren wird, wird auch der Steuerschieber 23 nach unten bewegt, so daß sich auch die im Steuerschieber 23 vorgesehene Umfangsnut 27 vom vorratsraumseitigen Verbindungskanal 20 wegbewegt. Hierdurch wird der Durchtrittsquerschnitt des Verbindungskanals 20 verkleinert, und zwar so lange, bis sich der Steuerschieber 23 vollständig nach unten in die Betriebsstellung gemäß Fig. 3 verschoben hat, in welcher der Verbindungskanal 20 vollständig geschlossen ist. In dieser Stellung hat die Pumpe den Förderdruck erreicht, so daß der Membranpumpenkopf dem Drucknetz der Anlage zugeschaltet wird.As already explained at the beginning, the control slide 23, which establishes the connection between the pressure chamber 5 and the storage chamber 7 via the connecting channel 20 and the channels 25, 26, 27 interacting therewith, is in the starting position according to FIG. 3 when the pump is switched on. Then when the pump is slowly started up from the minimum speed, the control slide 23 is also moved downward, so that the circumferential groove 27 provided in the control slide 23 also moves away from the connection channel 20 on the storage space side. As a result, the passage cross section of the connecting channel 20 is reduced until the control slide 23 has shifted completely downward into the operating position according to FIG. 3, in which the connecting channel 20 is completely closed. In this position, the pump has reached the delivery pressure, so that the diaphragm pump head is switched on to the system pressure network.

Die Betätigung des Steuerschiebers 23 erfolgt über einen Stellantrieb 33, der seinerseits elektrisch, magnetisch oder pneumatisch betätigt werden kann. Zu diesem Zweck steht der außen am Verschlußstopfen 21 der Anschlußbohrung 22 angebrachte Stellantrieb 33 über einen Betätigungsstößel 34 mit dem Steuerschieber 23 in Verbindung, so daß der Steuerschieber 23 entsprechend dem Hubrhythmus des Verdrängerkolbens 6 aus seiner Startstellung, in welcher der Verbindungskanal 20 offen ist, nach unten in seine gestrichelt dargestellte Betriebsstellung verschoben werden kann, in welcher der Verbindungskanal 20 geschlossen ist.The control slide 23 is actuated via an actuator 33, which in turn can be actuated electrically, magnetically or pneumatically. For this purpose, the actuator 33 attached to the outside of the plug 21 of the connecting bore 22 is connected to the control slide 23 via an actuating plunger 34, so that the control slide 23 according to the stroke rhythm of the displacer 6 from its starting position, in which the connecting channel 20 is open, after can be shifted below into its operating position shown in dashed lines, in which the connecting channel 20 is closed.

Bei der gegenüber Fig. 3 abgewandelten Ausführungsform gemäß Fig. 4 ist anstelle des Steuerschiebers 23 ein mit dem Betätigungsstößel 34 verbundener Ventilstößel 35 vorgesehen, der mit einem Ventilsitz 36 zusammenwirkt. Dieser Ventilsitz 36 ist in der Anschlußbohrung 22 durch eine dort bodenseitig geformte Schulter des druckraumseitigen Abschnittes des Verbindungskanals 20 gebildet. Demgemäß läßt sich dieses Ventil 35, 36 - analog dem Steuerschieber 23 - mittels des Stellantriebs 33 zwischen einer Startstellung, in welcher der Verbindungskanal 20 offen ist, und einer Betriebsstellung bewegen, in welcher der Verbindungskanal 20 geschlossen ist.In the embodiment according to FIG. 4 modified from FIG. 3, instead of the control slide 23, a valve tappet 35 connected to the actuating tappet 34 is provided, which cooperates with a valve seat 36. This valve seat 36 is formed in the connection bore 22 by a shoulder formed there on the bottom side of the section of the connecting channel 20 on the pressure chamber side. Accordingly, this valve 35, 36 - analogous to the control slide 23 - can be moved by means of the actuator 33 between a starting position in which the connecting channel 20 is open and an operating position in which the connecting channel 20 is closed.

Claims (9)

  1. Method of starting a hydraulic diaphragm pump under load with the aid of a starting connection, with operation of a diaphragm which separates a delivery chamber from a hydraulic chamber being effected by an oscillating displacement piston displaceable between the pressure chamber and a hydraulic supply chamber and, upon start-up of the pump, a displacement volume of the hydraulic fluid being transported by the displacement piston (6) in an open connection channel (20) between pressure chamber (5) and supply chamber (7), whereupon the movement of the diaphragm (1) is coupled to the displacement of the displacement piston (6) in that the connection between pressure chamber (5) and supply chamber (7) is interrupted,
    characterized in that
    interruption of the connection between pressure chamber (5) and supply chamber (7) is effected in an externally controlled manner at the minimum speed of the pump, which corresponds to a fraction of the rated speed.
  2. Method according to claim 1, characterized in that the displacement volume of the hydraulic fluid circulates in the connection channel (20) between pressure chamber (5) and supply chamber (7).
  3. Method according to claim 1, characterized in that the displacement volume of the hydraulic fluid in the connection channel (20) between pressure chamber (5) and supply chamber (7), because of the displacement piston (6), flows in such a way that it pulsates.
  4. Device for effecting the method according to one of claims 1 to 3, wherein the diaphragm pump is provided with at least one diaphragm (1), which separates a delivery chamber (4) from a hydraulic pressure chamber (5) and is clamped at its edge between the pump body (2) and a pump cover (3), and with a hydraulic diaphragm drive in the form of an oscillating displacement piston (6) which is displaceable in the pump body (2) between the pressure chamber (5) and a hydraulic supply chamber (7), and wherein on the pump drive side between the pressure chamber (5) and the supply chamber (7) a connection channel (20) is provided, which on start-up of the pump returns the hydraulic fluid displaced in the pressure chamber (5) by the displacement piston (6) to the supply chamber (7) and in the course of the further strokes of the displacement piston (6) is closable by a closing device (A) so that the pressure in the pressure chamber (5) rises up to the delivery pressure,
    characterized in that
    control of the closing device (A) is effected externally via an actuating drive (33), with the moment and/or rate of closure being variable, and that the closing device (A) has a movable closing element (23; 35, 36) which is displaceable between a starting position, in which it opens the flow cross-section of the connection channel (20), and an operating position, in which the flow cross-section of the connection channel (20) is closed.
  5. Device according to claim 4, characterized in that the actuating drive (33) operates as a function of the number or frequency of the strokes of the displacement piston (6) in such a way that, after the pump is switched on, the flow cross-section of the connection channel (20) available for the displaced hydraulic fluid is reduced upon each further pressure stroke.
  6. Device according to claim 4 or 5, characterized in that the closing element is a valve (35, 36), whose valve body (35) cooperates with a valve seat (36) formed in the connection channel (20).
  7. Device according to claim 4 or 5, characterised in that the closing element is a slide valve (23), which is disposed in the flow path of the connection channel (20) and via an outlet channel (27) controls the size of the flow cross-section of the connection channel (20).
  8. Device according to one of claims 4 to 7, characterised in that the closing element (23; 35, 36) is displaceable in an externally accessible connection bore (22).
  9. Device according to claim 8, characterised in that the connection bore (22) is disposed at a bend in the connection channel (20) in such a way that the pressure-chamber-side section of the connection channel (20) opens out into the bottom of the connection bore (22) and the supply-chamber-side section of the connection channel (20) opens out into the wall of the connection bore (22).
EP88104287A 1987-03-18 1988-03-17 Method and device for starting an hydraulic membrane pump against a load Expired - Lifetime EP0283026B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88104287T ATE86363T1 (en) 1987-03-18 1988-03-17 METHOD AND DEVICE FOR STARTING A DIAPHRAGM HYDRAULIC PUMP AGAINST LOAD.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873708868 DE3708868A1 (en) 1987-03-18 1987-03-18 METHOD AND DEVICE FOR STARTING A HYDRAULIC DIAPHRAGM PUMP AGAINST LOAD
DE3708868 1987-03-18

Publications (3)

Publication Number Publication Date
EP0283026A2 EP0283026A2 (en) 1988-09-21
EP0283026A3 EP0283026A3 (en) 1989-08-30
EP0283026B1 true EP0283026B1 (en) 1993-03-03

Family

ID=6323418

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104287A Expired - Lifetime EP0283026B1 (en) 1987-03-18 1988-03-17 Method and device for starting an hydraulic membrane pump against a load

Country Status (5)

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US (1) US4865528A (en)
EP (1) EP0283026B1 (en)
JP (1) JPS63314384A (en)
AT (1) ATE86363T1 (en)
DE (2) DE3708868A1 (en)

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JPH062664A (en) * 1992-06-22 1994-01-11 Nippon Soken Inc Diaphragm type pump
DE4327969C2 (en) * 1993-08-19 1997-07-03 Ott Kg Lewa Hydraulically driven diaphragm pump
DE4327970C2 (en) * 1993-08-19 1997-07-03 Ott Kg Lewa Hydraulically driven diaphragm pump with mechanical diaphragm stroke limitation
DE19726239B4 (en) * 1997-06-20 2014-04-03 Linde Hydraulics Gmbh & Co. Kg Hydrostatic drive system with a pump and a plurality of consumers connected thereto
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ES2393276T3 (en) * 1998-02-17 2012-12-20 Nikkiso Company, Ltd. Diaphragm pump
US6071089A (en) * 1998-02-20 2000-06-06 General Motors Corporation Hydraulic diaphragm pump
DE10056568C1 (en) 2000-11-15 2002-01-03 Horst Kleibrink Device, for controlling hydraulic membrane compressor, has control valve with throttle, where increasing differential pressure across throttle, causes control valve to open additional opening
JP4587098B2 (en) * 2004-07-21 2010-11-24 Ｓｍｃ株式会社 Pump device
US7425120B2 (en) * 2005-04-26 2008-09-16 Wanner Engineering, Inc. Diaphragm position control for hydraulically driven pumps
US7665974B2 (en) * 2007-05-02 2010-02-23 Wanner Engineering, Inc. Diaphragm pump position control with offset valve axis
JP2014177932A (en) * 2013-03-15 2014-09-25 Komatsu Denshi Kk Driving device for micro pump
DE102014109801A1 (en) * 2014-07-11 2016-01-14 Prominent Gmbh Diaphragm pump with reduced leakage supplement in case of overload
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Also Published As

Publication number Publication date
DE3878706D1 (en) 1993-04-08
DE3708868A1 (en) 1988-10-06
DE3708868C2 (en) 1990-08-23
EP0283026A3 (en) 1989-08-30
ATE86363T1 (en) 1993-03-15
US4865528A (en) 1989-09-12
JPS63314384A (en) 1988-12-22
EP0283026A2 (en) 1988-09-21

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