EP0248104B1 - Rotary pump - Google Patents

Rotary pump Download PDF

Info

Publication number
EP0248104B1
EP0248104B1 EP86107893A EP86107893A EP0248104B1 EP 0248104 B1 EP0248104 B1 EP 0248104B1 EP 86107893 A EP86107893 A EP 86107893A EP 86107893 A EP86107893 A EP 86107893A EP 0248104 B1 EP0248104 B1 EP 0248104B1
Authority
EP
European Patent Office
Prior art keywords
sub
block
input
blocks
diameter
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
Application number
EP86107893A
Other languages
German (de)
French (fr)
Other versions
EP0248104A1 (en
Inventor
Stephen Medgyesy
Fernando Bermudez
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.)
Sulzer AG
Original Assignee
Gebrueder Sulzer 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 Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0248104A1 publication Critical patent/EP0248104A1/en
Application granted granted Critical
Publication of EP0248104B1 publication Critical patent/EP0248104B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • F04D1/066—Multi-stage pumps of the vertically split casing type the casing consisting of a plurality of annuli bolted together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/20—Mounting rotors on shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/912—Interchangeable parts to vary pumping capacity or size of pump

Definitions

  • the invention relates to a centrifugal pump with an inner block which can be inserted axially into a radially undivided (pot) housing and which contains two multi-stage partial blocks separated from one another by a central piece to form two independent partial pumps, the diameter of the drive-side partial block being smaller than the housing bore of the drive block away from the drive, and wherein the largest outer diameter of the drive-side pump bearing is smaller than the smallest diameter of the housing bore receiving the inner block.
  • a centrifugal pump of the type mentioned above is known from CH-A-637 185.
  • the inner block of the known construction which is inserted axially as a whole into the housing from one side, the two partial blocks are built up from the center towards the end . This means that the impellers can only be pushed and wedged onto the shaft, but cannot be shrunk on, since the back of the impeller on the non-drive part block, on which the hub area of the shrink fit is located, is no longer accessible for heating.
  • pumps of this type are to be used for high pressures - for example greater than 200 bar - and / or high speeds - for example greater than 300 rpm, shrinking of the impellers is practically an imperative for reasons of strength and rotor dynamics.
  • the object of the invention is to design the known construction so that the use of impellers shrunk onto the shaft is possible.
  • this object is achieved in that the impellers mounted from the side remote from the drive are shrunk onto the shaft, for which purpose the shaft diameter between the sub-blocks is reduced by a step-shaped shoulder for the sub-block remote from the drive, and the ring-shaped shrink fit areas of the impellers of this sub-block are on the latter Suction side are located, further characterized in that on the circumference of the last stage stator of the drive-side sub-block alternating with this sub-block holding axial tie bolts in recesses bolts and nuts are arranged, which fix the drive-side sub-block and the center piece separating the two sub-pumps relative to each other.
  • the inner block so that it can be assembled in one direction from the drive end.
  • the reduction of the shaft diameter for the sub-block away from the drive makes it possible to increase the radial thickness of the hub on the inlet side of the impellers present in this sub-block, without necessarily changing the hydraulic characteristics - such as the impeller diameter and the specific speed or edge shape index.
  • the radial reinforcement makes it possible to move the area of the shrink fit to the inlet side of the impeller, so that accessibility for heating the shrink area is ensured.
  • the reduction of the shaft diameter is made possible, in particular in advantageous embodiments of the invention, in which the two sub-blocks are hydraulically identical, in that the drive power to be transmitted from the shaft to the sub-pump remote from the drive is only half of the total power.
  • the two sub-pumps - apart from the speed - are independent of each other, they can be connected in series to increase the delivery head with the same delivery rate or parallel to each other to increase the delivery rate with the same delivery rate.
  • one of the sub-pumps as a turbine to drive the other sub-pump when there is a corresponding supply of pressurized water.
  • 1 is an axially undivided housing 1 of a pump, an inner block 2 with a left-handed sub-block 3 and a right-handed sub-block 4;
  • the impellers 7 and 8 of both sub-blocks 3 and 4 are shrunk onto the drive shaft 13, which is supported on both sides in bearings 14 and 15, respectively.
  • Both sub-blocks 3 and 4 form two separate sub-pumps I and 11, which are independent of one another apart from the common drive shaft 13. Each of the sub-blocks 3 and 4 is therefore assigned a separate suction or pressure port 5 or 6 on the housing 1.
  • the shrink fit area 9 of the impellers 7 is located on them Back.
  • the shaft 13 has a step-shaped shoulder 40, against which a throttle bush 41 bears.
  • the hubs of the impellers 8 on the inlet side can be made radially thicker than the inlet-side hubs of the impellers 7 in order to achieve the same diameter D 3 in sub-block 4, which is one of the characteristics for the hydraulic design of the two sub-pumps and II forms.
  • the hydraulic characteristic data should be the same for both sub-blocks 3 and 4 or sub-pumps I and 11 in the pump according to FIG. 1; therefore, the outer diameters Di of the impellers 7 and 8 and their widths are the same for both sub-blocks 3 and 4 with corresponding steps.
  • the radially thicker hub areas of the impellers 8 allow the shrink fit area 10 to be provided on their inlet side.
  • connection from the last stage stator 12a of the sub-block 3 to the center piece 23 is made by means of separate screw bolts 16 and nuts 17, which are arranged on the circumference of the stage stator 12a alternately with the tension bolts 20 in recesses 28 and 30 (FIG. 4), as later is described in more detail.
  • the drive-remote bearing 15 is supported by a cover 24 from the housing 1, which is held by a type of bayonet lock 25 and is sealed with the aid of a flange ring 29 (DE-C 34 10 931).
  • the bearing 14 is carried by the inlet housing 26, which is centered in a bore 27 in the housing 1 and at the same time forms the drive-side cover of the housing 1.
  • Only schematically indicated mechanical seals 37 of conventional construction are arranged between the shaft 13 and the cover 24 or 26.
  • the pump is powered by a prime mover, not shown, e.g. an electric motor, which is connected to the pump shaft 13 by means of a coupling 31.
  • a prime mover not shown, e.g. an electric motor, which is connected to the pump shaft 13 by means of a coupling 31.
  • the hydraulic characteristic data of the partial pumps and II are different from one another; therefore, the impellers 32 of the sub-pump 11 remote from the drive have a hub diameter D s different from the diameter D 3 . Likewise, their outer diameter D 2 and their widths have changed compared to those of the impellers 8 and 7, respectively.
  • the different hydraulic characteristic data are necessary because the pump according to FIG. 2 is designed so that after the first sub-pump I, the delivery rate should be divided and a further pressure increase should only take place for a partial amount.
  • a pressure port 34 is connected for withdrawing a part of the quantity conveyed by this sub-block 3 and, on the other hand, an inner flow path 35 running in the housing 1 for a further pressure increase of the other part of the Funding is available through an internal series connection of sub-pump II to sub-pump I.
  • the required division of the partial quantities into the two flow paths can take place with the aid of an adjustable or controllable throttle device in the pressure line to be connected to the pressure port 34, which is not expressly shown.
  • the recesses 28 and 30 are distributed on the circumference of the stator 12a of the last stage of the sub-block 3 at uniform angular intervals of ⁇ / 6. Screws 16 end in the recesses 28, which are screwed into the center piece 22 on the one hand and are connected to the step stator 12a by nuts 17 on the other hand.
  • the recesses 30 accommodate the drive-distant ends of the tension bolts 20, which hold the stator of the sub-block 3 together via nuts 18.
  • the assembly can take place, for example, in such a way that, after the sub-block 3 has been set up and fixed, the middle piece 22, into which the screw bolts 16 are already screwed, is inserted into bores 36 (FIG. 3) of the stepped guide wheel 12a of the sub-block 3 and from the periphery
  • the nuts 17 can be fixed. If the sub-block 3 and the middle piece 22 are firmly connected to one another, the step-by-step construction of the sub-block 4 can be carried out, with the impellers 8 and 32 being heated according to the invention in the shrink fit area 10 on their inlet side facing away from the drive.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Die Erfindung betrifft eine Kreiselpumpe mit einem in ein radial ungeteiltes (Topf-)Gehäuse axial einschiebbaren Innenblock, der zwei durch ein Mittelstück getrenntes gegeneinander gerichtete mehrstufige Teilblöcke zur Bildung von zwei unabhängigen Teilpumpen enthält, wobei der Durchmesser des antriebsseitigen Teilblockes kleiner ist als die Gehäusebohrung des antriebsfernen Teilblockes, und wobei weiterhin der grösste Aussendurchmesser des antriebsseitigen Pumpenlagers kleiner ist als der kleinste Durchmesser der den Innenblock aufnehmenden Gehäusebohrung.The invention relates to a centrifugal pump with an inner block which can be inserted axially into a radially undivided (pot) housing and which contains two multi-stage partial blocks separated from one another by a central piece to form two independent partial pumps, the diameter of the drive-side partial block being smaller than the housing bore of the drive block away from the drive, and wherein the largest outer diameter of the drive-side pump bearing is smaller than the smallest diameter of the housing bore receiving the inner block.

Eine Kreiselpumpe der vorstehend genannten Art ist bekannt aus der CH-A-637 185. Bei dem Innenblock der bekannten Konstruktion, der als Ganzes axial von einer Seite in das Gehäuse eingeschoben wird, werden die beiden Teilblöcke von der Mitte aus zu dem Ende hin aufgebaut. Dies bedingt, dass die Laufräder auf die Welle nur aufgeschoben und verkeilt, aber nicht aufgeschrumpft werden können, da beim antriebsfernen Teilblock die Lauf- radrückseite,auf der sich der Nabenbereich des Schrumpfsitzes befindet, nicht mehr für eine Erwärmung zugänglich ist.A centrifugal pump of the type mentioned above is known from CH-A-637 185. In the inner block of the known construction, which is inserted axially as a whole into the housing from one side, the two partial blocks are built up from the center towards the end . This means that the impellers can only be pushed and wedged onto the shaft, but cannot be shrunk on, since the back of the impeller on the non-drive part block, on which the hub area of the shrink fit is located, is no longer accessible for heating.

Sollen derartige Pumpen für hohe Drücke - beispielsweise grösser 200 bar - und/oder hohe Drehzahlen - beikspielsweise grösser 300 U/min - verwendet werden, so ist ein Aufschrumpfen der Laufräder aus Festigkeits- und rotordynamischen Gründen praktisch eine zwingende Notwendigkeit.If pumps of this type are to be used for high pressures - for example greater than 200 bar - and / or high speeds - for example greater than 300 rpm, shrinking of the impellers is practically an imperative for reasons of strength and rotor dynamics.

Aufgabe der Erfindung ist es, die bekannte Konstruktion so zu gestalten, dass die Verwendung von auf die Welle aufgeschrumpften Laufrädern möglich wird. Erfindungsgemäss wird diese Aufgabe dadurch gelöst, dass die von der antriebsfernen Seite her montierten Laufräder auf die Welle aufgeschrumpft sind, wofür der Wellendurchmesser zwischen den Teilblöcken durch einen stufenförmigen Absatz für den antriebsfernen Teilblock reduziert ist, und sich die ringförmigen Schrumpfsitzbereiche der Laufräder dieses Teilblockes auf deren Saugseite befinden, ferner dadurch, dass auf dem Umfang des letzten Stufenleitrades des antriebsseitigen Teilblockes alternierend mit diesen Teilblock zusammenhaltenden axialen Zugbolzen in Ausnehmungen Schraubenbolzen und Muttern angeordnet sind, die den antriebsseitigen Teilblock und das die beiden Teilpumpen trennendes Mittelstück relativ zueinander fixieren.The object of the invention is to design the known construction so that the use of impellers shrunk onto the shaft is possible. According to the invention, this object is achieved in that the impellers mounted from the side remote from the drive are shrunk onto the shaft, for which purpose the shaft diameter between the sub-blocks is reduced by a step-shaped shoulder for the sub-block remote from the drive, and the ring-shaped shrink fit areas of the impellers of this sub-block are on the latter Suction side are located, further characterized in that on the circumference of the last stage stator of the drive-side sub-block alternating with this sub-block holding axial tie bolts in recesses bolts and nuts are arranged, which fix the drive-side sub-block and the center piece separating the two sub-pumps relative to each other.

Auf diese Weise wird es möglich, den Innenblock so zu konstruieren, dass er vom antriebsseitigen Ende her in einer Richtung aufgebaut werden kann. Die Reduktion des Wellendurchmessers für den antriebsfernen Teilblock ermöglicht es, die radiale Dicke der einlaufseitigen Nabe der in diesem Teilblock vorhandenen Laufräder zu verstärken, ohne zwangsweise dadurch die hydraulischen Kenndaten - wie den Laufraddurchmesser und die spezifische Drehzahl bzw. Randform-Kennzahl - zu ändern. Durch die radiale Verstärkung ist es möglich, den Bereich des Schrumpfsitzes auf die Einlaufseite des Laufrades zu verlegen, so dass die Zugänglichkeit für die Aufheizung des Schrumpfbereiches gewährleistet ist.In this way, it becomes possible to construct the inner block so that it can be assembled in one direction from the drive end. The reduction of the shaft diameter for the sub-block away from the drive makes it possible to increase the radial thickness of the hub on the inlet side of the impellers present in this sub-block, without necessarily changing the hydraulic characteristics - such as the impeller diameter and the specific speed or edge shape index. The radial reinforcement makes it possible to move the area of the shrink fit to the inlet side of the impeller, so that accessibility for heating the shrink area is ensured.

Die Reduktion des Wellendurchmessers wird, besonders bei vorteilhaften Ausführungsformen der Erfindung, bei denen die beiden Teilblöcke hydraulisch gleich ausgebildet sind, dadurch ermöglicht, dass die von der Welle auf die antriebsferne Teilpumpe zu übertragende Antriebsleistung nur noch die Hälfte der Gesamtleistung beträgt.The reduction of the shaft diameter is made possible, in particular in advantageous embodiments of the invention, in which the two sub-blocks are hydraulically identical, in that the drive power to be transmitted from the shaft to the sub-pump remote from the drive is only half of the total power.

Weiterhin erfordert der Aufbau von einer Seite her, dass die Zugbolzen, die die Teilblöcke zusammenhalten, ebenfalls von der antriebsfernen Seite her "eingefädelt" werden; das dabei auftretende Problem der Verbindung des antriebsseitigen Teilblockes mit dem Mittelstück wird durch die in Ausnehmungen versenkten Schraubenbolzen zwischen dem Mittelstück und dem letzten Stufengehäuse des antriebsseitigen Teilblockes und den zugehörigen Muttern gelöst, die von dem äusseren Umfang des Blockes aus angezogen werden.Furthermore, the construction from one side requires that the tension bolts that hold the sub-blocks together are also "threaded" from the side remote from the drive; The problem of the connection of the drive-side sub-block to the center piece is solved by the recessed screw bolts between the center piece and the last stage housing of the drive-side sub-block and the associated nuts, which are tightened from the outer circumference of the block.

Da die beiden Teilpumpen - abgesehen von der Drehzahl - unabhängig voneinander sind, können sie in Serie zur Erhöhung der Förderhöhe bei gleichbleibender Fördermenge oder parallel zueinander zur Erhöhung der Fördermenge bei gleichbleibender Förderhöhe zusammengeschaltet werden. Es ist jedoch auch möglich, bei Vorhandensein eines entsprechenden Druckwasservorrats eine der Teilpumpen als Turbine zum Antrieb der anderen Teilpumpe zu nutzen.Since the two sub-pumps - apart from the speed - are independent of each other, they can be connected in series to increase the delivery head with the same delivery rate or parallel to each other to increase the delivery rate with the same delivery rate. However, it is also possible to use one of the sub-pumps as a turbine to drive the other sub-pump when there is a corresponding supply of pressurized water.

Da selbstverständlich für die beiden Teilpumpen unterschiedliche hydraulische Auslegungen möglich sind, kann man nach der ersten Teilpumpe die geförderte Menge teilen und eine Teilmenge einer Nutzung zuführen, während die andere in der zweiten Teilpumpe auf ein zweites höheres Druckniveau gebracht wird. Hierfür ist es konstruktiv einfach und platzsparend, wenn beide Teilblöcke mindestens für eine Teilmenge durch einen gehäuseinternen Strömungsweg in Serie miteinander verbunden sind, wofür an das Stufenleitrad der letzten Stufe des antriebsseitigen Teilblockes für den Abzug einer Teilmenge ein Druckstutzen angeschlossen sein kann, dessen Strömungsquerschnitt einstellbar ist.Since different hydraulic designs are of course possible for the two sub-pumps, one can divide the delivered quantity after the first sub-pump and use a sub-quantity while the other is brought to a second higher pressure level in the second sub-pump. For this purpose, it is structurally simple and space-saving if the two sub-blocks are connected to one another in series for at least a subset by a flow path inside the housing, for which purpose a pressure connection, the flow cross section of which can be adjusted, can be connected to the stage stator of the last stage of the drive-side sub-block for the subtraction of a subset .

Im folgenden wird die Erfindung anhand von Ausführungsbeispielen im Zusammenhang mit der Zeichnung näher eräutert.

  • Fig. 1 zeigt im Längsschnitt eine erste Ausführungsform der neuen Pumpe, bei der die beiden Teilpumpen hydraulisch gleich ausgelegt sind;
  • Fig. 2 ist in gleicher Darstellung - jedoch mit in Umfangsrichtung um einen Winkel id6 gegenüber
  • Fig. 1 versetzter Schnittebene - ein zweites Ausführungsbeispiel, bei dem die linke und die rechte Teilpumpe in ihren hydraulischen Auslegungen unterschiedlich sind, da in der zweiten Teilpumpe nur noch eine Teilmenge des die erste Teilpumpe durchsetzenden Fördermittels gefördert wird;
  • Fig. 3 ist ein vergrössertes Detail A aus Fig. 1; während
  • Fig. 4 den Schnitt IV-IV von Fig. 3 wiedergibt.
The invention is explained in more detail below on the basis of exemplary embodiments in conjunction with the drawing.
  • Fig. 1 shows in longitudinal section a first embodiment of the new pump, in which the two sub-pumps are designed hydraulically the same;
  • Fig. 2 is in the same representation - but with an angle id6 opposite in the circumferential direction
  • Fig. 1 offset sectional plane - a second embodiment in which the left and right sub-pumps are different in their hydraulic designs, since in the second sub-pump only a subset of the conveying means passing through the first sub-pump is delivered;
  • Fig. 3 is an enlarged detail A from Fig. 1; while
  • Fig. 4 shows the section IV-IV of Fig. 3.

Nach Fig. 1 befindet sich in einem axial ungeteilten Gehäuse 1 einer Pumpe ein Innenblock 2 mit einem linksläufigen Teilblock 3 und einem rechtsläufigen Teilblock 4; die Laufräder 7 bzw. 8 beider Teilblöcke 3 und 4 sind erfindungsgemäss auf die Antriebswelle 13 aufgeschrumpft, die beidseitig in Lagern 14 bzw. 15 gelagert ist.1 is an axially undivided housing 1 of a pump, an inner block 2 with a left-handed sub-block 3 and a right-handed sub-block 4; According to the invention, the impellers 7 and 8 of both sub-blocks 3 and 4 are shrunk onto the drive shaft 13, which is supported on both sides in bearings 14 and 15, respectively.

Beide Teilblöcke 3 und 4 bilden zwei getrennte, abgesehen von der gemeinsamen Antriebswelle 13 voneinander unabhängige Teilpumpen I bzw. 11. Jedem der Teilblöcke 3 und 4 ist daher am Gehäuse 1 ein eigener Saug- bzw. Druckstutzen 5 bzw. 6 zugeordnet.Both sub-blocks 3 and 4 form two separate sub-pumps I and 11, which are independent of one another apart from the common drive shaft 13. Each of the sub-blocks 3 and 4 is therefore assigned a separate suction or pressure port 5 or 6 on the housing 1.

Bei den Laufrädern 7 des linken antriebsseitigen Teilblockes 3, in dessen Bereich der Wellendurchmesser Ds, der gleichzeitig der Nabendurchmesser der Laufräder 7 ist, erfindungsgemäss grösser ist als derjenige D4 im antriebsfernen Teilblock 4, befindet sich der Schrumpfsitz-Bereich 9 der Laufräder 7 auf deren Rückseite. Zwischen den beiden Teilblöcken 3 und 4 hat die Welle 13 einen stufenförmigen Absatz 40, an dem eine Drosselbüchse 41 anliegt.In the case of the impellers 7 of the left drive-side sub-block 3, in the area of which the shaft diameter Ds, which is also the hub diameter of the impellers 7, is larger than that D 4 in the sub-block 4 remote from the drive, the shrink fit area 9 of the impellers 7 is located on them Back. Between the two sub-blocks 3 and 4, the shaft 13 has a step-shaped shoulder 40, against which a throttle bush 41 bears.

Aufgrund des geringeren Wellendurchmessers D4 im Teilblock 4 können die Naben der Laufräder 8 auf der Einlaufseite radial dicker ausgeführt werden als die einlaufseitigen Naben der Laufräder 7, um im Teilblock 4 den gleichen Durchmesser D3 zu erreichen, der eine der Kenndaten für die hydraulische Auslegung der beiden Teilpumpen und II bildet. Die hydraulischen Kenndaten sollen, wie bereits erwähnt, bei der Pumpe nach Fig. 1 für beide Teilblöcke 3 und 4 bzw. Teilpumpen I und 11 gleich sein; daher sind bei ihnen auch die Aussendurchmesser Di der Laufräder 7 und 8 und deren Breiten bei sich entsprechenden Stufen für beide Teilblöcke 3 und 4 gleich.Due to the smaller shaft diameter D 4 in sub-block 4, the hubs of the impellers 8 on the inlet side can be made radially thicker than the inlet-side hubs of the impellers 7 in order to achieve the same diameter D 3 in sub-block 4, which is one of the characteristics for the hydraulic design of the two sub-pumps and II forms. As already mentioned, the hydraulic characteristic data should be the same for both sub-blocks 3 and 4 or sub-pumps I and 11 in the pump according to FIG. 1; therefore, the outer diameters Di of the impellers 7 and 8 and their widths are the same for both sub-blocks 3 and 4 with corresponding steps.

Die radial dickeren Nabenbereiche der Laufräder 8 erlauben es, bei ihnen den Schrumpfsitz-Bereich 10 an ihrer Einlaufseite vorzusehen.The radially thicker hub areas of the impellers 8 allow the shrink fit area 10 to be provided on their inlet side.

Die Statorteile des Teilblockes 3,bestehend aus einem Einlaufgehäuse 26, Stufengehäusen 11 und Leitapparaten 12, sowie des Teilblockes 4, bestehend aus Stufengehäusen 11 und Leitapparaten 12 - wobei das Austrittsleitrad der letzten Stufe jedes Teilblockes 3 bzw. 4 mit 12a bezeichnet ist -,werden von Zugbolzen 20 bzw. 21 und Muttern 18 (Fig. 2) bzw. 19 zusammengehalten; sind sie darüberhinaus mit einem Mittelstück 22 verbunden, das in einer Bohrung 23 im Gehäuse 1 zentriert ist. Während die Zugbolzen 21 des antriebsfernen Teilblockes 4 einfach in ein entsprechendes Gewinde im Mittelstück 22 eingeschraubt werden, halten die Zugbolzen 20 - wegen der Forderung, dass der Innenblock 2 vollständig von der Antriebsseite her in einer Richtung aufbaubar sein soll - nur den Teilblock 3 in sich zusammen. Die Verbindung vom letzten Stufenleitrad 12a des Teilblockes 3 zum Mittelstück 23 erfolgt mittels separater Schraubenbolzen 16 und Muttern 17, die auf dem Umfang des Stufenleitrades 12a alternierend mit den Zugbolzen 20 in Ausnehmungen 28 bzw. 30 (Fig. 4) angeordnet sind, wie später noch ausführlicher beschrieben wird.The stator parts of sub-block 3, consisting of an inlet housing 26, stage housings 11 and guide devices 12, and of sub-block 4, consisting of stage housings 11 and guide devices 12 - the outlet guide wheel of the last stage of each sub-block 3 or 4 being designated 12a held together by tie bolts 20 and 21 and nuts 18 (Fig. 2) and 19; they are also connected to a center piece 22 which is centered in a bore 23 in the housing 1. While the draw bolts 21 of the sub-block 4 remote from the drive are simply screwed into a corresponding thread in the middle piece 22, the draw bolts 20 - because of the requirement that the inner block 2 should be able to be completely assembled in one direction from the drive side - hold only the sub-block 3 in itself together. The connection from the last stage stator 12a of the sub-block 3 to the center piece 23 is made by means of separate screw bolts 16 and nuts 17, which are arranged on the circumference of the stage stator 12a alternately with the tension bolts 20 in recesses 28 and 30 (FIG. 4), as later is described in more detail.

Das antriebsferne Lager 15 ist über einen Deckel 24 vom Gehäuse 1 getragen, der durch eine Art Bajonettverschluss 25 gehalten und mit Hilfe eines Flanschringes 29 abgedichtet ist (DE-C 34 10 931). Auf der anderen Seite wird das Lager 14 durch das Einlaufgehäuse 26 getragen, das in einer Bohrung 27 im Gehäuse 1 zentriert ist und gleichzeitig den antriebsseitigen Deckel des Gehäuses 1 bildet. Zwischen der Welle 13 und dem Deckel 24 bzw. 26 sind nur schematisch angedeutete mechanische Dichtungen 37 konventioneller Konstruktion angeordnet.The drive-remote bearing 15 is supported by a cover 24 from the housing 1, which is held by a type of bayonet lock 25 and is sealed with the aid of a flange ring 29 (DE-C 34 10 931). On the other hand, the bearing 14 is carried by the inlet housing 26, which is centered in a bore 27 in the housing 1 and at the same time forms the drive-side cover of the housing 1. Only schematically indicated mechanical seals 37 of conventional construction are arranged between the shaft 13 and the cover 24 or 26.

Die Pumpe wird von einer nicht gezeigten Antriebsmaschine, z.B. einem Elektromotor, angetrieben, die mittels einer Kupplung 31 mit der Pumpenwelle 13 verbunden ist.The pump is powered by a prime mover, not shown, e.g. an electric motor, which is connected to the pump shaft 13 by means of a coupling 31.

Bei dem Ausführungsbeispiel nach Fig. 2 sind die hydraulischen Kenndaten der Teilpumpen und II verschieden voneinander; daher haben die Laufräder 32 der antriebsfernen Teilpumpe 11 einen von dem Durchmesser D3 verschiedenen Nabendurchmesser Ds. Ebenso sind ihre Aussendurchmesser D2 und ihre Breiten gegenüber denjenigen der Laufräder 8 bzw. 7 verändert. Die unterschiedlichen hydraulischen Kenndaten (Laufradnaben- und -Aussendurchmesser, Radform-Kennzahl) sind erforderlich, weil die Pumpe nach Fig. 2 so ausgelegt ist, dass nach der ersten Teilpumpe I eine Aufteilung der Fördermenge und eine weitere Druckerhöhung nur für eine Teilmenge erfolgen sollen. An den Ringraum 33 des letzten Stufenleitrades 12a des Teilblockes 3 ist daher zum einen ein Druckstutzen 34 für den Abzug eines Teiles der von diesem Teilblock 3 geförderten Menge angeschlossen und zum anderen ein im Gehäuse 1 verlaufender innerer Strömungsweg 35 für eine weitere Druckerhöhung der anderen Teilmenge des Fördermittels durch eine interne Serienschaltung der Teilpumpe II zur Teilpumpe I vorhanden. Die geforderte Aufteilung der Teilmengen auf die beiden Strömungswege kann mit Hilfe einer einstellbaren oder regelbaren Drosseleinrichtung in der an den Druckstutzen 34 anzuschliessenden Druckleitung erfolgen, was nicht ausdrücklich gezeigt ist.In the exemplary embodiment according to FIG. 2, the hydraulic characteristic data of the partial pumps and II are different from one another; therefore, the impellers 32 of the sub-pump 11 remote from the drive have a hub diameter D s different from the diameter D 3 . Likewise, their outer diameter D 2 and their widths have changed compared to those of the impellers 8 and 7, respectively. The different hydraulic characteristic data (impeller hub and outer diameter, wheel shape characteristic number) are necessary because the pump according to FIG. 2 is designed so that after the first sub-pump I, the delivery rate should be divided and a further pressure increase should only take place for a partial amount. To the annular space 33 of the last stage stator 12a of the sub-block 3, therefore, on the one hand, a pressure port 34 is connected for withdrawing a part of the quantity conveyed by this sub-block 3 and, on the other hand, an inner flow path 35 running in the housing 1 for a further pressure increase of the other part of the Funding is available through an internal series connection of sub-pump II to sub-pump I. The required division of the partial quantities into the two flow paths can take place with the aid of an adjustable or controllable throttle device in the pressure line to be connected to the pressure port 34, which is not expressly shown.

Wie Fig. 3 und 4 erkennen lassen, sind auf dem Umfang des Leitrades 12a der letzten Stufe des Teilblockes 3 in gleichmässigen Winkelabständen von π/6 die Ausnehmungen 28 und 30 verteilt. In den Ausnehmungen 28 enden Schraubenbolzen 16, die zum einen in das Mittelstück 22 eingeschraubt sind und zum anderen durch Muttern 17 mit dem Stufenleitrad 12a verbunden sind. Die Ausnehmungen 30 nehmen die antriebsfernen Enden der Zugbolzen 20 auf, die über Muttern 18 den Stator des Teilblockes 3 zusammenhalten.3 and 4, the recesses 28 and 30 are distributed on the circumference of the stator 12a of the last stage of the sub-block 3 at uniform angular intervals of π / 6. Screws 16 end in the recesses 28, which are screwed into the center piece 22 on the one hand and are connected to the step stator 12a by nuts 17 on the other hand. The recesses 30 accommodate the drive-distant ends of the tension bolts 20, which hold the stator of the sub-block 3 together via nuts 18.

Die Montage kann dabei beispielsweise so erfolgen, dass nach Aufbau und Fixierung des Teilblockes 3 das Mittelstück 22, in das die Schraubenbolzen 16 bereits eingeschraubt sind, in Bohrungen 36 (Fig. 3) des Stufenleitrades 12a des Teilblockes 3 eingeführt und von der Peripherie her mit Hilfe der Muttern 17 fixiert werden. Sind der Teilblock 3 und das Mittelstück 22 fest miteinander verbunden, so kann der schrittweise Aufbau des Teilblockes 4 durchgeführt werden, wobei erfindungsgemäss die Laufräder 8 bzw. 32 im Schrumpfsitz-Bereich 10 an ihrer antriebsabgewandten Einlaufseite erwärmt werden.The assembly can take place, for example, in such a way that, after the sub-block 3 has been set up and fixed, the middle piece 22, into which the screw bolts 16 are already screwed, is inserted into bores 36 (FIG. 3) of the stepped guide wheel 12a of the sub-block 3 and from the periphery The nuts 17 can be fixed. If the sub-block 3 and the middle piece 22 are firmly connected to one another, the step-by-step construction of the sub-block 4 can be carried out, with the impellers 8 and 32 being heated according to the invention in the shrink fit area 10 on their inlet side facing away from the drive.

Claims (5)

1. A centrifugal pump having an inner block which is introducible axially into a radially undivided (dished) casing and which has two multistage sub-blocks separated by a central member and directed towards one another and adapted to form two independent sub-pumps, the diameter of the sub-block on the input side being less than the casing bore of the sub-block remote from the input, the largest outside diameter of the pump bearing on the input side being smaller than the smallest diameter of the casing bore which receives the inner block, characterized in that the rotors (7, 8; 32), which are fitted from the side remote from the input or drive, are shrunk on to the shaft (13), to which end the shaft diameter (Ds) between the sub-blocks (3 and 4) is reduced (D4) by a step-like shoulder (40) for the sub-block (4) remote from the input; and the annular shrink fit zones (10) of the rotors (8, 32) of the last-mentioned sub-block (4) are disposed on the intake side thereof, also characterized in that screw- threaded pins (16) and nuts (17) are disposed, in alternation with axial anchor bolts (20) which hold the sub-block (3) together, on the periphery of the final stepped diffuser (12a) of the last-mentioned sub-block (3) in recesses (28) and secure relatively to one another the input-side sub-block (3) and the central member (22) which separates the two sub-pumps (I, II).
2. A pump according to claim 1, characterized in that the outside and hub diameters (Di, Ds) of the rotors (7, 8) and the specific speed (rotor shape coefficients) (ng) of the two sub-blocks (3, 4) are the same.
3. A pump according to claim 1, characterized in that the two sub-blocks (3, 4) are interconnected in series at least for a component quantity by a flow path (35) disposed inside the casing.
4. A pump according to claim 3, characterized in that a port (34) of adjustable flow cross-section is connected to the stepped diffuser (12a) of the last stage of the input-side sub-block (3) for the removal of a component quantity.
5. A pump according to claim 1, characterized in that the outside and/or hub diameter (Di, D2; D3, Ds) of the rotors (7, 32) and/or the specific speeds (rotor shape coefficients) (ng) in the two sub-blocks (3, 4) are different.
EP86107893A 1986-04-30 1986-06-10 Rotary pump Expired EP0248104B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1779/86 1986-04-30
CH1779/86A CH669979A5 (en) 1986-04-30 1986-04-30

Publications (2)

Publication Number Publication Date
EP0248104A1 EP0248104A1 (en) 1987-12-09
EP0248104B1 true EP0248104B1 (en) 1989-12-13

Family

ID=4218416

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86107893A Expired EP0248104B1 (en) 1986-04-30 1986-06-10 Rotary pump

Country Status (4)

Country Link
US (1) US4778334A (en)
EP (1) EP0248104B1 (en)
CH (1) CH669979A5 (en)
DE (1) DE3667525D1 (en)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4031936A1 (en) * 1990-10-09 1992-04-16 Klein Schanzlin & Becker Ag CONTROL DEVICE
DE4232020A1 (en) * 1992-09-24 1994-03-31 Sihi Gmbh & Co Kg Centrifugal machine, in particular centrifugal pump, in link housing design
DE4310467A1 (en) * 1993-03-31 1994-10-06 Klein Schanzlin & Becker Ag Pot housing pump
US5456577A (en) * 1994-07-28 1995-10-10 Ingersoll-Dresser Pump Company Centrifugal pump with resiliently biasing diffuser
GB0117941D0 (en) * 2001-07-24 2001-09-19 Weir Pumps Ltd Pump assembly
DE50301139D1 (en) 2002-11-12 2005-10-13 Sulzer Pumpen Ag Winterthur High-pressure centrifugal pump in a pot housing with a pressure cover
EP1420166B1 (en) * 2002-11-12 2005-09-07 Sulzer Pumpen Ag High pressure centrifugal pump housing with pressure cover
ITMI20032149A1 (en) * 2003-11-07 2005-05-08 Nuovo Pignone Spa MULTI-STAGE CENTRIFUGAL COMPRESSOR WITH HORIZONTALLY OPENABLE CASE
EP1799101A4 (en) * 2004-09-02 2008-11-19 Proteus Biomedical Inc Methods and apparatus for tissue activation and monitoring
US7871243B2 (en) * 2007-06-05 2011-01-18 Honeywell International Inc. Augmented vaneless diffuser containment
TW201031467A (en) * 2009-02-19 2010-09-01 Galemed Corp Mist sprayer
US8267645B2 (en) * 2009-07-31 2012-09-18 Baker Hughes Incorporated Shaftless centrifugal pump
JP5260577B2 (en) * 2010-02-24 2013-08-14 三菱重工業株式会社 Double casing pump and method for adjusting performance of double casing pump
RU2459117C1 (en) * 2011-02-04 2012-08-20 Общество С Ограниченной Ответственностью Научно-Производственное Предприятие "Насостехкомплект" Block-modular centrifugal pump
EP2719900B1 (en) * 2012-10-09 2020-07-15 Sulzer Management AG Pump
EP2759710A1 (en) * 2013-01-23 2014-07-30 Sulzer Pumpen AG A centrifugal pump and a sleeve for coupling the shaft of a centrifugal pump to a shaft of a drive motor
US9593694B2 (en) 2014-04-04 2017-03-14 Sulzer Management Ag Pump
DE102014218936A1 (en) * 2014-09-19 2016-03-24 Siemens Aktiengesellschaft Radial turbofan energy machine, method of assembly
US10718346B2 (en) * 2015-12-21 2020-07-21 General Electric Company Apparatus for pressurizing a fluid within a turbomachine and method of operating the same
CN106089795A (en) * 2016-06-20 2016-11-09 江苏大学 A kind of three operating mode even running centrifugal pump structure and methods for designing thereof
CN106402036B (en) * 2016-12-06 2019-01-25 江苏海天科技有限公司 A kind of horizontal bivalve radial direction subdivision is arranged symmetrically cartridge type centrifugal multistage pump multiple centrifugal pump
CN112392730A (en) * 2020-01-22 2021-02-23 陈科 Chemical pump with shaft-split middle-opening conveniently-disassembled structure
RU203322U1 (en) * 2020-11-30 2021-03-31 Акционерное общество "ГМС Ливгидромаш" Centrifugal double-casing multistage pump with opposite arrangement of groups of impellers

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118386A (en) * 1964-01-21 Multi-stage centrifugal pump
US2248312A (en) * 1938-10-03 1941-07-08 Byron Jackson Co Double casing pump
US2265834A (en) * 1939-12-21 1941-12-09 Standard Oil Dev Co Pump lubrication
US2859698A (en) * 1956-03-21 1958-11-11 United States Steel Corp Centrifugal pump
US3105632A (en) * 1960-03-14 1963-10-01 Dresser Ind High pressure centrifugal compressor
US3232235A (en) * 1963-10-25 1966-02-01 Laval Turbine Pump
US3861825A (en) * 1970-12-21 1975-01-21 Borg Warner Multistage pump and manufacturing method
IT946916B (en) * 1971-07-13 1973-05-21 Carrier Corp CENTRIFUGAL COMPRESSOR WITH TWO SECTIONS AND MULTIPLE STAGES
US3802795A (en) * 1972-04-19 1974-04-09 Worthington Cei Multi-stage centrifugal compressor
FR2295225A1 (en) * 1974-12-16 1976-07-16 Europ Turb Vapeur RELATED DISCS TURBINE SHAFT
CH637185A5 (en) * 1978-12-21 1983-07-15 Sulzer Ag Centrifugal pump
US4314396A (en) * 1979-03-05 1982-02-09 Sybron Corporation Separable blade agitator assembly and disassembly method
US4277223A (en) * 1979-11-29 1981-07-07 Guy F. Atkinson Company Case construction for multi-stage pump
JPS5870097A (en) * 1981-10-23 1983-04-26 Hitachi Ltd Horizontally split type casing
JPH0417762Y2 (en) * 1985-06-19 1992-04-21

Also Published As

Publication number Publication date
EP0248104A1 (en) 1987-12-09
DE3667525D1 (en) 1990-01-18
CH669979A5 (en) 1989-04-28
US4778334A (en) 1988-10-18

Similar Documents

Publication Publication Date Title
EP0248104B1 (en) Rotary pump
EP0170175B1 (en) Regenerative pump with force balancing
DE4234739C1 (en) Gearbox multi-shaft turbo compressor with feedback stages
EP0853726B1 (en) Twin pump with a charging pump
EP1181453A1 (en) Motor-pump unit
EP0618369B1 (en) Barrel-type pump
CH677009A5 (en)
DE2158518C3 (en) Horizontal multistage centrifugal pump
EP0070529A1 (en) Regenerative pump
EP0118027B1 (en) Self-priming lateral channel pump
DE3526517C2 (en)
EP1536139B1 (en) Pump unit with a gear pump and an electric motor
DE3628177C2 (en) Inlet housing for turbo machines with radial inflow
DE1528717B2 (en) DEVICE FOR COMPENSATING THE AXIAL THRUST IN MULTI-STAGE CENTRIFUGAL PUMPS
DE4110392A1 (en) Rotary vane pump for vehicle steering - has compact double rotor with double vanes mounted on drive shaft
EP0461131A1 (en) Device for relieving axial thrusts.
DE10214135B4 (en) Rotary piston pump
DE2857227A1 (en) LIQUID RING PUMP
DE4005923A1 (en) Multistage centrifugal pump aggregate - has combination of booster and main pump for offshore work
DE639105C (en) Multi-stage centrifugal pump with radial gap sealing surfaces
EP2205850A1 (en) Fuel pump for delivering fuel from a reservoir to an internal combustion engine
EP0511517B1 (en) Split guiding device
DE2618593A1 (en) Motor driven pump set with common rotor and impeller shaft - has bearing unit as subassembly easily removable through housing end cover
DE2337030A1 (en) UNIT OF ROTOR AND SHAFT FOR CENTRIFUGAL FAN
AT37998B (en) Device for balancing the axial pressure in centrifugal pumps and blowers.

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: A1

Designated state(s): DE FR GB NL

17P Request for examination filed

Effective date: 19880521

17Q First examination report despatched

Effective date: 19890414

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB NL

REF Corresponds to:

Ref document number: 3667525

Country of ref document: DE

Date of ref document: 19900118

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

Ref country code: GB

Payment date: 19970513

Year of fee payment: 12

Ref country code: FR

Payment date: 19970513

Year of fee payment: 12

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

Ref country code: NL

Payment date: 19970527

Year of fee payment: 12

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

Ref country code: DE

Payment date: 19970530

Year of fee payment: 12

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 NON-PAYMENT OF DUE FEES

Effective date: 19980610

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 NON-PAYMENT OF DUE FEES

Effective date: 19990101

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

Effective date: 19980610

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

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990226

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19990101

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

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990401

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST