EP1053402B1 - Roue mobile de pompe centrifuge, de structure radiale - Google Patents

Roue mobile de pompe centrifuge, de structure radiale Download PDF

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Publication number
EP1053402B1
EP1053402B1 EP98966841A EP98966841A EP1053402B1 EP 1053402 B1 EP1053402 B1 EP 1053402B1 EP 98966841 A EP98966841 A EP 98966841A EP 98966841 A EP98966841 A EP 98966841A EP 1053402 B1 EP1053402 B1 EP 1053402B1
Authority
EP
European Patent Office
Prior art keywords
radial
impeller
centrifugal pump
pump impeller
radial distance
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
EP98966841A
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German (de)
English (en)
Other versions
EP1053402A1 (fr
Inventor
Ralf Stahlkopf
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.)
GEA Tuchenhagen GmbH
Original Assignee
Tuchenhagen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE29801676U external-priority patent/DE29801676U1/de
Application filed by Tuchenhagen GmbH filed Critical Tuchenhagen GmbH
Publication of EP1053402A1 publication Critical patent/EP1053402A1/fr
Application granted granted Critical
Publication of EP1053402B1 publication Critical patent/EP1053402B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2216—Shape, geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2230/00—Manufacture
    • F05B2230/60—Assembly methods
    • F05B2230/601—Assembly methods using limited numbers of standard modules which can be adapted by machining

Definitions

  • the invention relates to a centrifugal pump impeller radial design, in which a straight Number of blades is provided, in which the individual blade channel between the blades bounding it either from a cover plate segment or from a back surface segment that alternates one another, is bordered, in which each vane channel is on its respective Cover or back surface segment opposite side of the Eintntts- is designed to be continuously open to the outlet area of the impeller, and in which the rear surface segments each have a passage opening that all start on an inner diameter, which is determined by one, in seen in the radial direction, extreme radial hub shape in the entrance area the blade channels, and which extend radially outward.
  • a centrifugal pump impeller of the generic type is known from DE-A-195 30 195 . It combines the properties of a so-called completely open and a closed impeller without taking on the disadvantages inherent in these impeller shapes.
  • the advantages and disadvantages of open and closed impellers are briefly outlined below.
  • Open impellers are solcne. where the top wall or the so-called Cover disc is missing and the blades alone with the hub wall or the so-called back surface are connected ([*]: Pfleiderer / Petermann, turbomachines, 4th edition, 1972, pages 175, 285 ff). Open wheels have that The advantage that the blade channels can be machined well if necessary (often ground or polished surfaces required) and the blade channels too Inspection purposes are visible.
  • Impellers with a cover plate have a better flow to be cleaned (they are CIP-cleanable, which means "cleaning on Place in the flow "), since an open channel inevitably becomes a smaller one has bordering surface and the existing with closed wheels Narrow wheel-side space on the suction side between the housing and the cover plate completely eliminated.
  • CIP-cleanable which means "cleaning on Place in the flow"
  • a blood pump for circulating blood is known from EP-A-0 599 138 , which also has all the features of a centrifugal pump of the generic type.
  • openings are shown in the hub-side impeller area, which, however, only grasp the rear surface segments there and each engage in one of the adjacent blades. Although this measure improves the entry conditions for the rear vane duct covered by cover plate segments, it does not create any more favorable conditions for reducing the axial forces.
  • centrifugal pump impeller in its outer area, no, about its circumference seen, has closed cover and rear surface, but only Cover plate and rear surface segments, it forms there in the built Condition in cooperation with the pump housing also no ring in closed wheel side space on the cover disk and rear surface, which would be problematic in terms of proper CIP cleaning.
  • the advantages of the proposed centrifugal pump impeller still go Beyond that of the well-known open wheel radial design, since here the Rear side wheel space still available and cleaning technology is problematic.
  • both the cover disk segments have the rear surface segments each have a passage opening, all of which are on begin with an inner diameter, which is determined by a radial one Seen in the direction, extreme radial hub shape in the entry area of the Blade channels, and which extend radially outwards.
  • the entrance area is through the cover plate segments limited bucket channels open.
  • the axial projection surfaces of the passage openings are all congruent executed. This creates complete congruence of the passage openings in addition, both in the hub-side impeller area and in the area of the remaining ones Cover and back surface segments complete congruence of all of the compressive forces effective areas. at least as far as it's a balance of forces acts in the axial direction, creating optimal conditions for the desired the greatest possible axial thrust compensation.
  • the proposed centrifugal pump impeller has optimized hydraulic properties on, it is manufacturing technology both as a cast and as a molded part (Sheet metal part) can be produced, and it has the necessary strength properties if it is configured in this way, as is provided for by a further embodiment. that the passage openings each next to their boundary through the outermost radial hub shape, which is a radial distance R2 from the axis of rotation of the impeller, by the contours of the two respective neighboring Blades and the other radially outside, from a circular boundary with a radial distance R1 from the axis of rotation of the impeller become.
  • the proposed Impeller can be started from a largest outer diameter Reduce in the radial direction until the top and back surface segments the individual blades only in the form of a narrow ring surface, which the strength conditional minimum requirements met, connects with each other.
  • the necessary strength of the impeller is ensured in that the outer radius R a of the impeller exceeds the radial distance R1 of the outside edge of the passage opening by a first radial distance ⁇ R F , which results from the necessary strength of the impeller.
  • the required range of variation of the head adjustment of an impeller nominal diameter is ensured by providing a second radial distance ⁇ R V in addition to the first radial distance ⁇ R F.
  • the outer radius R a of the impeller thus results from the radial distance R1 of the outer edge of the passage opening. the first radial distance ⁇ R F and the second radial distance ⁇ R V.
  • a further advantageous proposal is in the design point of the impeller the blade channel each dimensioned such that there is no one in it at any point absolute speed, the amount of which is a speed of 2 m / s significantly exceeds.
  • this is a gentle support of the respective fluid and, on the other hand, favorable suction behavior and thus a correspondingly high NPSH value is achieved.
  • a gentle one Funding is always desirable when the proposed centrifugal pump is used in the food and food sector. Good pumping speed is particularly required of it whenever it has hot liquids must promote. This is always the case, for example, when used as a detergent pump acts and detergent with a temperature of 80 ° C up to 90 ° C must still be sucked in.
  • the pumping speed and thus the NPSH value are influenced favorably if, as is also provided by another proposal, in the design point of the impeller on the one hand, the respective pressure edge of the blades is designed such that the flow leaves the pressure edge smoothly, and if on the other hand the respective Suction edge of the blades is designed such that the flow of the suction edge only with a flow that is worth mentioning the flow in the design point exceeds, flows smoothly.
  • the suction edge is at the design point the centrifugal pump works in part load mode, while the Pressure edge of the blade under these conditions a bumpless and therefore one experiences optimal outflow for the flow at the design point. It has found to be particularly advantageous in this context if the smooth flow against the suction edge is given at a flow rate that the Flow rate at the design point exceeds about twice.
  • the blade channel 5.1 is represented by a Cover plate segment 4.1
  • the vane duct 5.3 is partially closed by a cover plate segment 4.3
  • the vane duct 5.5 by a cover plate segment 4.5 on the upstream side of the centrifugal pump impeller 1 (cross-hatched areas).
  • the vane passage is 5.2 5.6 page on the side facing away by a rear surface segment 4.6 of the upstream side of the centrifugal pump impeller 1 each partially closed by a rear surface segment 4.2, the vane passage 5.4 through a rear surface segment 4.4 and the blade channel (left-handed hatched areas).
  • cover plate and rear surface segments 4.1, 4.3, 4.5 and 4.2, 4.4, 4.6. the, viewed in the circumferential direction, in succession in the respective alternation, no blade edge can be formed, the front and back of the blade in question - and thus two adjacent blade channels - each connect with each other by a short path. This effectively prevents gap flows and efficiency-reducing effects due to a pressure difference between the front and back of the blade.
  • the cover plate segments 4.1, 4.3 and 4.5 and the rear surface segments 4.2, 4.4 and 4.6 each have a passage opening 4.1a, 4.3a, 4.5a or 4.2a, 4.4a, 4.6a , all of which start on an inner diameter with radius R2 , the is determined by an outermost radial hub shape 2a , seen in the radial direction, in the inlet area of the blade channels 5.1 to 5.6 (hatched areas on the right), and which extend radially outward (see also FIG. 2 ).
  • the through openings 4.1a to 4.6a are characterized on the one hand by the contours of the two respective adjacent blades (for example the through opening 4.2a by the blades 3.2 and 3.3 ) and on the other , radially on the outside, by a circular one Bounded with a radial distance R1 from the axis of rotation of the impeller. ( Figures 1 and 2 ).
  • the illustrated configuration of the through openings 4.1a to 4.6a is selected such that the axial projection surfaces of these through openings are all congruent.
  • the radial extent of the top and rear surface segments 4.1 to 4.6 between the radial distance R1 and the outer radius R a of the impeller 1 can, if this is necessary as part of the adaptation of the impeller within the centrifugal pumps of a series, to be used to implement different impeller diameters .
  • a second radial distance ⁇ R v (preferably approx. 25 mm) is possible in the present case, for example, up to an outer radius that is larger than the radial one by a first radial distance ⁇ R F (preferably approx. 15 mm) Distance dimension is R1 .
  • the necessary strength requirements are met, which also include the avoidance of oscillations and vibrations of the blades.
  • the required range of variation of the head adjustment of an impeller nominal diameter can be sufficiently achieved.
  • the outermost radial hub shape 2a which extends radially so far outward, is provided in the inlet area of the vane channel 5.1 , 5.3 and 5.5 delimited by the respective cover disk segment 4.1, 4.3 and 4.5 . that it connects the rear surface segments 4.2, 4.4 and 4.6 of the vane channels 5.2 , 5.4 and 5.6 with one another over their entire area (see FIG . 1 ).
  • the hub 2 has a hub bore 2b and a driving groove 2c .
  • the impeller 1 is fixed via a shaft nut 10 to a recess of a pump shaft 6 , which is not described in more detail, the counter ring 9b being fixed between the recess and the impeller 1 . So that the fluid delivered by the impeller 1 does not reach the area between the shaft 6 and the hub 2 , there is a seal 11 between the impeller 1 and the counter ring 9b, a further seal 12 between the shaft nut 10 and the impeller 1 and a third seal 13 between the counter ring 9b and the shaft 6 provided.
  • the impeller 1 is bordered on its upstream side by a front pump housing 7 and on the opposite side by a rear pump housing 8 .
  • the front and rear pump housings 7 and 8 are in the area of the cover disk and rear surface segments 4.1; 4.3; 4.5; ... 4.n-1 and 4.2; 4.4; 4.6; ... 4.n equipped symmetrically and with the same projection surfaces , so that in cooperation with the likewise symmetrically and with respect to the rear surface and top surface segments equally formed impeller 1 of the above-described extensive compensation of axial forces is achieved.
  • the direction of rotation is identified by U ( FIG. 1 ); in this case the blades are curved backwards. wherein in the exemplary embodiment the respective blade is simply curved in itself.
  • the principle according to the invention is also readily applicable to purely radially oriented or forwardly curved blades.
  • the three blading shapes can in turn each have spatially curved, that is to say three-dimensional, blades.
  • the selected embodiment also relates to a slow-running centrifugal pump impeller of radial design (so-called slow-speed); the proposed invention extends, however, without restriction to centrifugal pump impellers (so-called center rotors).

Claims (9)

  1. Roue mobile de pompe centrifuge, de structure radiale, dans laquelle est prévu un nombre pair n d'aubes (3.1 à 3.n), où le canal individuel d'aube (5.1 à 5.n) est entouré entre les aubes (3.1 ; 3.2 ; 3.3 ; ... ; 3n) respectives le limitant, soit par un segment de couverture de disque (4.1 ; 4.3 ; 4.5 ; ... : 4.n-1) soit par un segment de couverture de la face arrière (4.2 ; 4.4 ; 4.6 ; ... ; 4.n) se suivant successivement en alternance, chaque canal d'aube étant formé ouvert en continu, sur son côté opposé au segment respectif de couverture ou de couverture de la face arrière à partir de la zone d'entrée jusqu'à la zone de sortie de la roue mobile (1) et où les segments de couverture de la face arrière (4.2 ; 4.4 ; 4.6 ; ... ; 4.n) présentent chacun une ouverture de passage (4.2a ; 4.4a ; 4.6a ; ... ; 4.na) commençant toutes sur un diamètre intérieur qui, vu dans une direction radiale, est déterminé par la saillie radiale extrême de moyeu (2a) dans la zone d'entrée des canaux d'aube, et qui s'étendent toutes radialement vers l'extérieur,
    caractérisée en ce que les segments de couverture de disque (4.1 ; 4.3 ; 4.5 ; ... ; 4.n.-1) présentent chacun une ouverture de passage (4.1a ; 4.3a ; 4.5a ; ... ; 4.n-1a), commençant toutes sur un diamètre intérieur qui, vu dans une direction radiale, est déterminé par la saillie radiale extrême de moyeu (2a) dans la zone d'entrée des canaux d'aube (5.1 ; 5.3 ; 5.5 ; ... ; 5-n-1) et qui s'entendent radialement vers l'extérieur.
  2. Roue mobile de pompe centrifuge, de structure radiale selon la revendication 1, caractérisée en ce que la saillie radiale extrême (2a) relie les segments de couverture de la face arrière (4.2 ; 4.4 ; 4.6 : ... ; 4.n) des canaux d'aube (5.2 ; 5.4 ; 5.6 ; ... ; 5 ;n) d'une manière plane et sur toute leur étendue.
  3. Roue mobile de pompe centrifuge, de structure radiale selon l'une quelconque des revendications 1 à 2, caractérisée en ce que les surfaces axiales de projection des ouvertures de passage (4.1a à 4.na) sont toutes congrues.
  4. Roue mobile de pompe centrifuge, de structure radiale, selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les ouvertures de passage (4.1a à 4.na) présentent, outre leur bordure formée par la saillie radiale extrême de moyeu (2a) présentant un écart (R2) radial de l'axe de rotation de la roue mobile (1), sont entourées chacune par des contours des deux aubes avoisinantes respectives (3.i ; 3.i+1) et, radialement extérieurement, par une limitation en forme de cercle d'un écart radial (R1) de l'axe de rotation de la roue mobile (1).
  5. Roue mobile de pompe centrifuge, de structure radiale selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le rayon extérieur (Ra) de la roue mobile (1) dépasse l'écart radial (R1) de la bordure extérieure de l'ouverture de passage (4.1a à 4.na) d'un premier écart radial (ΔRf) qui résulte de la solidité nécessaire de la roue mobile (1), plus d'un deuxième écart radial (ΔRV), qui résulte de la plage de variation requise de l'ajustage du levage d'un diamètre nominal de roue.
  6. Roue mobile de pompe centrifuge, de structure radiale selon la revendication 5, caractérisée en ce que le premier écart radial (ΔRf) est prévu avec 10 < (ΔRf) < 20 mm, de préférence (ΔRf) = 15 mm et que le deuxième écart radial (ΔRV) avec 20 <(ΔRV) < 30 mm, de préférence (ΔRV) = 25 mm.
  7. Roue mobile de pompe centrifuge, de structure radiale selon l'une quelconque des revendications 1 à 6, caractérisée en ce que, au point de la capacité normale de la roue mobile (1), chaque canal d'aube (5.1 à 5.n) est dimensionné à ce qu'il ne présente en aucun point une vitesse absolue dont la somme dépasserait d'une manière significative une vitesse de 2 m/s.
  8. Roue mobile de pompe centrifuge, de structure radiale selon l'une quelconque des revendications 1 à 7, caractérisée en ce que, au point de la capacité normale de la roue mobile (1), d'un côté, l'arête respective de pression (D) des aubes (3.1 à 3.n) est conçue de manière à ce que le flux quitte l'arête de pression (D) sans heurts, et que, d'un autre côté, l'arête d'aspiration (S) respective des aubes (3.1 à 3.n) est conçue de manière à ce que, pour un flux de débit dépassant d'une manière significative le flux de débit au point de la capacité normale, le flux arrive sans heurts à l'arête d'aspiration (S).
  9. Roue mobile de pompe centrifuge, de structure radiale selon la revendication 8, caractérisée en ce que l'arrivée sans heurts du flux à l'arête d'aspiration (S) est assurée avec un flux de débit dépassant le flux de débit au point de la capacité normale par environ le double de sa valeur.
EP98966841A 1998-02-02 1998-12-21 Roue mobile de pompe centrifuge, de structure radiale Expired - Lifetime EP1053402B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE29801676U 1998-02-02
DE29801676U DE29801676U1 (de) 1998-02-02 1998-02-02 Kreiselpumpenlaufrad radialer Bauart
DE19825418 1998-06-06
DE19825418 1998-06-06
PCT/EP1998/008377 WO1999039105A1 (fr) 1998-02-02 1998-12-21 Roue mobile de pompe centrifuge, de structure radiale

Publications (2)

Publication Number Publication Date
EP1053402A1 EP1053402A1 (fr) 2000-11-22
EP1053402B1 true EP1053402B1 (fr) 2002-08-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98966841A Expired - Lifetime EP1053402B1 (fr) 1998-02-02 1998-12-21 Roue mobile de pompe centrifuge, de structure radiale

Country Status (6)

Country Link
EP (1) EP1053402B1 (fr)
JP (1) JP2002502008A (fr)
AU (1) AU2513699A (fr)
DE (1) DE59805263D1 (fr)
DK (1) DK1053402T3 (fr)
WO (1) WO1999039105A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6887046B2 (en) * 1996-02-26 2005-05-03 Flowork Systems Ii Llc Coolant pump, mainly for automotive use
ITPN20020012U1 (it) 2002-02-26 2003-08-26 Electrolux Home Products Corpo Pompa centrifuga con girante perfezionata
DE10314425B4 (de) * 2002-06-22 2005-06-16 Tuchenhagen Gmbh Leitvorrichtung für ein in Blechbauweise ausgeführtes Gehäuse einer Kreiselpumpe
RU2522134C1 (ru) * 2012-12-11 2014-07-10 Открытое акционерное общество "Ракетно-космическая корпорация "Энергия" имени С.П. Королева" Центробежное рабочее колесо
CN104632696A (zh) * 2015-01-19 2015-05-20 安徽舜禹水务实业有限公司 一种高效节能水泵叶片

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1867290A (en) * 1929-08-12 1932-07-12 Weil Pump Co Centrifugal pump
US3139034A (en) * 1961-06-17 1964-06-30 Amirault Maxime Impeller for centrifugal pump
AT398812B (de) * 1986-03-07 1995-02-27 Fischer Gerhard Zentrifugalpumpe
EP0599138A3 (fr) 1992-11-27 1994-12-07 Urawa Kohgyo Co Ltd Pompe de sang pour faire circuler le sang.
DE19530195A1 (de) 1995-08-17 1997-02-20 Tuchenhagen Otto Gmbh Kreiselpumpenlaufrad radialer Bauart

Also Published As

Publication number Publication date
WO1999039105A1 (fr) 1999-08-05
DE59805263D1 (de) 2002-09-26
EP1053402A1 (fr) 2000-11-22
JP2002502008A (ja) 2002-01-22
DK1053402T3 (da) 2002-12-23
AU2513699A (en) 1999-08-16

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