AU714395B2 - Creación de Inventos y Patentes con Inteligencia Artificial

AU714395B2 – Axial fan
– Google Patents

AU714395B2 – Axial fan
– Google Patents
Axial fan

Download PDF
Info

Publication number
AU714395B2

AU714395B2
AU48854/97A
AU4885497A
AU714395B2
AU 714395 B2
AU714395 B2
AU 714395B2
AU 48854/97 A
AU48854/97 A
AU 48854/97A
AU 4885497 A
AU4885497 A
AU 4885497A
AU 714395 B2
AU714395 B2
AU 714395B2
Authority
AU
Australia
Prior art keywords
blade
axial fan
set forth
curved surface
trailing edge
Prior art date
1996-11-12
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.)

Ceased

Application number
AU48854/97A
Other versions

AU4885497A
(en

Inventor
Tadashi Ohnishi
Seiji Sato
Zhiming Zheng
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.)

Daikin Industries Ltd

Original Assignee
Daikin Industries 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.)
1996-11-12
Filing date
1997-11-07
Publication date
2000-01-06

1997-11-07
Application filed by Daikin Industries Ltd
filed
Critical
Daikin Industries Ltd

1998-06-03
Publication of AU4885497A
publication
Critical
patent/AU4885497A/en

2000-01-06
Application granted
granted
Critical

2000-01-06
Publication of AU714395B2
publication
Critical
patent/AU714395B2/en

2017-11-07
Anticipated expiration
legal-status
Critical

Status
Ceased
legal-status
Critical
Current

Links

Espacenet

Global Dossier

Discuss

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

F04D29/32—Rotors specially for elastic fluids for axial flow pumps

F04D29/38—Blades

F04D29/384—Blades characterised by form

Description

-1- AXIAL FAN TECHNICAL FIELD The present invention relates to an axial fan to be used for air-conditioner outdoor units and, more particularly, to an axial fan with an improved blade configuration.
BACKGROUND ART Conventionally, axial fans have been used as an air blower for air-conditioner outdoor units.
Figs. 11 and 12 are a schematic cross-sectional view and a schematic front view of a common outdoor unit for air conditioners, respectively. As shown in these figures, the air-conditioner outdoor unit contains an axial fan A equipped with a plurality of three) blades 2, 2, 2 around an outer circumference of a hub 1. On the suction side of the axial fan A, a heat exchanger B having an L-shaped cross section is placed, while on the discharge side of the axial fan A there is placed a crosspiece type discharge grille C. Reference character D denotes a compressor, and E denotes a partition plate which separates a heat exchange chamber F in which the axial fan A and the heat exchanger B are placed, from a machine chamber G TTN4, in which the compressor D is placed.
II
2 Meanwhile, in one of conventionally well-known axial fans, blades 2 (denoted by the same reference numeral as that used in Figs. 11, 12 for convenience) have a generally uniform blade thickness from its leading edge 2a to its trailing edge 2b, as shown in Fig. 13 (see, for example, Japanese Patent Laid-Open Publication No. 55-112898).
In such an axial fan, the blade configuration is designed such that air flows to the leading edge 2a of the blade 2 at an optimum angle the angle shown by solid-line arrow).
However, in the case of an air-conditioner outdoor unit with the above-described arrangement, since the outdoor unit is closed on the machine chamber G side, air is taken in from two sides of the heat exchanger B so that the direction of air flowing into the axial fan A tends to vary. Also, since frost is formed on the heat exchanger B that is functioning as an evaporator during the heating operation, the direction of air flowing into the axial fan A varies due to a nonuniform resistance to flow caused by the frost formation.
As a result, the inflow angle of air into the blade 2 also varies so that the flow around the blade 2 does not necessarily become an optimum state. That is, when an axial fan having the blade configuration shown in Fig. 13 is adopted Ri as the axial fan A for the outdoor unit of Figs. 11 and 12, the ir enters the leading edge 2a at an angle larger than or smaller 3 than the design angle as shown by broken-line arrows in Fig.
13. Thus, the air flow tends to be separated from the blade surface, resulting in a deteriorated aerodynamic performance and/or an increased aerodynamic sound level of the fan.
DISCLOSURE OF THE INVENTION The present invention having been accomplished in view of the above problems, an object thereof is to provide an axial fan which suppresses air separation from the blade surface as much as possible even if the inflow angle of air to the blade varies.
In order to achieve the above object, the present invention has a basic construction that, in an axial fan having a plurality of blades around an outer periphery of a hub, a cross-sectional configuration of each of the blades at an arbitrary distance from a center of the fan is set such that a blade thickness gradually increases moving away from a blade leading edge and then gradually decreases towards a blade trailing edge, and that, if a length of a camber line extending from the blade leading edge to a position where the blade thickness becomes maximum is taken to be L, and a length of a camber line extending from the blade leading edge to the blade trailing edge at said arbitrary distance is taken to be L 0 then
‘IZNL/L
0 falls within a range of 0.27 to 0.35.
-4- With this arrangement, because an aerofoil blade configuration superior in aerodynamic characteristics is obtained, air flow separation from the blade surface is suppressed even if the inflow angle of air has varied, allowing an improvement of aerodynamic performance and a reduction of the aerodynamic sound level in the fan. If L/L 0 0.27, then the position at which the blade thickness becomes maximum is too close to the blade leading edge. Thus, air separation will occur earlier. If L/L 0 0.35, then the position at which the blade thickness becomes maximum is too close to the blade trailing edge, so that the air inflow path to another blade on the rear side in the direction of rotation would be limited, resulting in an increased aerodynamic sound level.
In the basic constitution of the present invention, if a ratio, tmax/L 0 of a maximum tmax of the blade thickness to the camber line length L 0 is set to fall within a range of 0.04 to 0.12, the ratio of the maximum blade thickness tmax to the camber line length L 0 of the blade becomes optimum for the aerofoil blade configuration. This greatly contributes to the improvement of the aerodynamic performance.
Also, when the ratio, tmax/L 0 of the maximum blade thickness tmax to the camber line length L 0 is set so as to decrease with increasing ratio, 2R/D 0 of a double of a distance -from the fan center to a fan outer diameter Do, at least the ma um blade thickness tmax decreases towards an outer 5 circumferential edge of the blade. Therefore, separation of inflow air coming from the outer circumferential edge is effectively prevented from occurring.
When a pressure surface of each blade has a curved surface on an outer circumferential side thereof, the curved surface formed by rounding off the pressure surface from the outer circumferential edge of the blade over a distance S, inflow of air from the blade’s outer circumferential edge becomes smoother. Therefore, it is possible to suppress air separation in the vicinity of the blade’s outer circumference. In this case, if a length of a curve extending from a blade’s root to the blade’s outer circumferential edge, connecting maximumthickness positions of the blade with each other, is taken to be W 0 and S/W 0 on the curve is set to be within a range of 0.16 to 0.25, then the air separation on the blade’s outer circumferential side is prevented more effectively.
The curved surface may be formed extending from a position at a specified distance from the blade leading edge to the blade trailing edge. The reason of this is that on the blade leading edge side, the blade thickness is small due to the aerofoil blade configuration, so that air separation hardly occurs even without forming the curved surface on that side, in which case it is preferable that the curved surface is not R4ormed there.
6 Also, the curved surface may be formed extending from the blade leading edge to a position at a specified distance from the blade trailing edge. The reason of this is that the blade thickness is small on the blade trailing edge side due to the aerofoil blade configuration, so that not only air separation hardly occurs even without forming the curved surface, but also forming the curved surface on the blade trailing edge side may cause air leakage to occur there, in which case it is preferable that the curved surface is not formed at the relevant location.
Also, the curved surface may be formed extending from a position at a specified distance from the blade leading edge to a position at a specified distance from the blade trailing edge. The reason of this is that the blade thickness is small on both the blade leading edge side and the blade trailing edge side due to the aerofoil blade configuration, so that not only air separation hardly occurs even without forming the curved surface, but also forming the curved surface may cause air leakage to occur on the blade trailing edge side, in which case it is preferable that the curved surface is not formed at the relevant portions.
If, in a trailing edge-side outer circumferential portion of each blade where no curved surface is formed on the pressure surface, the blade’s outer circumferential edge forms n arc by having both the pressure surface and a negative- 7 pressure surface rounded off, a smooth inflow of air can be ensured at the portion where the blade thickness is small, and besides air leakage and disturbances of flow due to the air leakage are effectively suppressed.
If each of the blades has a cavity, weight of the blade is reduced in spite of the increase in blade thickness due to the aerofoil blade configuration.
In the case that the cavity is formed between a blade body and a cover plate joined to the blade body, the cavity can be formed easily.
BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a front view of an axial fan according to a first embodiment of the present invention; Fig. 2 is an enlarged sectional view taken along the line II II of Fig. 1; Fig. 3 is an enlarged sectional view taken along the line III- III of Fig. 1; Fig. 4 is a characteristic diagram showing the relationship between L/L 0 and the specific sound level in the axial fan according to the first embodiment of the present invention; Fig. 5 is a characteristic diagram showing the 7> relationship between S/W 0 and the specific sound level in the 8 axial fan according to the first embodiment of the present invention; Fig. 6 is a characteristic diagram showing the relationship between 2R/D 0 and tmax/L, in the axial fan according to the first embodiment of the present invention; Fig. 7 is a front view of an axial fan according to a second embodiment of the present invention; Fig. 8 is a front view of an axial fan according to a third embodiment of the present invention; Fig. 9 is an enlarged sectional view taken along the line IX IX of Fig. 8; Fig. 10 is a front view of an axial fan according to a fourth embodiment of the present invention; Fig. 11 is a cross sectional view of an ordinary air-conditioner outdoor unit; Fig. 12 is a front view of an ordinary air-conditioner outdoor unit; and Fig. 13 is a sectional view of a blade of an axial fan according to the prior art.
BEST MODE FOR CARRYING OUT THE INVENTION Several preferred embodiments of the present invention will be described in detail below with reference to 7/ the accompanying drawings. It is noted that in Figs. 1 through 9 3 and Figs. 7 through 10, components similar to those shown in Figs. 11 through 13 are designated by the same reference symbols.
(First Embodiment) Figs. 1 to 3 show an axial fan according to a first embodiment of the present invention.
This axial fan has a plurality of blades 2, 2, provided around an outer periphery of a cylindrical hub i, like the one described in the background art column.
The cross section of each blade 2 at an arbitrary distance from the fan center has an aerofoil configuration in which the blade thickness gradually increases moving away from the blade leading edge 2a and then gradually decreases towards the blade trailing edge 2b.
If the length of a camber line from the blade leading edge 2a to a position where the blade has a maximum thickness the position indicated by a curve X) is taken to be L, and the length of a camber line extending from the blade leading edge 2a to the blade trailing edge 2b at the aforementioned arbitrary distance is taken to be L 0 then L/L 0 is set so as to fall within a range of 0.27 to 0.35. Also, the ratio, tmax/L 0 of the maximum blade thickness value tmax to the camber line length L 0 is set so as to fall within a range of 0.04 to 0.12.
RA With this arrangement, the ratio of the maximum blade thickness Itax to the camber line length L 0 of the blade 2 becomes such 10 that an optimum aerofoil blade configuration is provided, which greatly contributes to improvement of the aerodynamic performance.
Further, each blade 2 has a cavity 3 formed between a blade body 4 and a cover plate 5 joined to the blade body 4, as shown in Fig. 2. This arrangement makes it possible to easily reduce the weight of the blade 2 in spite of the increase in blade thickness due to the aerofoil blade configuration.
With the above constitution, an aerofoil blade configuration superior in aerodynamic characteristics is obtained. Therefore, even if the axial fan is used in, for example, an air-conditioner outdoor unit in which the inflow angle of air to the blades 2 tends to vary, air separation from the blade surface is suppressed, thus allowing an improvement of the aerodynamic performance and a reduction of the aerodynamic sound level in the fan. Furthermore, the ratio of the camber line length L 0 of the blade 2 to the maximum blade thickness value tmax becomes optimum for the aerofoil blade configuration, which greatly contributes to the improvement of the aerodynamic performance. If L/L 0 0.27, the position at which the blade thickness becomes maximum is too close to the blade leading edge 2a so that the separation of inflow air would occur earlier. On the other hand, if L/L o 0.35, the position where the blade thickness becomes maximum is too close to the lade trailing edge 2b so that the air inflow path leading to 11 another blade 2 on the rear side in the direction of rotation would be limited, resulting in an increased aerodynamic sound level (see Fig. 4).
The ratio, tmax/L 0 of the blade thickness maximum value tmax to the camber line length L 0 is set so as to decrease with a ratio of a double of the distance R from the fan center, to the fan outer diameter D o increases, as shown by a curve Y shown in Fig. 6. With this arrangement, at least the maximum blade thickness tmax decreases towards the outer circumference of the blade 2, so that inflow air from an outer circumferential edge 2e of the blade 2 is effectively prevented from being separated.
On the outer circumferential side of a pressure surface 2c of each blade 2, there is a curved surface 2g formed by rounding off the pressure surface 2c from the blade’s outer circumferential edge 2e over a distance S inwards, as shown in Fig. 3. If the length of the curve X ranging from the blade’s root 2f to the blade’s outer circumferential edge 2e and connecting the maximum thickness positions of the blade 2 is taken to be W 0 then, S/W 0 on the curve X is set in a range of 0.16 to 0.25. With this arrangement, inflow of air from the blade’s outer circumferential edge 2e becomes smoother so that the air separation is effectively prevented from occurring in the vicinity of the blades’ outer circumferential edges 2e (see ig. If S/W 0 0.16, then the effect of the curved surface 12 2g is diluted, and if S/W 0 0.25, then it is impossible to ensure obtainment of the aerofoil blade configuration. Therefore, the aerodynamic performance is lowered in both cases.
(Second Embodiment) Fig. 7 shows an axial fan according to a second embodiment of the present invention.
In this embodiment, the curved surface 2g is formed from a position at a specified distance K, from the blade leading edge 2a to the blade trailing edge 2b, on the outer circumferential portion of the pressure surface 2c of each blade 2. Otherwise, the constitution and functional effects are the same as in the first embodiment and so, description about those is omitted here.
The reason for providing the curved surface 2g in the above manner is that because the blade thickness on the blade leading edge 2a side is thin due to the aerofoil blade configuration of the blade 2, air separation does not occur so much even without forming the curved surface on that side, in which case it is preferable that the curved surface 2g is not formed at the portion on the blade leading edge side. The distance K 1 is preferably in a range such that the blade thickness at this distance is not so large (up to about 7% of the length the blade’s outer circumferential edge 2e).
13 (Third Embodiment) Figs. 8 and 9 show an axial fan according to a third embodiment of the present invention.
In this embodiment, the curved surface 2g is formed from the blade leading edge 2a to a position shifted from the blade trailing edge 2b toward the leading edge side by a specified distance K 2 on the outer circumferential portion of the pressure surface 2c of the blade 2. In a trailing edge-side outer circumferential portion of each blade 2 where no curved surface 2g is formed on the pressure surface 2c, the blade’s outer circumferential edge 2e forms an arc 2h by having both the pressure surface 2c and a negative-pressure surface 2d rounded off, as shown in Fig. 9. Otherwise, the constitution and functional effects are the same as in the first embodiment and so, description about those is omitted here.
The reason for adopting the above configuration is that because the blade thickness on the blade trailing edge 2b side is thin due to the aerofoil blade configuration, not only air separation hardly occurs on the blade trailing edge 2b side even without forming the curved surface there, but also forming the curved surface 2g there may cause air leakage to occur on the blade trailing edge 2b side, in which case it is preferable that the curved surface 2g is not formed on the blade trailing edge 2b side. Moreover, a smooth inflow of air is ensured at the portion where the blade thickness is thin an outer 14 circumferential-side portion on the blade trailing edge side), and besides, air leakage and disturbances of flow due to the air leakage are effectively suppressed. The distance K 2 is preferably within a range such that the blade thickness at that distance is not so large (up to about 25% of the length of the blade’s outer circumferential edge 2e).
(Fourth Embodiment) Fig. 10 shows an axial fan according to a fourth embodiment of the present invention.
In this embodiment, in the outer circumferential portion of the pressure surface 2c of the blade 2, the curved surface 2g is formed from a position at the specified distance K, from the blade leading edge 2a to a position at the specified distance K 2 from the blade trailing edge 2b. That is, this embodiment is a combination of the second embodiment and the third embodiment. Otherwise, the constitution and functional effects are the same as in the first through the third embodiments and so, description about the same thing is omitted here.
INDUSTRIAL
APPLICABILITY
As described above, the axial fan of the present invention is used in air conditioners or the like.

Claims (12)

1. An axial fan having a plurality of blades around an outer periphery of a hub characterized in that: a cross-sectional configuration of each of the blades at an arbitrary distance from a center of the fan is set such that a blade thickness gradually increases moving away from a blade leading edge and then gradually decreases towards a blade trailing edge and U. 10 if a length of a camber line extending from the blade leading edge to a position where the blade thickness becomes maximum is taken to be L, and a length of a camber line extending from the blade leading edge to the blade trailing edge- at said arbitrary distance is taken to be Lo, then L/L. falls within a range of 0.27 to 0.35. S*e

2. The axial fan as set forth in Claim 1, wherein a ratio, tmax/L 0 of a maximum tmax of the blade thickness to the camber line length Lo falls within a range of 0.04 to 0.12.

3. The axial fan as set forth in Claim 2, wherein said ratio, tmax/L 0 of the maximum blade thickness tmax to the camber line length Lo is set so as to decrease as a ratio, 2R/D 0 of a double of a distance R from the fan center to a fan outer Sdiameter Do increases. 16

4. The axial fan as set forth in Claim 1, wherein a pressure surface of each blade has a curved surface on an outer circumferential side thereof, said curved surface formed by rounding off said pressure surface from an outer circumferential edge of the blade over a distance S. 6:09

5. The axial fan as set forth in Claim 4, wherein if a length of a curve extending from a blade’s root to the blade’s outer circumferential edge connecting maximum-thickness positions of the blade with each other, is taken to be W 0 then S/Wo on the curve falls within a range of 0.16 to 0.25. 15

6. The axial fan as set forth in Claim 4, wherein said -curved surface is formed extending from a position at .a specified distance from the blade leading edge to the blade trailing edge 0

7. The axial fan as set forth in Claim 4, wherein said curved surface is formed extending from the blade leading edge to a position at a specified distance from the blade trailing edge -17-

8. The axial fan as set forth in Claim 4, wherein said curved surface is formed extending from a position at a specified distance from the blade leading edge to a position at a specified distance from the blade trailing edge.

9. The axial fan as set forth in Claim 6, wherein in a trailing edge-side outer circumferential portion of each blade where no curved surface is formed on the pressure surface, said blade’s outer circumferential edge forms an arc by having both the pressure surface and a negative-pressure surface rounded off.

The axial fan as set forth in Claim 1, wherein each blade has a cavity.

11. The axial fan as set forth in Claim 10, wherein said cavity is formed between a blade body and a cover plate joined to the blade body.

12. An axial fan substantially as hereinbefore described with reference to Figs. 1 to 6, Fig. 7, Figs. 8 to 9 or Fig. 10 of the accompanying drawings. 0* S DATED this Fifteenth Day of July 1998 15 Daikin Industries, Ltd., Patent Attorneys for the Applicant/Nominated Person 0 °•SPRUSON FERGUSON 0 .0 0*0 0*0 [N:\LIBd00579:DMB

AU48854/97A
1996-11-12
1997-11-07
Axial fan

Ceased

AU714395B2
(en)

Applications Claiming Priority (3)

Application Number
Priority Date
Filing Date
Title

JP8300181A

JP3050144B2
(en)

1996-11-12
1996-11-12

Axial fan

JP8-300181

1996-11-12

PCT/JP1997/004058

WO1998021482A1
(en)

1996-11-12
1997-11-07
Axial fan

Publications (2)

Publication Number
Publication Date

AU4885497A

AU4885497A
(en)

1998-06-03

AU714395B2
true

AU714395B2
(en)

2000-01-06

Family
ID=17881721
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

AU48854/97A
Ceased

AU714395B2
(en)

1996-11-12
1997-11-07
Axial fan

Country Status (7)

Country
Link

US
(1)

US6113353A
(en)

EP
(1)

EP0877167A4
(en)

JP
(1)

JP3050144B2
(en)

CN
(1)

CN1093922C
(en)

AU
(1)

AU714395B2
(en)

HK
(1)

HK1018301A1
(en)

WO
(1)

WO1998021482A1
(en)

Families Citing this family (19)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

EP1083391B1
(en)

1999-09-07
2006-12-20
Lg Electronics Inc.
Axial flow fan for air conditioner

DE10110243A1
(en)

2001-03-05
2002-09-12
Glen Dimplex Deutschland Gmbh

heater

KR100484828B1
(en)

2002-11-27
2005-04-22
엘지전자 주식회사
Refrigerator’s cool air circulation axial flow fan

JP4432474B2
(en)

2003-11-27
2010-03-17
ダイキン工業株式会社

Centrifugal blower impeller and centrifugal blower provided with the impeller

CN100449151C
(en)

2005-04-21
2009-01-07
台达电子工业股份有限公司
Axial-flow fan

EP2696079B1
(en)

2005-08-03
2019-01-02
Mitsubishi Heavy Industries, Ltd.
Propeller fan for heat exchanger of in-vehicle air conditioner

US20070243064A1
(en)

2006-04-12
2007-10-18
Jcs/Thg,Llc.
Fan blade assembly for electric fan

CA2793456C
(en)

2010-04-05
2017-06-27
Moore Fans Llc
Commercial air cooled apparatuses incorporating axial flow fans comprising super low noise fan blades

CN102828996B
(en)

2011-06-14
2015-12-16
珠海格力电器股份有限公司
A kind of axial fan

DE102012000376B4
(en)

2012-01-12
2013-08-14
Ebm-Papst St. Georgen Gmbh & Co. Kg

Axial or diagonal fan

WO2014024305A1
(en)

2012-08-10
2014-02-13
三菱電機株式会社
Propeller fan, and fan, air conditioner and outdoor unit for supplying hot water provided with same

US9121287B2
(en)

2012-09-12
2015-09-01
United Technologies Corporation
Hollow fan blade with honeycomb filler

CN103032375B
(en)

2012-12-27
2015-05-20
江苏中金环保科技有限公司
Blade for draught fan

US9404511B2
(en)

2013-03-13
2016-08-02
Robert Bosch Gmbh
Free-tipped axial fan assembly with a thicker blade tip

JP6106760B2
(en)

2013-10-30
2017-04-05
日本曹達株式会社

Deodorant for toilet and anti-scattering agent

CN106287959B
(en)

2016-08-17
2022-03-22
芜湖美智空调设备有限公司
Quiet leaf wind wheel, cabinet air conditioner and air conditioner

CN107956736B
(en)

2017-12-10
2019-09-10
安徽银龙泵阀股份有限公司
A kind of centrifugation impeller of pump with negative pressure blade

CN110118197A
(en)

2018-02-07
2019-08-13
广东美的制冷设备有限公司
Axial-flow windwheel and air conditioner

CN108180169A
(en)

2018-02-09
2018-06-19
广东美的厨房电器制造有限公司
Fan and micro-wave oven

Citations (3)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

JPH06249196A
(en)

1993-03-02
1994-09-06

Matsushita Electric Ind Co Ltd

Impeller of axial blower

JPH06249195A
(en)

1993-03-02
1994-09-06

Matsushita Electric Ind Co Ltd

Impeller of axial blower

JPH06307396A
(en)

1993-04-23
1994-11-01

Daikin Ind Ltd

Axial-flow impeller

Family Cites Families (16)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

US1622222A
(en)

1925-07-01
1927-03-22
Frank W Caldwell
Impeller

GB429958A
(en)

1934-03-27
1935-06-11
John Marshall
Improvements relating to screw fans

DE731575C
(en)

1939-05-11
1943-02-11
Forsch Kraftfahrwesen Und Fahr

Axial flywheel

GB611650A
(en)

1946-05-02
1948-11-02
Adrian Albert Lombard
Improvements in or relating to blades for internal-combustion turbines

US2772855A
(en)

1950-08-03
1956-12-04
Stalker Dev Company
Fluid turning blades

GB676406A
(en)

1950-11-03
1952-07-23
Thomas Dever Spencer
Improvements in fan impellers

JPS59185898A
(en)

1983-04-08
1984-10-22
Aisin Seiki Co Ltd
Fan blade

JPS6412898A
(en)

1987-07-02
1989-01-17
Seiko Epson Corp
Stepping motor

JPH01315696A
(en)

1988-06-15
1989-12-20
Toshiba Corp
Fan for air-conditioner

US5215441A
(en)

1991-11-07
1993-06-01
Carrier Corporation
Air conditioner with condensate slinging fan

JPH06147193A
(en)

1992-11-11
1994-05-27
Matsushita Electric Ind Co Ltd
Impeller of axial blower

JP3337248B2
(en)

1992-12-03
2002-10-21
三菱重工業株式会社

Propeller fan

CN1039748C
(en)

1992-12-28
1998-09-09
中国科学院化工冶金研究所
Method and probe for measuring concentration and velocity of heterogeneous gas-solid rolling particles

JP3083928B2
(en)

1993-02-01
2000-09-04
東芝キヤリア株式会社

Axial fan

WO1995013472A1
(en)

1993-11-12
1995-05-18
Penn Ventilator Co. Inc.
Air moving system with optimized air foil fan blades

JP4727845B2
(en)

2001-05-25
2011-07-20
オリンパス株式会社

Washing sterilizer

1996

1996-11-12
JP
JP8300181A
patent/JP3050144B2/en
not_active
Expired – Fee Related

1997

1997-11-07
US
US09/101,340
patent/US6113353A/en
not_active
Expired – Fee Related

1997-11-07
WO
PCT/JP1997/004058
patent/WO1998021482A1/en
not_active
Application Discontinuation

1997-11-07
AU
AU48854/97A
patent/AU714395B2/en
not_active
Ceased

1997-11-07
EP
EP97911480A
patent/EP0877167A4/en
not_active
Withdrawn

1997-11-07
CN
CN97191658A
patent/CN1093922C/en
not_active
Expired – Fee Related

1999

1999-08-02
HK
HK99103333A
patent/HK1018301A1/en
not_active
IP Right Cessation

Patent Citations (3)

* Cited by examiner, † Cited by third party

Publication number
Priority date
Publication date
Assignee
Title

JPH06249196A
(en)

1993-03-02
1994-09-06
Matsushita Electric Ind Co Ltd
Impeller of axial blower

JPH06249195A
(en)

1993-03-02
1994-09-06
Matsushita Electric Ind Co Ltd
Impeller of axial blower

JPH06307396A
(en)

1993-04-23
1994-11-01
Daikin Ind Ltd
Axial-flow impeller

Also Published As

Publication number
Publication date

EP0877167A4
(en)

2002-12-04

WO1998021482A1
(en)

1998-05-22

HK1018301A1
(en)

1999-12-17

CN1207161A
(en)

1999-02-03

EP0877167A1
(en)

1998-11-11

CN1093922C
(en)

2002-11-06

JP3050144B2
(en)

2000-06-12

JPH10141286A
(en)

1998-05-26

AU4885497A
(en)

1998-06-03

US6113353A
(en)

2000-09-05

Información de contacto