EP0446900B1 - Compresseur à écoulement mixte - Google Patents

Compresseur à écoulement mixte Download PDF

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Publication number
EP0446900B1
EP0446900B1 EP91103850A EP91103850A EP0446900B1 EP 0446900 B1 EP0446900 B1 EP 0446900B1 EP 91103850 A EP91103850 A EP 91103850A EP 91103850 A EP91103850 A EP 91103850A EP 0446900 B1 EP0446900 B1 EP 0446900B1
Authority
EP
European Patent Office
Prior art keywords
flow
impeller
guide vanes
mixed
outlet
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
EP91103850A
Other languages
German (de)
English (en)
Other versions
EP0446900A1 (fr
Inventor
Hideo Nishida
Hiromi Kobayashi
Haruo Miura
Takeo Takagi
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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 Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0446900A1 publication Critical patent/EP0446900A1/fr
Application granted granted Critical
Publication of EP0446900B1 publication Critical patent/EP0446900B1/fr
Anticipated expiration legal-status Critical
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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/06—Helico-centrifugal 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
    • F04D29/40—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
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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 mixed-flow compressor comprising a mixed-flow impeller, in which the flow path in the meridional plane of the impeller is slanted relative to a radial direction, and a pair of diffuser plates provided downstream of the mixed-flow impeller, such that the inlet portion of the flow path through said diffuser plates is substantially aligned with the outlet flow path of said mixed-flow impeller and the outlet portion of the flow path through said diffuser plates is directed in a radial direction, and guide vanes arranged on one of the diffuser plates circumferentially around the rotary axis of the impeller in a circular row.
  • the GB 693 727 discloses a mixed-flow compressor comprising guide vanes which are attached to the hub and the shroud, the inner diameter of the guides being larger than the outer diameter of the impeller.
  • a mixed-flow impeller in which the outlet of the impeller is slanted from the radial direction.
  • the curvature of a flow path in a meridional plane i.e., a cross section including the rotary shaft center
  • a meridional flow path is decreased, so that the flow may be kept substantially uniform in the widthwise direction at the outlet of the impeller, i.e., at the inlet of the diffuser. It is thus possible to prevent the generation of the flow deflected toward the hub.
  • a mixed-flow compressor comprising a mixed flow diffuser without vanes has an increased length in the axial direction. Therefore, the compressor is large in size and the friction loss in the flow path is high.
  • guide vanes each having a height corresponding to 10 to 50% of the width of the meridional flow path are provided on the hub side of the diffuser.
  • this could not sufficiently attain the object.
  • There are still unsolved problems such as the increase in friction loss and a reduction in critical speed.
  • the problem underlying the invention is to provide a mixed-flow compressor that is small in size and ensures a high performance.
  • the guide vanes the height of which being smaller than the width of the flow path, are provided at the curved portion on the flow path surface of the diffuser plate on the shroud side curved in the radial direction in the vicinity of the outlet of the mixed-flow impeller, and the inlet and outlet angles are equal to the impeller outlet average flow angle at the design point, the flow on the shroud side of the mixed-flow impeller outlet is introduced with almost no shock into the guide vanes. Then, since the fluid introduced into the guide vanes is forcibly led, the fluid will flow without separating away from the wall surface of the shroud side and will reach the guide vane outlet portion.
  • the flow angle of the fluid led by the guide vane is equal to the flow angle of the fluid at the portion where guide vanes are not provided. Also, since at the end of the curved portion, the curvature of the meridional plane flow path is small, the meridional flow velocity is also kept substantially uniform in the widthwise direction. After all, the flow may be kept uniform in the widthwise direction.
  • the guide vanes the height of which is smaller than the width of the flow path, are provided on the surface of the flow path of the diffuser plate on the shroud side bent to the radial direction immediately after the impeller outlet, and the inlet and the outlet vane angle are equal to the impeller outlet average flow angle at the design point, the fluid of the outlet of the mixed-flow impeller on the shroud side is introduced into the guide vanes with almost no shock. Then, since the fluid introduced into the guide vanes is forcibly led by the guide vanes, the fluid will flow without separating from the wall surface of the shroud side and will reach the outlet portion of the guide vanes.
  • the vane angle is equal to the average flow angle of the design point
  • the flow angle of the fluid led by the guide vanes is equal to the flow angle of the fluid at the portion where guide vanes are not provided.
  • the curvature of the meridional plane flow path is small at the outlet of the guide vanes so that the meridional plane flow velocity is also kept substantially uniform in the widthwise direction. After all, the flow is kept constant in the width-wise direction.
  • Fig. 1 is a longitudinal sectional view showing a mixed-flow compressor in accordance with an embodiment of the invention, in which a mixed-flow impeller 1 having a small curvature in a meridional flow path is fixed to a rotary shaft 2 by a nut 3.
  • a pair of diffuser plates 4 and 5 each having a curvature in the vicinity of an outlet of the impeller 1 are provided outside of the impeller 1.
  • the diffuser plates 4 and 5 of the outlet form a diffuser 6 which has a curvature in the vicinity of the impeller 1.
  • One of the diffuser plates 4 is locted on a so-called shroud side, whereas the other of the diffuser plates 5 is located on a hub side.
  • Guide vanes 7 are arranged in a circular row at the curved portion of the flow path surface of the diffuser plate 4.
  • the guide vanes 7 are partially provided in the width-wise direction of the flow path and it is preferable that their height ranges between 20 to 50% of the flow path width.
  • an inlet vane angle ⁇ 1 and an outlet vane angle ⁇ 2 are equal to an average flow angle of the outlet of the mixed-flow impeller 1 at a design point (i.e., an average value of an angle defined by a fluid absolute velocity of the impeller outlet at the design flow rate point with respect to a tangential direction (circumferential direction)).
  • the height of the guide vanes is in the range of 20 to 50% is that the effect preventing reverse flow at the curved portion would be eliminated at the curved portion below 20% and the incidence (or shock) loss at the off-design flow rate point (i.e., a loss generated due to the difference between the flow angle and the vane angle) is increased to lower the performance of the compressor above 50% (for example 100%).
  • a minimum inlet radius r a of the guide vanes 7 is larger than a maximum outlet radius r b of the impeller 1.
  • a casing 8 is provided radially outwardly of the diffuser plates 4 and 5 to define an outlet flow path 9.
  • a suction pipe 10 is fixed on a gas suction side of the diffuser plate 4.
  • the gas is sucked into the impeller 1 through the suction pipe 10 and then gas is discharged into the diffuser 6 from the impeller 1.
  • the gas flow is decelerated within the diffuser 6 and is introduced into the casing 8.
  • the flow at the outlet of the impeller 1 becomes uniform in the widthwise direction. Accordingly, the flow angle of the fluid on the side of the diffuser plate 4 at the outlet of the impeller 1 is substantially equal to the average flow angle in the widthwise direction, so that the fluid on the side of the diffuser plate 4 is introduced into the guide vanes 7 with almost no shock.
  • the fluid may flow without separating away from the wall surface of the diffuser plate 4 and reach the outlet portion of the guide vanes 7. Since the curvature of the meridional plane flow path is small at the outlet portion of the guide vanes 7, i.e., the terminal portion of the curvature, the flow is forcibly led by the guide vanes 7 (whose height is 40% of the the diffuser 6) and becomes uniform in the widthwise direction as shown in Fig. 3.
  • Fig. 4 shows the specific advantage according to this embodiment and the adiabatic efficiency ratio between a conventional mixed-flow compressor using the radially curved diffuser without any vanes and the compressor according to the present embodiment.
  • Curve F indicates the adiabatic efficiency ratio at each suction flow rate of the conventional mixed-flow compressor
  • curve E indicates the adiabatic efficiency ratio at each suction flow rate of the mixed-flow compressor according to the present embodiment.
  • the reference value is defined by regarding as 1.0 the maximum value of the adiabatic efficiency of the mixed-flow compressor according to the present embodiment. As is apparent from Fig. 4, it is possible to considerably improve the adiabatic efficiency ratio in comparison with the conventional mixed-flow compressor having the diffuser without vanes.
  • the present embodiment since according to the present embodiment it is possible to prevent the separation of the flow at the curved portion of the diffuser, it is possible to considerably reduce the loss at the curved portion and to make uniform the flow in the widthwise direction at the outlet portion of the guide vanes, thereby largely enhancing the performance of the diffuser after the outlet portion of the guide vanes.
  • the meridional plane flow path of the diffuser since the meridional plane flow path of the diffuser is curved in the radial direction, the length of the flow path may be reduced in comparison with that of the conventional mixed-flow diffuser and the frictional loss may also be reduced. As a result, the performance of the mixed-flow compressor may be largely enhanced in comparison with the conventional compressor.
  • the rotary shaft of the compressor may be shortened, the critical speed of the rotor may be increased.
  • Fig. 5 is an illustration of the assemblage of the compressor of the embodiment shown in Fig. 1.
  • the mixed-flow impeller 1 is fitted with the rotary shaft 2 by moving the impeller in the axial direction as indicated by the arrow A.
  • the impeller 1 is fastened to the rotary shaft 2 by the nut 3.
  • the casing 8 integral with the diffuser plate 4 on which the guide vanes 7 are mounted is moved in the axial direction as indicated by the arrow B and is inserted into a fit portion 12 of the diffuser plate 5 which has been coupled with the rotary shaft 2 through bearings.
  • the minimum inlet diameter of the guide vanes 7 is larger than the maximum outlet diameter of the impeller 1, it is also advantageously easy to assemble the compressor.
  • Fig. 6 is a longitudinal view showing another embodiment.
  • the diffuser 6 is composed of a pair of diffuser plates 4 and 5 each having a curvature in the meridional plane and guide vanes 7 arranged in a circular row at the curved portion on the flow path surface of the diffuser plate 4.
  • the inlet angle and the outlet angle of the guide vanes 7 are substantially equal to an impeller outlet average flow angle at the design point.
  • the height of the guide vanes 7 ranges between 20 to 50% of the flow path width. Then, the inlet radius r a of the guide vanes 7 is larger than the outlet maximum radius r b of the impeller 1 and is kept constant.
  • the fluid on the side of the diffuser plate 4 at the outlet of the mixed-flow impeller 1 is led by the guide vanes without separating away from the wall surface and reaches the outlet of the curved portion.
  • the flow is kept substantially constant in the widthwise direction at the outlet of the curved portion. Accordingly, in the same manner as in Fig. 1, the performance of the diffuser 6 is considerably enhanced. Furthermore, since the meridional plane flow path is curved in the radial direction, the axial length of the compressor is shortened. Therefore, also in this embodiment, it is possible to make the mixed-flow compressor small in size and it is also possible to increase the critical speed of the rotor.
  • the inlet radius of the guide vanes 7 is larger than the maximum outlet radius of the impeller 1 and kept constant, it is possible to facilitate the assemblage of the compressor and easier to manufacture the diffuser than in the case of Fig. 1.
  • Fig. 7 is a longitudinal sectional view showing still another embodiment.
  • Fig. 8 is a cross-sectional view taken along the line VIII-VIII of Fig. 7.
  • the diffuser 6 is composed of a pair of diffuser plates 4 and 5 each having a curvature in the meridional plane and guide vanes 11 arranged in a circular row on the flow path surface of the diffuser plate 4.
  • the guide vanes 11 are provided not only on the curved portion of the flow path surface of the diffuser plate 4 but also on the parallel portion downstream of the curved portion.
  • the inlet and outlet angles are substantially equal to the impeller outlet average flow angle at the design point.
  • the height of the guide vanes 11 ranges between 20 to 50% of the flow path width.
  • the inlet radius r a of the guide vanes 11 is larger than the outlet maximum radius r b of the impeller 1 and is kept constant.
  • the fluid on the side of the diffuser plate 4 at the outlet of the mixed-flow impeller 1 is led by the guide vanes 11 without separating away from the flow path surface and reaches the outlet of the curved portion.
  • the flow is made substantially uniform in the widthwise direction.
  • no guide vanes 11 are provided at the parallel portion downstream of the curved portion, it is possible that the distortion of inlet flow is increased toward the downstream side.
  • the guide vanes 11 are provided to extend to the parallel portion to thereby keep uniform the flow along the parallel portion, it is also possible to enhance the diffuser performance, i.e., the performance of the mixed-flow compressor in comparison with the case shown in Fig. 1.
  • the axial length of the compressor may be reduced. It is therefore possible to make small the mixed-flow compressor and to increase the critical speed of the rotor also in this embodiment.
  • Fig. 9 is a longitudinal sectional view according to still another embodiment.
  • the diffuser 6 is composed of a diffuser plate 5 having a curvature in the meridional plane, a diffuser plate 4 bent in the radial direction immediately after the inlet thereof, and guide vanes 11 arranged in a circular row on the flow path surface of the diffuser plate 4.
  • the guide vanes 11 are provided at a section between the inlet and outlet of the diffuser 6.
  • the inlet and outlet angles are substantially the same as the impeller outlet average flow angle at the design point.
  • the height of the guide vanes 11 is in the range of 20 to 50% of the flow path width.
  • the inlet radius r a of the guide vanes 11 is larger than the outlet maximum radius r b of the impeller 1 and is kept constant in the widthwise direction.
  • this mixed-flow compressor in the same manner as in Fig. 1, since the fluid on the side of the diffuser plate 4 at the outlet of the mixed-flow impeller 1 is led by the guide vanes 11 without separating away from the flow path surfaces, the flow within the diffuser is kept substantially uniform in the widthwise direction. Accordingly, the performance of the diffuser 6 is largely improved. Furthermore, since the meridional plane flow path of the diffuser 6 is curved in the radial direction immediately after the inlet, the axial length of the compressor is shorter than that shown in Fig. 1. Accordingly, it is possible to make smaller the mixed-flow compressor and to increase the critical speed of the rotor in this embodiment.

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

Claims (4)

  1. Compresseur à flux mixte comprenant
    - un rotor à flux mixte (1), dans lequel le trajet d'écoulement dans le plan méridional du rotor (1) est incliné par rapport à une direction radiale, et
    - un couple de plaques de diffuseur (4,5) disposées en aval du rotor à flux mixte (1) de sorte que la partie d'entrée du trajet d'écoulement au travers desdites plaques de diffuseur (4,5) est sensiblement alignée avec le trajet d'écoulement de sortie dudit rotor à flux mixte (1) et que la partie de sortie du trajet d'écoulement passant entre lesdites plaques de diffuseur (4,5) est dirigée dans une direction radiale, et
    - des aubes directrices (7) disposées sur l'une des plaques de diffuseur (4), circonférentiellement autour de l'axe de rotation du rotor, suivant une rangée circulaire,
    caractérisé en ce que
    - le trajet d'écoulement du diffuseur est incurvé dans un plan méridional au voisinage de la sortie dudit rotor à flux mixte (1), et
    - les aubes directrices (7) sont disposées sur la plaque de diffuseur (4) sur le côté enveloppe de sorte que, dans la direction radiale du rotor (1), le rayon minimum d'entrée (ra) des aubes diretrices (7) est supérieur au rayon maximum (rb) dudit rotor à flux mixte (1),
    - la hauteur des aubes directrices (7) dans la direction axiale du rotor (1) étant inférieure à la distance entre les plaques de diffuseur (4,5).
  2. Compresseur à flux mixte selon la revendication 1, caractérisé en ce que les aubes directrices (7) s'étendent jusqu'à la partie de sortie dudit trajet d'écoulement entre les plaques de diffuseur (4,5).
  3. Compresseur selon la revendication 1 ou 2, caractérisé en ce que l'angle d'entrée (α₁) des aubes directrices (7,11) par rapport à une tangente à un cercle passant par les extrémités amont respectives desdites aubes directrices (7,11) et l'angle de sortie (α₂) des aubes directrices (7,11) par rapport a une tangente à un cercle passant par les extrémités aval respectives desdites aubes directrices (7,11) sont sensiblement égaux.
  4. Compresseur selon l'une quelconque des revendications précédentes, caractérisé en ce que la hauteur desdites aubes directrices (7,11) dans la direction axiale du rotor (1) est comprise entre 20 et 50 % de la largeur du trajet d'écoulement.
EP91103850A 1990-03-14 1991-03-13 Compresseur à écoulement mixte Expired - Lifetime EP0446900B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2060973A JPH07103874B2 (ja) 1990-03-14 1990-03-14 斜流圧縮機
JP60973/90 1990-03-14

Publications (2)

Publication Number Publication Date
EP0446900A1 EP0446900A1 (fr) 1991-09-18
EP0446900B1 true EP0446900B1 (fr) 1994-12-28

Family

ID=13157878

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91103850A Expired - Lifetime EP0446900B1 (fr) 1990-03-14 1991-03-13 Compresseur à écoulement mixte

Country Status (3)

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EP (1) EP0446900B1 (fr)
JP (1) JPH07103874B2 (fr)
DE (1) DE69106179T2 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5316441A (en) * 1993-02-03 1994-05-31 Dresser-Rand Company Multi-row rib diffuser
JP3153409B2 (ja) * 1994-03-18 2001-04-09 株式会社日立製作所 遠心圧縮機の製作方法
JPH11117898A (ja) * 1997-10-09 1999-04-27 Ebara Corp ターボ機械
DE102008017121A1 (de) * 2008-04-02 2009-10-08 Behr Gmbh & Co. Kg Gebläsegehäuse
JP5905268B2 (ja) * 2012-01-17 2016-04-20 三菱重工業株式会社 遠心圧縮機
US10280936B2 (en) 2012-07-06 2019-05-07 Toyota Jidosha Kabushiki Kaisha Compressor for supercharger of internal combustion engine
ITCO20130037A1 (it) * 2013-09-12 2015-03-13 Internat Consortium For Advanc Ed Design Girante resistente al liquido per compressori centrifughi/liquid tolerant impeller for centrifugal compressors
DE102016108762A1 (de) 2016-05-12 2017-11-16 Man Diesel & Turbo Se Radialverdichter
ITUA20164221A1 (it) * 2016-06-09 2017-12-09 Fieni Giovanni S R L Gruppo di ventilazione per atomizzazione ed irrorazione
EP3760876A1 (fr) 2019-07-04 2021-01-06 Siemens Aktiengesellschaft Diffuseur pour une turbomachine
EP3805572A1 (fr) 2019-10-07 2021-04-14 Siemens Aktiengesellschaft Diffuseur, turbocompresseur radial
JP2021124046A (ja) * 2020-02-04 2021-08-30 三菱重工業株式会社 遠心圧縮機のディフューザ構造及び遠心圧縮機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB693727A (en) * 1950-01-25 1953-07-08 Power Jets Res & Dev Ltd Improvements relating to bladed rotary fluid-flow machines
JPS53123607U (fr) * 1977-03-09 1978-10-02
JPS608359B2 (ja) * 1979-08-01 1985-03-02 株式会社日立製作所 遠心圧縮機のディフュ−ザ
US4626168A (en) * 1985-05-15 1986-12-02 Dresser Industries, Inc. Diffuser for centrifugal compressors and the like
JPH0658116B2 (ja) * 1986-08-06 1994-08-03 松下電器産業株式会社 送風装置
US4850795A (en) * 1988-02-08 1989-07-25 Dresser-Rand Company Diffuser having ribbed vanes followed by full vanes
US4900225A (en) * 1989-03-08 1990-02-13 Union Carbide Corporation Centrifugal compressor having hybrid diffuser and excess area diffusing volute

Also Published As

Publication number Publication date
JPH07103874B2 (ja) 1995-11-08
JPH03264796A (ja) 1991-11-26
DE69106179T2 (de) 1995-07-27
EP0446900A1 (fr) 1991-09-18
DE69106179D1 (de) 1995-02-09

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