EP0203218B1 - Volute de pompe et revêtement pour la stabilisation de l'écoulement - Google Patents

Volute de pompe et revêtement pour la stabilisation de l'écoulement Download PDF

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Publication number
EP0203218B1
EP0203218B1 EP85106700A EP85106700A EP0203218B1 EP 0203218 B1 EP0203218 B1 EP 0203218B1 EP 85106700 A EP85106700 A EP 85106700A EP 85106700 A EP85106700 A EP 85106700A EP 0203218 B1 EP0203218 B1 EP 0203218B1
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EP
European Patent Office
Prior art keywords
volute
region
impeller
liner
pair
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
EP85106700A
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German (de)
English (en)
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EP0203218A1 (fr
Inventor
John Hyll
Harold Basmadjian
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.)
Baker Hughes Holdings LLC
Original Assignee
Baker Hughes Inc
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 Baker Hughes Inc filed Critical Baker Hughes Inc
Priority to DE8585106700T priority Critical patent/DE3572521D1/de
Priority to AT85106700T priority patent/ATE45787T1/de
Publication of EP0203218A1 publication Critical patent/EP0203218A1/fr
Application granted granted Critical
Publication of EP0203218B1 publication Critical patent/EP0203218B1/fr
Expired 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4286—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps inside lining, e.g. rubber
    • 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

Definitions

  • the invention relates to centrifugal pumps of the volute type, and more particularly to modified pump casings and/or removable volute liners for pumps designed for pumping slurries.
  • the section of the pump casing surrounding the periphery of the impeller is of changing cross-section.
  • the outer peripheral profile is made to approximate a volute shape having a radius of curvature increasing to a maximum at a point where it becomes tangential to a discharge nozzle.
  • the cross-sectional area of this volute section of the casing vary but the cross-sectional profile also varies around the periphery of the pump.
  • the normal volute type casing therefore has a complex shape.
  • Centrifugal pumps are often fitted with replaceable abrasion resistant liners, especially pumps for pumping slurries.
  • liners generally have contours which essentially correspond to the contours of the pump casings into which they will be inserted.
  • casing liners having uniquely contoured interior surfaces which may or may not correspond to the interior wall configuration of the pump casing.
  • the disclosure of Warman refers to obtaining gains in pump performance. by controlling the shapes of the hydraulic passages in the volute region.
  • Unstable flow through a pump is defined as an abrupt change in pressure or efficiency. A cyclic pattern of flow and pressure swings could trigger surging or vibration which is known to be damaging to both the pump and the system.
  • high specific speed pumps and fans are characterized by an inherently unstable flow at low flow rates. The mechanism causing the instability in these cases is thought to be due to flow streamlines stalling or separating at the impeller inlet vanes. This condition is acknowledged and generally accepted in the industry such that pump or fan operation in such unstable zones is generally avoided.
  • the unstable flow conditions can result from other mechanisms and/or parameters, such as "distorted", i.e., unusually wide (compared to the width of the impeller discharge opening) volute hydraulic passages.
  • Slurry pumps typically have very wide impellers dictated by low velocity designs so as to minimize wear and provide the required thick shrouds to allow space for expellers or allowances for sacrificial wear.
  • unstable flow has been found to occur closer to design point than is the case for clear water pumps.
  • unstable flow in a slurry pump is known to accelerate wear due to the dissipation of energy.
  • a sudden drop in pressure and efficiency is an index of this dissipation of energy.
  • the loss in static pressure is believed to be due to turbulence or destructive high velocity vortices, which occur in the zone of instability.
  • the purpose of the instant invention is to provide a volute pump having a uniquely contoured interior surface defined by the pump casing walls or a liner, which stabilizes the flow patterns therethrough, especially a pump having a wide impeller and wide volute for pumping slurries.
  • a centrifugal pump comprising a casing, an impeller mounted in said casing having at least one impeller discharge opening in an outer periphery, a drive shaft extending axially for rotating said impeller mounted in said casing, a pair of side wall portions disposed opposite and spaced apart from one another, one of the pair of side wall portions having an opening for receiving said impeller drive shaft, the other of the pair having a fluid inlet opening, a volute passage defined by a volute wall portion connecting said pair of said side wall portions which has a fluid outlet discharge nozzle tangentially leading therefrom, said volute passage having a contoured interior surface with a volute region extending from a cutwater to a throat portion, said discharge nozzle extending outwardly from said throat portion, said contoured interior surface in the volute wall portion of the volute region comprising in axial cross-section a circumferentially extending recirculation region adjacent said outer periphery of said impeller extending away from said impeller,
  • the centrifugal pump is characterized in that said contoured interior surface further comprises a circumferentially extending collector region radially outwardly of said recirculation region, the axial width of said collector region being less than the axial width of said recirculation region, said axial width of said recirculation region decreasing continuously at a first rate in a direction radially outwardly of said impeller, said axial width of said collector region decreasing continuously at a second rate in a direction radially outwardly of said impeller.
  • the first rate may be greater than the second rate.
  • the recirculation region of the pump of the previous paragraph defines a pair of buffer zones on opposite sides of the impeller discharge opening which act to channel the flow exiting the impeller discharge opening into the collector region.
  • a removable volute liner for a pump casing comprising:
  • said volute wall portion including said fluid outlet discharge nozzle when assembled within the casing forming a complete volute liner passage around a pump impeller, which passage has a contoured interior surface, which is preferably arcuately contoured, having a volute region extending from a cutwater to a throat portion and a discharge nozzle region extending outwardly from the throat portion, the arcuately contoured interior surface in the volute wall portion of the volute region comprising in axial cross-section a trio of concave portions which are interconnected.
  • the interconnection is by a. pair of convex portions. These portions cooperate to provide a flowingly contoured surface of changing axial cross-section in the volute wall portion of the volute region.
  • the concave portions comprise a central concave portion with a variable radius R flanked on each side by one of a pair of side concave portions having fixed radii r, and r 2 , wherein R may vary from R greater than one of r, and r 2 near the cutwater to R less than or equal to one of r, and r 2 near the throat portion, said flowingly contoured surface extending past the throat portion into the discharge nozzle region wherein said surface gradually becomes circular in axial cross-section.
  • the collection of flow leaving the pump discharge openings of the impeller should be accomplished' as smoothly as possible to minimize accelerations and decelerations of the fluid flow.
  • the flow areas throughout the collector or volute are typically designed to achieve the best possible efficiency at a predetermined target flow by optimizing the hydraulic interaction between the impeller (with or without expeller vanes) and the volute.
  • a wide impeller can cause the volute passage to be "distorted", i.e., unusually wide (compared to the width of the impeller discharge opening), for the typically required flow area.
  • a wide volute passage results for pumps having wide impellers, because a fixed width for a fixed flow area dictates a given average passage height. Tests have proven that this "distorted" volute passage shape results in flow instabilities, especially for impellers having no expeller vanes or having worn expeller vanes.
  • the uniquely contoured interior surfaces of this invention have been found to eliminate undesirable flow instabilities and by inference to stabilize the flow patterns through centrifuged pumps of the volute type.
  • the interior surfaces may be defined by the pump casing, but are preferable defined by a volute liner.
  • the volute interior surfaces comprise a volute region and a fluid outlet discharge nozzle region which define a volute passage and which are both at least in part contoured interior surfaces and preferably, arcuately contoured interior surfaces.
  • the novel volute passage contours according to this invention preferably provide smooth, flowing transitions at all stations within the volute, e.g., from cutwater around to throat and out the discharge nozzle.
  • the volute liners of this invention may be fabricated from any suitable materials such as plastics; elastomers, such as a silicon elastomer; or rubbers, such as vulcanized rubber and neoprene.
  • the liners may be fabricated of metal, such as white cast iron; metal alloys; and composite materials may be used, such as rubberized fabrics including but not limited to, for example, a fiberglass reinforced molded neoprene liner.
  • the replaceable liners serve to prevent wear to the interior of the pump casing and choice of materials is dictated by the fluids to be pumped, as is well-known in the art.
  • a preferred embodiment according to this invention is a multi-piece liner having two or more sections. Sections which are subject to greater wear may thus be singlely and more frequently replaced.
  • the liner may be fabricated and split into as many sections as desired. For example, when the liner is a two-section or two- piece liner, the liner may be split through a plane which extends perpendicularly to the longitudinal axis of the impeller drive shaft or through the same plane as the longitudinal axis of the impeller drive shaft, or through any other plane.
  • a centrifugal pump of the volute type includes a pump casing which surround an impeller and a drive shaft for rotating the impeller.
  • the casing is typically comprised of a pair of side wall portions disposed opposite and spaced apart from one another.
  • One of the pair of side wall portions has an opening for receiving the impeller drive shaft which has a longitudinal axis.
  • the other of the pair of side wall portions has a fluid inlet opening.
  • the pair of side wall portions lie in planes which extend generally in the same planes as the side wall portions of the impeller.
  • the casing is further comprised of a volute wall portion which connects together the pair of side wall portions and has a fluid outlet opening.
  • a casing interior is comprised of the interior surfaces of said pair of side wall portions and said volute wall portion including said fluid outlet opening.
  • the casing in general is split into two halves. The casing halves sealingly engaged one another and cooperate to form a complete volute passage around the pump impeller when the pump is assembled.
  • the contoured interior surface in the volute wall portion of the volute region comprises in axial cross-section, a circumferentially extending recirculation region adjacent the outer periphery of the impeller, which extends away from the impeller.
  • the contoured interior surface further comprises a circumferentially extending collector region radially outwardly of said recirculation region.
  • the axial width of the collector region is preferable at least equal to or greater than the width of the periphery of the impeller proximate said impeller and is less than the axial width of the recirculation region.
  • the axial width of the recirculation region decreases continuously at a first rate in a direction radially outwardly of the impeller.
  • the axial width of the collector region decreases continuously at a second rate in a direction radially outwardly of the impeller.
  • the first rate is preferably greater than the second rate. There may be a sharp inflection point as the first rate changes to the second rate, where the rate of change may become very large.
  • the recirculation region may further include a pair of buffer zones on opposite sides of the impeller discharge opening. These zones each extend in axial cross-section from the impeller shrouds to the wall defining the recirculation region.
  • the impeller shrouds extend from the impeller discharge opening to the side walls of the impeller.
  • the buffer zones act to channel the flow exiting the impeller discharge opening into the collector region. Flow deceleration is believed to be minimized thereby.
  • this contoured interior surface is arcuately contoured and comprises an axiai cross-section a trio of concave portions which are interconnected, most preferably the interconnection being by a pair of convex portions which cooperate to provide a flowingly contoured surface of changing axial cross-sections in the volute wall portion of the volute region.
  • the concave portions comprise a central concave portion (which corresponds to the collector region) with a radius R, which radius R is preferably variable and is most advantageously greater near the cutwater and gradually varys to a radius R which is smaller near the throat portion.
  • the central concave portion is flanked on each side by one of a pair of side concave portions having radii r, and r 2 , which are preferably fixed.
  • r may equal r 2 or be different from r 2 .
  • Central concave portion radius R may vary from R greater than one of r, and r 2 near the cutwater to R less than or equal to one of r, and r 2 nearthe throat portion.
  • the central concave portion and the pair of side concave portions are interconnected. Interconnection most preferably is by a pair of convex portions, one of said pair of convex portions on either side of the central concave portion.
  • the radii of the pair of convex portions are selected so as to provide a flowingly contoured surface of changing axial cross-section in the volute wall portion of the volute region.
  • the flowingly contoured surface extends, moreover, past the throat portion, into the discharge nozzle region wherein said surface gradually becomes circular in axial cross-section.
  • the flow-stabilizing interior surface contours for the casings or the volute liners according to this invention provide improved flow stability for centrifugal pumps in operation, especially for pumps designed for pumping slurries.
  • a two section liner according to this invention is shown in a break-away isometric view of the pertinent portion of a centrifugal pump.
  • the pump comprises a motor 1 having a shaft 2.
  • the casing shown generally at 3, is a split casing having a first section 4 and a second section 5, the two casing sections 4, 5 (shown as symmetrical halves) being so constructed as to matingly engage, and being provided with a closure means (not shown), which is generally an array of nuts and bolts.
  • the impeller 6 is surrounded by a linershown generally at when the pump is assembled.
  • the liner 7 is shown as a two section liner having a pair of wall portions 8 and 9 and a volute wall portion 10which includes a discharge nozzle 11.
  • the interior 12 of the volute wall portion 10 is shown as having a uniquely contoured surface which is the subject of this invention.
  • FIG. 2 shown is an inside view of half of a two section liner 7.
  • the volute shape i.e. spiral shape
  • the volute shape may be either an ideal volute shape or, as a matter of design and fabrication convenience, it may be a modified volute shape.
  • Shown generally in this view is the cutwater 13 of the volute region shown generally at 14.
  • the volute region 14 extends from this cutwater 13 to a throat portion shown generally at 15.
  • the discharge nozzle region shown generally at 16 extends outwardly from the throat portion 15 to a connection means (not shown) which may be a pipe.
  • Figure 2 is provided with section lines A through K so that the interior contour 12 of the volute wall portion 10 (shown without any split section lines) may be better understood in Figures 3A through 3K.
  • Figures 3A through 3H are partial axial cross-sections at various section lines A through H.
  • Figures 31 through 3K are axial cross-sections at various section lines I through K.
  • FIG. 3G a partial axial cross-section through section line G of the interior contour 12 of the volute wall portion 10 according to this invention as viewed from the interior of the liner (without any split section lines) is shown.
  • Section G is selected from upstream of the throat region shown generally at 15.
  • This view clearly shows the arcuately contoured interior surface 12 of the volute wall portion 10 in the volute region 14.
  • Shown are a trio of concave portions interconnected by a pair of convex portions which cooperate to provide a flowingly contoured surface.
  • a central concave portion 17 having a radius R is flanked on each side by one of a pair of side concave portions 18 and 19, having a radii r 1 and r 2 , respectively.
  • FIG. 17 and the pair of side concave portions 18 and 19 are interconnected by a pair of convex portions 20 and 21 which cooperate to provide the flowingly contoured surface of changing axial cross-section according to this invention.
  • Figure 3G also shows the recirculation zone having a width W1 and the collector zone having a width w Z .
  • Figures 3A through 3H serially show this changing axial cross-section.
  • the flowingly contoured surface of the interior 12 of the volute wall portion 10 in the volute region 14 extends past the throat portion shown generally at 15 into the discharge nozzle region shown generally at 16, wherein the surface gradually becomes circular in axial cross-section.
  • Figures 31 through 3K which are axial cross-sections through section lines I, J and K, respectively, the flowingly contoured surface is serially shown to extend past the throat portion 15 into the discharge nozzle region shown generally at 16.
  • the flowingly contoured surface gradually becomes circular in axial cross-section as shown in Figure 3K.
  • Figure 4 is an axial cross-sectional view (without split section lines) through section line I (see Figure 2) showing a partial axial cross-sectional view through section line H (see Figure 2) in phantom.
  • This figure more clearly shows the smooth transition of the interior contours of the volute region as they flowingly move into the discharge nozzle region. Shown clearly also is the slight asymmetry of this example of the uniquely contoured surfaces according to this invention, which results from the fact that radii r, and r 2 of side concave portions 18 and 19 are not shown as equal.
  • the nozzle at section line I includes concave portions 24 and 25 which are positioned to bleed off a portion of the flow from the recirculation zone.
  • Figure 5 is an axial cross-sectional view through section line 5 (see Figure 2).
  • the general flow of fluids from the impeller discharge openings 22 is shown.
  • the central concave portion 17 (the collector region) is shown as having an axial width which is slightly greater than the width of the impeller discharge openings 22 and as serving to receive the main flow from the impeller discharge openings 22.
  • the pair of buffer zones extend in axial cross-section from the impeller . shrouds 23 to the walls of the side concave portions 18 and 19.
  • the buffer zones channel the main flow from the impeller discharge openings 22 into the collector region as generally shown by the flow arrows in Figure 5.
  • a pump performance graph is shown which compares the performance of a pump having a volute liner according to the instant invention, liner A, with that of a pump having a volute liner typically encountered in industry, liner B.
  • Test volute liner B had a continuously arcuately concave surface when viewed from the interior of the liner, and had a variable radius R' which was, at any section line of the annular wall portion of the liner, the same value as the variable radius R of the central concave portion 40 according to test volute liner A.
  • Both liner A and liner B were fabricated of thick-walled molded elastomer.
  • volute liner according to this invention liner A, indicated by A on the graph, exhibits slightly higher efficiency without any instability. This is considered to be a most significant finding and is believed to be due to the novel, flowingly contoured volute liner interior surfaces according to the instant invention.
  • the removable volute liners A and B were performance tested with water. If the performance tests were made with abrasive slurry, similar performance results would be anticipated such that at a flow rate of around 600 GPM, for the same TDH (pressure), higher speed and more power would be required for the conventional unstable volute liner B by inference from the comparative performance curve of Figure 6. It is therefore believed reasonable to conclude that the extra power would be absorbed by the fluid in the form of turbulence, which in turn would act to accelerate wear compared to the stable volute liner A according to this invention, without the turbulence.

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Claims (13)

1. Pompe centrifuge comportant un boîtier (4, 5), un rotor (6) monté dans ledit boitier (4, 5) et présentant sur sa périphérie extérieure au moins une ouverture (22) d'évacuation du rotor; un arbre d'entrainement (2) s'étendant axialement pour entrainer en rotation ledit rotor (6) monté dans ledit boîtier (4, 5); une paire de portions (8, 9) de paroi latérale disposées en vis-à-vis et espacées l'une de l'autre, l'une des portions de la paire de portions de paroi latérale présentant unè ouverture pour recevoir ledit arbre d'entraine- ment du rotor, l'autre portion de la paire de portions présentant une ouverture d'entrée du fluide; un passage en volute, défini par une portion (10) de paroi en volute qui relie ladite paire desdites portions (8, 9) de paroi latérale et qui présente une buse (11) de sortie d'évacuation du fluide, guidant tangentiellement, à partir de là, ledit passage en volute présentant une surface intérieure (12) profilée avec une région en volute (14) s'étendant depuis un éperon (13) jusqu'à une portion formant gorge (15), ladite buse de sortie (11) s'étendant à l'extérieur depuis ladite portion formant gorge (15), ladite surface intérieure profilée (12) de la portion de paroi en volute (10) de la région en volute (14) comportant, en section droite axiale, une région de recyclage (18,19) qui s'étend circonférentiellement à côté de ladite périphérie dudit rotor (6) et qui s'étend en s'éloignant dudit rotor (6), caractérisée en ce que ladite surface intérieure profilée (12) comporte en outre, une région collectrice (17), s'étendant circonférentiellement et située radialement à l'extérieur de ladite région de recyclage (18, 19), la largeur axiale (W2) de ladite région collectrice (17) étant inférieure à la largeur axiale (W1) de ladite région de recyclage (18,19), ladite largeur axiale (Wi) de ladite région de recyclage (18, 19) décroissant de façon continue, suivant un premier rapport dans une direction radiale vers l'extérieur dudit rotor (6), ladite largeur axiale (W2) de ladite région collectrice (17) décroissant de façon continue, suivant un second rapport dans une direction radiale vers l'extérieur dudit rotor (6).
2. Pompe centrifuge selon la revendication 1, caractérisée en ce que ladite région de recyclage (18, 19) comporte, sur les côtés opposés de ladite ouverture d'évacuation (22) du rotor, une paire de zones d'amortissement qui agissent pour canaliser dans ladite région collectrice (17) le flux qui sort de ladite ouverture (22) d'évacuation du rotor.
3. Pompe centrifuge selon la revendication 1 ou 2, caractérisée en ce que les portions (8, 9) de paroi latérale et la portion (10) de paroi en volute comporte une chemise amovible en volute pour ledit boîtier de pompe (4, 5).
4. Pompe centrifuge selon l'une des revendications 1 à 3, caractérisée en ce que les portions (8, 9) de paroi latérale sont dans des plans qui s'étendent, généralement, perpendiculairement à l'axe longitudinal de l'arbre (2), en ce qu'une portion (10) de paroi en volute de la chemise relie ensemble ladite paire de portions (8, 9) de paroi latérale, lorsque la chemise est montée à l'intérieur du boîtier (4, 5), et présente une buse (11 ) de sortie d'évacuation du fluide guidant tangentiellement à partir de là, ladite portion (10) de paroi en volute, une fois montée à l'intérieur du boîtier (4, 5), formant, autour dudit rotor (6) de la pompe, un passage chemisé complet en volute, lequel passage présente une surface intérieure (12) profilée en arc qui comporte une région en volute, s'étendant depuis l'éperon (13) jusqu'à la portion formant gorge (15) et une région (16) formant buse d'évacuation s'étendant vers l'extérieur, depuis la portion formant gorge (15), la surface intérieure (12) profilée en arc, de la portion de paroi en volute (10) de la région en volute (14) comportant, en section droite axiale, un trio de portions concaves (17, 18, 19) qui sont interconnectées et qui collaborent pour donner une surface profilée de façon favorable à l'écoulement, de section droite axiale changeante, de la portion de paroi en volute (10) de la région en volute (14).
5. Pompe centrifuge selon la revendication 4, caractérisée en ce que le trio de portions concaves (17, 18, 19) est interconnecté par une paire de portions convexes (20, 21) qui collaborent pour donner une surface profilée de façon favorable à l'écoulement, de section droite axiale changeante dans la portion de paroi en volute (10) de la région en volute (14), lesdites sections concaves (17, 18, 19) comportant une portion concave centrale (17), de rayon R bordée, de chaque côté, par une portion d'une paire de portions concaves latérales (18,19) de rayons r, et r2, R pouvant varier depuis R supérieur à l'un des deux, de r, et de r2, près de l'éperon (13) jusqu'à R inférieur ou égal à l'un des deux, de ri et de r2, près de la portion formant gorge (15).
6. Pompe centrifuge selon l'une des revendications 3 à 5, caractérisée en ce que le boîtier est divisé en deux moitiés, lesdites moitiés s'ajustant de façon étanche l'une avec l'autre et collaborant pour former un passage complet en volute autour dudit rotor de pompe lorsque la pompe est montée, et en ce que chaque portion de paroi de la paire des portions de paroi latérale de la chemise et de la buse d'évacuation présente une surface extérieure qui s'ajuste avec une portion correspondante de la surface intérieure du boîtier, étant précisé que la surface profilée de façon favorable à l'écoulement s'étend, au-delà de la portion formant gorge (15), dans la région de la buse d'évacuation (16) où ladite surface devient progressivement circulaire en section droite axiale.
7. Pompe centrifuge selon l'une des revendications 3 à 6, caractérisée en ce que la portion de paroi en volute de la chemise est reliée à la paire de portions (8, 9) de paroi latérale de la chemise, et en ce que la chemise est divisée en deux parties par l'un ou l'autre, d'un plan perpendiculaire audit axe longitudinal de l'arbre (2) d'entrainement du rotor, et d'un plan qui passe par ledit axe longitudinal de cet arbre (2).
8. Pompe centrifuge selon l'une des revendications 3 à 6, caractérisée en ce que la portion de paroi en volute de la chemise est reliée à la paire de portions (8, 9) de paroi latérale de la chemise; et en ce que la chemise est divisée en une pluralité de parties.
9. Pompe centrifuge selon l'une des revendications 5 à 8, caractérisée en ce que r, est égal à r2.
10. Pompe centrifuge selon l'une des revendications 5 à 9, caractérisée en ce que les rayons r1 et r2 varient le long de la circonférence.
11. Pompe centrifuge selon l'une des revendications 5 à 8, caractérisée en ce que l'un des rayons r1 et r2 est fixe et que l'autre varie selon la circonférence.
12. Pompe centrifuge selon la revendication 1, caractérisée en ce que ledit premier taux de décroissance est supérieur audit second taux de décroissance.
13. Pompe centrifuge selon la revendication 1, caractérisée en ce que la surface, profilée de façon favorable à l'écoulement, de l'intérieur (12) de la portion de paroi en volute (10) de la région en volute (14) s'étend, au-delà de ladite portion formant gorge (15), dans une région (16) formant buse d'évacuation où la surface devient progressivement circulaire en section droite axiale.
EP85106700A 1984-03-20 1985-05-30 Volute de pompe et revêtement pour la stabilisation de l'écoulement Expired EP0203218B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8585106700T DE3572521D1 (en) 1985-05-30 1985-05-30 Flow-stabilizing volute pump and liner
AT85106700T ATE45787T1 (de) 1985-05-30 1985-05-30 Pumpenvolute und auskleidung zur stromstabilisierung.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US59228984A 1984-03-20 1984-03-20

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EP0203218A1 EP0203218A1 (fr) 1986-12-03
EP0203218B1 true EP0203218B1 (fr) 1989-08-23

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ZA (1) ZA851063B (fr)

Cited By (1)

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CN103307030A (zh) * 2012-03-05 2013-09-18 日本电产株式会社 离心风扇

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DE4012041C2 (de) * 1990-04-11 1996-06-13 Duechting Pumpen Maschf Gmbh Hochdruckkreiselpumpe
CN103912521A (zh) * 2014-04-04 2014-07-09 含山县恒翔机械制造有限公司 一种轻型泵体铸件

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Publication number Priority date Publication date Assignee Title
DE29654C (fr) * Neuerung an Centrifugalpumpen und Ventilatoren. (Zusatz zu P. R. 24421.) — C. SCHIELE in Frankfurt a. M., Sömmeringstr. 4
US1585669A (en) * 1921-04-08 1926-05-25 Hansen Rubber Products Company Pump
FR752623A (fr) * 1932-06-21 1933-09-27 Perfectionnements aux pompes et compresseurs centrifuges
FR1167542A (fr) * 1955-01-27 1958-11-26 Procédé de fabrication de ventilateurs et pompes centrifuges, et machines conformes à celles obtenues par ledit procédé ou procédé similaire

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103307030A (zh) * 2012-03-05 2013-09-18 日本电产株式会社 离心风扇
CN103307030B (zh) * 2012-03-05 2015-12-09 日本电产株式会社 离心风扇

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EP0203218A1 (fr) 1986-12-03
ZA851063B (en) 1985-08-14

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