KR20110109056A - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

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Publication number
KR20110109056A
KR20110109056A KR1020100028604A KR20100028604A KR20110109056A KR 20110109056 A KR20110109056 A KR 20110109056A KR 1020100028604 A KR1020100028604 A KR 1020100028604A KR 20100028604 A KR20100028604 A KR 20100028604A KR 20110109056 A KR20110109056 A KR 20110109056A
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KR
South Korea
Prior art keywords
casing
diffuser
centrifugal compressor
impeller
diffuser vanes
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Application number
KR1020100028604A
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Korean (ko)
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KR101429516B1 (en
Inventor
김승민
Original Assignee
삼성테크윈 주식회사
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Priority to KR1020100028604A priority Critical patent/KR101429516B1/en
Publication of KR20110109056A publication Critical patent/KR20110109056A/en
Application granted granted Critical
Publication of KR101429516B1 publication Critical patent/KR101429516B1/en

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    • 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
    • F04D17/08—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
    • F04D29/26—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
    • 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
    • F04D29/30—Vanes
    • 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
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid 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
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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

Abstract

The present invention relates to a centrifugal compressor, and the centrifugal compressor according to the present invention includes a casing, an impeller rotatably disposed in the casing, and a rotatable arrangement along the periphery of the impeller within the casing. And a plurality of first diffuser vanes disposed between the impeller and the first diffuser vanes and disposed along a circumference of the impeller and fixed to the inside of the casing.

Description

Centrifugal Compressor {Centrifugal Compressor}

The present invention relates to a centrifugal compressor, and more particularly, to a centrifugal compressor having a variable diffuser vane.

Centrifugal compressors are devices that allow fluids to be compressed by centrifugal force by passing them through an impeller rotating at high speed.

Such centrifugal compressors generally have a plurality of diffuser vanes on a circumference around the impeller. The radially moved fluid by the impeller is decelerated by the diffuser vanes and compressed with increasing pressure.

On the other hand, the performance characteristics of the centrifugal compressor, that is, the compression ratio and the efficiency, etc. vary depending on the shape and arrangement of the diffuser vanes. Accordingly, centrifugal compressors having variable diffuser vanes are known to be able to use centrifugal compressors for various use conditions.

Since the variable diffuser vanes are rotatably disposed inside the casing of the centrifugal compressor, the compression characteristics of the centrifugal compressor can be effectively changed according to the situation by appropriately rotating the variable diffuser vanes as the temperature of the inflow fluid changes. That is, a centrifugal compressor having a variable diffuser vane has an advantage of wide operating range.

However, since the variable diffuser vanes are rotatably disposed inside the casing, they are inevitably spaced apart from the casing at predetermined intervals. The gap between the variable diffuser vane and the casing is caused by errors in manufacturing and assembly, and thus it is practically impossible to completely eliminate it. The fluid may flow in such a gap, in which case there is a problem in that the compression characteristics of the centrifugal compressor appear or the performance of the centrifugal compressor is deteriorated.

In particular, when the gap between the variable diffuser vane and the inner side of the casing is large or the velocity of the fluid passing through the variable diffuser vanes is high, more fluid is drawn out through the gap, so that the compression characteristics of the centrifugal compressor and The decrease in performance is even greater.

SUMMARY OF THE INVENTION In order to solve the above problems, the present invention provides a centrifugal compressor having a variable diffuser vane, which can effectively suppress a reduction in compression ratio and efficiency due to a gap between a variable diffuser vane and a casing while having a wide operating range. There is this.

In order to achieve the above object, the centrifugal compressor according to the present invention includes a casing, an impeller rotatably disposed inside the casing, and disposed along the periphery of the impeller inside the casing, each of which is rotatably disposed. And a plurality of first diffuser vanes, and a plurality of second diffuser vanes disposed between the impeller and the first diffuser vanes along a circumference of the impeller and fixedly disposed inside the casing.

According to the centrifugal compressor according to the present invention, it is effectively suppressed that the compression ratio and the efficiency are reduced due to the gap between the variable diffuser vanes and the casing, while the operating range is wide with the variable diffuser vanes.

1 is a schematic cross-sectional view of a centrifugal compressor according to an embodiment of the present invention.
FIG. 2 is a schematic enlarged view of portion II of FIG. 1.
FIG. 3 is a schematic enlarged view of portion III of FIG. 1.
4 is a schematic plan view of a part of a conventional centrifugal compressor.
FIG. 5 is a schematic plan view of some components of the centrifugal compressor shown in FIG. 1.
6 is a graph schematically illustrating a relationship between a flow rate and a compression ratio according to a change in the gap between the variable diffuser vane and the casing in a conventional centrifugal compressor.
FIG. 7 is a graph schematically illustrating a relationship between a flow rate and an efficiency according to a change in a gap between a variable diffuser vane and a casing in a conventional centrifugal compressor.
8 is a graph schematically illustrating that a relationship between a flow rate and a compression ratio is changed according to a change in a gap between a variable diffuser vane and a casing in a centrifugal compressor according to an embodiment of the present invention.
9 is a graph schematically illustrating a relationship between a flow rate and an efficiency according to a change in a gap between a variable diffuser vane and a casing in a centrifugal compressor according to an embodiment of the present invention.
10 is a schematic cross-sectional view of a centrifugal compressor according to another embodiment of the present invention.

Hereinafter, a centrifugal compressor according to an embodiment of the present invention will be described with reference to the drawings.

1 is a schematic cross-sectional view of a centrifugal compressor according to an embodiment of the present invention, FIG. 2 is a schematic enlarged view of part II of FIG. 1, and FIG. 3 is a schematic enlarged view of part III of FIG. 1. 4 is a schematic plan view of some components of a conventional centrifugal compressor, and FIG. 5 is a schematic plan view of some components of the centrifugal compressor shown in FIG. 6 is a graph schematically illustrating a relationship between a flow rate and a compression ratio according to a change in the gap between the variable diffuser vane and the casing in a conventional centrifugal compressor. FIG. 7 is a graph schematically illustrating a relationship between a flow rate and an efficiency according to a change in a gap between a variable diffuser vane and a casing in a conventional centrifugal compressor. 8 is a graph schematically illustrating that a relationship between a flow rate and a compression ratio is changed according to a change in a gap between a variable diffuser vane and a casing in a centrifugal compressor according to an embodiment of the present invention. 9 is a graph schematically illustrating a relationship between a flow rate and an efficiency according to a change in a gap between a variable diffuser vane and a casing in a centrifugal compressor according to an embodiment of the present invention.

1 to 3 and 5, the centrifugal compressor 1 according to the present embodiment includes a casing 100, an impeller 200, a first diffuser vane 300, and a second diffuser vane 400. do.

The casing 100 has an inner space 150, and has an inlet 112 through which fluid is introduced and an outlet (not shown) through which the introduced fluid flows out. The casing 100 in this embodiment has a shroud 110 and a volute 120. Inlet 112 is provided in the shroud 110, the volute 120 is disposed around the shroud (110). The fluid introduced into the inlet 112 is moved to the volute 120 through the inside of the shroud 110 and exits the centrifugal compressor 1 through an outlet (not shown) formed in the volute 120.

The impeller 200 is rotatably disposed in the inner space 150 of the casing, that is, the inner space of the shroud 110. The rotating shaft 220 of the impeller 200 is coupled to the casing 100 by a mechanical seal (not shown), so that the fluid is rotatable with respect to the casing 100 but does not leak to the coupling portion. Impeller 200 has impeller vanes 210 disposed radially about its center of rotation axis C1. Therefore, when the impeller 200 rotates, the inflow fluid is forced to move radially by the impeller vane 210.

A plurality of first diffuser vanes 300 are disposed in the inner space 150 of the casing 100, that is, inside the shroud 110. Referring to FIG. 4, the first diffuser vanes 300 are arranged to draw a circumference along the circumference of the impeller 200, and extend in a direction away from the impeller 200. The first diffuser vane 300 is a variable diffuser vane and is rotatably disposed at a predetermined angle with respect to the casing 100 about its rotation axis 310.

Referring to FIG. 2, the rotation shaft 310 of the first diffuser vane 300 is rotatably coupled to the casing 100, and the rotation center axis line C2 of the first diffuser vane 300 is rotated with the rotation center axis line C1 of the impeller 200. Arranged in parallel. One side of the rotation shaft 310 of the first diffuser vanes 300 is connected to a driving means (not shown) disposed outside the casing 100 so that the first diffuser vanes 300 rotate. Meanwhile, a gap may be formed between the first diffuser vane 300 and the inner circumferential surface 102 of the casing 100 due to a manufacturing or assembly error. That is, the first diffuser vanes 300 and the casing 100 may be spaced at a predetermined spacing d.

Meanwhile, the rotation angle of the first diffuser vane 300 is appropriately adjusted in consideration of the temperature, compression ratio, and efficiency of the fluid flowing into the centrifugal compressor.

The second diffuser vane 400 is disposed in the inner space 150 of the casing 100, that is, the shroud 110, between the impeller 200 and the first diffuser vane 300. The second diffuser vane 400 is arranged to draw a circumference along the inner circumference of the first diffuser vane 100 and the outer circumference of the impeller 200. That is, the first diffuser vanes 300 and the second diffuser vanes 400 are arranged in the shape of drawing concentric circles about the impeller 200.

Each second diffuser vane 400 is disposed to extend in a direction away from the impeller 200, and is fixed to be in close contact with the inner surface of the housing 100. The second diffuser vane 400 may be manufactured integrally with the casing 100, that is, the shroud 110, and fixed to the casing 100, or may be welded to the inner surface 102 of the casing 100 to allow the inside of the casing to be fixed. It may be fixed to the side. Since the second diffuser vane 400 is in close contact with the inner side surface 102 of the casing 100, there is no gap between the second diffuser vane 400 and the inner side surface 102 of the casing 100. Thus, fluid cannot escape between the second diffuser vanes 400 and the inner surface 102 of the casing 100.

In general, the higher the solididy of the diffuser vanes in the centrifugal compressor, the higher the efficiency. The higher the solidity of the diffuser vanes arranged outside, the higher the efficiency. Therefore, in the centrifugal compressor 1 according to the present embodiment, the extension length of the first diffuser vanes 300 is longer than the extension length of the second diffuser vanes 400, thereby effectively increasing the efficiency.

Next, the operation form and effect of the centrifugal compressor 1 which concerns on a present Example are demonstrated.

Referring to FIG. 5, when the impeller 200 rotates, the fluid introduced into the inlet 112 is forced to move radially as indicated by the solid arrow. The radially pressurized fluid from the impeller 200 flows through the second diffuser vane 400 and the first diffuser vane 100 in order into the volute 120. In this process, the fluid passes between the second diffuser vanes 400 and between the first diffuser vanes 300 to decrease the speed and increase the pressure.

Meanwhile, referring to FIG. 4, the conventional centrifugal compressor has a first diffuser vane 300 that is a variable vane, but does not include a second diffuser vane fixedly disposed inside the first diffuser vane 300. In the course of the fluid passing between the first diffuser vanes 300, some of the fluid exits into the gap between the first diffuser vanes 300 and the casing 100. Conventional centrifugal compressors do not have a second diffuser vane, so the speed of the fluid passing between the first diffuser vanes 300 is high. Therefore, even if the gap between the first diffuser vanes 300 and the casing 100 is small, a large amount of fluid escapes into the gap. That is, as indicated by the dashed arrows in FIG. 4, a large amount of fluid is moved from the high pressure side of the first diffuser vane 300 to the low pressure side through the gap.

As described above, the conventional centrifugal compressor has a large amount of fluid that escapes into the gap between the first diffuser vane 300 and the inner surface 112 of the casing 100, thereby affecting the compression characteristics and the efficiency of the centrifugal compressor 1. The larger the spaced interval between the first diffuser vanes 300 and the casing 100, the faster the velocity of the fluid passing through the first diffuser vanes 300 increases the amount of fluid that moves to the gap, so that the centrifugal compressor ( The compression characteristics and the efficiency of 1) are greatly changed.

However, since the centrifugal compressor 1 according to the present embodiment has a second diffuser vane 400 between the first diffuser vanes 300 and the impeller 200, unlike the conventional centrifugal compressors, the fluid has a first diffuser vane ( The speed is primarily reduced before entering between 300). Thus, the amount of fluid moving in the gap between the first diffuser vane 300 and the inner side surface 102 of the casing 100 is effectively reduced. As a result, the centrifugal compressor 1 according to the present embodiment has an advantage in that the compression characteristics and the efficiency are not greatly changed even if a slight gap is formed between the first diffuser vanes 300 and the housing 100.

The results of numerical analysis to support this are shown in FIGS. 6 to 9.

6 and 7 as a result of the numerical analysis of the conventional centrifugal compressor lacking the second diffuser vanes 400 in the centrifugal compressor 1 according to the present embodiment, the second diffuser vanes 300 ) And the relationship between the flow rate and the compression ratio, the flow rate, and the isentropic efficiency while varying the separation gap d between the inner circumferential surface 102 of the casing 100. 6 and 7, it can be seen that as the separation interval d is changed, the compression ratio and the isentropic efficiency are different for the same flow rate. The performance characteristics of the centrifugal compressor are not significantly different as compared to the case in which the separation distance d of the first diffuser vane 300 and the casing 100 is 0.05 mm, but the separation distance d is 0.05. It can be seen that the performance characteristics of the centrifugal compressor change significantly as it exceeds mm. Therefore, in order to maintain the performance characteristics of the centrifugal compressor (1), the spacing (d) of the first diffuser vanes 300 and the casing 100 should be maintained within 0.05 mm. However, in reality, it is very difficult to manufacture a centrifugal compressor such that the spacing d between the first diffuser vanes 300 and the casing 100 is within 0.05 mm.

Meanwhile, FIGS. 8 and 9 show the first diffuser vane as a result of numerical analysis of the centrifugal compressor 1 according to the present embodiment having the second diffuser vane 400 together with the first diffuser vane 300. The relationship between the flow rate and the compression ratio, the flow rate, and isentropic efficiency is shown while varying the spacing d between the inner peripheral surface 102 of the casing 100 and 300. Referring to FIGS. 8 and 9, the centrifugal compressor 1 according to the present embodiment has a flow rate for the flow rate even when the distance d between the first diffuser vane 300 and the casing 100 is 0.05 mm to 0.4 mm. It can be seen that the compression ratio and isentropic efficiency are not significantly different from the case where there is no spacing (d).

In other words, the performance characteristics of the centrifugal compressor 1 according to the present embodiment are maintained almost constant within 0.4 mm between the first diffuser vane 300 and the casing 100. Therefore, the centrifugal compressor 1 according to the present embodiment can effectively suppress the change in the performance characteristics even if a gap occurs between the first diffuser vane 300 and the housing 100 due to manufacturing errors.

Next, a centrifugal compressor according to another embodiment of the present invention will be described with reference to the drawings.

FIG. 10 shows a casing 100, an impeller 200, a first diffuser vane 300, and a second centrifugal compressor 2 according to another embodiment of the present invention, similar to the centrifugal compressor 1 according to the above-described embodiment. A diffuser vane 400 is provided, and a third diffuser vane 800 is additionally provided. In this embodiment, since the configuration having the same member number as the centrifugal compressor 2 according to the embodiment described above is substantially the same configuration, a detailed description thereof will be omitted.

Referring to FIG. 10, the third diffuser vanes 800 are disposed along the outer circumference of the first diffuser vanes 300 and are rotatable in the inner space 150 of the casing 100 like the first diffuser vanes 300. Variable diffuser vanes. The third diffuser vanes 800 are disposed between the first diffuser vanes 300 and the volute 120, and likewise the first diffuser vanes 300 may change their arrangement. Therefore, in the centrifugal compressor 2 according to the present embodiment, the first diffuser vanes 300 and the second diffuser vanes 800 may be operated together to increase the variation in performance characteristics thereof.

In the centrifugal compressor 1 according to the present embodiment, since the second diffuser vanes 400 are disposed around the inner periphery of the first diffuser vanes 300, the first diffuser vanes 300 and the third diffuser vanes 800 are disposed. Reduce the speed of the fluid passing through it. Thus, the amount of fluid that escapes into the gap between the first diffuser vanes 300, the third diffuser vanes 800, and the inner surface 102 of the casing 100 is effectively reduced. Therefore, even if a small gap occurs due to assembly or fabrication error, etc., the centrifugal compressor 2 according to the present embodiment is not significantly affected by the performance characteristics.

Meanwhile, in the centrifugal compressors 1 and 2 according to the embodiment, the first diffuser vanes 300 are described to be formed longer than the second diffuser vanes 400. However, the first diffuser vanes 300 are different from each other. The length of the second diffuser vane 400 may be equal to or smaller than that of the second diffuser vane 400.

Although the centrifugal compressor according to some embodiments of the present invention has been described above, the present invention is not limited thereto and may be embodied in various forms within the scope of the technical idea of the present invention.

1,2 ... centrifugal compressor 100 ... casing
110 ... shroud 112 ... inlet
120 ... Volute 200 ... Impeller
210 ... impeller vanes 220 ... axis of rotation
300 ... first diffuser vanes 400 ... second diffuser vanes
800 ... third diffuser vane C1 ... impeller rotational axis
C2 ... first diffuser vane center of rotation axis
C3 ... 3rd diffuser vane center of rotation axis

Claims (5)

Casing,
An impeller rotatably disposed inside the casing;
A plurality of first diffuser vanes disposed along the circumference of the impeller in the casing, each of which is rotatably disposed;
And a plurality of second diffuser vanes disposed between the impeller and the first diffuser vanes along a circumference of the impeller and fixedly disposed in the casing. The method of claim 1,
The second diffuser vane is in close contact with the inner surface of the casing. The method of claim 1,
The first diffuser vanes,
Centrifugal compressors are spaced apart from the inner surface of the casing at intervals of 0.05 mm to 4 mm. The method of claim 1,
The second diffuser vanes,
A centrifugal compressor whose extension length is longer than the extension length of the first diffuser vane. The method of claim 1,
And a plurality of third diffuser vanes disposed along an outer circumference of the first diffuser vane and rotatably disposed in the casing.
KR1020100028604A 2010-03-30 2010-03-30 Centrifugal Compressor KR101429516B1 (en)

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Application Number Priority Date Filing Date Title
KR1020100028604A KR101429516B1 (en) 2010-03-30 2010-03-30 Centrifugal Compressor

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Application Number Priority Date Filing Date Title
KR1020100028604A KR101429516B1 (en) 2010-03-30 2010-03-30 Centrifugal Compressor

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KR20110109056A true KR20110109056A (en) 2011-10-06
KR101429516B1 KR101429516B1 (en) 2014-08-14

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104613019A (en) * 2014-11-28 2015-05-13 江苏大学 Centrifugal impeller back guide blade with self-adaptation function

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100433324B1 (en) 2001-07-16 2004-05-27 미츠비시 쥬고교 가부시키가이샤 Centrifugal compressor
KR100700541B1 (en) 2005-07-11 2007-03-28 엘지전자 주식회사 Guide vane for the fan-motor of a vacuum cleaner
JP2009270467A (en) 2008-05-06 2009-11-19 Toyota Motor Corp Centrifugal compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104613019A (en) * 2014-11-28 2015-05-13 江苏大学 Centrifugal impeller back guide blade with self-adaptation function

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