[go: up one dir, main page]

EP0196575B1 - Device for mixing at least one flow medium - Google Patents

Device for mixing at least one flow medium Download PDF

Info

Publication number
EP0196575B1
EP0196575B1 EP86103912A EP86103912A EP0196575B1 EP 0196575 B1 EP0196575 B1 EP 0196575B1 EP 86103912 A EP86103912 A EP 86103912A EP 86103912 A EP86103912 A EP 86103912A EP 0196575 B1 EP0196575 B1 EP 0196575B1
Authority
EP
European Patent Office
Prior art keywords
impellers
pump
pump impellers
currents
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP86103912A
Other languages
German (de)
French (fr)
Other versions
EP0196575A2 (en
EP0196575A3 (en
Inventor
Angelo Cadeo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tetra Pak Processing Equipment AG
Original Assignee
Miteco AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Miteco AG filed Critical Miteco AG
Priority to AT86103912T priority Critical patent/ATE70203T1/en
Publication of EP0196575A2 publication Critical patent/EP0196575A2/en
Publication of EP0196575A3 publication Critical patent/EP0196575A3/en
Application granted granted Critical
Publication of EP0196575B1 publication Critical patent/EP0196575B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F27/00—Mixers with rotary stirring devices in fixed receptacles; Kneaders
    • B01F27/40—Mixers with rotor-rotor system, e.g. with intermeshing teeth
    • B01F27/41—Mixers with rotor-rotor system, e.g. with intermeshing teeth with the mutually rotating surfaces facing each other
    • B01F27/412—Mixers with rotor-rotor system, e.g. with intermeshing teeth with the mutually rotating surfaces facing each other provided with ribs, ridges or grooves on one surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F27/00—Mixers with rotary stirring devices in fixed receptacles; Kneaders
    • B01F27/80—Mixers with rotary stirring devices in fixed receptacles; Kneaders with stirrers rotating about a substantially vertical axis
    • B01F27/81—Mixers with rotary stirring devices in fixed receptacles; Kneaders with stirrers rotating about a substantially vertical axis the stirrers having central axial inflow and substantially radial outflow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F27/00—Mixers with rotary stirring devices in fixed receptacles; Kneaders
    • B01F27/80—Mixers with rotary stirring devices in fixed receptacles; Kneaders with stirrers rotating about a substantially vertical axis
    • B01F27/84—Mixers with rotary stirring devices in fixed receptacles; Kneaders with stirrers rotating about a substantially vertical axis with two or more stirrers rotating at different speeds or in opposite directions about the same axis

Definitions

  • the invention relates to a device for mixing at least one flow medium, wherein at least two partial flows of the flow medium are brought together to produce a very strongly turbulent flow.
  • Such a device is known from US Pat. No. 3,147,957 which has at least two pump impellers for the partial flows which are parallel and coaxial to one another, adjacent pump impellers being opposed, each pump impeller being assigned one of the partial flows.
  • the mixing of the flow media or media takes place within the device.
  • the mechanical shear action acts on the medium.
  • the impellers are provided with grooves or ribs and the impellers are made of hard metal (carborundum) in order to exert the greatest possible shear effects on, for example, the liquids to be mixed.
  • the effect of such a known device with two counter-rotating impellers is such that only the relative speed due to the two medium disks of opposite direction of rotation changes.
  • the aim is to create a device with which the aforementioned disadvantages can be avoided so that great turbulence can be achieved in an economical manner.
  • the pump impellers can be manufactured much cheaper since they are no longer subject to the abrasions mentioned. The shear effect on the media or media no longer has to be acted upon, in any case no special precautions have to be taken to achieve this.
  • the pump impellers are provided with forward-curved blades, so that they thereby become pure centrifugal impellers, which only have the task of converting the mechanical energy into hydraulic energy with the highest possible efficiency.
  • the two partial flows are only mixed outside the pump impellers in that large cross flows (transverse to the two flowing medium disks) and consequently large turbulences occur in a small ring outside the device.
  • the very high mixing effect is achieved by counteracting two cross flows with the high tangential velocity.
  • the two pump impellers with forward curved blades and opposite direction of rotation are necessary for this.
  • the tangential speed of the medium emerging from each pump impeller cannot have the same high value (at a given speed) since the tangential speed of the emerging medium is only of the same size like the peripheral speed of the pump impeller.
  • the two medium disks meet at their tangential speeds outside the device, so that the large transverse flows form, which result in very strong turbulence, which result in the at least one flow medium being mixed as intensively as possible.
  • Fig. 1 there are two pump impellers 1 and 2 which are parallel and coaxial to each other. Both pump impellers 1 and 2 rotate about one and the same axis 3, but in the opposite direction of rotation.
  • a first partial flow flows in the direction of the arrows 4 to the pump impeller 1, and a second partial flow flows in the direction of the arrows 5 to the second pump impeller 2.
  • the first partial flow emerges as a rotating medium disk 6 from the pump impeller 1, and the second partial flow likewise emerges as a rotating medium disk 7 from the pump impeller 2. Both media discs 6 and 7 rotate in opposite directions.
  • the two pump impellers 1 and 2 are expediently designed identically to one another and consequently, apart from the direction of rotation, have the same hydrodynamic characteristics.
  • the two oppositely rotating liquid disks 6 and 7 touch each other at point 8, the two opposite circumferential components of the two liquid disks meeting each other and canceling each other practically immediately.
  • the two liquid disks 6 and 7 have low radial speed components that determine the throughput of the pump impellers. Because of the sudden abolition of the mutually opposed tangential speed components, oscillating transverse movements of the liquid particles occur, which result in a very large amount of turbulence in the liquid region 9.
  • the two pump impellers 1 and 2 are shown somewhat more clearly.
  • the pump impeller 1 is supported by a hollow shaft 10, and the pump impeller 2 is seated on an inner shaft 11 which is surrounded by the hollow shaft 10.
  • the pump impeller 1 has a suction nozzle 12 for the partial flow 4
  • the pump impeller 2 has a suction nozzle 13 for the partial flow 5. Both pump impellers 1 and 2 rotate in opposite directions about the axis 3.
  • the two pump impellers 1 and 2 are driven by a single drive motor 14 for rotating in opposite directions.
  • the pump impeller 1 is seated on the hollow shaft 10 and the pump impeller 2 is carried by the inner shaft 11.
  • the drive motor 14 drives via a belt 15 on pinion 16 and 17.
  • the pinion 17 is rotatably connected to the inner shaft 11.
  • the pinion 16 is rotatably connected to a wheel 18 which meshes with a wheel 19 which is rotatably connected to the hollow shaft 10. In this way, the two shafts 10 and 11 are driven in opposite directions.
  • the two pump impellers 1 and 2 are driven in opposite directions by two drive motors 20 and 21.
  • the motor 20 drives directly on the inner shaft 11 on which the pump impeller 2 is seated, and the motor 21 drives via a belt 22 on a pulley 23 which is connected to the hollow shaft 10 in a rotationally fixed manner.
  • the two motors 20 and 21 have opposite directions of rotation.
  • the pump impeller 1 is seated on a shaft 24, and the pump impeller 2 is seated on a shaft 25.
  • the two coaxial drive shafts 24 and 25 of the two pump impellers 1 and 2 are thus on opposite sides of the pump impellers.
  • a motor 26 is used to drive the shaft 24 and thus the pump impeller 1
  • a motor 27 is used to drive the shaft 25 and thus the pump impeller 2.
  • An intake port 28 leads to the pump impeller 1 and an intake port 29 leads to the pump impeller 2 merged flow media flow away via a nozzle 30.
  • pump impellers 1 and 2 are designed as centrifugal impellers with forward curved blades, so that the peripheral component of the speed of the emerging medium disks 6 and 7 is very strong has been increased.
  • the circumferential component of the speed (tangential speed) of the two medium disks 6 and 7 can be set correspondingly large by appropriate speed of the pump impellers 1 and 2.

Landscapes

  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Mixers Of The Rotary Stirring Type (AREA)
  • Paper (AREA)

Abstract

The mixing apparatus has a plurality of pump impellers having one common axis and extending parallel to each other. Immediately adjacent pump impellers have opposite directions of rotation. The blading of the pump impellers is such that the currents of the mediums exiting the pump impellers have an as large as possible peripheral component. The medium currents exiting the adjacent pump impellers and having opposite senses of rotation are guided together and generate at the mutual point of contact an extremely high turbulence because the peripheral components of the exiting rotating currents of the mediums are directed oppositely to each other and eliminate each other practically immediately.

Description

Die Erfindung betrifft eine Vorrichtung zum Durchmischen von zumindest einem Strömungsmedium, wobei zumindest zwei Teilströme des Strömungsmediums zum Erzeugen einer sehr stark turbulenten Strömung zusammengeführt werden.The invention relates to a device for mixing at least one flow medium, wherein at least two partial flows of the flow medium are brought together to produce a very strongly turbulent flow.

Durch die US-A-3 147 957 ist eine solche Vorrichtung bekannt, die zumindest zwei zueinander parallel und koaxial zueinander liegende Pumpenlaufräder für die Teilströme aufweist, wobei benachbarte Pumpenlaufräder gegenläufig sind, wobei jedem Pumpenlaufrad einer der Teilströme zugeordnet ist. Bei dieser bekannten Vorrichtung findet das Durchmischen des oder der Strömungsmedien innerhalb der Vorrichtung statt. Beim Mischen in dieser bekannten Vorrichtung wird mit der mechanischen Scherwirkung auf das Medium eingewirkt. Man versieht die Laufräder mit Rillen oder Rippen und stellt die Laufräder aus Hartmetall (Karborundum) her, um möglichst grosse Scherwirkungen auf z.B. die zu mischenden Flüssigkeiten auszuüben. Die Wirkung einer solchen bekannten Vorrichtung mit zwei gegenläufigen Laufrädern ist hierbei so, dass durch die beiden entstehenden Mediumscheiben gegensätzlicher Drehrichtung lediglich die Relativgeschwindigkeit sich ändert. Die gleiche Wirkung kann man bei einer Vorrichtung mit nur einem Laufrad erzielen, wenn man das Laufrad mit doppelter Drehzahl rotieren lässt. Bei der bekannten Vorrichtung unterliegen die Laufräder erheblicher Abnutzung (Erosion, Korrosion, Kavitation) und haben trotz teurer Herstellung eine Standzeit, die man gern erhöhen würde.Such a device is known from US Pat. No. 3,147,957 which has at least two pump impellers for the partial flows which are parallel and coaxial to one another, adjacent pump impellers being opposed, each pump impeller being assigned one of the partial flows. In this known device, the mixing of the flow media or media takes place within the device. When mixing in this known device, the mechanical shear action acts on the medium. The impellers are provided with grooves or ribs and the impellers are made of hard metal (carborundum) in order to exert the greatest possible shear effects on, for example, the liquids to be mixed. The effect of such a known device with two counter-rotating impellers is such that only the relative speed due to the two medium disks of opposite direction of rotation changes. The same effect can be achieved with a device with only one impeller if the impeller is rotated at double speed. In the known device, the impellers are subject to considerable wear (erosion, corrosion, cavitation) and, despite expensive manufacture, have a service life that one would like to increase.

Es wird die Schaffung einer Vorrichtung bezweckt, mit der die vorerwähnten Nachteile vermieden werden können, damit in wirtschaftlicher Weise grosse Turbulenzen erzielt werden können.The aim is to create a device with which the aforementioned disadvantages can be avoided so that great turbulence can be achieved in an economical manner.

Die erfindungsgemässe Ausbildung der Vorrichtung ergibt sich aus dem kennzeichnenden Teil des Patentanspruches 1.The inventive design of the device results from the characterizing part of patent claim 1.

Es wird somit ein anderes Mischverfahren benutzt als bei der erwähnten bekannten Vorrichtung. Bei der erfindungsgemässen Vorrichtung können die Pumpenlaufräder viel billiger hergestellt werden, da sie nicht mehr den erwähnten Abnutzungen unterliegen. Es muss nicht mehr mit der Scherwirkung auf das oder die Medien eingewirkt werden, jedenfalls müssen keine besonderen Vorkehrungen getroffen werden, um dies zu erreichen. Die Pumpenlaufräder werden erfindungsgemäss mit vorwärts gekrümmten Laufschaufeln versehen, so dass sie hierdurch zu reinen Zentrifugalrädern werden, welche nur die Aufgabe haben, die mechanische Energie mit möglichst hohem Wirkungsgrad in hydraulische Energie umzuformen. Die Mischung der beiden Teilströme erfolgt erfindungsgemäss erst ausserhalb der Pumpenlaufräder dadurch, dass grosse Querströmungen (quer zu den beiden strömenden Mediumscheiben) und demzufolge grosse Turbulenzen in einem kleinen Ring ausserhalb der Vorrichtung entstehen. Diese vorerwähnten Querströmungen wirken als Turbulenzverstärker (siehe hierzu Lueger, Lexikon der Technik, vierte Auflage, Band 1 und 14, Seiten 587 und 589 bzw. Seiten 521, 522). Die vorerwähnten Querströmungen erfolgen bei den vorwärts gekrümmten Laufschaufeln der beiden Pumpenlaufräder mit einer Tangentialgeschwindigkeit, die für den möglichst guten Mischvorgang die wichtigste Geschwindigkeitskomponente ist. Die Radialgeschwindigkeit bestimmt, bei gegebener Geometrie, die Fördermenge jedes Pumpenlaufrades und ist für den Mischvorgang ohne Bedeutung, da die Radialkomponenten beider Pumpenlaufräder gleiche Richtung haben und demzufolge keinen Beitrag zur Turbulenzerhöhung leisten. Ganz anders sind die Verhältnisse bei den Tangentialgeschwindigkeiten beider Pumpenlaufräder, die entgegengerichtet sind. Durch das Gegeneinanderrichten von zwei Querströmungen mit der hohen Tangentialgeschwindigkeit wird der sehr hohe Mischungseffekt erzielt. Notwendig hierfür sind die beiden Pumpenlaufräder mit vorwärts gekrümmten Laufschaufeln und gegensätzlicher Drehrichtung. Bei der bekannten Vorrichtung der US-A-3 147 957 sind gerade Pumpenlaufschaufeln vorhanden und deshalb kann die Tangentialgeschwindigkeit des aus jedem Pumpenlaufrad austretenden Mediums nicht den gleichen hohen Wert haben (bei gegebener Drehzahl), da die Tangentialgeschwindigkeit des austretenden Mediums nur die gleiche Grösse hat wie die Umfangsgeschwindigkeit des Pumpenlaufrades. Demgegenüber treffen bei der erfindungsgemässen Vorrichtung die beiden Mediumscheiben mit ihren Tangentialgeschwindigkeiten ausserhalb der Vorrichtung aufeinander, so dass sich die grossen Querströmungen ausbilden, die eine sehr starke Turbulenz ergeben, die eine möglichst intensive Durchmischung des zumindest einem Strömungsmediums ergeben.A different mixing method is thus used than in the known device mentioned. In the device according to the invention, the pump impellers can be manufactured much cheaper since they are no longer subject to the abrasions mentioned. The shear effect on the media or media no longer has to be acted upon, in any case no special precautions have to be taken to achieve this. According to the invention, the pump impellers are provided with forward-curved blades, so that they thereby become pure centrifugal impellers, which only have the task of converting the mechanical energy into hydraulic energy with the highest possible efficiency. According to the invention, the two partial flows are only mixed outside the pump impellers in that large cross flows (transverse to the two flowing medium disks) and consequently large turbulences occur in a small ring outside the device. These aforementioned cross flows act as turbulence enhancers (see also Lueger, Lexicon der Technik, fourth edition, Vol. 1 and 14, pages 587 and 589 and Pages 521, 522). The above-mentioned cross flows take place in the forward curved blades of the two pump impellers at a tangential speed, which is the most important speed component for the best possible mixing process. The radial speed determines, for a given geometry, the delivery rate of each pump impeller and is irrelevant for the mixing process, since the radial components of both pump impellers have the same direction and therefore do not contribute to increasing the turbulence. The conditions for the tangential speeds of both pump impellers, which are opposite, are completely different. The very high mixing effect is achieved by counteracting two cross flows with the high tangential velocity. The two pump impellers with forward curved blades and opposite direction of rotation are necessary for this. In the known device of US-A-3 147 957 there are straight pump blades and therefore the tangential speed of the medium emerging from each pump impeller cannot have the same high value (at a given speed) since the tangential speed of the emerging medium is only of the same size like the peripheral speed of the pump impeller. In contrast, in the device according to the invention, the two medium disks meet at their tangential speeds outside the device, so that the large transverse flows form, which result in very strong turbulence, which result in the at least one flow medium being mixed as intensively as possible.

In der Zeichnung sind mehrer Ausführungsbeispiele des Erfindungsgegenstandes dargestellt. Es zeigen:

  • Fig. 1 zwei Pumpenlaufräder mit Auftreffpunkt und Flüssigkeitsgebiet mit grosser Turbulenz, in schematischer Darstellung,
  • Fig. 2 die zwei Pumpenräder in konstruktiver Ausführung mit Innenwelle und Hohlwelle,
  • Fig. 3 die Vorrichtung mit einem einzigen Antriebsmotor für die beiden Pumpenlaufräder, in schaubildlicher Darstellung,
  • Fig. 4 die Vorrichtung mit zwei Antriebsmotoren für die beiden Pumpenlaufräder, und
  • Fig. 5 eine weitere Ausführungsform der Vorrichtung mit zwei Antriebsmotoren, wobei die beiden Antriebswellen der beiden Laufräder auf voneinander abgewandten Seiten der Laufräder liegen.
Several exemplary embodiments of the subject matter of the invention are shown in the drawing. Show it:
  • 1 shows two pump impellers with impact point and liquid area with high turbulence, in a schematic representation,
  • 2 shows the two pump wheels in a design with an inner shaft and a hollow shaft,
  • 3 shows the device with a single drive motor for the two pump impellers, in a diagram,
  • Fig. 4 shows the device with two drive motors for the two pump impellers, and
  • Fig. 5 shows a further embodiment of the device with two drive motors, wherein the two drive shafts of the two impellers are on opposite sides of the impellers.

In Fig. 1 sind zwei Pumpenlaufräder 1 und 2 vorhanden, die parallel und koaxial zueinander liegen. Beide Pumpelaufräder 1 und 2 rotieren um ein und dieselbe Achse 3, aber in gegenläufiger Drehrichtung. Ein erster Teilstrom strömt in Richtung der Pfeile 4 dem Pumpenlaufrad 1 zu, und ein zweiter Teilstrom strömt in Richtung der Pfeile 5 dem zweiten Pumpenlaufrad 2 zu. Der erste Teilstrom tritt als drehende Mediumscheibe 6 aus dem Pumpenlaufrad 1 aus, und der zweite Teilstrom tritt ebenfalls als drehende Mediumscheibe 7 aus dem Pumpenlaufrad 2 aus. Beide Medienscheiben 6 und 7 rotieren gegenläufig. Die beiden Pumpenlaufräder 1 und 2 sind zweckmässig einander gleich ausgebildet und haben demzufolge, von der Drehrichtung abgesehen, die gleichen hydrodynamischen Charakteristiken. Die beiden entgegengesetzt drehenden Flüssigkeitsscheiben 6 und 7 berühren einander im Punkt 8, wobei die beiden einander entgegengerichteten Umfangskomponenten der beiden Flüssigkeitsscheiben aufeinander treffen und sich praktisch unverzüglich aufheben. Die beiden Flüssigkeitsscheiben 6 und 7 haben geringe radiale Geschwindigkeitskomponenten, die den Durchsatz der Pumpenlaufräder bestimmen. Wegen der plötzlichen Aufhebung der einander entgegengerichteten tangentialen Geschwindigkeitskomponenten entstehen schwingende Querbewegungen der Flüssigkeitsteilchen, die im Flüssigkeitsbereich 9 eine sehr grosse Turbulenz ergeben.In Fig. 1 there are two pump impellers 1 and 2 which are parallel and coaxial to each other. Both pump impellers 1 and 2 rotate about one and the same axis 3, but in the opposite direction of rotation. A first partial flow flows in the direction of the arrows 4 to the pump impeller 1, and a second partial flow flows in the direction of the arrows 5 to the second pump impeller 2. The first partial flow emerges as a rotating medium disk 6 from the pump impeller 1, and the second partial flow likewise emerges as a rotating medium disk 7 from the pump impeller 2. Both media discs 6 and 7 rotate in opposite directions. The two pump impellers 1 and 2 are expediently designed identically to one another and consequently, apart from the direction of rotation, have the same hydrodynamic characteristics. The two oppositely rotating liquid disks 6 and 7 touch each other at point 8, the two opposite circumferential components of the two liquid disks meeting each other and canceling each other practically immediately. The two liquid disks 6 and 7 have low radial speed components that determine the throughput of the pump impellers. Because of the sudden abolition of the mutually opposed tangential speed components, oscillating transverse movements of the liquid particles occur, which result in a very large amount of turbulence in the liquid region 9.

In Fig. 2 sind die beiden Pumpenlaufräder 1 und 2 etwas deutlicher dargestellt. Das Pumpenlaufrad 1 wird von einer Hohlwelle 10 getragen, und das Pumpenlaufrad 2 sitzt auf einer Innenwelle 11, die von der Hohlwelle 10 umgeben ist. Das Pumpenlaufrad 1 hat einen Saugstutzen 12 für den Teilstrom 4, und das Pumpenlaufrad 2 hat einen Saugstutzen 13 für den Teilstrom 5. Beide Pumpenlaufräder 1 und 2 rotieren gegenläufig um die Achse 3.2, the two pump impellers 1 and 2 are shown somewhat more clearly. The pump impeller 1 is supported by a hollow shaft 10, and the pump impeller 2 is seated on an inner shaft 11 which is surrounded by the hollow shaft 10. The pump impeller 1 has a suction nozzle 12 for the partial flow 4, and the pump impeller 2 has a suction nozzle 13 for the partial flow 5. Both pump impellers 1 and 2 rotate in opposite directions about the axis 3.

Beim Beispiel nach Fig. 3 werden die beiden Pumpenlaufräder 1 und 2 von einem einzigen Antriebsmotor 14 zum gegenläufigen Umlaufen angetrieben. Wie schon erwähnt, sitzt das Pumpenlaufrad 1 auf der Hohlwelle 10, und das Pumpenlaufrad 2 wird von der Innenwelle 11 getragen. Der Antriebsmotor 14 treibt über einen Riemen 15 auf Ritzel 16 und 17. Das Ritzel 17 ist mit der Innenwelle 11 drehfest verbunden. Das Ritzel 16 ist mit einem Rad 18 drehfest verbunden, das mit einem Rad 19 kämmt, das mit der Hohlwelle 10 drehfest verbunden ist. Auf diese Weise werden die beiden Wellen 10 und 11 gegenläufig angetrieben.In the example according to FIG. 3, the two pump impellers 1 and 2 are driven by a single drive motor 14 for rotating in opposite directions. As already mentioned, the pump impeller 1 is seated on the hollow shaft 10 and the pump impeller 2 is carried by the inner shaft 11. The drive motor 14 drives via a belt 15 on pinion 16 and 17. The pinion 17 is rotatably connected to the inner shaft 11. The pinion 16 is rotatably connected to a wheel 18 which meshes with a wheel 19 which is rotatably connected to the hollow shaft 10. In this way, the two shafts 10 and 11 are driven in opposite directions.

Beim Beispiel nach Fig. 4 werden die beiden Pumpenlaufräder 1 und 2 durch zwei Antriebsmotore 20 und 21 gegenläufig angetrieben. Der Motor 20 treibt direkt auf die Innenwelle 11, auf dem das Pumpenlaufrad 2 sitzt, und der Motor 21 treibt über einen Riemen 22 auf eine mit der Hohlwelle 10 drehfest verbundene Riemenscheibe 23. Die beiden Motore 20 und 21 haben gegenläufige Drehrichtungen.4, the two pump impellers 1 and 2 are driven in opposite directions by two drive motors 20 and 21. The motor 20 drives directly on the inner shaft 11 on which the pump impeller 2 is seated, and the motor 21 drives via a belt 22 on a pulley 23 which is connected to the hollow shaft 10 in a rotationally fixed manner. The two motors 20 and 21 have opposite directions of rotation.

Beim Beispiel der Vorrichtung nach Fig. 5 sitzt das Pumpenlaufrad 1 auf einer Welle 24, und das Pumpenlaufrad 2 sitzt auf einer Welle 25. Die beiden zueinander koaxialen Antriebswellen 24 und 25 der beiden Pumpenlaufräder 1 und 2 liegen somit auf voneinander abgewandten Seiten der Pumpenlaufräder. Zum Antrieb der Welle 24 und damit des Pumpenlaufrades 1 dient ein Motor 26, und zum Antrieb der Welle 25 und damit des Pumpenlaufrades 2 dient ein Motor 27. Zum Pumpenlaufrad 1 führt ein Ansaugstutzen 28, und zum Pumpenlaufrad 2 führt ein Ansaugstutzen 29. Die beiden zusammengeführten Strömungsmedien strömen über einen Stutzen 30 weg.In the example of the device according to FIG. 5, the pump impeller 1 is seated on a shaft 24, and the pump impeller 2 is seated on a shaft 25. The two coaxial drive shafts 24 and 25 of the two pump impellers 1 and 2 are thus on opposite sides of the pump impellers. A motor 26 is used to drive the shaft 24 and thus the pump impeller 1, and a motor 27 is used to drive the shaft 25 and thus the pump impeller 2. An intake port 28 leads to the pump impeller 1 and an intake port 29 leads to the pump impeller 2 merged flow media flow away via a nozzle 30.

Bei einem anderen nicht dargestellten Ausführungsbeispiel könnten auch mehr als zwei Pumpenlaufräder vorhanden sein, wobei immer benachbarte Pumpenlaufräder gegenläufig sind. Mit drei solchen Pumpenlaufrädern könnten dann drei Teilströme als abwechselnd in unterschiedliche Drehrichtung drehende Flüssigkeitsscheiben erzielt werden, die an einem Punkt zusammengeführt werden. Die Pumpenlaufräder 1 und 2 sind als Zentrifugalräder mit vorwärts gekrümmten Laufschaufeln ausgebildet, so daß die Umfangskomponente der Geschwindigkeit der austretenden Medium-scheiben 6 und 7 sehr stark gesteigert worden ist. Durch entsprechende Drehzahl der Pumpenlaufräder 1 und 2 kann die Umfangskomponente der Geschwindigkeit (Tangentialgeschwindigkeit) der beiden Mediumscheiben 6 und 7 entsprechend gross eingestellt werden.In another embodiment, not shown, there could also be more than two pump impellers, with adjacent pump impellers always being in opposite directions. With three such pump impellers, three partial flows could then be achieved as liquid disks rotating alternately in different directions of rotation, which are brought together at one point. The pump impellers 1 and 2 are designed as centrifugal impellers with forward curved blades, so that the peripheral component of the speed of the emerging medium disks 6 and 7 is very strong has been increased. The circumferential component of the speed (tangential speed) of the two medium disks 6 and 7 can be set correspondingly large by appropriate speed of the pump impellers 1 and 2.

Claims (2)

  1. Device for mixing at least one fluid, in which at least two partial currents (4, 5) of the fluid are brought together in order to generate a strongly turbulent current (9), comprising at least two parallel and coaxial pump impellers (1, 2) for the partial currents (4, 5), where neighbouring impellers rotate in opposite directions, each impeller being allocated to one partial current, characterized in that the impellers (1, 2) are centrifugal impellers with vanes that are curved forward so that the partial currents (4, 5) leaving the centrifugal impellers are shaped as rotary fluid disks (6, 7) in such a way that neighbouring fluid disks (6, 7) collide in a location (8) located outside the centrifugal impellers in order to generate a strongly turbulent current in a region (9) outside the centrifugal impellers.
  2. Device according to claim 1, characterized in that the capacity of flow and the peripheral speed of the rotary fluid disk (6, 7) expelled by neighbouring pump impellers (1, 2) are the same.
EP86103912A 1985-04-03 1986-03-21 Device for mixing at least one flow medium Expired - Lifetime EP0196575B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86103912T ATE70203T1 (en) 1985-04-03 1986-03-21 DEVICE FOR MIXING AT LEAST ONE FLOW MEDIUM.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1453/85A CH665959A5 (en) 1985-04-03 1985-04-03 DEVICE FOR MIXING AT LEAST ONE FLOW MEDIUM.
CH1453/85 1985-04-03

Publications (3)

Publication Number Publication Date
EP0196575A2 EP0196575A2 (en) 1986-10-08
EP0196575A3 EP0196575A3 (en) 1988-11-30
EP0196575B1 true EP0196575B1 (en) 1991-12-11

Family

ID=4210820

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86103912A Expired - Lifetime EP0196575B1 (en) 1985-04-03 1986-03-21 Device for mixing at least one flow medium

Country Status (6)

Country Link
US (1) US4786183A (en)
EP (1) EP0196575B1 (en)
JP (1) JPH0790160B2 (en)
AT (1) ATE70203T1 (en)
CH (1) CH665959A5 (en)
DE (1) DE3682799D1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6607783B1 (en) 2000-08-24 2003-08-19 Kimberly-Clark Worldwide, Inc. Method of applying a foam composition onto a tissue and tissue products formed therefrom

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20002920U1 (en) * 2000-02-18 2000-04-20 Schröder & Boos Misch- und Anlagentechnik GmbH & Co. KG, 27578 Bremerhaven Homogenizer
WO2015032008A1 (en) 2013-09-06 2015-03-12 Miteco Ag Device for mixing and/or homogenizing at least one liquid product
JP2015066503A (en) * 2013-09-30 2015-04-13 大日本印刷株式会社 Stirring apparatus and stirring method
KR101780329B1 (en) * 2015-05-06 2017-09-20 주식회사 케이엔에스컴퍼니 A system structure of impeller for dispersion-emulsion apparatus based on dual rotator

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR744390A (en) * 1933-04-19
GB1051539A (en) * 1900-01-01
GB205672A (en) * 1922-10-11 1923-10-25 Edgar Allison Burrows Improvements in the means for and method of mixing the ingredients used in the manufacture of soap, in a mixing pan
DE648783C (en) * 1934-09-02 1937-08-09 Johann Aebi Color mixing machine
FR950579A (en) * 1947-07-23 1949-09-30 Separation Sa Franc Pour La Improvements to processes, devices and installations involving spraying and atomization operations
CH341478A (en) * 1955-08-12 1959-10-15 Peter Prof Willems Kneading and mixing mechanism
US3147957A (en) * 1960-05-31 1964-09-08 W J Cooper Liquid mixing device
DE1454743B2 (en) * 1962-06-07 1970-05-14 Beck, Erich, 6520 Worms Process and device for compacting and agglomerating powdery to granular thermoplastic materials
FR1404962A (en) * 1963-08-22 1965-07-02 Dosing and mixing device for fluids
US3252690A (en) * 1964-06-15 1966-05-24 Warner J Cooper Liquid mixing device
JPS4836764A (en) * 1971-09-16 1973-05-30
US3942766A (en) * 1974-03-08 1976-03-09 Lage James R Process and arrangement for producing a strong turbulence in at least one fluid or quasi-fluid medium

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6607783B1 (en) 2000-08-24 2003-08-19 Kimberly-Clark Worldwide, Inc. Method of applying a foam composition onto a tissue and tissue products formed therefrom

Also Published As

Publication number Publication date
JPH0790160B2 (en) 1995-10-04
DE3682799D1 (en) 1992-01-23
CH665959A5 (en) 1988-06-30
JPS61230726A (en) 1986-10-15
EP0196575A2 (en) 1986-10-08
ATE70203T1 (en) 1991-12-15
US4786183A (en) 1988-11-22
EP0196575A3 (en) 1988-11-30

Similar Documents

Publication Publication Date Title
DE69914134T2 (en) Wheel
DE4006604C2 (en)
EP0290033B1 (en) Homogenising machine for the production of fluid products
DE2754901A1 (en) SEPARATING DEVICE
DE3342304C2 (en) Device for the production of emulsions
CH678352A5 (en)
EP0196575B1 (en) Device for mixing at least one flow medium
DE4208202A1 (en) CENTRIFUGAL PUMP
DE1453730A1 (en) Radial pump
DE821734C (en) Device for limiting the speed of gas turbines
DE1964308C3 (en) Device for gassing and circulating liquids
WO2000029721A1 (en) Turbo-machine, especially a turbo-generator comprising a turbo-machine and an electric machine
DE3922782A1 (en) Molecular pump in a unit design
DE1110810B (en) Counter-rotating compressor or pump
EP0947472A1 (en) Gyroscope-aerator
DE102015111291B4 (en) Turbo machine with paddle wheels rotating in opposite directions
EP0475015A1 (en) Method and apparatus for continuously grinding and dispersing solids in fluids
DE1213206B (en) Disk mill for grinding, dispersing, emulsifying, etc. like
DE19912314A1 (en) Feed pump
AT53197B (en) Device for diluting or compressing gases or vapors.
DE19608222A1 (en) Dispersing pump for producing emulsions and dispersions
DE3048436A1 (en) Wear-resistant centrifugal sludge pump - has freely rotatable assembly with pre-whirl blades at entry and deceleration blades at exit of bladed impeller
AT359433B (en) CENTRIFUGAL CLEANER FOR FLUESSIKEITES
DE68906484T2 (en) Blasting ring for mixers.
DE468499C (en) Turbine or centrifugal pump, the impeller of which has two sprockets of rotating blades

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE DE FR GB IT LU NL SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE DE FR GB IT LU NL SE

17P Request for examination filed

Effective date: 19890524

17Q First examination report despatched

Effective date: 19900111

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE DE FR GB IT LU NL SE

REF Corresponds to:

Ref document number: 70203

Country of ref document: AT

Date of ref document: 19911215

Kind code of ref document: T

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ITF It: translation for a ep patent filed
REF Corresponds to:

Ref document number: 3682799

Country of ref document: DE

Date of ref document: 19920123

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
EPTA Lu: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 86103912.1

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: GB

Payment date: 20050314

Year of fee payment: 20

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

Ref country code: SE

Payment date: 20050324

Year of fee payment: 20

Ref country code: IT

Payment date: 20050324

Year of fee payment: 20

Ref country code: DE

Payment date: 20050324

Year of fee payment: 20

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

Ref country code: LU

Payment date: 20050325

Year of fee payment: 20

Ref country code: FR

Payment date: 20050325

Year of fee payment: 20

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

Ref country code: AT

Payment date: 20050329

Year of fee payment: 20

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

Ref country code: NL

Payment date: 20050331

Year of fee payment: 20

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

Ref country code: BE

Payment date: 20050502

Year of fee payment: 20

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

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20060320

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

Ref country code: NL

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20060321

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

EUG Se: european patent has lapsed
NLV7 Nl: ceased due to reaching the maximum lifetime of a patent

Effective date: 20060321

BE20 Be: patent expired

Owner name: *CADEOANGELO

Effective date: 20060321

Owner name: *MITECO A.G.

Effective date: 20060321