EP0723081B1 - Anger pump for conveying fluid material - Google Patents
Anger pump for conveying fluid material Download PDFInfo
- Publication number
- EP0723081B1 EP0723081B1 EP95120203A EP95120203A EP0723081B1 EP 0723081 B1 EP0723081 B1 EP 0723081B1 EP 95120203 A EP95120203 A EP 95120203A EP 95120203 A EP95120203 A EP 95120203A EP 0723081 B1 EP0723081 B1 EP 0723081B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stator
- hoses
- pump
- eccentric
- rotor
- 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
Links
- 239000000463 material Substances 0.000 title claims description 19
- 239000012530 fluid Substances 0.000 title 1
- 238000005086 pumping Methods 0.000 claims description 4
- 238000005056 compaction Methods 0.000 claims 3
- 230000009969 flowable effect Effects 0.000 abstract description 4
- 238000007789 sealing Methods 0.000 description 15
- 230000010349 pulsation Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 2
- 239000013013 elastic material Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000006887 Ullmann reaction Methods 0.000 description 1
- 230000003679 aging effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002572 peristaltic effect Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000002250 progressing effect Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000004065 wastewater treatment Methods 0.000 description 1
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
- F04B43/12—Machines, pumps, or pumping installations having flexible working members having peristaltic action
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
- F04C2/1076—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member orbits or wobbles relative to the other member which rotates around a fixed axis
Definitions
- a worm pump of the construction described above is made known by GB-A-2 029 514.
- This points including one driven by a drive axle helically wound eccentric screw rotor with constant circular cross section.
- the one in a stator room longitudinal elastic hoses are by means of end plates through the stator.
- openings are provided in the aforementioned plates.
- central openings that accommodate the recording serve a drive or rotational axis.
- the gap play or Fit between eccentric screw rotor and stator like this adjust that this is about twice the wall thickness of the corresponds to elastic hoses. Consequently, attack the Hoses running in the longitudinal direction to which can lead to unavoidable damage. Especially can be stretched, for example in connection with Aging effects can lead to tearing, not to be excluded.
- the invention is based on the technical problem Worm pump of the construction described above with regard Improve resistance and wear problems.
- the invention teaches to solve this technical problem in a generic screw pump for flowable Pump material that the stator chamber is longitudinal, partially cylindrical Stator wall sections and at least two between the Stator wall sections longitudinal cavities for the has resilient hoses disposed therein, and that the stator wall sections with a clearance to the Sum of eccentricity distance and cross section radius of the Eccentric screw rotor adapted radius.
- the invention is based on the knowledge that despite of the open, helical channel between the eccentric screw rotor and the partially cylindrical stator wall sections can achieve a promotional effect if the stator between the stator wall sections with longitudinal Cavities and hoses arranged in them is provided: between the longitudinal hoses and the helical circumferential areas of the Eccentric screw rotor creates cutting areas with Sealing lines used to generate lengthways spaced sealing areas of the hoses are used. Sealing areas and conveying spaces enclosed between them by rotating the eccentric screw rotor in the conveying direction moved so that the pumped material is conveyed.
- Auger pump multi-flow that is, for simultaneous Promotion of several, independent pump material flows suitable.
- the pumping material is conveyed in sections compressed hoses is basically known as Peristaltic pumps known from practice (see Ullmanns Encyclopedia of Technical Chemistry, 1973, Volume 3, page 169).
- a hose through several, along the Hose moving displacers such as rollers or Sliding shoes compressed.
- a multi-flow arrangement requires and is an increase in the number of these displacers constructively complex.
- the hoses while reducing their lifespan in the longitudinal direction stretched.
- the screw pump according to the invention produces on the other hand, no expansion of the hoses because of frictional forces between rotor and hose essentially only in the circumferential direction of the eccentric screw rotor act.
- the eccentric screw rotor not only with one, but with several gears. Due to the increase in the length of the pump stator Number of sealing areas can be the tightness of the Increase the screw pump and the achievable pressure.
- the Pump stator of the screw pump according to the invention can are basically made of any material. For The use of a has been gentle on the hoses elastic material with a hardness between 90 and 95 Shore A especially proven. Regarding an even and low pulsation running of the screw pump, it is from Advantage, cavities and hoses equidistant on the Distribute the circumference of the stator space.
- Another preferred embodiment lie to promote the same Hoses serving the goods to be pumped on each other in pairs opposite the circumference of the stator space, so that at one later merging of the streams does not equal pumped goods Pulsation occurs.
- Another preferred embodiment provides for hoses in the cavities different diameters are recordable. Hereby different amounts in the individual tubes are funded by Pumpgut. The ratio of the funded The quantity depends on the speed and gradient of the eccentric screw rotor and thus the total output independently, so that the device according to the invention be used especially for dosing and mixing tasks can, with the control of various individual pumps There is no change in the total output. It goes without saying that the depths and breadth of the cavities the different hose diameters can be adjusted.
- the device shown in the figures serves as a screw pump for flowable pump material.
- the necessary ones Units for drive, storage of the eccentric screw rotor as well as for the supply and removal of the pumped goods have been improved Clarity not shown.
- FIG. 1 shows hatched the circular cross section of the Eccentric screw rotor.
- the center 3 of the eccentric screw rotor points to the axis of rotation 4 Eccentricity distance e on.
- the pump stator 5 includes one Stator chamber 6, in which the eccentric screw rotor 2 as is rotatably arranged.
- a comparative 1 and 2 it can be seen that the stator space 6 longitudinally running, partially cylindrical stator wall sections 7 having.
- Fig. 2 shows a fitting game s between the Eccentric screw rotor 2 and the pump stator 5, through which allows wear-free operation of the two components becomes.
- the radius R of the partially cylindrical stator wall sections 7 is out of the sum with this fit s Cross-sectional radius r of the eccentric screw rotor 2 and Eccentricity adjusted e, as can be seen in Fig. 2.
- the Eccentricity e is 23% of the embodiment Eccentric screw rotor diameter. It can be seen that the Rotation axis 4 and the longitudinal axis 4 of the stator space 6 coincide and so far a central drive of the Eccentric screw rotor takes place.
- Fig. 2 shows four Cavities 8 in the stator chamber 6. These run as shown in FIG. 1 shows in the longitudinal direction between the Stator wall sections 7. In the cavities 8 are elastic hoses 9 arranged. The one shown The worm pump has four channels. The funding mechanism is in 1 can be seen well.
- the Sealing line between eccentric screw rotor 2 and hoses 9 runs in one of the pitch of the eccentric screw rotor 2 dependent angles to the longitudinal direction of the tubes 9.
- the eccentric screw rotor 2 shown is catchy, it can but can also be easily carried out in multiple courses.
- Hoses 9 are made of elastic rubber or plastic be made.
- the pump stator 5 Use of an elastic material with a hardness of 90 Up to 95 Shore A advantageous for protecting the hoses. in the the rest of the chemical resistance of the Eccentric screw rotor and pump stator material only low requirements, so that inexpensive materials can be used.
- Fig. 2 shows that the tubes 9th are distributed equidistantly around the circumference of the stator space.
- two different items to be pumped be promoted, so it is beneficial to low pulsation Convey each pump good in pairs on the circumference of the stator chamber 6 opposite hoses 9 use.
- the hoses 9 shown in Fig. 2 have the same diameter and promote the same Pump material flows. It is easy to see in Fig. 2 that the Diameter of the hoses can be changed easily can to increase the delivery rate of the individual hoses vary. In operation, the ratio of those in the Hoses 9 pumped material flows constant and from Total throughput or of speed and slope of the Eccentric screw rotor 2 be independent.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Reciprocating Pumps (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
Description
Die Erfindung betrifft eine Schneckenpumpe für fließfähiges Pumpgut, - mit angetriebenem und schraubenförmig gewundenem Exzenterschneckenrotor mit konstantem, kreisförmigen Querschnitt, dessen Mittelpunkt von der Rotationsachse des Exzenterschneckenrotors um einen Exzentrizitätsabstand beabstandet ist, mit einem Pumpenstator mit Statorraum, und mit im Statorraum längslaufenden, in diesen hineinragenden, elastischen Schläuchen, wobei
- der Exzenterschneckenrotor im Statorraum drehbar angeordnet ist, wobei ferner
- die Rotationsachse des Exzenterschneckenrotors und die Längsachse des Statorraums zusammenfallen, wobei weiter
- die Schläuche durch die von der Rotationsachse fernsten Bereiche des Exzenterschneckenrotors abschnittsweise in Dichtbereichen komprimiert werden und zwischen den Dichtbereichen Förderräume aufweisen, und wobei
- die Dichtbereiche und die Förderräume durch Rotation des Exzenterschneckenrotors in Förderrichtung längs der Schläuche verschoben werden.
- the eccentric screw rotor is rotatably arranged in the stator space, furthermore
- the axis of rotation of the eccentric screw rotor and the longitudinal axis of the stator space coincide, with further
- the tubes are compressed in sections by the regions of the eccentric screw rotor furthest from the axis of rotation in sealing regions and have conveying spaces between the sealing regions, and wherein
- the sealing areas and the delivery spaces can be moved along the hoses by rotating the eccentric screw rotor in the delivery direction.
Eine Schneckenpumpe des eingangs beschriebenen Aufbaus ist durch die GB-A-2 029 514 bekannt geworden. Diese weist unter anderem einen über eine Antriebsachse angetriebenen schraubenförmig gewundenen Exzenterschneckenrotor mit konstantem kreisförmigen Querschnitt auf. Die in einem Statorraum längs verlaufenden elastischen Schläuche werden mittels endseitigen Platten durch den Statorraum geführt. Hierzu sind Öffnungen in den vorgenannten Platten vorgesehen. Ferner finden sich Zentralöffnungen, welche der Aufnahme einer Antriebs- bzw. Rotationsachse dienen. Um die Schläuche abschnittsweise in Dichtbereichen zu komprimieren und zwischen den Dichtbereichen Förderräume zu definieren, kommt es einzig und allein darauf an, das Spaltspiel bzw. Passungsspiel zwischen Exzenterschneckenrotor und Stator so einzustellen, daß dieses etwa der zweifachen Wanddicke der elastischen Schläuche entspricht. Folglich greifen an die Schläuche in Längsrichtung verlaufende Kräfte an, welche zu unvermeidbaren Beschädigungen führen können. Insbesondere lassen sich Dehnungen, die beispielsweise in Verbindung mit Alterungseffekten zum Reißen führen können, nicht ausschließen.A worm pump of the construction described above is made known by GB-A-2 029 514. This points including one driven by a drive axle helically wound eccentric screw rotor with constant circular cross section. The one in a stator room longitudinal elastic hoses are by means of end plates through the stator. For this purpose, openings are provided in the aforementioned plates. There are also central openings that accommodate the recording serve a drive or rotational axis. To the Compress hoses in sections in sealing areas and to define conveying spaces between the sealing areas, the only thing that matters is the gap play or Fit between eccentric screw rotor and stator like this adjust that this is about twice the wall thickness of the corresponds to elastic hoses. Consequently, attack the Hoses running in the longitudinal direction to which can lead to unavoidable damage. Especially can be stretched, for example in connection with Aging effects can lead to tearing, not to be excluded.
Im übrigen sind Schneckenpumpen mit Exzenterschneckenrotor
beispielsweise aus Hartinger, "Taschenbuch der Abwasserbehandlung",
Band 2, Carl Hanser Verlag, 1977, bekannt. Bei
diesen Pumpen besitzt der Statorraum schraubenförmige Ausnehmungen
mit doppelter Gangzahl und Steigung des Exzenterschneckenrotors.
Rotationsachse des Exzenterschneckenrotors
und Längsachse des Statorraums sind um die Exzentrizität
des Exzenterschneckenrotors versetzt. Die bekannte Pumpe
ist hinsichtlich der Pumpenstatorfertigung und hinsichtlich
des Antriebes konstruktiv vergleichsweise aufwendig. Der
Pumpenstator ist wegen des dichtenden Kontraktes zum Exzenterschneckenrotor
verschleißanfällig. Das Pumpenstatormaterial
und der Exzenterschneckenrotor-Werkstoff müssen
hinsichtlich ihrer Beständigkeit an das zu fördernde Pumpgut
angepaßt werden. Die bekannten Exzenterschneckenpumpen
arbeiten einflutig, d.h., pro Rotor-Stator-Paarung kann nur
ein Pumpgutstrom gefördert werden.Otherwise, there are screw pumps with eccentric screw rotors
for example from Hartinger, "Paperback of Wastewater Treatment",
Der Erfindung liegt das technische Problem zugrunde, eine Schneckenpumpe des eingangs beschriebenen Aufbaus hinsichtlich Beständigkeits- und Verschleißproblemen zu verbessern.The invention is based on the technical problem Worm pump of the construction described above with regard Improve resistance and wear problems.
Zur Lösung dieses technischen Problems lehrt die Erfindung bei einer gattungsgemäßen Schneckenpumpe für fließfähiges Pumpgut, daß der Statorraum längslaufende, teilzylindrische Statorwandabschnitte und zumindest zwei zwischen den Statorwandabschnitten längslaufende Auskammerungen für die hierin angeordneten elastischen Schläuche aufweist, und daß die Statorwandabschnitte einen mit Passungsspiel an die Summe aus Exzentrizitätsabstand und Querschnittsradius des Exzenterschneckenrotors angepaßten Radius besitzen.The invention teaches to solve this technical problem in a generic screw pump for flowable Pump material that the stator chamber is longitudinal, partially cylindrical Stator wall sections and at least two between the Stator wall sections longitudinal cavities for the has resilient hoses disposed therein, and that the stator wall sections with a clearance to the Sum of eccentricity distance and cross section radius of the Eccentric screw rotor adapted radius.
Die Erfindung geht von der Erkenntnis aus, daß sich trotz des offenen, schraubenförmigen Kanals zwischen Exzenterschneckenrotor und den teilzylindrischen Statorwandabschnitten eine Förderwirkung erzielen läßt, wenn der Statorraum zwischen den Statorwandabschnitten mit längslaufenden Auskammerungen und darin angeordneten Schläuchen versehen wird: Zwischen den längslaufenden Schläuchen und den schraubenförmig umlaufenden, von der Rotationsachse fernsten Bereichen des Exzenterschneckenrotors entstehen Schnittbereiche mit Dichtlinien, die zur Erzeugung von in Längsrichtung beabstandeten Dichtbereichen der Schläuche genutzt werden. Dichtbereiche und zwischen diesen eingeschlossene Förderräume werden durch Rotation des Exzenterschneckenrotors in Förderrichtung verschoben, so daß das Pumpgut gefördert wird. Durch die Verwendung mehrerer Schläuche ist die erfindungsgemäße Schneckenpumpe mehrflutig, das heißt zur gleichzeitigen Förderung mehrerer, voneinander unabhängiger Pumpgutströme geeignet. Insbesondere können verschiedene Pumpgüter gleichzeitig gefördert werden. Pumpenstator und Exzenterschneckenrotor arbeiten praktisch verschleißfrei und ohne Beständigkeitsprobleme, da sie durch die Schläuche voneinander und vom Pumpgut getrennt sind. Der Aufbau der erfindungsgemäßen Schneckenpumpe ist konstruktiv einfach.The invention is based on the knowledge that despite of the open, helical channel between the eccentric screw rotor and the partially cylindrical stator wall sections can achieve a promotional effect if the stator between the stator wall sections with longitudinal Cavities and hoses arranged in them is provided: between the longitudinal hoses and the helical circumferential areas of the Eccentric screw rotor creates cutting areas with Sealing lines used to generate lengthways spaced sealing areas of the hoses are used. Sealing areas and conveying spaces enclosed between them by rotating the eccentric screw rotor in the conveying direction moved so that the pumped material is conveyed. By the use of several hoses is the one according to the invention Auger pump multi-flow, that is, for simultaneous Promotion of several, independent pump material flows suitable. In particular, different pump goods be promoted at the same time. Pump stator and eccentric screw rotor work practically without wear and without Resistance problems as they pass through the hoses are separated from each other and from the pump material. The structure of the Screw pump according to the invention is structurally simple.
Die Föderung von Pumpgut mittels abschnittsweise
komprimierter Schläuche ist grundsätzlich durch sogenannte
Schlauchpumpen aus der Praxis bekannt (vgl. Ullmanns
Encyklopädie der technischen Chemie, 1973, Band 3, Seite
169). Hierbei wird ein Schlauch durch mehrere, längs des
Schlauches bewegte Verdrängungskörper wie Rollen oder
Gleitschuhe komprimiert. Eine mehrflutige Anordnung erfordert
eine Erhöhung der Anzahl dieser Verdrängungskörper und ist
konstruktiv aufwendig. Darüber hinaus werden die Schläuche
unter Verringerung ihrer Lebensdauer in Längsrichtung
gedehnt. Die erfindungsgemäße Schneckenpumpe erzeugt
demgegenüber keine Dehnung der Schläuche, da Reibungskräfte
zwischen Rotor und Schlauch im wesentlichen nur in Umfangsrichtung
des Exzenterschneckenrotors wirken. Darüber hinaus
fördert die erfindungsgemäße Schneckenpumpe wegen des durch
die Steigung des Exzenterschneckenrotors bedingten Winkels
der Dichtlinien zur Förderrichtung und wegen der durch die
Geometrie des Exzenterschneckenrotors bedingten allmählichen
Freigabe des Förderraumes am Pumpenausgang besonders
pulsationsarm.The pumping material is conveyed in sections
compressed hoses is basically known as
Peristaltic pumps known from practice (see Ullmanns
Encyclopedia of Technical Chemistry, 1973,
Im Rahmen der Erfindung liegt es, den Exzenterschneckenrotor nicht nur mit einem, sondern mit mehreren Gängen zu versehen. Durch die bei gleichbleibender Pumpenstatorlänge vergrößerte Zahl von Dichtbereichen läßt sich so die Dichtigkeit der Schneckenpumpe und der erzielbare Druck erhöhen. Der Pumpenstator der erfindungsgemäßen Schneckenpumpe kann grundsätzlich aus beliebigem Werkstoff gefertigt werden. Zur Schonung der Schläuche hat sich die Verwendung eines elastischen Materials mit einer Härte zwischen 90 und 95 Shore A besonders bewährt. Hinsichtlich eines gleichmäßigen und pulsationsarmen Laufes der Schneckenpumpe ist es von Vorteil, Auskammerungen und Schläuche äquidistant auf dem Umfang des Statorraumes zu verteilen. Bei einer weiteren bevorzugten Ausführungsform liegen zur Förderung des gleichen Pumpgutes dienende Schläuche einander jeweils paarweise auf dem Umfang des Statorraumes gegenüber, so daß bei einer späteren Zusammenführung der Ströme gleichen Pumpgutes keine Pulsation auftritt. Eine weitere bevorzugte Ausführungsform sieht vor, daß in den Auskammerungen Schläuche unterschiedlichen Durchmessers aufnehmbar sind. Hierdurch können in den einzelnen Schläuchen unterschiedliche Mengen von Pumpgut gefördert werden. Das Verhältnis der geförderten Mengen ist dabei von Drehzahl und Steigung des Exzenterschneckenrotors und somit von der Gesamtfördermenge unabhängig, so daß die erfindungsgemäße Vorrichtung insbesondere für Dosier- und Mischaufgaben eingesetzt werden kann, wobei die Regelung verschiedener Einzelpumpen bei Änderung der Gesamtfördermenge entfällt. Es versteht sich, daß hierzu die Auskammerungen in ihrer Tiefe und Breite an die verschiedenen Schlauchdurchmesser angepaßt werden können. Im allgemeinen ist dies jedoch nicht erforderlich, sofern die Wandstärke der Schläuche unterschiedlichen Durchmessers im wesentlichen übereinstimmt. Es versteht sich weiter, daß die Summe aus Tiefe der Auskammerung und Passungsspiel an die doppelte Wandstärke des in der Auskammerung angeordneten Schlauches angepaßt ist.It is within the scope of the invention, the eccentric screw rotor not only with one, but with several gears. Due to the increase in the length of the pump stator Number of sealing areas can be the tightness of the Increase the screw pump and the achievable pressure. Of the Pump stator of the screw pump according to the invention can are basically made of any material. For The use of a has been gentle on the hoses elastic material with a hardness between 90 and 95 Shore A especially proven. Regarding an even and low pulsation running of the screw pump, it is from Advantage, cavities and hoses equidistant on the Distribute the circumference of the stator space. Another preferred embodiment lie to promote the same Hoses serving the goods to be pumped on each other in pairs opposite the circumference of the stator space, so that at one later merging of the streams does not equal pumped goods Pulsation occurs. Another preferred embodiment provides for hoses in the cavities different diameters are recordable. Hereby different amounts in the individual tubes are funded by Pumpgut. The ratio of the funded The quantity depends on the speed and gradient of the eccentric screw rotor and thus the total output independently, so that the device according to the invention be used especially for dosing and mixing tasks can, with the control of various individual pumps There is no change in the total output. It goes without saying that the depths and breadth of the cavities the different hose diameters can be adjusted. In general, however, this is not necessary if the Wall thickness of the hoses of different diameters in the essentially coincides. It is further understood that the Sum of the depth of the recess and fit clearance to the double the wall thickness of the arranged in the chamber Hose is adjusted.
Im folgenden wird die Erfindung anhand einer lediglich ein Ausführungsbeispiel darstellenden Zeichnung ausführlicher Erläutert. Es zeigen in schematischer Darstellung
- Fig. 1
- einen Längsschnitt durch Exzenterschneckenrotor, Pumpenstator und Schläuche der erfindungsgemäßen Schneckenpumpe,
- Fig. 2
- einen Schnitt durch den Gegenstand der Fig. 1 aus der in Fig. 1 eingezeichneten Blickrichtung A-A.
- Fig. 1
- 2 shows a longitudinal section through the eccentric screw rotor, pump stator and hoses of the screw pump according to the invention,
- Fig. 2
- a section through the object of FIG. 1 from the viewing direction AA shown in Fig. 1.
Die in den Figuren gezeigte Vorrichtung dient als Schneckenpumpe für fließfähiges Pumpgut. Die insoweit erforderlichen Aggregate für Antrieb, Lagerung des Exzenterschneckenrotors sowie für Zu- und Abfuhr des Pumpgutes wurden zur besseren Übersichtlichkeit nicht dargestellt. The device shown in the figures serves as a screw pump for flowable pump material. The necessary ones Units for drive, storage of the eccentric screw rotor as well as for the supply and removal of the pumped goods have been improved Clarity not shown.
Zum grundsätzlichen Aufbau der Schneckenpumpen 1 gehört ein
schraubenförmiger, angetriebener Exzenterschneckenrotor 2.
Fig. 1 zeigt schraffiert den kreisförmigen Querschnitt des
Exzenterschneckenrotors. Der Mittelpunkt 3 des Exzenterschneckenrotors
weist zu der Rotationsachse 4 einen
Exzentrizitätsabstand e auf. Erkennbar ist weiterhin der
Pumpenstator 5, der im Ausführungsbeispiel aus NBR-Kautschuk
gefertigt sein mag. Der Pumpenstator 5 umfaßt einen
Statorraum 6, in dem der Exzenterschneckenrotor 2 wie
eingezeichnet drehbar angeordnet ist. Einer vergleichenden
Betrachtung der Fig. 1 und 2 entnimmt man, daß der Statorraum
6 längslaufende, teilzylindrische Statorwandabschnitte 7
aufweist. Fig. 2 zeigt ein Passungspiel s zwischem dem
Exzenterschneckenrotor 2 und dem Pumpenstator 5, durch das
ein verschleißfreier Betrieb der beiden Bauteile ermöglicht
wird. Der Radius R der teilzylindrischen Statorwandabschnitte
7 ist mit diesem Passungspiel s an die Summe aus
Querschnittsradius r des Exzenterschneckenrotors 2 und
Exzentrizität e angpaßt, wie Fig. 2 zu entnehmen ist. Die
Exzentrizität e beträgt im Ausführungsbeispiel 23% des
Exzenterschneckenrotor-Durchmessers. Man erkennt, daß die
Rotationsachse 4 und die Längsachse 4 des Statorraumes 6
zusammenfallen und insoweit ein zentrischer Antrieb des
Exzenterschneckenrotors erfolgt. Fig. 2 zeigt vier
Auskammerungen 8 im Statorraum 6. Diese verlaufen, wie Fig. 1
erkennen läßt, in Längsrichtung zwischen den
Statorwandabschnitten 7. In den Auskammerungen 8 sind
elastische Schläuche 9 angeordnet. Die gezeigte
Schneckenpumpe ist vierflutig. Der Fördermechanismus ist in
Fig. 1 gut zu erkennen. Die der Rotationsachse 4 fernsten
Bereiche des Exzenterschneckenrotors laufen schraubenförmig
um und sind als Linie auf dem Rotor 2 angedeutet. Man
erkennt, daß im Schnitt dieser Bereiche mit den in
Längsrichtung verlaufenden Schläuchen 9 abschnittsweise
Dichtbereiche 10 gebildet werden, in denen die Schläuche 9
komprimiert werden. Fig. 1 zeigt, daß die Schläuche 9
zwischen den Dichtbereichen 10 Förderräume 11 aufweisen. Man
erkennt, daß durch Rotation des Exzenterschneckenrotors 2
Förderräume 11 und Dichtbereiche 10 längs der Schläuche 9
verschoben werden, wodurch das in den Förderräumen 11
eingeschlossene Volumen in Förderrichtung gefördert wird. Die
Förderrichtung ist in Fig. 1 als Pfeil gekennzeichnet. Die
Dichtlinie zwischen Exzenterschneckenrotor 2 und Schläuchen 9
verläuft in einem von der Steigung des Exzenterschneckenrotors
2 abhängigen Winkel zur Längsrichtung der Schläuche 9.
Der gezeigte Exzenterschneckenrotor 2 ist eingängig, er kann
aber auch ohne weiteres mehrgängig ausgeführt sein. Der
Exzenterschneckenrotor 2 wird regelmäßig aus Stahl, die
Schläuche 9 werden aus elastischem Gummi oder Kunststoff
gefertigt sein. Hinsichtlich des Pumpenstators 5 ist die
Verwendung eines elastischen Materials mit einer Härte von 90
bis 95 Shore A für die Schonung der Schläuche vorteilhaft. Im
übrigen werden an die chemische Beständigkeit des
Exzenterschneckenrotor- und des Pumpenstatorwerkstoffes nur
geringe Anforderungen gestellt, so daß preiswerte Materialien
verwendet werden können. Fig. 2 zeigt, daß die Schläuche 9
äquidistant auf dem Umfang des Statorraumes verteilt sind.
Sollen im Ausführungsbeispiel zwei verschiedene Pumpgüter
gefördert werden, so ist es vorteilhaft, zur pulsationsarmen
Förderung jedes Pumpgutes einander paarweise auf dem Umfang
des Statorraumes 6 gegenüberliegende Schläuche 9 zu
verwenden. Die in Fig. 2 gezeigten Schläuche 9 haben den
gleichen Durchmesser und fördern insofern gleiche
Pumpgutströme. Man erkennt unschwer in Fig. 2, daß die
Durchmesser der Schläuche ohne weiteres verändert werden
können, um die Förderleistung der einzelnen Schläuche zu
variieren. Im Betrieb wird hierbei das Verhältnis der in den
Schläuchen 9 geförderten Pumpgutströme konstant und vom
Gesamtdurchsatz bzw. von Drehzahl und Steigung des
Exzenterschneckenrotors 2 unabhängig sein.A part of the basic structure of the screw pumps 1
helical, driven
Claims (6)
- A spiral pump (1) for free-flowing pumping material,having a driven, helically wound eccentric spiral rotor (2) which has a constant, circular cross-section, the centre (3) of which is spaced apart from the axis of rotation (4) of the eccentric spiral rotor (2) by an eccentricity interval (e),having a pump stator (5) with a stator space (6) , andhaving flexible hoses (9) which run longitudinally in the stator space (6) and which protrude into the latter, whereinthe eccentric spiral rotor (2) is rotatably disposed in the stator space (6), wherein in additionthe axis of rotation (4) of the eccentric spiral rotor (2) and the longitudinal axis (4) of the stator space (6) coincide, wherein in additionthe hoses (9) are compressed sectionally in compaction regions (10) by the regions of the eccentric spiral rotor (2) which are furthest from the axis of rotation (4) and comprise conveying spaces (11) between the compaction regions (10), and whereinthe compaction regions (10) and the conveying spaces (11) are displaced along the hoses (9) in the direction of conveying by the rotation of the eccentric spiral rotor (2),the stator space (6) comprises longitudinally extending, partially cylindrical wall sections (7) and at least two chamber-like recesses (8), which extend longitudinally between the stator wall sections (7), for the flexible hoses (9) disposed therein, and thatthe stator wall sections (7) have a radius (R) which is matched with a fitting clearance (s) to the sum of the eccentricity interval (e) and the cross-sectional radius (r) of the eccentric spiral rotor (2).
- A spiral pump according to claim 1, characterised in that the eccentric spiral rotor is multiple-threaded.
- A spiral pump according to claims 1 or 2, characterised in that the pump stator (5) is manufactured from a flexible material with a hardness between 90 and 95 Shore A.
- A spiral pump according to any one of claims 1 to 3, characterised in that the chamber-like recesses (8) are disposed equidistantly on the periphery of the stator space (6).
- A spiral pump according to any one of claims 1 to 4, characterised in that hoses (9) which are acted upon by the same pumping material are disposed opposite each other in pairs on the periphery of the stator space (6).
- A spiral pump according to any one of claims 1 to 5, characterised in that hoses (9) of different diameters can be accommodated in the chamber-like recesses (8).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19501441 | 1995-01-19 | ||
DE19501441A DE19501441C1 (en) | 1995-01-19 | 1995-01-19 | Multi=flow eccentric screw pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0723081A1 EP0723081A1 (en) | 1996-07-24 |
EP0723081B1 true EP0723081B1 (en) | 1999-02-03 |
Family
ID=7751802
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95120203A Expired - Lifetime EP0723081B1 (en) | 1995-01-19 | 1995-12-20 | Anger pump for conveying fluid material |
Country Status (8)
Country | Link |
---|---|
US (1) | US5620313A (en) |
EP (1) | EP0723081B1 (en) |
JP (1) | JPH08319939A (en) |
CN (1) | CN1133944A (en) |
AT (1) | ATE176520T1 (en) |
CA (1) | CA2167545C (en) |
DE (2) | DE19501441C1 (en) |
ES (1) | ES2127460T3 (en) |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3414171B2 (en) | 1996-11-29 | 2003-06-09 | 株式会社デンソー | Heat exchanger |
US6267570B1 (en) | 1999-02-16 | 2001-07-31 | Arne D. Armando | Peristaltic pump |
DE10125939A1 (en) * | 2001-05-23 | 2002-12-05 | Gunter Kraus | Pump pref. for use in wind power generators with pressure chamber between rotor and stator continuously reduced in cross section by eccentric elements on rotor/stator |
US6905319B2 (en) | 2002-01-29 | 2005-06-14 | Halliburton Energy Services, Inc. | Stator for down hole drilling motor |
US7396351B2 (en) * | 2003-11-05 | 2008-07-08 | Boston Scientific Scimed, Inc. | Device and method for the delivery of viscous fluids in the body |
MX2007012489A (en) * | 2005-04-07 | 2008-03-11 | Marion H Bobo | A head for peristaltic pump. |
US20070237642A1 (en) * | 2006-04-10 | 2007-10-11 | Murrow Kurt D | Axial flow positive displacement worm pump |
US20090211474A1 (en) * | 2008-02-22 | 2009-08-27 | Atwater Richard G | Printing press inking systems |
DE202009001865U1 (en) | 2009-02-11 | 2010-07-22 | Krauss, Gunter | Pump, in particular peristaltic pump |
US8777597B1 (en) * | 2010-01-27 | 2014-07-15 | Robert C. Geschwender | Linear peristaltic pump having a platen and pressure plate with curved surfaces |
DE102010022704A1 (en) * | 2010-06-04 | 2011-12-08 | Wilo Se | Lifting plant for the disposal of domestic sewage |
US9693896B2 (en) | 2013-03-15 | 2017-07-04 | Novartis Ag | Systems and methods for ocular surgery |
KR20160082968A (en) * | 2013-11-05 | 2016-07-11 | 노바르티스 아게 | Ophthalmic lubrication system and associated apparatus, systems, and methods |
DE102014118924A1 (en) * | 2014-12-17 | 2016-06-23 | Qonqave Gmbh | conveyor |
DE102014118926B4 (en) * | 2014-12-17 | 2023-02-02 | Watson Marlow Gmbh | conveyor |
CN108260840A (en) * | 2016-12-30 | 2018-07-10 | 周安定 | The straight line peristaltic pump of food printing |
DE202018003997U1 (en) | 2018-08-28 | 2019-12-04 | Gunter Krauss | Pump, especially peristaltic pump |
DE102019116601A1 (en) * | 2019-06-19 | 2021-01-07 | Ralf Hannibal | Peristaltic pump |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2015123A (en) * | 1934-05-11 | 1935-09-24 | Pennell Samuel | Blood transfusion apparatus |
US2621605A (en) * | 1945-10-12 | 1952-12-16 | Clayton Mark & Company | Pump |
US2629333A (en) * | 1950-07-01 | 1953-02-24 | Roger G Olden | Rotary compress pump |
US2752860A (en) * | 1953-02-25 | 1956-07-03 | Du Pont | Pump |
GB800154A (en) * | 1955-09-30 | 1958-08-20 | Ahmad Aziz | Improvements in or relating to rotary pumps or motors |
FR1335006A (en) * | 1962-06-12 | 1963-08-16 | Rotary machine usable in particular as a pump | |
US3340817A (en) * | 1965-10-18 | 1967-09-12 | Gustave W Kemnitz | Pump |
US3951576A (en) * | 1974-09-23 | 1976-04-20 | Lofquist Jr Alden A | Rotary diaphragm pump |
DE2964884D1 (en) * | 1978-03-23 | 1983-03-31 | Daniel Joseph Bradley | Apparatus and method for recording high-speed repetitive optical phenomena |
GB2029514A (en) * | 1978-08-31 | 1980-03-19 | Charlesworth M | Peristaltic fluid-machines |
JPS5692387A (en) * | 1979-12-26 | 1981-07-27 | Kuraray Co Ltd | Liquid feeding pump utilizing spiral-type rotary body |
JPS58116690A (en) * | 1981-12-28 | 1983-07-11 | Denki Kagaku Kogyo Kk | Preparation of d-beta-hydroxyamino acid |
FR2523656A1 (en) * | 1982-03-18 | 1983-09-23 | Commissariat Energie Atomique | Rotating screw pump with membrane - has locating grooves for membrane to prevent damage |
GB8510382D0 (en) * | 1985-04-24 | 1985-05-30 | Russell D | Peristaltic pump |
JPS6321375A (en) * | 1986-07-15 | 1988-01-28 | Mitsui Constr Co Ltd | Fluidized substance pressure-feeding device |
JPH02171308A (en) * | 1988-12-24 | 1990-07-03 | Sumitomo Rubber Ind Ltd | Pneumatic tire |
RU2004850C1 (en) * | 1991-04-03 | 1993-12-15 | Станислав Владимирович Варварин | Wave pump with hoses |
HU212559B (en) * | 1993-02-12 | 1996-08-29 | Ferenczy | Rotating piston pump for fluids and gases |
-
1995
- 1995-01-19 DE DE19501441A patent/DE19501441C1/en not_active Expired - Fee Related
- 1995-12-20 ES ES95120203T patent/ES2127460T3/en not_active Expired - Lifetime
- 1995-12-20 AT AT95120203T patent/ATE176520T1/en not_active IP Right Cessation
- 1995-12-20 DE DE59505030T patent/DE59505030D1/en not_active Expired - Lifetime
- 1995-12-20 EP EP95120203A patent/EP0723081B1/en not_active Expired - Lifetime
-
1996
- 1996-01-17 US US08/587,668 patent/US5620313A/en not_active Expired - Lifetime
- 1996-01-18 CN CN96101309A patent/CN1133944A/en active Pending
- 1996-01-18 CA CA002167545A patent/CA2167545C/en not_active Expired - Fee Related
- 1996-01-19 JP JP8007701A patent/JPH08319939A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
EP0723081A1 (en) | 1996-07-24 |
CA2167545A1 (en) | 1996-07-20 |
CN1133944A (en) | 1996-10-23 |
JPH08319939A (en) | 1996-12-03 |
DE59505030D1 (en) | 1999-03-18 |
DE19501441C1 (en) | 1996-04-04 |
US5620313A (en) | 1997-04-15 |
CA2167545C (en) | 2000-10-03 |
ATE176520T1 (en) | 1999-02-15 |
ES2127460T3 (en) | 1999-04-16 |
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