WO1989012174A1 - Guide vane for an axial fan - Google Patents

Guide vane for an axial fan Download PDF

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Publication number
WO1989012174A1
WO1989012174A1 PCT/SE1989/000324 SE8900324W WO8912174A1 WO 1989012174 A1 WO1989012174 A1 WO 1989012174A1 SE 8900324 W SE8900324 W SE 8900324W WO 8912174 A1 WO8912174 A1 WO 8912174A1
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WO
WIPO (PCT)
Prior art keywords
guide vane
fan
edge
condition
vane
Prior art date
Application number
PCT/SE1989/000324
Other languages
French (fr)
Inventor
Anders Bengtsson
Erik BÖÖS
Original Assignee
ABB Fläkt AB
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
Family has litigation
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Application filed by ABB Fläkt AB filed Critical ABB Fläkt AB
Priority to DE68915278T priority Critical patent/DE68915278T2/en
Priority to AT8989906852T priority patent/ATE105609T1/en
Priority to UA4831937A priority patent/UA12318A/en
Priority to BR898907459A priority patent/BR8907459A/en
Priority to EP89906852A priority patent/EP0418303B1/en
Publication of WO1989012174A1 publication Critical patent/WO1989012174A1/en
Priority to DK199002842A priority patent/DK173521B1/en
Priority to FI905984A priority patent/FI104509B/en
Priority to NO905297A priority patent/NO170738C/en
Priority to SU904831937A priority patent/RU1834989C/en

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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/542—Bladed diffusers
    • F04D29/544—Blade shapes

Definitions

  • the present invention relates to a guide vane for an axial fan.
  • Fi gure 1 thus illustrates the result of measurements made with an axial fan.
  • the flow direction angle towards the central axis is greater at the top and root of the blade, and the angle passes through a minimum value therebetween.
  • the exact appearance of the graph is affected by such parameters as the blade angles on the impeller and the selected operat ⁇ ing point in the corresponding fan diagram (pressure flow diagram), but the shape of the graph is gualitively the same, with a mini, um between the posi ⁇ tions of the blade root and top.
  • guide vanes In attempts to adapt the inlet angle of the guide vane to the rotation component, which varies radially, guide vanes have been produced with varying curvature, which requires a very complicated manufacturing technique, how ⁇ ever.
  • Guide vanes have also been made with an oblique edge between the inner and outer longitudinal edges of the guide vane, so that the arcuate length of the guide vane along the inner edge is longer than the arcuate length along the radially outer edge. For a constant curvature of the guide vane there is thus obtained a greater inlet angle at the radially inward portion of the guide vane than at its radially- outward portion.
  • the object of the present invention is to provide a new guide vane, starting from the above-mentioned knowledge of the radial variation of the rotation, which vane is adapted on its inlet side to the direction of the impinging gas in a considerably improved way along the entire radial e- x ension of the guide vane, while the guide vane is simple and cheap to manufacture.
  • the vane By giving the edge of the vane portion facing towards the axial rotor a configuration substantially following the variation of the rotation illustrated in Figure 1, the vane can be produced with single curvature and simultaneously obtains excellent adaption of the inlet angle to the direction of the impinging gas at every point.
  • the inlet angle ⁇ j at the radially inward portion or root portion meets the condition: 40° ⁇ ⁇ £ ⁇ _ ⁇ 70° preferably
  • the ratio between the radius of curvature R and the length ⁇ of the radially inward edge of the guide vane meets the condition: 0,83 ⁇ R/Li ⁇ 1,45 preferably 0,83 ⁇ R/L ⁇ ⁇ 1,10.
  • the relationship between the length ⁇ of the radially inward edge of the guide vane and the length L 2 of the guide vane at the level of the web meets the condition: and the web level is given by the condition: 0,4 ⁇ B_/H 2 ⁇ 0,9 preferably where H denotes the height for the web position from the radially inward edge and ⁇ 2 the total height of the guide vane.
  • the inlet angle of the guide vane at the vane top must be related, e.g.
  • Figure 1 illustrates the radial variation of the angle between the flow direction and the central axis from the blade root to the blade top.
  • Figure 2 illustrates an axial fan with guide vanes arranged downstream in accordance with the invention.
  • Figure 3 illustrates a preferred embodiment of the inventive guide vane extended in a plane.
  • Figure 4 illustrates the guide vane of Figure 3 with constant curvature
  • Figure 5 illustrates an alternative embodiment of the guide vane in accordance with the invention, also extended in a plane.
  • FIG. 2 there is illustrated an axial fan 2, installed in a duct 4, with the air flow direction indicated by the arrow q. Downstream the fan and at a given distance from it a ring of guide vanes 6 is mounted, the radial extension of the guide vanes substantially corresponding to that of the fan blades 8. As will be particularly seen from the vane 6', the vanes have a substantially axial outlet angle while the inlet angle forms a given angle to the central axis of the fan.
  • FIG 3 there is illustrated a preferred embodiment of a guide vane 6, extended in a plane.
  • the end portion of the guide vane 6 which is intended to face towards the fan has an edge 10 with a parabola like shape so that between the inner and outer longitudinal edges 12 and 14 of the guide vane 6 there is obtained a web with a shorter lenth L 2 along the vane than said edges ⁇ and L 3 .
  • the vane 6 has a stright trailing edge 16.
  • the height of the web from the inner longitudinal edge 12 is denoted by Hi and the total height of the vane by H 2 -
  • the position of the web is deter ⁇ mined by the condition: 0,4 ⁇ ⁇ _/ ⁇ 2 ⁇ 0,9 preferably
  • the radius of curvature R To enable optimization of the guide vane at different operating points in the pressure-flow diagram, i.e. both for large flow and high pressure, the radius of curvature R, see Figure 4, and must meet the condition: 0,83 ⁇ l ⁇ ⁇ 1,45 preferably 0,83 ⁇ R/ ⁇ ⁇ 1,10
  • the vane will thus be useful for practically all axial fans used in practice.
  • ⁇ corresponds to the radius of the impeller hub
  • R 2 corresponds to the radius in the flow duct 4 in question, which also substantially agrees with the radius of the blade wheel, cf.
  • Figure 5 there is illustrated an alternative embodiment of a guide vane in accordance with the invention, the edge intended to face towards the fan being formed by a polygonal train of three sides 20, 22, 24. The side 22 will then form the intermediate web portion. It should be noted that the web portion 22 is displaced closer to the outer edge 14, compared with the inner edge 12. This vane is also curved with a constant radius of curvature, as illustrated in Figure 4. This is a simple guide vane configuration, which gives a considerable increase in efficiency compared with previous embodiments with a monotonously extending oblique edge, as indicated by the dashed line 26 in the figure.

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

Abstract

A guide vane for an axial fan is formed in the end portion facing towards the fan with a web between the radially outer and inner portions of the guide vane. The arc length L2 along the single-curved vane is shorter at the level of the web than at said outer and inner portions L3 and L1 respectively.

Description

Guide vane for an axial fan.
The present invention relates to a guide vane for an axial fan.
When a gas passes through a fan the gas is deflected by the impeller rotor blades and a pressure increase is obtained across the impeller. How¬ ever, the deflection means that the gas flow velocity has a rotation component after passage through the impeller. This rotation component forms a rotation energy which is often lost in the continued gas transport downstream the fan.
It is known to arrange a ring of guide vanes downstream the impeller to make use of this rotation energy and then raise the pressure increase of the fan as well as its efficiency. The rotation energy of the gas flow after the impeller is thus converted into a static pressure increase on passing over the guide vanes. This conversion is not free of losses, and to minimize the losses it is essential that the inlet angle of the guide vanes substantially coincides with the direction of gas flow leaving the impeller. If the inlet side of the guide vanes is not adapted to the direction of the impinging gas, a strong release of the flow is obtained at the guide vane, with large energy losses and acompanying decrease of the fan efficiency as a result. The guide vanes are also implemented so that the gas on the outlet side is given a substantially axial direction.
It has been found that the magnitude of the rotation component varies in radial direction, which means that the angle which the flow direction forms with the central axis varies with the radius. The flow is very complex, and secondary effects result in that the rotation after the fan blades will be larger at the root and top of the blades. At the root of blades, i.e. att the point of attachment of the blades to the hub, the gas flow is given an increased rotation by back flow in gaps and by the rotation of the hub, and at the top of the blades there is an increased rotation as a result of back flow which lowers the axial component. In addition, it should be noted that the exterior limiting surface, e.g. the wall of a flow duct or the like, does not only retard the tangential movement component but also the axial one. Taken together this gives the unexpected radial variation of the flow direction illustrated in Figure 1.
Fi»gure 1 thus illustrates the result of measurements made with an axial fan. As will be seen, the flow direction angle towards the central axis is greater at the top and root of the blade, and the angle passes through a minimum value therebetween. The exact appearance of the graph is affected by such parameters as the blade angles on the impeller and the selected operat¬ ing point in the corresponding fan diagram (pressure flow diagram), but the shape of the graph is gualitively the same, with a mini, um between the posi¬ tions of the blade root and top. In attempts to adapt the inlet angle of the guide vane to the rotation component, which varies radially, guide vanes have been produced with varying curvature, which requires a very complicated manufacturing technique, how¬ ever.
Guide vanes have also been made with an oblique edge between the inner and outer longitudinal edges of the guide vane, so that the arcuate length of the guide vane along the inner edge is longer than the arcuate length along the radially outer edge. For a constant curvature of the guide vane there is thus obtained a greater inlet angle at the radially inward portion of the guide vane than at its radially- outward portion. The object of the present invention is to provide a new guide vane, starting from the above-mentioned knowledge of the radial variation of the rotation, which vane is adapted on its inlet side to the direction of the impinging gas in a considerably improved way along the entire radial e- x ension of the guide vane, while the guide vane is simple and cheap to manufacture.
This object is achieved with a guide vane of the kind described in the introduction and with the characterizing features stated in claim 1.
By giving the edge of the vane portion facing towards the axial rotor a configuration substantially following the variation of the rotation illustrated in Figure 1, the vane can be produced with single curvature and simultaneously obtains excellent adaption of the inlet angle to the direction of the impinging gas at every point.
With the guide vane in accordance with the invention, improvements of the fan efficiency up to 20% can be obtained compared with guide vanes generally available on the market.
In accordance with an advantageous embodiment of the inventive guide vane, the inlet angle ^j at the radially inward portion or root portion meets the condition: 40° < <£■_ < 70° preferably
52° < O^ < 70° according to another advantageous embodiment of the inventive guide vane having a constant radius of curvature, the ratio between the radius of curvature R and the length ^ of the radially inward edge of the guide vane meets the condition: 0,83 < R/Li < 1,45 preferably 0,83 < R/Lχ < 1,10.
Optimization of the guide vane configuration to the selected operating point in the area in the pressure-flow diagram which is of interest is thus enabled.
According to a still further advantageous embodiment of the inventive guide vane, the relationship between the length ^ of the radially inward edge of the guide vane and the length L2 of the guide vane at the level of the web meets the condition:
Figure imgf000005_0001
and the web level is given by the condition: 0,4 < B_/H2 < 0,9 preferably
Figure imgf000005_0002
where H denotes the height for the web position from the radially inward edge and ~ 2 the total height of the guide vane. The inlet angle of the guide vane at the vane top must be related, e.g. to the inlet angle at the guide vane root, and according to another advantageous embodiment of the inventive guide vane this relationship is given by the condition: 0,5 < I^/ -L < 0,7 where L3 and Lj denote the lengths of the radially outer and inner edges of the guide vane.
If the above indicated limits of the different parameters determining the configuration of the guide vane are exceeded, disturbances of different kinds occur, e.g. separation of the gas flow from the guide vane with energy losses as a result.
Embodiments of the guide vane in accordance with the invention, selected as examples, will now be described in more detail in connection with figures 2-5.
Figure 1 illustrates the radial variation of the angle between the flow direction and the central axis from the blade root to the blade top.
Figure 2 illustrates an axial fan with guide vanes arranged downstream in accordance with the invention.
Figure 3 illustrates a preferred embodiment of the inventive guide vane extended in a plane.
Figure 4 illustrates the guide vane of Figure 3 with constant curvature, and
Figure 5 illustrates an alternative embodiment of the guide vane in accordance with the invention, also extended in a plane.
In Figure 2 there is illustrated an axial fan 2, installed in a duct 4, with the air flow direction indicated by the arrow q. Downstream the fan and at a given distance from it a ring of guide vanes 6 is mounted, the radial extension of the guide vanes substantially corresponding to that of the fan blades 8. As will be particularly seen from the vane 6', the vanes have a substantially axial outlet angle while the inlet angle forms a given angle to the central axis of the fan.
In Figure 3 there is illustrated a preferred embodiment of a guide vane 6, extended in a plane. The end portion of the guide vane 6 which is intended to face towards the fan has an edge 10 with a parabola like shape so that between the inner and outer longitudinal edges 12 and 14 of the guide vane 6 there is obtained a web with a shorter lenth L2 along the vane than said edges ^ and L3. The vane 6 has a stright trailing edge 16.
The height of the web from the inner longitudinal edge 12 is denoted by Hi and the total height of the vane by H2- The position of the web is deter¬ mined by the condition: 0,4 < ~_/~ 2 < 0,9 preferably
0,5 < _/ 2 < °'8- When the guide vane of Figure 3 is given a constant curvature with a radius of curvature according to Figure 4, there is obtained a greater inlet angle in relation to the central axis at the inner portion of the guide vane, which will be at the level of the blade root, that at the outer portion of the vane 6, which will be at the level of the vane top, since the inner longitudinal edge 12 is longer than the outer longitudinal edge 14, see Figure 3. In the intermediate web portion, the inlet angle will be still less, and thus there is achieved in a simple way a radial variation in the inlet angle which agrees with the radial variation of the gas flow rotation component, as discussed above. For 0,50 < I^/l^ < 0,70 there are obtained the ratios between the inlet angles at the outer and inner portions of the vane, which are well suited to practical applications. The lengths ~ -^ and 1_ meet the condition:
Figure imgf000007_0001
To enable optimization of the guide vane at different operating points in the pressure-flow diagram, i.e. both for large flow and high pressure, the radius of curvature R, see Figure 4, and must meet the condition: 0,83 < l^ < 1,45 preferably 0,83 < R/ χ < 1,10
The ratio between the radii R^ and R2 from the central axis 18 of the fan to the inner edge 12 of the guide vane and the outer edge 14, re- spectively, meets the condition: 0,3 < R!/R2 0,8 preferably 0,45 < i/ 2 < 0,72
The vane will thus be useful for practically all axial fans used in practice.
In addition, ^ corresponds to the radius of the impeller hub, while the radius R2 corresponds to the radius in the flow duct 4 in question, which also substantially agrees with the radius of the blade wheel, cf. Figure 2. In Figure 5 there is illustrated an alternative embodiment of a guide vane in accordance with the invention, the edge intended to face towards the fan being formed by a polygonal train of three sides 20, 22, 24. The side 22 will then form the intermediate web portion. It should be noted that the web portion 22 is displaced closer to the outer edge 14, compared with the inner edge 12. This vane is also curved with a constant radius of curvature, as illustrated in Figure 4. This is a simple guide vane configuration, which gives a considerable increase in efficiency compared with previous embodiments with a monotonously extending oblique edge, as indicated by the dashed line 26 in the figure.
It will be obvious that a number of curve shapes are possible for the edge facing towards the fan, these shapes having a web as described above. In practical application the curve shape giving an optimum result is of course selected.

Claims

Claims
1. Guide vane for an axial fan, c h a r a c t e r i z e d in that in the portion facing towards the fan a web is formed between the radially outward and inward portions of the guide vane, the arc length along the single curved guide vane at the level of the web is shorter than at said outward and inward portions.
2. Guide vane as claimed in claim 1, c h a r a c t e r i z e d in that the edge of the end portion facing towards the fan has a continous concave shape.
3. Guide vane as claimed in claim 2, c h a r a c t e r i z e d in that the edge has a parabola-like shape.
4. Guide vane as claimed in claim 1, c h a r a c t e r i z e d in that the edge of the end portion facing towards the fan has the shape of a polygonal train.
5. Guide vane as claimed in claim 4, c h a r a c t e r i z e d in that the edge of the end portion facing towards the fan has the form of a tri¬ lateral polygonal train.
6. Guide vane as claimed in anyone of claims 2-5, c h a r a c t e r i z e d in that the ratio between the length -^ of the ra¬ dially inward edge of the guide vane and the length L2 of the guide vane at the level for the web meets the condition:
Figure imgf000008_0001
7. Guide vane as claimed in any one of claims 1-6, c h a r a c t e r i z e d in that the inlet angle C(, at the root portion of the guide vane meets the condition
40° < OC < 70° preferably
52° < d_ι < 70°.
8. Guide vane as claimed in.any one of claims 1-7, c h a r a c t e r i z e d in that the single-curved guide vane has a constant radius of curvature R.
9. Guide vane as claimed in claim 8, c h a r a c t e r i z e d in that the ratio between the radius of curvature R and the length L-^ of the radially inward edge of the guide vane meets the condition
0,83 < / χ < 1,45 preferably
0,83 < R/L1 < 1,10.
10. Guide vane as claimed in any one of claims 2-9, c h a r a c t e r i z e d in that the ratio between the height H-^ of the position of the web from the radially inward edge and the total height H2 of the guide vane meets the condition 0,4 < ~_-/~ 2 < 0,9 preferably
0,5 < &_ ~2 < 0,8.
11. Guide vane as claimed in any one of claims 2-10, c h a r a c t e r i z e d in that the ratio between the lengths L3 and L*^ of the radially outward and inward edges respectively of the -guide vane meets the condition
Figure imgf000009_0001
12. Guide vane as claimed in any one of claims 1-11, c h a r a c t e r i z e d in that the ratio between the radii R-^ and R2 from the fan axis to the outer and inner edges of the guide vane meets the condition
0,3 < R_/R2 < 0,8 preferably
0,45 < K_/~X_ < 0,72.
PCT/SE1989/000324 1988-06-08 1989-06-08 Guide vane for an axial fan WO1989012174A1 (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
DE68915278T DE68915278T2 (en) 1988-06-08 1989-06-08 GUIDE BLADE FOR AXIAL BLOWERS.
AT8989906852T ATE105609T1 (en) 1988-06-08 1989-06-08 GUIDE BLADE FOR AXIAL BLOWER.
UA4831937A UA12318A (en) 1988-06-08 1989-06-08 Guide rib of axial ventilator
BR898907459A BR8907459A (en) 1988-06-08 1989-06-08 GUIDE REED FOR AN AXIAL FAN
EP89906852A EP0418303B1 (en) 1988-06-08 1989-06-08 Guide vane for an axial fan
DK199002842A DK173521B1 (en) 1988-06-08 1990-11-29 Axial blower guide vane
FI905984A FI104509B (en) 1988-06-08 1990-12-04 Axial fan guide rail
NO905297A NO170738C (en) 1988-06-08 1990-12-07 AXIAL FAN LEAD BOWL
SU904831937A RU1834989C (en) 1988-06-08 1990-12-07 Guide vane of axial ventilator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8802136A SE461112B (en) 1988-06-08 1988-06-08 LED LIGHT SHOWS AN AXIAL FLAT
SE8802136-5 1988-06-08

Publications (1)

Publication Number Publication Date
WO1989012174A1 true WO1989012174A1 (en) 1989-12-14

Family

ID=20372552

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1989/000324 WO1989012174A1 (en) 1988-06-08 1989-06-08 Guide vane for an axial fan

Country Status (11)

Country Link
EP (1) EP0418303B1 (en)
JP (1) JP2837207B2 (en)
AU (1) AU636845B2 (en)
BR (1) BR8907459A (en)
DE (1) DE68915278T2 (en)
DK (1) DK173521B1 (en)
FI (1) FI104509B (en)
RU (1) RU1834989C (en)
SE (1) SE461112B (en)
UA (1) UA12318A (en)
WO (1) WO1989012174A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0441097A1 (en) * 1990-02-07 1991-08-14 United Technologies Corporation Airfoil for the compression section of a rotary machine
WO1993001415A1 (en) * 1991-07-09 1993-01-21 ABB Fläkt Aktiebolag Guide vane means
FR2731306A1 (en) * 1995-03-02 1996-09-06 Lucas Aerospace Power Equip MONOBLOC COOLING AIR DIFFUSER FOR ELECTROMECHANICAL DEVICE
EP1998052A2 (en) 2007-06-01 2008-12-03 EVG Lufttechnik GmbH Axial ventilator with subsequent guide vane apparatus
CN103696983A (en) * 2013-12-31 2014-04-02 江苏大学 Method for optimally designing impellers of bidirectional axial flow pumps

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5577888A (en) * 1995-06-23 1996-11-26 Siemens Electric Limited High efficiency, low-noise, axial fan assembly
CN100453821C (en) * 2003-07-22 2009-01-21 奇鋐科技股份有限公司 Wind direction outlet controlling means
CN103557185B (en) * 2013-10-31 2016-01-20 江苏国泉泵业制造有限公司 A kind of axial pump vane Airfoil Optimization method

Citations (5)

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Publication number Priority date Publication date Assignee Title
CH477628A (en) * 1966-04-15 1969-08-31 Joy Mfg Co Axial flow apparatus
US3932054A (en) * 1974-07-17 1976-01-13 Western Engineering & Mfg. Co. Variable pitch axial fan
FR2277257A1 (en) * 1974-07-02 1976-01-30 Rotron Inc REDUCED NOISE LEVEL FAN
US4318669A (en) * 1980-01-07 1982-03-09 The United States Of America As Represented By The Secretary Of The Air Force Vane configuration for fluid wake re-energization
SU941691A1 (en) * 1980-12-17 1982-07-07 Предприятие П/Я Г-4974 Axial fan

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JPS5925846A (en) * 1982-08-05 1984-02-09 Canon Inc Recording liquid
JPS6270698A (en) * 1985-09-21 1987-04-01 Matsushita Electric Works Ltd Motor fan

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH477628A (en) * 1966-04-15 1969-08-31 Joy Mfg Co Axial flow apparatus
FR2277257A1 (en) * 1974-07-02 1976-01-30 Rotron Inc REDUCED NOISE LEVEL FAN
US3932054A (en) * 1974-07-17 1976-01-13 Western Engineering & Mfg. Co. Variable pitch axial fan
US4318669A (en) * 1980-01-07 1982-03-09 The United States Of America As Represented By The Secretary Of The Air Force Vane configuration for fluid wake re-energization
SU941691A1 (en) * 1980-12-17 1982-07-07 Предприятие П/Я Г-4974 Axial fan

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0441097A1 (en) * 1990-02-07 1991-08-14 United Technologies Corporation Airfoil for the compression section of a rotary machine
WO1993001415A1 (en) * 1991-07-09 1993-01-21 ABB Fläkt Aktiebolag Guide vane means
FR2731306A1 (en) * 1995-03-02 1996-09-06 Lucas Aerospace Power Equip MONOBLOC COOLING AIR DIFFUSER FOR ELECTROMECHANICAL DEVICE
EP1998052A2 (en) 2007-06-01 2008-12-03 EVG Lufttechnik GmbH Axial ventilator with subsequent guide vane apparatus
EP1998052A3 (en) * 2007-06-01 2009-10-28 EVG Lufttechnik GmbH Axial ventilator with subsequent guide vane apparatus
CN103696983A (en) * 2013-12-31 2014-04-02 江苏大学 Method for optimally designing impellers of bidirectional axial flow pumps
CN103696983B (en) * 2013-12-31 2017-03-01 江苏大学 A kind of Double-way axial flow impeller of pump Optimization Design

Also Published As

Publication number Publication date
DK173521B1 (en) 2001-01-29
SE461112B (en) 1990-01-08
FI905984A0 (en) 1990-12-04
DE68915278D1 (en) 1994-06-16
DK284290A (en) 1990-11-29
AU636845B2 (en) 1993-05-13
DK284290D0 (en) 1990-11-29
BR8907459A (en) 1991-04-02
UA12318A (en) 1996-12-25
DE68915278T2 (en) 1994-10-27
SE8802136D0 (en) 1988-06-08
JP2837207B2 (en) 1998-12-14
RU1834989C (en) 1993-08-15
EP0418303B1 (en) 1994-05-11
JPH03504996A (en) 1991-10-31
FI104509B (en) 2000-02-15
AU3765289A (en) 1990-01-05
EP0418303A1 (en) 1991-03-27

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