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WO1996008655A1 - Roue de compresseur a vitesse specifique faible - Google Patents

Roue de compresseur a vitesse specifique faible Download PDF

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Publication number
WO1996008655A1
WO1996008655A1 PCT/EP1995/003606 EP9503606W WO9608655A1 WO 1996008655 A1 WO1996008655 A1 WO 1996008655A1 EP 9503606 W EP9503606 W EP 9503606W WO 9608655 A1 WO9608655 A1 WO 9608655A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
vanes
flow passages
flow
free pitch
Prior art date
Application number
PCT/EP1995/003606
Other languages
English (en)
Inventor
Dan Adler
Original Assignee
Dan Adler
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 Dan Adler filed Critical Dan Adler
Priority to AU36068/95A priority Critical patent/AU3606895A/en
Publication of WO1996008655A1 publication Critical patent/WO1996008655A1/fr

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

  • the invention relates to turbo-comprssors for low discharge at high pressure, particularly to a novel design of impellers for turbo-compressors.
  • the invention relates to impellers for coicpressors adapted to convey a gas, at high Mach numbers, from one point to another and to raise its pressure, pareticularly to compressors designed for compressing a relatively small gas volume to a relatively high pressure.
  • the conventional centrifugal turbo-impeller is provided with a plurality of curved vanes of small thickness with the aim of presenting large fluid passsages.
  • the inlet and outlet ends of the vanes or blades are made as sharp and narrow as possible in order to reduce inlet and outlet losses, as well as blockage, to a minimum.
  • the thin outlet ends of the vanes are also supposed to provide a uniform fluid flow all around the impeller circumference, instead of a flow interrupted by wider vane ends.
  • the actual flow in and around an impeller is not uniform in reality, as will be shown in the following:-
  • FIG. 1 A typical example of a conventional impeller is iilastrated in Figure 1, wherein the impeller is provided with backward-curved vanes, the impeller rotating in the direction of the arrow F.
  • the outflow velocities v 1 to v 7 are shown in the traditional manner, and for simple calculations a median velocity is being chosen up to the present day.
  • modern research has shown that the actual flow through the flow passages between vanes is not gradually decreasing from left to right as shown on the left side of the drawing,, but increases abruptly from low to high velocity at about a third of the outlet path between every two vanes, as shown on the right side of Figure 1, denoted by "1b".
  • the impoller for relatively low discharge at high pressure has been designed with regard of the fact a) that there is no uniform, axisymmetrical flow along the impeller circum ference, even if it is equipped with narrow, sharp-ending vanes, and b) that the width of the flow passage in axial direction cannot be reduced indefinitely, in view of the high friction losses and boundary layer blockage along the impeller sides.
  • a preferred embodiment of the impeller of the present invention designed for high pressure ratio at low discharge is characterized by a flow passage between adjoining vanes which is of substantially constant free pitch between inlet and outlet diameter, or of decreasing free pitch towards the outlet.
  • the vanes in this impeller increase in thickness from a sharp inlet towards the periphery of the impeller, where they may occupy more than one third of the total circumferential length, i.e. the
  • peripheral width of the vane may be considerably larger than the outlet end of the flow passage between adjoining vanes.
  • the impeller vanes are preferably backward curved, but may be radial or forward curved as well. In order to obtain the required high pressure, it is proposed that the impeller has a relatively small diameter and that it is rotated at high revolutions.
  • the impeller may be of any kind used in high-pressure compressors such as radial or mixed-flow, open or closed, provided the vanes are designed in accordance with the present invention.
  • Figure 1 is a cross section of a conventional impeller, showing both theoretical and actual throughflow diagrams
  • Figure 2 is a cross section of an impeller with vanes of increasing thickness in outward direction forming backward curved flow passages of constant free pitch.
  • Figure 3 is a cross section of an impeller similar to that shown in Figure 2, with backward-curved flow passages of converging free pitch,
  • Figure 4 is a cross section of an impeller similar to that shown in Figure 2 , with flow passages of diverging free pitch,
  • Figure 5 is a meridional section of a closed, impeller designed for radial entry and radial outflow between the vanes
  • Figure 6 is a raeridional section of an open impeller designed for axial entry and radial outflow between vanes
  • Figure 7 is a meridional section of a closed impeller including mixed radial and axial flow passages.
  • the standard or conventional impeller shown in Figure 1 has been duly discussed herein before and need not be explained in this section.
  • the impeller shown in Figure 2 shows four vanes 1 extending between an inlet diameter d and an cutlet diameter D and forming four flow passages 2 therebetween.
  • Each vane has a sharp inlet point 3 and gradually increases in thickness to a blunt end of maximum thickness 4 at the periphery of the impeller.
  • the vanes are shown to have backward-curved envelopes 5 and 6 formed by large diameters or otherwise curved lines, so as to effect a smooth fluid flow.
  • the flow passages 2 are of constant free pitch, thus not apt to create flew separation.
  • the impeller shown in meridional section in Figure 5 has been designed for a small discharge at high pressure ratio by employing the vanes and flow passages illustrated in either of the Figures 2, 3 or 4, permitting a flow passage of relative large width in axial direction.
  • the impeller includes a hub 7 and a shroud 8 as well as the flow passages 2 and vanes 1 between shroud and hub, the inlet ends of the vanes being denoted by numeral 3 and the blunt outlet ends by numeral 4.
  • the impeller has an axial entry 9 and a radial outlet 10, while the vanes and flow passages occupy the radial portion only.
  • the impeller shown in Figure 6 is similar in design to that shown in Figure 5, but for the difference of being open without a shroud.
  • the vanes start at the entry 9 in the form of sharp inlet ends 3 and extend to the impeller periphery in tne form of blunt ends 4. Except for the fact that it includes the thick blades and flow passages of narrow free pitch, it is in all other aspects identical with a conventional open impeller.
  • the mixed-flow impeller of Figure 7 includes a hub 7' and a shroud 8' enclosing vanes and flow passages 1 and 2 respectively.
  • the flow passages and vanes extend from the axial entry 9' to the axial-radial outlet 10' and are characterized by the narrow free pitch of the flow passages due to the vanes of increasing thickness in outward direction.
  • An impeller designed for a small air conditioning unit and provided with vanes of increasing thickness similar to that shown in Figure 3 of the drawings, has the following dimensions:-

Landscapes

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

Abstract

Roue d'un compresseur centrifuge conçu pour supporter des pressions élevées avec une décharge relativement faible, caractérisée par une pluralité de passages (2) de flux qui possèdent une inclinaison libre étroite, sont placés entre les ailettes (1) et augmentent en épaisseur à partir d'un orifice d'entrée (3) effilé en direction de la périphérie de la roue, tandis que la largeur des passages est suffisamment grande pour empêcher des pertes élevées par friction ainsi qu'un blocage par des couches limites épaisses. L'inclinaison libre des passages de flux est soit constante, soit décroissante en direction de l'orifice de sortie. Les ailettes (1) sont soit radiales vers l'arrière, soit courbées vers l'avant, tandis que le compresseur peut être à un ou à plusieurs étages selon les performances demandées.
PCT/EP1995/003606 1994-09-13 1995-09-13 Roue de compresseur a vitesse specifique faible WO1996008655A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU36068/95A AU3606895A (en) 1994-09-13 1995-09-13 Low specific speed impeller

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IL110951 1994-09-13
IL11095194A IL110951A0 (en) 1994-09-13 1994-09-13 Turbo machines for high pressure and low discharge

Publications (1)

Publication Number Publication Date
WO1996008655A1 true WO1996008655A1 (fr) 1996-03-21

Family

ID=11066549

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1995/003606 WO1996008655A1 (fr) 1994-09-13 1995-09-13 Roue de compresseur a vitesse specifique faible

Country Status (3)

Country Link
AU (1) AU3606895A (fr)
IL (1) IL110951A0 (fr)
WO (1) WO1996008655A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19647612A1 (de) * 1996-11-18 1998-05-20 Bosch Gmbh Robert Lüfterrad
EP1013938A1 (fr) * 1998-12-18 2000-06-28 Lothar Reckert Rotor de soufflante radiale à vitesse spécifique réduite
EP4368838A1 (fr) * 2022-11-10 2024-05-15 BMTS Technology GmbH & Co. KG Compresseur

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1865918A (en) * 1928-06-30 1932-07-05 Junkers Hugo Impeller and method of making same
DE861142C (de) * 1950-06-25 1952-12-29 Licentia Gmbh Doppelseitig beaufschlagtes Laufrad fuer Kreiselmaschinen, insbesondere fuer Radialverdichter
DE927821C (de) * 1948-10-02 1955-05-16 Demag Ag Turboverdichter-Laufrad
DE2228797A1 (de) * 1972-06-13 1974-01-03 Siemens Ag Hochdruckgeblaese
US3788765A (en) * 1971-11-18 1974-01-29 Laval Turbine Low specific speed compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1865918A (en) * 1928-06-30 1932-07-05 Junkers Hugo Impeller and method of making same
DE927821C (de) * 1948-10-02 1955-05-16 Demag Ag Turboverdichter-Laufrad
DE861142C (de) * 1950-06-25 1952-12-29 Licentia Gmbh Doppelseitig beaufschlagtes Laufrad fuer Kreiselmaschinen, insbesondere fuer Radialverdichter
US3788765A (en) * 1971-11-18 1974-01-29 Laval Turbine Low specific speed compressor
DE2228797A1 (de) * 1972-06-13 1974-01-03 Siemens Ag Hochdruckgeblaese

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19647612A1 (de) * 1996-11-18 1998-05-20 Bosch Gmbh Robert Lüfterrad
EP1013938A1 (fr) * 1998-12-18 2000-06-28 Lothar Reckert Rotor de soufflante radiale à vitesse spécifique réduite
US6340291B1 (en) 1998-12-18 2002-01-22 Lothar Reckert High pressure impeller with high efficiency for small volume flows for radial blowers of different size
EP4368838A1 (fr) * 2022-11-10 2024-05-15 BMTS Technology GmbH & Co. KG Compresseur
WO2024100238A1 (fr) * 2022-11-10 2024-05-16 BMTS Technology GmbH & Co. KG Compresseur

Also Published As

Publication number Publication date
IL110951A0 (en) 1994-11-28
AU3606895A (en) 1996-03-29

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