WO1991002165A1 - Variable skew fan - Google Patents
Variable skew fan Download PDFInfo
- Publication number
- WO1991002165A1 WO1991002165A1 PCT/US1990/004515 US9004515W WO9102165A1 WO 1991002165 A1 WO1991002165 A1 WO 1991002165A1 US 9004515 W US9004515 W US 9004515W WO 9102165 A1 WO9102165 A1 WO 9102165A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- blades
- hub
- fan
- blade
- curvature
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
- F04D29/328—Rotors specially for elastic fluids for axial flow pumps for axial flow fans with unequal distribution of blades around the hub
-
- 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
- F04D29/386—Skewed blades
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
Definitions
- This invention relates generally to fans having several blades used to move a fluid such as air.
- the invention features a fan having blades with variable skew. (I.e., the blade skew varies between at least two of the fan blades.)
- Fans are typically constructed with identical blades that are attached at a common hub, the hub being rotated by, e.g., an electric motor through a shaft attached to the hub.
- the blades are usually evenly spaced around the periphery of the hub.
- the fan will often generate audible tones at frequencies corresponding to the blade passing frequency (i.e., the frequency at which the blades pass a fixed point) and multiples of the blade passing frequency.
- fans In order to reduce the magnitude of these tones, fans have been constructed with blades located at uneven intervals around the periphery of the hub. (See, e.g., U.S. Patent No. 3,315,749 to K. W. Parsons et al.)
- tones are generated at the same frequency as the frequency at which the shaft rotates, and at multiples of that frequency. Since the shaft rotation frequency is much less than the blade passing frequency, the total number of tones generated within any frequency band is much greater than in the case of evenly spaced blades, and the strength of each tone is correspondingly reduced. If reduced sufficiently, these tones can become inaudible due to the masking effect of various broadband noise sources, including the fan itself.
- a further advantage of having blades that are unevenly spaced is that the frequency of the lowest frequency tones produced is in a frequency - 2 - range where the human ear is relatively insensitive. In this way fan noise can be made less objectionable.
- the fan of the invention generally comprises: a central hub rotatable on an axis; and a plurality of blades extending from the hub, each of the blades comprising a root portion adjacent to the hub, and terminating in a tip portion, the root portions of the blades being " approximately evenly spaced around the hub; wherein each of the blades exhibits a curvature from the root portion of the blade to the blade's tip portion, the curvature beiit in a plane that is perpendicular to the axis on whic ⁇ aae fan rotates; and wherein the curvature differs between at least two of the blades, such that the distance between the -tip portions of at least two sets of adjacent blades is unequal.
- the blades are "backskewed” (i.e., skewed in a direction opposite to the direction of rotation of the fan) , and each of the blades is skewed by a different amount.
- the fan includes at least two identical groups of blades. The distance between the blade tips of at least two sets of adjacent blades varies by at least a factor of 1.5. The blade tips are connected by a band.
- Fig. 1 is a plan view of a fan according to the invention.
- a fan 10 has a cylindrical hub section 12 for housing a motor (not shown) .
- the motor shaft is attached to the hub at aperture 14 and thus rotates the fan.
- a plurality of blades, blades 16- 19 being shown as illustrative, extend radially outward from hub 12 to their respective tips, where they are joined to band 11.
- the fan blades have different shapes, with each of the blades having a different "blade skew.”
- the blade skew is defined as the angle A b between the midpoint (M r ) of the blade root and the midpoint (M t ) of the blade tip.
- the skew angle A b is substantially greater for blade 17 than for blade 18.
- all blades are approximately evenly spaced at the hub so that the distance between the midpoints M of each blade root in fan 10 is approximately equal. Since the blades have a variable skew as described above, the distance between the tips of the blades will vary. I.e., the distance between the midpoints M t will vary, achieving the advantages of reduced noise described above. Since the blades are evenly spaced at the hub, however, the hub will have a high solidity resulting in superior aerodynamic performance, as explained in detail below.
- a disadvantage of having uneven blade spacing is that the aerodynamic performance can be degraded, particularly for the sections of the blades near the hub, which work at a higher "non-dimensional loading" than the sections of the blades near the tips of the blades.
- Non-dimensional loading is the ratio of the change of pressure across the fan to the product of the density of the fluid moved by the fan and the square of the speed of the fan blades. Since non-dimensional loading is inversely proportional to the square of the blade speed, and because the speed of the tips of the blades is greater than the speed of the sections of the blades near the hub, fans are more heavily JLoaded near the hub, and therefore require a higher solidity near the hub than near the tip sections.
- This solidity is often limited by the requirement that the fan be injection moldable (i.e., the blades cannot overlap) . If the root sections of the blades are unevenly spaced, the requirement tha ' t the blades not overlap will further limit blade design in the areas where the blades are close together. In those areas where the blades are spread further apart, high solidity will-be achievable only by increasing blade chords, which in turn will increase the projected width of the fan. In applications such as automotive cooling systems, where the fan must be compact, this increase in fan width is often not acceptable, so the solidity at the blade root wij.1 be made smaller than aerodynamic considerations deem desirable.
- the present invention uses blades with varied skew to achieve the advantage of varied spacing at the tips of the blades, while maintaining even spacing near the hub, resulting in high solidity near the hub.
- the preferred embodiment is a fan with blades whose skew distribution varies from blade to blade.
- two or more identical groups of blades may be used, each of which would contain at least two blades.
- a fan 20 is shown that comprises two identical blades 22 and two identical blades 24, forming at least two identical groups of blades (i.e., each group includes one blade 22 and one blade 24) .
- the use of identical groups makes it easier to design a fan that is both dynamically and statically balanced. Using identical groups of blades also reduces the number of different blade designs.
Abstract
An axial flow fan (10, 20) comprising: a central hub (12) rotatable on an axis; and a plurality of blades (16, 17, 18, 19) extending from the hub, each of the blades comprising a root portion adjacent to the hub, and terminating in a tip portion, the root portions of the blades being approximately evenly spaced around the hub; wherein each of the blades exhibits a curvature from the root portion of the blade to the blade's tip portion, the curvature being in a plane that is perpendicular to the axis on which the fan rotates; and wherein the curvature differs between at least two of the blades, such that the distance between the tip portions of at least two sets of adjacent blades is unequal. The invention therefore achieves the advantage of having uneven blade spacing near the tips while maintaining high solidity near the hub, where the blade spacing is even.
Description
VARIABLE SKEW FAN Background of the Invention
This invention relates generally to fans having several blades used to move a fluid such as air. In particular, the invention features a fan having blades with variable skew. (I.e., the blade skew varies between at least two of the fan blades.)
Fans are typically constructed with identical blades that are attached at a common hub, the hub being rotated by, e.g., an electric motor through a shaft attached to the hub. The blades are usually evenly spaced around the periphery of the hub. When the inflow velocity of air entering a fan varies (especially circumferential variations) , the fan will often generate audible tones at frequencies corresponding to the blade passing frequency (i.e., the frequency at which the blades pass a fixed point) and multiples of the blade passing frequency.
In order to reduce the magnitude of these tones, fans have been constructed with blades located at uneven intervals around the periphery of the hub. (See, e.g., U.S. Patent No. 3,315,749 to K. W. Parsons et al.) When the blades are unevenly spaced, tones are generated at the same frequency as the frequency at which the shaft rotates, and at multiples of that frequency. Since the shaft rotation frequency is much less than the blade passing frequency, the total number of tones generated within any frequency band is much greater than in the case of evenly spaced blades, and the strength of each tone is correspondingly reduced. If reduced sufficiently, these tones can become inaudible due to the masking effect of various broadband noise sources, including the fan itself. A further advantage of having blades that are unevenly spaced is that the frequency of the lowest frequency tones produced is in a frequency
- 2 - range where the human ear is relatively insensitive. In this way fan noise can be made less objectionable.
SUMMARY OF THE INVENTION
The invention generally features an axial flow fan that achieves the advantages of having the blades unevenly spaced without sacrificing performance as do previous fans that employ uneven blade spacing. The fan of the invention, unlike previous fans, uses blades that are essentially evenly spaced near the hub, but have variable spacing near the tip sections of the blades, to reduce audible tones. Since the noise produced by the sections of the fan blades near the hub is negligible compared to the noise produced by the tip sections of the blades, the advantages of uneven blade spacing are realized by having only the tip sections of the blades unevenly spaced. This is achieved by varying the "skew" of at least t o of the blades. Skew is defined as the angle between the midpoint of the blade root and the midpoint of the blade tip, and is explained in greater detail below.
The fan of the invention generally comprises: a central hub rotatable on an axis; and a plurality of blades extending from the hub, each of the blades comprising a root portion adjacent to the hub, and terminating in a tip portion, the root portions of the blades being "approximately evenly spaced around the hub; wherein each of the blades exhibits a curvature from the root portion of the blade to the blade's tip portion, the curvature beiit in a plane that is perpendicular to the axis on whicϊΛaae fan rotates; and wherein the curvature differs between at least two of the blades, such that the distance between the -tip portions of at least two sets of adjacent blades is unequal.
!_V ""*
In one preferred embodiment, the blades are "backskewed" (i.e., skewed in a direction opposite to the direction of rotation of the fan) , and each of the blades is skewed by a different amount. In another preferred embodiment, the fan includes at least two identical groups of blades. The distance between the blade tips of at least two sets of adjacent blades varies by at least a factor of 1.5. The blade tips are connected by a band.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Drawings
Fig. 1 is a plan view of a fan according to the invention.
Fig. 2 is a plan view of a second embodiment of the invention.
Structure and Operation
Referring to Fig. 1, a fan 10 has a cylindrical hub section 12 for housing a motor (not shown) . The motor shaft is attached to the hub at aperture 14 and thus rotates the fan. A plurality of blades, blades 16- 19 being shown as illustrative, extend radially outward from hub 12 to their respective tips, where they are joined to band 11.
The fan blades have different shapes, with each of the blades having a different "blade skew." The blade skew is defined as the angle Ab between the midpoint (Mr) of the blade root and the midpoint (Mt) of the blade tip. As can be seen in Fig. 1, the skew angle Ab is substantially greater for blade 17 than for blade 18. However, all blades are approximately evenly spaced at the hub so that the distance between the midpoints M of each blade root in fan 10 is approximately equal. Since the blades have a variable skew as described above, the
distance between the tips of the blades will vary. I.e., the distance between the midpoints Mt will vary, achieving the advantages of reduced noise described above. Since the blades are evenly spaced at the hub, however, the hub will have a high solidity resulting in superior aerodynamic performance, as explained in detail below.
A disadvantage of having uneven blade spacing is that the aerodynamic performance can be degraded, particularly for the sections of the blades near the hub, which work at a higher "non-dimensional loading" than the sections of the blades near the tips of the blades. Non- dimensional loading is the ratio of the change of pressure across the fan to the product of the density of the fluid moved by the fan and the square of the speed of the fan blades. Since non-dimensional loading is inversely proportional to the square of the blade speed, and because the speed of the tips of the blades is greater than the speed of the sections of the blades near the hub, fans are more heavily JLoaded near the hub, and therefore require a higher solidity near the hub than near the tip sections. This solidity is often limited by the requirement that the fan be injection moldable (i.e., the blades cannot overlap) . If the root sections of the blades are unevenly spaced, the requirement tha't the blades not overlap will further limit blade design in the areas where the blades are close together. In those areas where the blades are spread further apart, high solidity will-be achievable only by increasing blade chords, which in turn will increase the projected width of the fan. In applications such as automotive cooling systems, where the fan must be compact, this increase in fan width is often not acceptable, so the solidity at the blade root wij.1 be made smaller than aerodynamic considerations deem desirable. As explained above,
however, the present invention uses blades with varied skew to achieve the advantage of varied spacing at the tips of the blades, while maintaining even spacing near the hub, resulting in high solidity near the hub. As described above, the preferred embodiment is a fan with blades whose skew distribution varies from blade to blade. However, two or more identical groups of blades may be used, each of which would contain at least two blades. Referring to Fig. 2, a fan 20 is shown that comprises two identical blades 22 and two identical blades 24, forming at least two identical groups of blades (i.e., each group includes one blade 22 and one blade 24) . The use of identical groups makes it easier to design a fan that is both dynamically and statically balanced. Using identical groups of blades also reduces the number of different blade designs.
The preferred embodiments are merely illustrative and other embodiments are within the scope of the appended claims.
Claims
1. An axial flow fan comprising: a central hub rotatable on an axis; and a plurality of blades extending from said hub, each of said blades comprising a root portion adjacent said hub, and terminating in a tip portion, said root portions being approximately evenly spaced around said hub; wherein each of said blades exhibits a curvature from said root portion to said tip portion, said curvature being in a plane that is perpendicular to said axis; and wherein said curvature differs between at least two of said blades, such that the distance between the midpoint of said tip portions of at least two sets of adjacent blades is unequal.
2. The fan of claim 1 wherein said blades are backskewed. t
3. The fan of claim 1 comprising at least two identical groups of blades.
4. The fan of claim 1 wherein the distance between said blade tips of said at least two sets of adjacent blades varies by at least a factor of 1.5.
5. The fan of claim 1 where said blade tips are connected by a band.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE69022730T DE69022730T2 (en) | 1989-08-11 | 1990-08-10 | FAN WITH CHANGING INCLINATION. |
EP90911885A EP0487563B1 (en) | 1989-08-11 | 1990-08-10 | Variable skew fan |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US392,769 | 1989-08-11 | ||
US07/392,769 US5000660A (en) | 1989-08-11 | 1989-08-11 | Variable skew fan |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1991002165A1 true WO1991002165A1 (en) | 1991-02-21 |
Family
ID=23551937
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1990/004515 WO1991002165A1 (en) | 1989-08-11 | 1990-08-10 | Variable skew fan |
Country Status (5)
Country | Link |
---|---|
US (1) | US5000660A (en) |
EP (1) | EP0487563B1 (en) |
DE (1) | DE69022730T2 (en) |
ES (1) | ES2078975T3 (en) |
WO (1) | WO1991002165A1 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0546361A1 (en) * | 1991-12-12 | 1993-06-16 | Behr GmbH & Co. | Axial fan |
EP0945625A1 (en) * | 1998-03-23 | 1999-09-29 | SPAL S.r.l. | Axial flow fan |
FR2781843A1 (en) * | 1998-07-28 | 2000-02-04 | Valeo Thermique Moteur Sa | OPTIMIZED COMPACT FAN PROPELLER |
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Families Citing this family (46)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
IT1241368B (en) * | 1990-12-21 | 1994-01-10 | Fiatgeotech | AXIAL FAN, PARTICULARLY FOR AGRICULTURAL VEHICLES. |
US5191813A (en) * | 1991-07-22 | 1993-03-09 | Tecumseh Products Company | Hydrostatic transaxle having a fan and pulley arrangement |
ES2128357T3 (en) * | 1991-08-30 | 1999-05-16 | Airflow Res & Mfg | FAN APPLIANCE MISSING FORWARD WITH TILT. |
US5489186A (en) * | 1991-08-30 | 1996-02-06 | Airflow Research And Manufacturing Corp. | Housing with recirculation control for use with banded axial-flow fans |
US5454690A (en) * | 1994-01-13 | 1995-10-03 | Shop Vac Corporation | Air flow housing |
US5624234A (en) * | 1994-11-18 | 1997-04-29 | Itt Automotive Electrical Systems, Inc. | Fan blade with curved planform and high-lift airfoil having bulbous leading edge |
US5588804A (en) * | 1994-11-18 | 1996-12-31 | Itt Automotive Electrical Systems, Inc. | High-lift airfoil with bulbous leading edge |
US5588178A (en) * | 1995-06-07 | 1996-12-31 | Mcculloch Corporation | Impeller for blower/vacuum |
US5667361A (en) * | 1995-09-14 | 1997-09-16 | United Technologies Corporation | Flutter resistant blades, vanes and arrays thereof for a turbomachine |
US5832606A (en) * | 1996-09-17 | 1998-11-10 | Elliott Turbomachinery Co., Inc. | Method for preventing one-cell stall in bladed discs |
US5681145A (en) * | 1996-10-30 | 1997-10-28 | Itt Automotive Electrical Systems, Inc. | Low-noise, high-efficiency fan assembly combining unequal blade spacing angles and unequal blade setting angles |
US5966525A (en) * | 1997-04-09 | 1999-10-12 | United Technologies Corporation | Acoustically improved gas turbine blade array |
JPH11236803A (en) * | 1997-12-03 | 1999-08-31 | United Technol Corp <Utc> | Rotor step for gas turbine engine |
US6082969A (en) * | 1997-12-15 | 2000-07-04 | Caterpillar Inc. | Quiet compact radiator cooling fan |
US7043055B1 (en) * | 1999-10-29 | 2006-05-09 | Cognex Corporation | Method and apparatus for locating objects using universal alignment targets |
JP4075264B2 (en) * | 2000-01-28 | 2008-04-16 | セイコーエプソン株式会社 | Axial fan, centrifugal fan, and electronic equipment using them |
US6447251B1 (en) | 2000-04-21 | 2002-09-10 | Revcor, Inc. | Fan blade |
US20040258531A1 (en) * | 2000-04-21 | 2004-12-23 | Ling-Zhong Zeng | Fan blade |
US6814545B2 (en) * | 2000-04-21 | 2004-11-09 | Revcor, Inc. | Fan blade |
US6712584B2 (en) * | 2000-04-21 | 2004-03-30 | Revcor, Inc. | Fan blade |
US6491499B1 (en) * | 2000-09-27 | 2002-12-10 | Torrington Research Company | Axial flow fan |
US6457941B1 (en) * | 2001-03-13 | 2002-10-01 | The United States Of America As Represented By The Secretary Of The Navy | Fan rotor with construction and safety performance optimization |
US6386830B1 (en) * | 2001-03-13 | 2002-05-14 | The United States Of America As Represented By The Secretary Of The Navy | Quiet and efficient high-pressure fan assembly |
US6599085B2 (en) | 2001-08-31 | 2003-07-29 | Siemens Automotive, Inc. | Low tone axial fan structure |
AU2003218221A1 (en) * | 2002-03-15 | 2003-09-29 | Robert Bosch Corporation | Engine-cooling fan assembly with overlapping fans |
US6789998B2 (en) | 2002-09-06 | 2004-09-14 | Honeywell International Inc. | Aperiodic struts for enhanced blade responses |
KR100484828B1 (en) * | 2002-11-27 | 2005-04-22 | 엘지전자 주식회사 | Refrigerator's cool air circulation axial flow fan |
US6942457B2 (en) * | 2002-11-27 | 2005-09-13 | Revcor, Inc. | Fan assembly and method |
US20050013685A1 (en) * | 2003-07-18 | 2005-01-20 | Ricketts Jonathan E. | Cross flow fan |
US7033137B2 (en) | 2004-03-19 | 2006-04-25 | Ametek, Inc. | Vortex blower having helmholtz resonators and a baffle assembly |
US8180596B2 (en) * | 2004-07-13 | 2012-05-15 | General Electric Company | Methods and apparatus for assembling rotatable machines |
KR20070072850A (en) | 2004-07-16 | 2007-07-06 | 벨 헬리콥터 텍스트론, 인크. | Counter-torque device for a helicopter |
US7654793B2 (en) * | 2005-05-13 | 2010-02-02 | Valeo Electrical Systems, Inc. | Fan shroud supports which increase resonant frequency |
US7597541B2 (en) * | 2005-07-12 | 2009-10-06 | Robert Bosch Llc | Centrifugal fan assembly |
KR101328559B1 (en) * | 2006-02-03 | 2013-11-13 | 한라비스테온공조 주식회사 | Axial flow fan |
KR20080039599A (en) * | 2006-11-01 | 2008-05-07 | 현대자동차주식회사 | Fan structure for a vehicle |
TWI433995B (en) * | 2010-10-15 | 2014-04-11 | Delta Electronics Inc | Impeller |
US8678752B2 (en) | 2010-10-20 | 2014-03-25 | General Electric Company | Rotary machine having non-uniform blade and vane spacing |
US8684685B2 (en) | 2010-10-20 | 2014-04-01 | General Electric Company | Rotary machine having grooves for control of fluid dynamics |
US20140072434A1 (en) * | 2012-09-13 | 2014-03-13 | Asia Vital Components Co., Ltd. | Fan impeller structure of centrifugal fan |
US20160356287A1 (en) * | 2015-06-03 | 2016-12-08 | Twin City Fan Companies, Ltd. | Asymmetric vane fan and method |
US10422350B2 (en) | 2015-07-02 | 2019-09-24 | Apple Inc. | Fan having a blade assembly with different chord lengths |
CN206617363U (en) * | 2017-03-01 | 2017-11-07 | 讯凯国际股份有限公司 | Impeller |
US20190063464A1 (en) * | 2017-08-31 | 2019-02-28 | Ford Global Technologies, Llc | Engine cooling fans with uneven blade spacing |
JP7363328B2 (en) * | 2019-10-09 | 2023-10-18 | ニデック株式会社 | Impeller and axial fan |
CN115419613B (en) * | 2022-08-24 | 2024-02-20 | 雷勃电气(无锡)有限公司 | Special-shaped combined blade low-noise high-efficiency fan |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4569632A (en) * | 1983-11-08 | 1986-02-11 | Airflow Research And Manufacturing Corp. | Back-skewed fan |
US4569631A (en) * | 1984-08-06 | 1986-02-11 | Airflow Research And Manufacturing Corp. | High strength fan |
US4684324A (en) * | 1985-08-02 | 1987-08-04 | Gate S.P.A. | Axial fan, particularly for motor vehicles |
US4685513A (en) * | 1981-11-24 | 1987-08-11 | General Motors Corporation | Engine cooling fan and fan shrouding arrangement |
US4729714A (en) * | 1985-05-02 | 1988-03-08 | Papst-Motoren Gmbh & Co. Kg | Built-in fan |
Family Cites Families (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US332309A (en) * | 1885-12-15 | Screw-propeller | ||
US268292A (en) * | 1882-11-28 | Windmill | ||
US360833A (en) * | 1887-04-05 | vogelsang | ||
US1893184A (en) * | 1929-01-24 | 1933-01-03 | Hoover Co | Fan |
DE568402C (en) * | 1929-11-13 | 1933-01-19 | Siemens Schuckertwerke Akt Ges | Overpressure blading for steam or gas turbines |
US1983606A (en) * | 1931-02-12 | 1934-12-11 | Gen Motors Corp | Fan |
US1868008A (en) * | 1931-04-04 | 1932-07-19 | Automotive Fan & Bearing Co | Fan |
US2098640A (en) * | 1936-05-15 | 1937-11-09 | Hayes Ind Inc | Fan construction |
US2097205A (en) * | 1936-06-16 | 1937-10-26 | Hayes Ind Inc | Multiblade fan construction |
US2238749A (en) * | 1939-01-30 | 1941-04-15 | Clarence B Swift | Fan blade |
US2269049A (en) * | 1940-05-27 | 1942-01-06 | Zellweger Walter | Fan |
US2426270A (en) * | 1943-04-05 | 1947-08-26 | Power Jets Res & Dev Ltd | Blades for axial flow compressors and turbines |
FR1012041A (en) * | 1949-05-21 | 1952-07-02 | Improvements to the wheels and diffusers of turbo-machines | |
US3006603A (en) * | 1954-08-25 | 1961-10-31 | Gen Electric | Turbo-machine blade spacing with modulated pitch |
US2916258A (en) * | 1956-10-19 | 1959-12-08 | Gen Electric | Vibration damping |
GB957393A (en) * | 1962-09-24 | 1964-05-06 | Continental Motors Corp | Improvements in or relating to a noise suppressed fan structure |
US3315749A (en) * | 1965-07-01 | 1967-04-25 | Universal American Corp | Fan construction |
DE1475509B1 (en) * | 1965-09-22 | 1970-07-09 | J M Voith Getriebe Kg | Core ringless hydrodynamic coupling with constant filling |
DE1503520A1 (en) * | 1965-09-22 | 1970-02-26 | Daimler Benz Ag | Impeller of axial or centrifugal compressors |
US3398866A (en) * | 1965-11-12 | 1968-08-27 | Gen Motors Corp | Dishwasher pump assembly with sound damped impeller |
US3356154A (en) * | 1966-11-16 | 1967-12-05 | Ford Motor Co | Flexible blade engine cooling fan |
GB1293553A (en) * | 1969-02-18 | 1972-10-18 | Cav Ltd | Radial flow fans |
CH516747A (en) * | 1970-05-27 | 1971-12-15 | Bbc Brown Boveri & Cie | Method and blading to reduce the snaking movement of a mass particle when flowing through a turbo machine |
DK230975A (en) * | 1974-06-04 | 1975-12-01 | Mitsubishi Heavy Ind Ltd | AXIAL BLESER |
GB1523884A (en) * | 1976-02-26 | 1978-09-06 | Nu Aire Contracts Ltd | Mixed flow fans |
JPS5525555A (en) * | 1978-08-12 | 1980-02-23 | Hitachi Ltd | Impeller |
US4306839A (en) * | 1979-08-23 | 1981-12-22 | The United States Of America As Represented By The Secretary Of The Navy | Semi-tandem marine propeller |
EP0072177B1 (en) * | 1981-08-07 | 1987-01-07 | Holset Engineering Company Limited | Impeller for centrifugal compressor |
SE450635B (en) * | 1982-10-20 | 1987-07-13 | Mitsui Shipbuilding Eng | ship's propeller |
JPS6017296A (en) * | 1983-07-08 | 1985-01-29 | Matsushita Electric Ind Co Ltd | Vane wheel of crossing current blower |
US4548548A (en) * | 1984-05-23 | 1985-10-22 | Airflow Research And Manufacturing Corp. | Fan and housing |
DE3801353C1 (en) * | 1988-01-19 | 1989-03-23 | Rhein-Flugzeugbau Gmbh, 4050 Moenchengladbach, De |
-
1989
- 1989-08-11 US US07/392,769 patent/US5000660A/en not_active Expired - Lifetime
-
1990
- 1990-08-10 EP EP90911885A patent/EP0487563B1/en not_active Expired - Lifetime
- 1990-08-10 DE DE69022730T patent/DE69022730T2/en not_active Expired - Lifetime
- 1990-08-10 WO PCT/US1990/004515 patent/WO1991002165A1/en active IP Right Grant
- 1990-08-10 ES ES90911885T patent/ES2078975T3/en not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4685513A (en) * | 1981-11-24 | 1987-08-11 | General Motors Corporation | Engine cooling fan and fan shrouding arrangement |
US4569632A (en) * | 1983-11-08 | 1986-02-11 | Airflow Research And Manufacturing Corp. | Back-skewed fan |
US4569631A (en) * | 1984-08-06 | 1986-02-11 | Airflow Research And Manufacturing Corp. | High strength fan |
US4729714A (en) * | 1985-05-02 | 1988-03-08 | Papst-Motoren Gmbh & Co. Kg | Built-in fan |
US4684324A (en) * | 1985-08-02 | 1987-08-04 | Gate S.P.A. | Axial fan, particularly for motor vehicles |
Non-Patent Citations (1)
Title |
---|
See also references of EP0487563A4 * |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0546361A1 (en) * | 1991-12-12 | 1993-06-16 | Behr GmbH & Co. | Axial fan |
EP0945625A1 (en) * | 1998-03-23 | 1999-09-29 | SPAL S.r.l. | Axial flow fan |
WO1999049223A1 (en) * | 1998-03-23 | 1999-09-30 | Spal S.R.L. | Axial flow fan |
US6554574B1 (en) | 1998-03-23 | 2003-04-29 | Spal S.R.L. | Axial flow fan |
FR2781843A1 (en) * | 1998-07-28 | 2000-02-04 | Valeo Thermique Moteur Sa | OPTIMIZED COMPACT FAN PROPELLER |
WO2000006913A1 (en) * | 1998-07-28 | 2000-02-10 | Valeo Thermique Moteur | Fan blade |
US6350104B1 (en) | 1998-07-28 | 2002-02-26 | Valeo Thermique Moteur | Fan blade |
WO2008101576A2 (en) * | 2007-02-23 | 2008-08-28 | Sew-Eurodrive Gmbh & Co. Kg | Ventilator wheel, system and transmission line |
WO2008101577A2 (en) * | 2007-02-23 | 2008-08-28 | Sew-Eurodrive Gmbh & Co. Kg | Ventilator wheel, system and transmission line |
WO2008101577A3 (en) * | 2007-02-23 | 2008-10-16 | Sew Eurodrive Gmbh & Co | Ventilator wheel, system and transmission line |
WO2008101576A3 (en) * | 2007-02-23 | 2008-10-23 | Sew Eurodrive Gmbh & Co | Ventilator wheel, system and transmission line |
EP3214316A1 (en) | 2007-02-23 | 2017-09-06 | Sew-Eurodrive GmbH & Co. KG | System and series of gears |
DE102008010912B4 (en) * | 2007-02-23 | 2020-11-12 | Sew-Eurodrive Gmbh & Co Kg | Fan wheel, system and gear series |
FR3010747A1 (en) * | 2013-09-16 | 2015-03-20 | Valeo Systemes Thermiques | AUTOMOBILE FAN WITH OPTIMIZED BLADES FOR ACOUSTICS AND AERODYNAMICS |
WO2017085680A1 (en) * | 2015-11-19 | 2017-05-26 | Spal Automotive S.R.L. | Process for calculating an angular spacing between the blades of an axial fan |
CN108350902A (en) * | 2015-11-19 | 2018-07-31 | 斯佩尔汽车有限公司 | The method of the angular separation between blade for calculating tube-axial fan |
RU195479U1 (en) * | 2019-11-01 | 2020-01-29 | Хаят Шаукат | Axial fan impeller |
Also Published As
Publication number | Publication date |
---|---|
DE69022730D1 (en) | 1995-11-02 |
US5000660A (en) | 1991-03-19 |
EP0487563A4 (en) | 1992-04-09 |
DE69022730T2 (en) | 1996-04-18 |
EP0487563B1 (en) | 1995-09-27 |
EP0487563A1 (en) | 1992-06-03 |
ES2078975T3 (en) | 1996-01-01 |
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