EP0616131B1 - Radial wheel - Google Patents

Radial wheel Download PDF

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Publication number
EP0616131B1
EP0616131B1 EP94100758A EP94100758A EP0616131B1 EP 0616131 B1 EP0616131 B1 EP 0616131B1 EP 94100758 A EP94100758 A EP 94100758A EP 94100758 A EP94100758 A EP 94100758A EP 0616131 B1 EP0616131 B1 EP 0616131B1
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EP
European Patent Office
Prior art keywords
disc
blade ring
hub
cover
blades
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
EP94100758A
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German (de)
French (fr)
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EP0616131A1 (en
Inventor
Ernst Wiemann
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.)
Grenzebach GmbH and Co KG
Original Assignee
Babcock BSH AG
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Publication of EP0616131A1 publication Critical patent/EP0616131A1/en
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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
    • F04D29/26—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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers

Definitions

  • the invention relates to a radial impeller according to the preamble of claim 1.
  • DE 29 40 773 A1 shows options for optimally designing the contour of the cover plate and various dimensions and angles with a view to a high power density and good efficiency.
  • the invention is based on impellers which are described in this document. With these impellers, the blades can be designed as profiled or non-profiled blades. In the latter case, they can be curved in the shape of a circular arc or parabolic, or they can also be designed as straight blades. The outer edges of the blades run parallel to the axis of rotation.
  • the document also shows an embodiment in which the outer diameter of the blade ring increases from the hub disk to the cover disk.
  • the increase is between about 10.5 and 35%.
  • the edge of the hub disk carrying the blades is bent in the direction away from the cover disk by an angle of 10 to 25 degrees.
  • the tangent to the cover disk at its outer edge encloses an angle of 20 to 30 degrees with a radial line, that is, a line directed at right angles to the impeller axis. With this configuration, the emerging air flow is acute to the axis directed.
  • Such impellers are usually referred to as diagonal or semi-axial wheels.
  • a diagonal wheel is known from the magazine HLH Volume 40 (1989) No. 8 - August, pages 426 to 428, in which the outer diameter of the blade ring on the cover disk is approximately 29% larger than on the hub disk.
  • the blades have a curvature and a twist.
  • EP-B1-0 112 932 also deals with the problem of increasing the power density and the efficiency of radial impellers. It describes an impeller whose blades are deformed by twisting or shearing, the inside diameter of the blade ring decreasing from the cover disk to the hub disk.
  • the outside diameter is constant in some embodiments. In one embodiment, it varies such that it assumes its minimum value on the cover disk and its maximum value on the hub disk.
  • the invention is not concerned with impellers made by casting. It is not concerned with complicatedly shaped impellers that can only be economically produced in large series due to the high tooling costs. Rather, it deals with the impellers specified in the preamble of claim 1, which can be produced in single or small series production with little effort on special tools.
  • the invention has for its object to further improve a radial impeller according to the preamble of claim 1, so that the efficiency and the power density are increased.
  • the impeller shown in Fig. 1 consists of a flat hub disc 1, an annular cover plate 2 and a plurality of blades 3, which form a blade ring.
  • the cover plate 2 is shaped like a trumpet in a known manner. 1 has approximately the shape of a circular arc of 90 degrees, so that the tangent on the inner edge runs approximately parallel to the axis of rotation and radially on the outer edge, i.e. encloses an angle of 90 degrees with the axis of rotation.
  • the blades 3 are flat or cylindrically curved sheets or also wing-like profiles. They are welded between the hub disc 1 and cover disc 2, e.g. by spot welding.
  • the inner edges of the blades 3 consist of a rectilinear section parallel to the axis of rotation, which extends from the hub disk 1 to an intermediate plane 4, and an adjoining, slightly outwardly curved section which extends from the intermediate plane 4 to the cover disk 2 .
  • the outer edges are flush with both the edge of the hub disc 1 and the outer edge of the cover disc 2.
  • the outer diameter of the cover disk 2 is approximately 3% larger than the diameter of the hub disk 1. Therefore, the outer diameter of the blade ring increases from the hub disk 1 to the cover disk 2.
  • the outer edge of the blade 3 consists of two rectilinear sections.
  • the first section 5 extends from the hub disc 1 in the axial direction over a height a to the intermediate plane 4 parallel to the hub disc 1.
  • the second section 6 extends between the intermediate level 4 and the cover plate 2 over a height b. It is parallel to the axis of rotation.
  • the ratio a: b, in which the intermediate plane 4 divides the distance between the hub disk 1 and the cover disk 2, is approximately 7: 3.

Abstract

In the case of conventional radial wheels, the outside diameter of the blade ring between hub disc and cover disc is constant. The problem here is that the flow rate decreases greatly in the vicinity of the cover disc. As a result, efficiency and power density of the wheel are impaired. Wheels are also already known, in the case of which the diameter of the blade ring increases from the hub disc to the cover disc by about 10.5 to 35 %. According to calculations of the inventor, undesired shear flows here, involving considerable losses, can be avoided only by twisting the blades. For the manufacture of twisted blades, complicated special tools are required, so that a single-piece or small-series production is not economical as a rule. The new wheel has blades (3) which are simple to manufacture and are plane or cylindrically curved. An increase in the efficiency and power density is achieved in that the diameter of the blade ring on the cover disc (2) is 1 to 6 % greater than on the hub disc (1). The wheel is particularly suitable for single-piece or small-series production. <IMAGE>

Description

Die Erfindung betrifft ein Radiallaufrad gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a radial impeller according to the preamble of claim 1.

Es ist bei Radiallaufrädern der angegebenen Gattung lange bekannt, daß die Strömungsgeschwindigkeit in der Nähe der Deckscheibe stark abfällt. Dadurch werden Wirkungsgrad und Leistungsdichte des Laufrades beeinträchtigt.It has long been known for radial impellers of the type specified that the flow velocity drops sharply in the vicinity of the cover plate. This affects the efficiency and power density of the impeller.

Der DE 29 40 773 A1 sind Möglichkeiten zu entnehmen, die Kontur der Deckscheibe sowie verschiedene Maßverhältnisse und Winkel im Hinblick auf eine hohe Leistungsdichte und einen guten Wirkungsgrad optimal zu gestalten. Die Erfindung geht von Laufrädern aus, die in diesem Dokument beschrieben sind. Bei diesen Laufrädern können die Schaufeln als profilierte oder auch nicht profilierte Schaufeln ausgebildet sein. In dem letzteren Falle können sie kreisbogenförmig oder parabelförmig gekrümmt oder auch als gerade Schaufeln ausgebildet sein. Die Außenkanten der Schaufeln verlaufen parallel zur Drehachse.DE 29 40 773 A1 shows options for optimally designing the contour of the cover plate and various dimensions and angles with a view to a high power density and good efficiency. The invention is based on impellers which are described in this document. With these impellers, the blades can be designed as profiled or non-profiled blades. In the latter case, they can be curved in the shape of a circular arc or parabolic, or they can also be designed as straight blades. The outer edges of the blades run parallel to the axis of rotation.

Die Schrift zeigt auch ein Ausführungsbeispiel, bei dem der Außendurchmesser des Schaufelkranzes von der Nabenscheibe zur Deckscheibe hin zunimmt. Die Zunahme liegt zwischen etwa 10,5 und 35 %. Bei diesem Schaufelkranz ist der die Schaufeln tragende Rand der Nabenscheibe in Richtung von der Deckscheibe weg um einen Winkel von 10 bis 25 Grad abgebogen. Die Tangente zur Deckscheibe an deren äußerem Rand schließt mit einer radialen, d.h. rechtwinklig zur Laufradachse gerichteten Linie einen Winkel von 20 bis 30 Grad ein. Bei dieser Konfiguration ist der austretende Luftstrom spitzwinklig zur Achse gerichtet. Derartige Laufräder werden üblicherweise als Diagonal- oder Halbaxialräder bezeichnet. Nach Berechnungen des Erfinders können bei einem Laufrad, dessen Schaufelkranzdurchmesser an der Deckscheibe mehr als etwa 6 % größer ist als an der Nabenscheibe, unerwünschte Scherströmungen, die mit erhöhten Verlusten verbunden sind, nur durch Verwindung der Schaufeln vermieden werden. Für die Herstellung verwundener Schaufeln sind komplizierte Spezialwerkzeuge erforderlich, so daß eine Einzel- oder Kleinserienfertigung in der Regel nicht wirtschaftlich ist.The document also shows an embodiment in which the outer diameter of the blade ring increases from the hub disk to the cover disk. The increase is between about 10.5 and 35%. In the case of this blade ring, the edge of the hub disk carrying the blades is bent in the direction away from the cover disk by an angle of 10 to 25 degrees. The tangent to the cover disk at its outer edge encloses an angle of 20 to 30 degrees with a radial line, that is, a line directed at right angles to the impeller axis. With this configuration, the emerging air flow is acute to the axis directed. Such impellers are usually referred to as diagonal or semi-axial wheels. According to the inventor's calculations, in the case of an impeller whose blade ring diameter on the cover disk is more than approximately 6% larger than on the hub disk, undesirable shear flows, which are associated with increased losses, can only be avoided by twisting the blades. Complicated special tools are required for the production of twisted blades, so that one-off or small series production is generally not economical.

Durch die Zeitschrift HLH Band 40 (1989) Nr. 8 - August, Seiten 426 bis 428, ist ein Diagonalrad bekannt geworden, bei dem der Außendurchmesser des Schaufelkranzes an der Deckscheibe etwa 29 % größer ist als an der Nabenscheibe. Die Schaufeln haben eine Wölbung und eine Verwindung.A diagonal wheel is known from the magazine HLH Volume 40 (1989) No. 8 - August, pages 426 to 428, in which the outer diameter of the blade ring on the cover disk is approximately 29% larger than on the hub disk. The blades have a curvature and a twist.

Auch die EP-B1-0 112 932 befaßt sich mit dem Problem, die Leistungsdichte und den Wirkungsgrad von Radiallaufrädern zu erhöhen. Sie beschreibt ein Laufrad, dessen Schaufeln durch Verwindung oder Scherung verformt sind, wobei der Innendurchmesser des Schaufelkranzes von der Deckscheibe zur Nabenscheibe hin abnimmt. Der Außendurchmesser ist bei einigen Ausführungsbeispielen konstant. Bei einem Ausführungsbeispiel variiert er in der Weise, daß er seinen minimalen Wert an der Deckscheibe und seinen maximalen Wert an der Nabenscheibe annimmt.EP-B1-0 112 932 also deals with the problem of increasing the power density and the efficiency of radial impellers. It describes an impeller whose blades are deformed by twisting or shearing, the inside diameter of the blade ring decreasing from the cover disk to the hub disk. The outside diameter is constant in some embodiments. In one embodiment, it varies such that it assumes its minimum value on the cover disk and its maximum value on the hub disk.

Durch die DE-PS 35 20 218 sind Radiallaufräder bekannt, die durch Spritzgießen hergestellt sind. Die Form des Laufrades richtet sich dabei nach den Möglichkeiten und Erfordernisen der Spritzgießtechnik; das gilt insbesondere für die Durchmesser der verschiedenen Teile als Funktion der axialen Koordinate. Bei den dargestellten Ausführungsbeispielen nimmt der Innendurchmesser ebenso wie der Außendurchmesser des Schaufelkranzes von der Nabenscheibe in Richtung auf die Deckscheibe zu.From DE-PS 35 20 218 radial impellers are known which are produced by injection molding. The shape of the impeller depends on the possibilities and requirements of injection molding technology; this applies in particular to the diameters of the different parts as a function of the axial coordinate. In the illustrated embodiments, the inner diameter as well as the outer diameter of the Blade ring from the hub disc towards the cover disc.

Die Erfindung befaßt sich nicht mit Laufrädern, die durch Gießen hergestellt sind. Sie befaßt sich überhaupt nicht mit kompliziert geformten Laufrädern, die wegen des hohen Werkzeugaufwandes nur in großen Serien wirtschaftlich hergestellt werden können. Sie befaßt sich vielmehr mit den im Oberbegriff des Anspruchs 1 angegebenen Laufrädern, die in Einzel- oder Kleinserienfertigung mit geringem Aufwand an Spezialwerkzeugen herstellbar sind.The invention is not concerned with impellers made by casting. It is not concerned with complicatedly shaped impellers that can only be economically produced in large series due to the high tooling costs. Rather, it deals with the impellers specified in the preamble of claim 1, which can be produced in single or small series production with little effort on special tools.

Der Erfindung liegt die Aufgabe zugrunde, ein Radiallaufrad gemäß dem Oberbegriff des Anspruchs 1 weiter zu verbessern, so daß der Wirkungsgrad und die Leistungsdichte erhöht werden.The invention has for its object to further improve a radial impeller according to the preamble of claim 1, so that the efficiency and the power density are increased.

Diese Aufgabe wird durch das kennzeichnende Merkmal des Anspruchs 1 gelöst. Durch den in der Nähe der Deckscheibe vergrößerten Durchmesser erfährt die Luftströmung in diesem Bereich eine stärkere Zentrifugalbeschleunigung. Dadurch wird die Austrittsgeschwindigkeit über der äußeren Schaufelbreite vergleichmäßigt, und es ergibt sich eine deutliche Verbesserung von Wirkungsgrad und Leistungsdichte, ohne daß eine Verwindung der Schaufeln erforderlich ist.This object is achieved by the characterizing feature of claim 1. Due to the enlarged diameter near the cover plate, the air flow in this area experiences a stronger centrifugal acceleration. This evens out the exit velocity over the outer blade width and results in a significant improvement in efficiency and power density without the need to twist the blades.

Vorteilhafte weitere Merkmale der Erfindung sind in den Ansprüchen 2 bis 4 angegeben.Advantageous further features of the invention are specified in claims 2 to 4.

Die Zeichnung dient zur Erläuterung der Erfindung anhand eines vereinfacht dargestellten Ausführungsbeispiels.

Fig. 1
zeigt im Schnitt ein Radiallaufrad gemäß der Erfindung.
Fig. 2
zeigt eine Gegenüberstellung der Kennlinien eines erfindungsgemäßen Laufrades und eines Laufrades nach dem Stand der Technik.
The drawing serves to explain the invention with reference to an embodiment shown in simplified form.
Fig. 1
shows in section a radial impeller according to the invention.
Fig. 2
shows a comparison of the characteristics of an impeller according to the invention and an impeller according to the prior art.

Das in Fig. 1 dargestellte Laufrad besteht aus einer ebenen Nabenscheibe 1, einer ringförmigen Deckscheibe 2 und mehreren Schaufeln 3, die einen Schaufelkranz bilden. Die Deckscheibe 2 ist in bekannter Weise trompetenartig geformt. Die Kontur hat in der Darstellung der Fig. 1 annähernd die Form eines Kreisbogens von 90 Grad, so daß die Tangente am inneren Rand etwa parallel zur Drehachse und am äußeren Rand radial verläuft, d.h. mit der Drehachse einen Winkel von 90 Grad einschließt. Die Schaufeln 3 sind ebene oder zylindrisch gebogene Bleche oder auch tragflügelartige Profile. Sie sind zwischen Nabenscheibe 1 und Deckscheibe 2 eingeschweißt, z.B. durch Punktschweißen.The impeller shown in Fig. 1 consists of a flat hub disc 1, an annular cover plate 2 and a plurality of blades 3, which form a blade ring. The cover plate 2 is shaped like a trumpet in a known manner. 1 has approximately the shape of a circular arc of 90 degrees, so that the tangent on the inner edge runs approximately parallel to the axis of rotation and radially on the outer edge, i.e. encloses an angle of 90 degrees with the axis of rotation. The blades 3 are flat or cylindrically curved sheets or also wing-like profiles. They are welded between the hub disc 1 and cover disc 2, e.g. by spot welding.

Die Innenkanten der Schaufeln 3 bestehen aus einem geradlinigen zur Drehachse parallelen Abschnitt, der sich von der Nabenscheibe 1 bis zu einer Zwischenebene 4 erstreckt, und einem daran anschließenden, schwach nach außen gekrümmten bogenförmigen Abschnitt, der sich von der Zwischenebene 4 bis zur Deckscheibe 2 erstreckt. Die Außenkanten schließen sowohl mit dem Rand der Nabenscheibe 1 als auch mit dem Außenrand der Deckscheibe 2 bündig ab. Der Außendurchmesser der Deckscheibe 2 ist etwa 3 % größer als der Durchmesser der Nabenscheibe 1. Daher nimmt der Außendurchmesser des Schaufelkranzes von der Nabenscheibe 1 zur Deckscheibe 2 hin zu. Die Außenkante der Schaufel 3 besteht aus zwei geradlinigen Abschnitten. Der erste Abschnitt 5 ersteckt sich von der Nabenscheibe 1 in axialer Richtung über eine Höhe a bis zu der zur Nabenscheibe 1 parallelen Zwischenebene 4. Er schließt mit der Drehachse einen spitzen Winkel ein. Der zweite Abschnitt 6 erstreckt sich zwischen der Zwischenebene 4 und der Deckscheibe 2 über eine Höhe b. Er ist parallel zur Drehachse. Das Verhältnis a:b, in dem die Zwischenebene 4 den Abstand zwischen Nabenscheibe 1 und Deckscheibe 2 unterteilt, liegt bei etwa 7:3.The inner edges of the blades 3 consist of a rectilinear section parallel to the axis of rotation, which extends from the hub disk 1 to an intermediate plane 4, and an adjoining, slightly outwardly curved section which extends from the intermediate plane 4 to the cover disk 2 . The outer edges are flush with both the edge of the hub disc 1 and the outer edge of the cover disc 2. The outer diameter of the cover disk 2 is approximately 3% larger than the diameter of the hub disk 1. Therefore, the outer diameter of the blade ring increases from the hub disk 1 to the cover disk 2. The outer edge of the blade 3 consists of two rectilinear sections. The first section 5 extends from the hub disc 1 in the axial direction over a height a to the intermediate plane 4 parallel to the hub disc 1. It forms an acute angle with the axis of rotation. The second section 6 extends between the intermediate level 4 and the cover plate 2 over a height b. It is parallel to the axis of rotation. The ratio a: b, in which the intermediate plane 4 divides the distance between the hub disk 1 and the cover disk 2, is approximately 7: 3.

In Fig. 2 sind in dimensionsloser Darstellung die Druckzahl ψ und der Wirkungsgrad η über der Volumenzahl ϕ aufgetragen. Der Index 1 bezeichnet den Stand der Technik, der Index 2 die Erfindung. Es ist deutlich erkennbar, daß sowohl der Wirkungsgrad als auch die Druckzahl durch die Erfindung verbessert werden. Das Maximum des Wirkungsgrades, das den optimalen Arbeitspunkt angibt, ist zu einer höheren Volumenzahl verschoben. Da somit im optimalen Arbeitspunkt sowohl Druckzahl als auch Volumenzahl im Vergleich zum Stand der Technik vergrößert sind, ergibt deren Produkt eine deutlich erhöhte Leistungsdichte.2, the pressure number zahl and the efficiency η are plotted against the volume number ϕ in a dimensionless representation. Index 1 denotes the state of the art, index 2 the invention. It can be clearly seen that both the efficiency and the pressure coefficient are improved by the invention. The maximum of the efficiency, which indicates the optimal working point, is shifted to a higher volume number. Since both the number of prints and the number of volumes are increased in comparison to the prior art at the optimum operating point, their product results in a significantly increased power density.

Claims (4)

  1. A radial wheel,
    with a hub disc (1),
    with an annular cover disc (2) formed to resemble a trumpet,
    and with a blade ring, comprising several flat or cylindrically curved blades (3) which are fastened by simple connections, such as welding, rivet or plug connections, to the hub disc (1) and the cover disc (2),
    characterised in that the external diameter of the blade ring on the cover disc (2) is 1 to 6 % larger than the external diameter of the blade ring on the hub disc (1).
  2. A radial wheel according to Claim 1, characterised in that the external diameter of the blade ring between the hub disc (1) and an intermediate plane (4) parallel to the hub disc increases steadily and is constant between the intermediate plane and the cover disc (2), the intermediate plane (4) dividing the distance between the hub disc (1) and the cover disc (2) in the ratio of at least 7:3.
  3. A radial wheel according to Claim 1 or 2, characterised in that the hub disc (1) is flat.
  4. A radial wheel according to any one of Claims 1 to 3, characterised in that the tangent to the cover disc (2) extends in a radial manner to the external edge thereof.
EP94100758A 1993-03-13 1994-01-20 Radial wheel Expired - Lifetime EP0616131B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9303711U DE9303711U1 (en) 1993-03-13 1993-03-13
DE9303711U 1993-03-13

Publications (2)

Publication Number Publication Date
EP0616131A1 EP0616131A1 (en) 1994-09-21
EP0616131B1 true EP0616131B1 (en) 1996-11-20

Family

ID=6890598

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94100758A Expired - Lifetime EP0616131B1 (en) 1993-03-13 1994-01-20 Radial wheel

Country Status (3)

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EP (1) EP0616131B1 (en)
AT (1) ATE145451T1 (en)
DE (2) DE9303711U1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4318580A1 (en) * 1993-06-04 1994-12-08 Sel Alcatel Ag Radial fan
FI122563B (en) 2005-02-21 2012-03-30 Flaekt Woods Ab Centrifugal Impeller
DE102015122132A1 (en) * 2015-12-17 2017-06-22 Ebm-Papst Mulfingen Gmbh & Co. Kg Edgebanding of a rotating element and impeller

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR397702A (en) * 1908-05-28 1909-05-15 James Keith Improvements to rotary fans
GB191321353A (en) * 1913-09-29 1914-03-19 Ralph Hancock Improvements in Centrifugal Fans.
US1341882A (en) * 1915-09-07 1920-06-01 Buffalo Forge Co Centrifugal fan
GB139717A (en) * 1919-07-21 1920-03-11 William Patchett Denton Improvements in and connected with air blowers
DE1063323B (en) * 1957-06-29 1959-08-13 Willi Keil Centrifugal fan or pump
DE1046247B (en) * 1957-12-14 1958-12-11 Winkelstraeter G M B H Geb Impeller of centrifugal blowers and centrifugal fans
US3179329A (en) * 1961-08-16 1965-04-20 Ruth D Mayne Turbine type blower wheel
US3257071A (en) * 1964-06-26 1966-06-21 Rotron Mfg Co Impeller assembly
DE2437001B2 (en) * 1974-08-01 1978-01-26 Wilhelm Gebhardt GmbH, 7112 Waidenburg RADIAL FAN WITH BACK CURVED PROFILED BLADES
DE2940773C2 (en) * 1979-10-08 1986-08-14 Punker GmbH, 2330 Eckernförde High-performance centrifugal fan
ATE13711T1 (en) * 1982-12-29 1985-06-15 Gebhardt Gmbh Wilhelm CENTRIFUGAL FAN WITH BACKWARDS CURVED, PROFILED BLADES.
DE3520218A1 (en) * 1984-06-08 1985-12-12 Hitachi, Ltd., Tokio/Tokyo IMPELLER FOR A RADIAL BLOWER

Also Published As

Publication number Publication date
ATE145451T1 (en) 1996-12-15
DE9303711U1 (en) 1993-05-13
EP0616131A1 (en) 1994-09-21
DE59401057D1 (en) 1997-01-02

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