EP0567589A1 - Moyeu arbitraire pour roue a aubes - Google Patents

Moyeu arbitraire pour roue a aubes

Info

Publication number
EP0567589A1
EP0567589A1 EP92905376A EP92905376A EP0567589A1 EP 0567589 A1 EP0567589 A1 EP 0567589A1 EP 92905376 A EP92905376 A EP 92905376A EP 92905376 A EP92905376 A EP 92905376A EP 0567589 A1 EP0567589 A1 EP 0567589A1
Authority
EP
European Patent Office
Prior art keywords
hub
rotation
axis
blade
circle
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Withdrawn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
EP92905376A
Other languages
German (de)
English (en)
Other versions
EP0567589A4 (fr
Inventor
William Jansen
Melvin Platt
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.)
Ingersoll Rand Co
Original Assignee
Northern Research and Engineering Corp
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 Northern Research and Engineering Corp filed Critical Northern Research and Engineering Corp
Publication of EP0567589A4 publication Critical patent/EP0567589A4/fr
Publication of EP0567589A1 publication Critical patent/EP0567589A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors

Definitions

  • This invention relates generally to centrifugal impellers and more particularly to arbitrary hub designs for centrifugal impellers.
  • each point on the hub which is located in the same plane normal to the axis of rotation is approximately the same distance from the axis of rotation.
  • This configuration is referred to as concentric or non arbitrary hub design or contour.
  • the non arbitrary hub designs often are not the optimal design considering the compressibility of fluids, nonuniform flow across the passage between the impeller blades, resistance of the impeller to loads placed thereupon and the fact that the impeller rotates in one direction. For these reasons, among others, the impeller with a non arbitrary hub configuration often will not be the most efficient, or will limit the range of rotational speeds at which the impeller may operate.
  • a centrifugal impeller comprising a hub formed about an axis of rotation with a plurality of substantially radially extending blades are affixed to the hub, each blade having a suction surface, a pressure surfac is formed on the adjacent blade facing the suction surface.
  • the blades have a height being measured in a radial direction from the hub.
  • a portion of the hub, having a hub configuration, extends between the pressure surface and the suction surface.
  • An imaginary plane extending in a direction normal to the axis of rotation is used to define a cross-sectional view of the impeller.
  • a first and a second concentric circle are formed in the plane with the center of the concentric circle being the axis of rotation. The first circle passes through a point on the hub located closest to the axis of rotation.
  • the second circle has a radius greater than the first circle by an amount equal to five percent of said blade height, wherein a portion of the hub extends outside of the second circle.
  • Fig. 1 is a perspective top and side view illustrating a prior art embodiment of a centrifugal impeller, showing a plane which is normal to the axis of rotation of the impeller that identifies a cross-sectional view of the impeller;
  • Fig. 2 is the cross-sectional view of one quadrant of the impeller, identified by the plane in Fig. 1;
  • Fig 3 is a cross-sectional view, similar to Fig. 2, of one embodiment of an arbitrary hub of the instant invention
  • Fig. 4 is a cross-sectional view, similar to Fig. 2, of an alternate embodiment of an arbitrary hub of the instant invention
  • Fig. 5 is a cross-sectional view taken along sectional line 5-5 of Fig. 4 during the milling of the impeller?
  • Fig. 6 is a cross-sectional view, similar to Fig. 5, after milling, showing a stationary (i.e., nonrotating) shroud in its proper location;
  • Fig. 7 is a diagram illustrating fluid flow velocities along line A-A of Fig. 2 for an ideal centrifugal impeller with no surface friction;
  • Fig. 8 is a view similar to Fig. 7 for the actual prior art centrifugal impeller of Figs. 1 and 2 when surface friction is taken into account;
  • Fig. 9 is a view similar to Fig. 7 for the impeller of the present invention as illustrated in Fig. 3;
  • Fig. 10 is a cross-sectional view, similar to Fig 2, of a non reflexive arbitrary hub of the instant invention.
  • Fig. 11 is an elevational view of the centrifugal impeller of the instant invention with the blades removed illustrating the two imaginary surfaces used to determine whether a particular hub surface is arbitrary, the first imaginary surface being the imaginary plane 20 and the second imaginary surface being the imaginary frusto-conical surface 86.
  • This invention relates to the contour of a hub 10 for a centrifugal impeller 12.
  • the hub and the impeller are concentrically formed and rotate about an axis of rotation 14.
  • a plurality of substantially radially extending blades 26 are affixed to the hub 10 of the centrifugal impeller 12. Each blade has a first or suction side 28 and a second or pressure side 30 with a distinct portion of the hub being located between the first side 28 and the second side 30.
  • the impeller rotates about the axis of rotation in the direction of rotation 31.
  • a transition fillet 32 may be located between hub 10 and the sides 28, 30.
  • Two concentric circles 22 and 22' can be generated, in the plane, about the axis of rotation.
  • the hub contour 23 closely corresponds to a concentric circle 22.
  • Whether a hub profile is arbitrary can be determined as follows. For each plane, the concentric circle 22 (Fig. 2 and 3) is drawn to intersect a point 33 on the hub 10 which is closest to the axis of rotation 14. The second concentric circle 22' is drawn with a radius being greater than the first concentric circle 22 by a distance equal to five percent of the height 25 of a blade 26 taken in the radial direction.
  • the hub is concentric or non arbitrary (as illustrated in Fig. 2). If a portion of the hub 24 extends outside of the second concentric circle 22' (as in Fig. 3), then the hub is considered arbitrary or non concentric.
  • a first ray 33 extends from the axis of rotation 14 to a first point 33', which is the point on the hub which is closest to the axis of rotation.
  • a second ray 35 extends from the axis of rotation 14 to a second point 35', which is the point on the hub 10 which is furthest from the axis of rotation.
  • the difference in length between the first ray 33 and the second ray 35 must exceed 5 percent of the total height 36 (measured radially) of the blade 26. No point located within the transition fillets 32, or sides of the blades 28, 30 are to be considered in determining whether a surface is arbitrary.
  • a certain impeller with an arbitrary hub design may have a series of planes having arbitrary hub profiles while another series of planes in the same impeller do not have an arbitrary profile.
  • the specific profile of the arbitrariness, or the purpose for the arbitrariness may be altered from plane to plane within the impeller 12.
  • the arbitrariness of a hub surface may be similarly defined by an imaginary plane normal to the primary flow direction, as it has been defined above by an imaginary plane normal to the axis of rotation.
  • the sides 28, 30 are curved surfaces, often they can be generated with a flank 42 of a miller 34 since the curve which forms the sides may be formed from a series of straight lines (as described in U.S. Patent No. 5,014,421, issued May 14, 1991 incorporated herein by reference).
  • a point 44 of the miller 34 is forming a portion of the hub 10 as shown in Fig. 5. Often the entire hub 10 is formed by point milling. In the prior art the hub has scalloped surfaces 23 after machining (see Fig. 2). An arbitrary surface pertains to a much greater surface irregularity than that of a scalloped surface.
  • a curved surface takes approximately the same time to machine by point milling as a flat surface
  • an arbitrary hub surfaces (being curved as desired by the impeller designer) as illustrated in Figs. 3 and 4 may be machined with a point miller nearly as efficiently as a concentric surface.
  • Arbitrary hub profiles have improved flow characteristics in centrifugal impellers as follows.
  • a specific arbitrary hub surface may have different effects o impeller efficiencies based upon the RPM of the impeller, the specific characteristics of the fluid being pumped or compressed, and the specific blade geometry of the impeller.
  • centrifugal impelle 12 There are only four surfaces in the centrifugal impelle 12 which are in direct contact with the working fluid, and which therefore may affect fluid flow characteristics. These surfaces are the suction side 28 of the blade, the pressure side 30 of the blade, the hub 10 and the shroud 45. These four surfaces 28, 30, 10 and 45 form a passage 52 through which fluid passes as it traverses the impeller.
  • the shroud 45 forms the fourth side of the passage which restrictsizid flow within the passage along with the two blades and the hub 10.
  • the shroud may be stationary and separate from the impeller or may be attached to and rotate with the impeller.
  • the shroud 45, if it is attached, may be formed in an arbitrary design to produce results similar t that of the hub.
  • an arbitrary hub profile 24 illustrated in Fig. 3 is contoured wherein fluid entering the center of passage 5 will tend to be diverted to either wall.
  • the resultant velocity profile of fluid passing through this passage is illustrated in Fig. 9 which is closer to the ideal velocity profile than the prior art centrifugal impellers.
  • an alternate arbitrary hub configuration involves channels 65 which extend in a meridional direction (into the page) . These channels resist the tendency of fluid passing through passage 52 to flow across the passage. Cross flow tends to create turbulence which will decrease the efficiency of the impeller as well as limit the range at which the impeller will operate stably.
  • a third reason for forming an arbitrary hub involves structural considerations as illustrated in Fig. 10.
  • the impellers When the impellers are exposed to high rotational velocities about the axis of rotation 14, an unacceptable stress may b placed upon the blades or the hub. This stress may be increased in those designs where the shroud 45 rotate? with the impeller.
  • the hub may be built up by an arbitrary contour at a location where the flow characteristics is not critical.
  • an imaginary plane is used to determine whether a surface is arbitrary.
  • An alternate device which may be used to determine whether a surface is arbitrary is an imaginary frusto-conical surfac 86 which is generated as a series of rays 88 which extends from the axis of rotation 14, and is perpendicular to a general fluid flow direction 90 adjacent each hub point 92.
  • a suction intersection 70 is the point, in the surface 20, where the suction plane 28 intersects the hub 10.
  • a pressure intersection 72 is the point where the pressure surface 30, of an adjacent blade, intersects the hub 10. Fillets are not considered in determining the intersection points.
  • a first ray 74 is constructed from the axis of rotation 14 to the suction intersection 70.
  • a second ray 76 is constructed from the axis of rotation to the pressure intersection 72.
  • a third ray 78 is constructed to bisect the angle between the first ray and the second ray.
  • a mirror image 80 of the hub between the third ray and the first ray is produced between the third ray and the ⁇ 5 second ray. If the hub is reflexive or concentric, the mirror image will approximate the hub between the third ray and the second ray.

Landscapes

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

Abstract

Une roue à aubes centrifuge comprend un moyeu formé autour d'un axe de rotation (14) avec une pluralité d'aubes s'étendant sensiblement radialement (26) et fixées au moyeu. Les aubes ont une hauteur mesurée dans une direction radiale à partir du moyeu. Un plan imaginaire s'étendant dans une direction normale à l'axe de rotation est utilisé pour définir une vue en coupe de la roue à aubes. Un premier cercle concentrique (22) et un second cercle concentrique (22') sont formés dans le plan, leur centre étant l'axe de rotation. Le premier cercle passe par un point sur le moyeu situé le plus proche de l'axe de rotation. Le second cercle possède un rayon plus grand que celui du premier cercle d'une quantité égale à 5 % de la hauteur de l'aube, une portion (24) du moyeu s'étendant à l'extérieur du second cercle.
EP92905376A 1991-01-15 1992-01-08 Moyeu arbitraire pour roue a aubes Withdrawn EP0567589A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US64143291A 1991-01-15 1991-01-15
US641432 1991-01-15
FR9208673A FR2693515A1 (fr) 1991-01-15 1992-07-13 Moyeu arbitraire pour roues centrifuges.

Publications (2)

Publication Number Publication Date
EP0567589A4 EP0567589A4 (fr) 1993-09-14
EP0567589A1 true EP0567589A1 (fr) 1993-11-03

Family

ID=26229591

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92905376A Withdrawn EP0567589A1 (fr) 1991-01-15 1992-01-08 Moyeu arbitraire pour roue a aubes

Country Status (4)

Country Link
EP (1) EP0567589A1 (fr)
JP (1) JPH06504351A (fr)
FR (1) FR2693515A1 (fr)
WO (1) WO1992013197A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2782755B1 (fr) * 1998-09-02 2000-09-29 Inst Francais Du Petrole Turmomachine polyphasique a melange de phases ameliore et methode associee
JP2002364587A (ja) * 2001-06-05 2002-12-18 Toyota Central Res & Dev Lab Inc 遠心圧縮機のインペラ
FR2931214B1 (fr) * 2008-05-15 2013-07-26 Turbomeca Pale de rouet de compresseur a raccordement evolutif
DE102015214854A1 (de) * 2015-08-04 2017-02-09 Bosch Mahle Turbo Systems Gmbh & Co. Kg Verdichterrad für einen Abgasturbolader
JP6992504B2 (ja) * 2017-12-27 2022-01-13 トヨタ自動車株式会社 インペラの製造方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2141262A1 (de) * 1971-08-18 1973-02-22 Daimler Benz Ag Verdichter
GB2007302A (en) * 1977-09-26 1979-05-16 Gen Motors Corp Gas turbine engine
US4820115A (en) * 1987-11-12 1989-04-11 Dresser Industries, Inc. Open impeller for centrifugal compressors

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2735612A (en) * 1956-02-21 hausmann
FR999826A (fr) * 1946-01-11 1952-02-05 Rateau Soc Perfectionnements aux rouets à grande vitesse des compresseurs centrifuges
US2918254A (en) * 1954-05-10 1959-12-22 Hausammann Werner Turborunner
GB944166A (en) * 1960-03-02 1963-12-11 Werner Hausammann Rotor for turbines or compressors
US3481531A (en) * 1968-03-07 1969-12-02 United Aircraft Canada Impeller boundary layer control device
DE3023466C2 (de) * 1980-06-24 1982-11-25 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Einrichtung zur Verminderung von Sekundärströmungsverlusten in einem beschaufelten Strömungskanal
DE3202855C1 (de) * 1982-01-29 1983-03-31 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Einrichtung zur Verminderung von Sekundaerstroemungsverlusten in einem beschaufelten Stroemungskanal
SU1059217A1 (ru) * 1982-09-08 1983-12-07 Всесоюзный Научно-Исследовательский Институт "Гелиевая Техника" Рабочее колесо центростремительной турбины
JPS6069211A (ja) * 1983-08-26 1985-04-19 Mitsubishi Heavy Ind Ltd ラジアルタ−ビン
WO1990002265A1 (fr) * 1988-08-16 1990-03-08 Dresser-Rand Company Aubes de hauteur partielle pour roues a aubes

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2141262A1 (de) * 1971-08-18 1973-02-22 Daimler Benz Ag Verdichter
GB2007302A (en) * 1977-09-26 1979-05-16 Gen Motors Corp Gas turbine engine
US4820115A (en) * 1987-11-12 1989-04-11 Dresser Industries, Inc. Open impeller for centrifugal compressors

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO9213197A1 *

Also Published As

Publication number Publication date
EP0567589A4 (fr) 1993-09-14
FR2693515A1 (fr) 1994-01-14
JPH06504351A (ja) 1994-05-19
WO1992013197A1 (fr) 1992-08-06

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