EP0341553A1 - Centrifugal pump - Google Patents

Centrifugal pump Download PDF

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Publication number
EP0341553A1
EP0341553A1 EP89107914A EP89107914A EP0341553A1 EP 0341553 A1 EP0341553 A1 EP 0341553A1 EP 89107914 A EP89107914 A EP 89107914A EP 89107914 A EP89107914 A EP 89107914A EP 0341553 A1 EP0341553 A1 EP 0341553A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
rotor
centrifugal pump
narrowing
extending
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.)
Withdrawn
Application number
EP89107914A
Other languages
German (de)
French (fr)
Inventor
Jean Poulain
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.)
Alstom Holdings SA
Original Assignee
Alstom SA
GEC Alsthom SA
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 Alstom SA, GEC Alsthom SA filed Critical Alstom SA
Publication of EP0341553A1 publication Critical patent/EP0341553A1/en
Withdrawn legal-status Critical Current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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a centrifugal pump.
  • the flow at the outlet of a centrifugal pump wheel is not a uniform flow.
  • the blades (or wings) are followed by a wake area, that is to say an area where the speeds are low and often close to zero. Between two wings there is a zone of healthy flow where the speed is high, without being completely uniform.
  • This speed configuration rotates at the speed of rotation of the wheel and is driven through the diffuser towards the volute.
  • n being the number of wings of the wheel
  • N the speed of rotation N
  • n.N the noise of well-defined frequency whose amplitude is large and often represents the most important signal read by a pressure fluctuation sensor brought into direct contact with the flow.
  • the object of the invention is to greatly reduce the amplitude of the line n.N which represents a specific signature which is often identifiable.
  • the invention thus relates to a centrifugal pump comprising a rotor provided with blades and a stator surrounding the rotor, comprising an axial inlet and extending the outlet, in the form of a radial circular crown, of the rotor by a fixed diffuser extending radially to the beyond the outlet of the rotor, said fixed diffuser extending by a volute, characterized in that said fixed diffuser comprises, on a part of its radial extension, an axial annular narrowing in the form of a bump whose angle makes its face downstream with the mean plane of the diffuser is between 35 ° and 90 °.
  • the angle made by the upstream face of said boss with the mean plane of the diffuser is understood between 30 and 90 °.
  • the principle of the invention consists in mixing the flow by remixing the zones at low speed (wakes) with zones at high speeds (healthy flow) so as to create a flow as uniform as possible, and also a flow having lost, as much as possible, its periodicity, and the phase concordance between the different threads.
  • the flow is stirred thanks to the hump, creating a voluntary but limited detachment which generates a high local turbulence, that is to say the penetration of turbulent nuclei, from one zone to the other. Tests have shown that the resulting yield loss is small and entirely acceptable.
  • the centrifugal pump shown, of axis 1, comprises a rotor 2 and a stator 3.
  • the rotor 2 is provided with blades 4.
  • the stator 3 delimits an axial axial inlet 5, envelops the rotor 3 and extends it at its outlet 6 which forms a radial circular crown, by a fixed diffuser 7 without blades. Beyond the diffuser 7 is a volute 8.
  • the axial dimension d of the diffuser corresponds to the axial dimension s of the outlet 6 of the wheel 2.
  • the fixed diffuser 7 comprises, over part of its radial extension, an annular axial narrowing.
  • This axial narrowing has, in the axial section as seen in the figure, the shape of a bump 9, and it is of course annular.
  • This annular narrowing is either coaxial with axis 1 of the pump, or eccentric.
  • This bump 9 is located only on one side of the diffuser.
  • the angle ⁇ made by the downstream face of the boss 9 with the mean plane of the diffuser is between 35 ° and 90 °. This angle should not be too small because it requires a sudden widening to obtain the detachment which occurs downstream of the bump and which ensures the remixing.
  • the angle ⁇ made by the upstream face of the boss 9 with the mean plane of the diffuser is advantageously between 30 and 90 °.
  • this narrowing 9 closes the axial dimension d of the diffuser 7 by 50%.
  • the rotor 2 is followed by a smooth diffuser 7 immediately followed by the volute 8.

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

Abstract

Centrifugal pump comprising a rotor (2) fitted with blades (4), and a stator (3) surrounding the rotor (2), comprising an axial inlet (5) and extending the outlet (6), in the form of a radial circular crown, of the rotor by a fixed diffuser (7) extending radially beyond the outlet of the rotor (2), the said fixed diffuser (7) extending by way of a spiral (8), characterised in that the said fixed diffuser (7) comprises, on part of its radial extension, an annular axial contraction (9) in the form of a boss, the angle between the downstream face of the latter and the centre plane of the diffuser being between 35 and 90 DEG . <IMAGE>

Description

La présente invention concerne une pompe centrifuge. L'écoulement à la sortie d'une roue de pompe centrifuge n'est pas un écoulement uniforme. Les pales (ou ailes) sont suivies d'une zone de sillage, c'est-à-dire une zone où les vitesses sont faibles et souvent proches de zéro. Entre deux ailes existe une zone d'écoulement sain où la vitesse est élevée, sans être tout à fait uniforme.The present invention relates to a centrifugal pump. The flow at the outlet of a centrifugal pump wheel is not a uniform flow. The blades (or wings) are followed by a wake area, that is to say an area where the speeds are low and often close to zero. Between two wings there is a zone of healthy flow where the speed is high, without being completely uniform.

Cette configuration de vitesse tourne à la vitesse de rotation de la roue et est entraînée à travers le diffuseur vers la volute. Lorsque cet écoulement de périodicité n (n étant le nombre d'ailes de la roue) et tournant à la vitesse de rotation N rencontre le bec de la volute, il génère un bruit dont la fréquence est égale à n.N. Il s'agit donc d'un bruit de fréquence bien définie dont l'amplitude est grande et représente souvent le signal le plus important lu par un capteur de fluctuations de pression mis en contact direct avec l'écoulement.This speed configuration rotates at the speed of rotation of the wheel and is driven through the diffuser towards the volute. When this flow of periodicity n (n being the number of wings of the wheel) and rotating at the speed of rotation N meets the beak of the volute, it generates a noise whose frequency is equal to n.N. It is therefore a noise of well-defined frequency whose amplitude is large and often represents the most important signal read by a pressure fluctuation sensor brought into direct contact with the flow.

Le but de l'invention est de diminuer fortement l'amplitude de la raie n.N qui représente une signature spécifique souvent identifiable.The object of the invention is to greatly reduce the amplitude of the line n.N which represents a specific signature which is often identifiable.

Il a été proposé dans le brevet français 855 124 de diminuer d'une manière générale le bruit d'une pompe centrifuge en réalisant un diffuseur dont la largeur axiale diminue sensiblement à partir de la périphérie intérieure sur une certaine distance dans le sens radial et augmente ensuite progressivement suivant une courbe divergente continue. Cette mesure a un effet insuffisant et en particulier ne permet pas d'atténuer suffisamment la raie n.N citée plus haut.It has been proposed in French patent 855,124 to generally reduce the noise of a centrifugal pump by producing a diffuser whose axial width decreases substantially from the inner periphery over a certain distance in the radial direction and increases then gradually following a continuous diverging curve. This measure has an insufficient effect and in particular does not make it possible to sufficiently attenuate the line n.N mentioned above.

L'invention a ainsi pour objet une pompe centrifuge comprenant un rotor muni de pales et un stator entourant le rotor, comprenant une entrée axiale et prolongeant la sortie, en forme de couronne circulaire radiale, du rotor par un diffuseur fixe s'étendant radialement au-delà de la sortie du rotor, ledit diffuseur fixe se prolongeant par une volute, caractérisée en ce que ledit diffuseur fixe comporte, sur une partie de son extension radiale, un rétrécissement axial annulaire en forme de bosse dont l'angle que fait sa face aval avec le plan moyen du diffuseur est compris entre 35° et 90°.The invention thus relates to a centrifugal pump comprising a rotor provided with blades and a stator surrounding the rotor, comprising an axial inlet and extending the outlet, in the form of a radial circular crown, of the rotor by a fixed diffuser extending radially to the beyond the outlet of the rotor, said fixed diffuser extending by a volute, characterized in that said fixed diffuser comprises, on a part of its radial extension, an axial annular narrowing in the form of a bump whose angle makes its face downstream with the mean plane of the diffuser is between 35 ° and 90 °.

Selon une autre caractéristique de l'invention, l'angle que fait la face amont de ladite bosse avec le plan moyen du diffuseur est compris entre 30 et 90°.According to another characteristic of the invention, the angle made by the upstream face of said boss with the mean plane of the diffuser is understood between 30 and 90 °.

Ainsi, le principe de l'invention consiste à réaliser un brassage de l'écoulement en remélangeant les zones à faible vitesse (sillages) avec des zones à vitesses élevées (écoulement sain) de façon à créer un écoulement aussi uniforme que possible, et également un écoulement ayant perdu, autant que possible, sa périodicité, et la concordance de phase entre les différents filets. Le brassage de l'écoulement est assuré grâce à la bosse en créant un décollement volontaire, mais limité qui génère une turbulence locale élevée, c'est-à-dire la pénétration de noyaux turbulents, d'une zone dans l'autre. Les essais ont montré que la perte de rendement qui s'en suit est faible et tout à fait acceptable.Thus, the principle of the invention consists in mixing the flow by remixing the zones at low speed (wakes) with zones at high speeds (healthy flow) so as to create a flow as uniform as possible, and also a flow having lost, as much as possible, its periodicity, and the phase concordance between the different threads. The flow is stirred thanks to the hump, creating a voluntary but limited detachment which generates a high local turbulence, that is to say the penetration of turbulent nuclei, from one zone to the other. Tests have shown that the resulting yield loss is small and entirely acceptable.

La décoordination des phases entre le filet intérieur et le filet extérieur est assurée par l'usage d'une bosse dissymétrique, c'est-à-dire placée sur une seule face du diffuseur. Le filet situé du côté de la bosse voit donc le chemin à parcourir allongé en même temps que sa vitesse est réduite, il prend donc un retard de phase par rapport au filet qui circule du côté où il n'y a pas de bosse. En d'autres termes, s'il reste des perturbations (non mélangées), elles n'arriveront pas en même temps sur le bec de volute et créeront des fluctuations de pression indépendantes décalées dans le temps et qui ne seront pas additives.The decoordination of the phases between the internal thread and the external thread is ensured by the use of an asymmetrical hump, that is to say placed on one side of the diffuser. The net located on the side of the hump therefore sees the path to be lengthened at the same time as its speed is reduced, it therefore takes a phase delay compared to the net which circulates on the side where there is no hump. In other words, if disturbances (unmixed) remain, they will not arrive at the same time on the volute nozzle and will create independent pressure fluctuations offset in time and which will not be additive.

On va maintenant donner la description d'un exemple particulier de mise en oeuvre de l'invention en se référant au dessin annexé qui comprend une figure unique montrant schématiquement une vue partielle en coupe axiale d'une pompe centrifuge selon l'invention.We will now give the description of a particular example of implementation of the invention with reference to the accompanying drawing which includes a single figure schematically showing a partial view in axial section of a centrifugal pump according to the invention.

La pompe centrifuge représentée, d'axe 1, comprend un rotor 2 et un stator 3. Le rotor 2 est muni de pales 4. Le stator 3 délimite une entrée axiale 5 circulaire, enveloppe le rotor 3 et le prolonge à sa sortie 6 qui forme une couronne circulaire radiale, par un diffuseur fixe 7 sans aubes. Au-delà du diffuseur 7 se trouve une volute 8.The centrifugal pump shown, of axis 1, comprises a rotor 2 and a stator 3. The rotor 2 is provided with blades 4. The stator 3 delimits an axial axial inlet 5, envelops the rotor 3 and extends it at its outlet 6 which forms a radial circular crown, by a fixed diffuser 7 without blades. Beyond the diffuser 7 is a volute 8.

Dans l'exemple particulier représente sur la figure, la dimension axiale d du diffuseur correspond à la dimension axiale s de la sortie 6 de la roue 2.In the particular example shown in the figure, the axial dimension d of the diffuser corresponds to the axial dimension s of the outlet 6 of the wheel 2.

Conformément à l'invention, le diffuseur fixe 7 comporte, sur une partie de son extension radiale, un rétrécissement axial annulaire. Ce rétrécissement axial présente, dans la section axiale telle que vue sur la figure, la forme d'une bosse 9, et elle est bien entendu annulaire. Ce rétrécissement annulaire est, soit coaxial à l'axe 1 de la pompe, soit excentré. Cette bosse 9 n'est située que sur un seul côté du diffuseur.According to the invention, the fixed diffuser 7 comprises, over part of its radial extension, an annular axial narrowing. This axial narrowing has, in the axial section as seen in the figure, the shape of a bump 9, and it is of course annular. This annular narrowing is either coaxial with axis 1 of the pump, or eccentric. This bump 9 is located only on one side of the diffuser.

L'angle α que fait la face aval de la bosse 9 avec le plan moyen du diffuseur est compris entre 35° et 90°. Cet angle ne doit pas être trop faible car il faut un élargissement brusque pour obtenir le décollement qui se produit en aval de la bosse et qui assure le remélange. L'angle β que fait la face amont de la bosse 9 avec le plan moyen du diffuseur est avantageusement compris entre 30 et 90°.The angle α made by the downstream face of the boss 9 with the mean plane of the diffuser is between 35 ° and 90 °. This angle should not be too small because it requires a sudden widening to obtain the detachment which occurs downstream of the bump and which ensures the remixing. The angle β made by the upstream face of the boss 9 with the mean plane of the diffuser is advantageously between 30 and 90 °.

Dans l'exemple particulier représenté, ce rétrécissement 9 obture la dimension axiale d du diffuseur 7 de 50 %.In the particular example shown, this narrowing 9 closes the axial dimension d of the diffuser 7 by 50%.

Une obstruction des deux tiers du canal produirait un meilleur remélange mais en revanche, la perte de rendement serait plus élevée. Inversement, l'efficacité diminue si la pénétration de la bosse dans le canal diminue. Une pénétration de 50 % comme représentée sur le dessin donne un bon résultat avec une faible perte de rendement. Enfin, il est souhaitable que la bosse soit située assez loin du bec de volute, en effet, le phénomène de remélange se situant en aval de la bosse, il faut laisser le temps à l'écoulement de s'homogénéiser et de se réorganiser. Il ne faut pas non plus disposer la bosse à proximité immédiate de la roue, en effet, étant donné l'importance de l'obstruction, on risquerait de réduire le débit dans la roue sur une partie de sa surface débitante extérieure et de modifier sensiblement les caractéristiques.An obstruction of two thirds of the canal would produce better mixing, but on the other hand, the loss of yield would be higher. Conversely, the efficiency decreases if the penetration of the hump in the canal decreases. A penetration of 50% as shown in the drawing gives a good result with a low loss of yield. Finally, it is desirable that the bump is located far enough from the volute beak, in fact, the remixing phenomenon being located downstream of the bump, it is necessary to allow time for the flow to homogenize and reorganize. The hump should also not be placed in the immediate vicinity of the wheel, in fact, given the importance of the obstruction, there would be a risk of reducing the flow in the wheel over part of its external flow surface and modifying appreciably characteristics.

Pour un diffuseur long comme celui représenté sur la figure, il est bon de placer la bosse environ au tiers de la distance roue volute en partant de la roue. Dans un diffuseur plus court, on peut être amené à la disposer à mi-distance de l'intervalle roue-volute. En fait la position de la bosse est à adapter cas par cas.For a long diffuser like the one shown in the figure, it is good to place the bump about a third of the distance from the volute wheel from the wheel. In a shorter diffuser, it may be necessary to arrange it halfway between the wheel-volute interval. In fact the position of the hump is to be adapted case by case.

Dans l'exemple représenté sur le dessin, le rotor 2 est suivi d'un diffuseur lisse 7 immédiatement suivi de la volute 8.In the example shown in the drawing, the rotor 2 is followed by a smooth diffuser 7 immediately followed by the volute 8.

On peut également, après le rétrécissement 9 et avant la volute 8, prévoir des ailettes de façon à constituer un diffuseur aileté.It is also possible, after the narrowing 9 and before the scroll 8, to provide fins so as to constitute a finned diffuser.

Claims (4)

1/ Pompe centrifuge comprenant un rotor (2) muni de pales (4), et un stator (3) entourant le rotor, comprenant une entrée axiale (5) et prolongeant la sortie (6), en forme de couronne circulaire radiale, du rotor par un diffuseur fixe (7) s'étendant radialement au-delà de la sortie du rotor, ledit diffuseur fixe se prolongeant par une volute (8), caractérisée en ce que ledit diffuseur fixe (7) comporte, sur une partie de son extension radiale, un rétrécissement axial (9) annulaire en forme de bosse dont l'angle que fait sa face aval avec le plan moyen du diffuseur est compris entre 35 et 90°.1 / Centrifugal pump comprising a rotor (2) provided with blades (4), and a stator (3) surrounding the rotor, comprising an axial inlet (5) and extending the outlet (6), in the form of a circular circular crown, of the rotor by a fixed diffuser (7) extending radially beyond the outlet of the rotor, said fixed diffuser extending by a volute (8), characterized in that said fixed diffuser (7) comprises, on a part of its radial extension, an axial narrowing (9) in the form of a bump, the angle of which its downstream face makes with the mean plane of the diffuser is between 35 and 90 °. 2/ Pompe centrifuge selon la revendication 1, caractérisée en ce que l'angle que fait la face amont de ladite bosse avec le plan moyen du diffuseur est compris entre 30° et 90°.2 / centrifugal pump according to claim 1, characterized in that the angle made by the upstream face of said boss with the mean plane of the diffuser is between 30 ° and 90 °. 3/ Pompe centrifuge selon l'une des revendications 1 ou 2, caractérisée en ce que ledit rétrécissement axial annulaire est excentré.3 / Centrifugal pump according to one of claims 1 or 2, characterized in that said annular axial narrowing is eccentric. 4/ Pompe centrifuge selon l'une des revendications précédentes, caractérisée en ce que le diffuseur (7) est muni d'ailettes au-delà dudit rétrécissement (9), entre ce rétrécissement et la volute (8).4 / Centrifugal pump according to one of the preceding claims, characterized in that the diffuser (7) is provided with fins beyond said narrowing (9), between this narrowing and the volute (8).
EP89107914A 1988-05-09 1989-05-02 Centrifugal pump Withdrawn EP0341553A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8806218 1988-05-09
FR8806218A FR2631084B1 (en) 1988-05-09 1988-05-09 CENTRIFUGAL PUMP

Publications (1)

Publication Number Publication Date
EP0341553A1 true EP0341553A1 (en) 1989-11-15

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Application Number Title Priority Date Filing Date
EP89107914A Withdrawn EP0341553A1 (en) 1988-05-09 1989-05-02 Centrifugal pump

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EP (1) EP0341553A1 (en)
FR (1) FR2631084B1 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992012349A1 (en) * 1991-01-14 1992-07-23 Opytnoe Konstruktorskoe Bjuro Mashinostroenia Centrifugal pump
US5419680A (en) * 1992-11-25 1995-05-30 Nippondenso Co., Ltd. Multi-blade blower
EP2107251A1 (en) * 2008-04-02 2009-10-07 Behr GmbH & Co. KG Fan housing
DE102010043727A1 (en) * 2010-11-10 2012-05-10 E.G.O. Elektro-Gerätebau GmbH pump
RU2493439C1 (en) * 2012-02-17 2013-09-20 Общество с ограниченной ответственностью Деловой центр "Галактика" Centrifugal pump
EP2628958A3 (en) * 2012-02-17 2014-01-08 E.G.O. ELEKTRO-GERÄTEBAU GmbH Diffuser for an impeller pump and impeller pump
GB2551804A (en) * 2016-06-30 2018-01-03 Cummins Ltd Diffuser for a centrifugal compressor
DE102017101590A1 (en) 2017-01-27 2018-08-02 Man Diesel & Turbo Se Centrifugal compressor and turbocharger
US11408439B2 (en) * 2017-03-28 2022-08-09 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1663998A (en) * 1925-05-28 1928-03-27 Westinghouse Electric & Mfg Co Means for minimizing fluid pulsations
FR649330A (en) * 1927-02-21 1928-12-20 Sulzer Ag Rotary machines applicable as fans, pumps or turbines
FR855124A (en) * 1939-05-22 1940-05-03 Improvements to blowers and centrifugal pumps with helical casing
GB554166A (en) * 1941-12-19 1943-06-23 Robert William Corbitt Improvements in or relating to centrifugal pumps and compressors
FR1486168A (en) * 1966-07-08 1967-06-23 Caterpillar Tractor Co Diffuser without vanes, more particularly of centrifugal compressor
JPS54104007A (en) * 1978-02-01 1979-08-15 Hitachi Ltd Diffuser for centrifugal compressor
US4315715A (en) * 1978-07-26 1982-02-16 Nissan Motor Company, Limited Diffuser for fluid impelling device

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1663998A (en) * 1925-05-28 1928-03-27 Westinghouse Electric & Mfg Co Means for minimizing fluid pulsations
FR649330A (en) * 1927-02-21 1928-12-20 Sulzer Ag Rotary machines applicable as fans, pumps or turbines
FR855124A (en) * 1939-05-22 1940-05-03 Improvements to blowers and centrifugal pumps with helical casing
GB554166A (en) * 1941-12-19 1943-06-23 Robert William Corbitt Improvements in or relating to centrifugal pumps and compressors
FR1486168A (en) * 1966-07-08 1967-06-23 Caterpillar Tractor Co Diffuser without vanes, more particularly of centrifugal compressor
JPS54104007A (en) * 1978-02-01 1979-08-15 Hitachi Ltd Diffuser for centrifugal compressor
US4315715A (en) * 1978-07-26 1982-02-16 Nissan Motor Company, Limited Diffuser for fluid impelling device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 3, no. 126 (M-77)(131) 20 octobre 1979, & JP-A-54 104007 (HITACHI SEISAKUSHO) *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992012349A1 (en) * 1991-01-14 1992-07-23 Opytnoe Konstruktorskoe Bjuro Mashinostroenia Centrifugal pump
US5419680A (en) * 1992-11-25 1995-05-30 Nippondenso Co., Ltd. Multi-blade blower
EP2107251A1 (en) * 2008-04-02 2009-10-07 Behr GmbH & Co. KG Fan housing
DE102010043727A1 (en) * 2010-11-10 2012-05-10 E.G.O. Elektro-Gerätebau GmbH pump
RU2493439C1 (en) * 2012-02-17 2013-09-20 Общество с ограниченной ответственностью Деловой центр "Галактика" Centrifugal pump
EP2628958A3 (en) * 2012-02-17 2014-01-08 E.G.O. ELEKTRO-GERÄTEBAU GmbH Diffuser for an impeller pump and impeller pump
US9388822B2 (en) 2012-02-17 2016-07-12 E.G.O. Elektro-Gerätebau GmbH Guide ring for an impeller pump and impeller pump
GB2551804A (en) * 2016-06-30 2018-01-03 Cummins Ltd Diffuser for a centrifugal compressor
GB2551804B (en) * 2016-06-30 2021-04-07 Cummins Ltd Diffuser for a centrifugal compressor
US11125235B2 (en) 2016-06-30 2021-09-21 Cummins Ltd. Centrifugal compressor with diffuser with throat
DE102017101590A1 (en) 2017-01-27 2018-08-02 Man Diesel & Turbo Se Centrifugal compressor and turbocharger
US11408439B2 (en) * 2017-03-28 2022-08-09 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger

Also Published As

Publication number Publication date
FR2631084B1 (en) 1994-03-11
FR2631084A1 (en) 1989-11-10

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