US3695775A - Cross flow blower - Google Patents

Cross flow blower Download PDF

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Publication number
US3695775A
US3695775A US79453A US3695775DA US3695775A US 3695775 A US3695775 A US 3695775A US 79453 A US79453 A US 79453A US 3695775D A US3695775D A US 3695775DA US 3695775 A US3695775 A US 3695775A
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United States
Prior art keywords
rotor
spiral
radius
periphery
percent
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US79453A
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English (en)
Inventor
Kurt Dr Ing Zenkner
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.)
KURT ZENKNER DR ING
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KURT ZENKNER DR ING
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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
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • 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
    • Y10S415/914—Device to control boundary layer

Definitions

  • ABSTRACT A cross flow blower has a plate guide which extends along a spiral curve the distances from which to the periphery of the rotor increase gradually from the beginning of the spiral at the point of the smallest distance between the guide sheet and the periphery of is] 3,695,775 [.451 qc 22.1
  • the invention refers to a cross flow blower and more particularly to a cross flow blower having a wedgeshaped vortex forming tongue to separate the incoming flow from the issuing flow and having, further, a guide plate to guide the flow, the distance from said guide plate to the periphery of the rotor increasing gradually from the inlet up to a spiral form, the said vortex forming tongue having the shape of a wedge-like body, the apex or tip of said tongue being directed towards the periphery of the rotor, the leg on the suction side and the leg on the pressure side of the said wedge-like body enclosing between them an angle of 10 to 60 and the leg on the suction side of the said body or tongue enclosing with the periphery of the rotor a gap narrowing towards the vortex and in direction opposite to the direction of the rotation.
  • a further aim of the invention is to provide a blower of the kind here in question with which departing from the idea that the transport and throughput of energy is proportional to the flow speed and to the variations of the component in the peripheral direction, the shape and the path of the high speed strearn-lines are attended to with especially high carefulness and these high speed streamlines participate as much as possible in the transport of energy.
  • the guide sheet extends along a spiral curve the distances from which to the periphery of the rotor increase gradually from the begin of the spiral at the point of the smallest distance between the guide sheet and the periphery of the rotor up to a maximum, this distance to the periphery of the rotor corresponding at the beginning of the spiral approximatively to 10 30 percent of the radius of the rotor, then increasing after a central angle of about 60 by further 5 to 30 percent of the radius of the rotor, then again increasing after a central angle of about 30 by about to 30 percent of the radius of the rotor, and increase thereafter after a further central angle of about 30 by about 20 to 35 percent, whereafter it increases up to reaching the end of the spiral by about 20 to 50 percent of the radius of the rotor, the end of the spiral being reached after a central angle of about 140 to 190 as seen from the beginning or starting point of the guide plate the part of this guide plate extending after the said end of
  • the shape of the guide sheet is optimally adapted to the distribution of the high speed streamlines.
  • the wedge-like shape of the vortex forming tongue having the above mentioned angle between the leg on the suction side and the leg on the pressure side serves to separate or keep apart the incoming flow from the issuing flow as much as possible.
  • the peripheral component A0 in the equation c.
  • leg of the vortex forming tongue on the suction side with a finely porous or cascade-like shaped wall pervious or permeable for air so that through it finely distributed and energy containing air arrives on the suction side of the blower which air comes from the pressure side of the blower through openings in the pressure side leg, which leg may consist for example also of a finely porous wall pervious or permeable for air, thereby preventing the generation of a boundary layer within the incoming .flow.
  • the arrangement can be such that between the wall on the suction side and the wall on the pressure side there may be arranged a filtering substance pervious for air and producing pressure losses, for example, foamed articial material, glasswool, rock wool filtering material impregnated with artificial resins etc.
  • a filtering substance pervious for air and producing pressure losses for example, foamed articial material, glasswool, rock wool filtering material impregnated with artificial resins etc.
  • FIG. 1 and FIG. 2 are two difierent embodiments of the object of the invention in diagrammatic representation
  • FIG. 3 is a diagram showing the path of the flow within a flower according to the invention and FIG. 4 is a further variation of the invention in schematical representation.
  • FIG. 1 The embodiment of the invention shown in FIG. 1 has a rotor 1, a vortex forming tongue 2 and a guide wall 3 as its most important parts.
  • the rotor l is constructed like a drum and carries on its periphery in a manner known per se equally spaced and uniformly distributed blades held with their axial ends between two end discs.
  • the rotor rotates according to arrow 4 around the rotation axis 5.
  • the vortex forming tongue 2 separates and keeps apart the incoming flow from the issuing flow and has a leg 6 on the suction side and a leg 7 on the pressure side.
  • the guide wall deviates immediately after the inlet 8 from the rotor blading so that the distances between the guide wall and the rotor periphery increase gradually as the guide wall takes the form of a spiral.
  • the guide wall'runs along a spiral curve the distances of which from the periphery of the rotor 1 increase gradually from the beginning 9 of the spiral, i.e. the point where the guide wall and the periphery of the rotor are closest to one another up to a maximum.
  • the distance a between the guide wall and the periphery of the rotor corresponds approximately to 10 30 percent of the radius r of the rotor.
  • the distance a After going through a central angle of about 60 the distance a, is greater, it increases by about 30 percent of the radius r After another central angle of 30, the distance a has increased again by about 30 percent of the radius r After covering a further central angle of 30 the distance between guide wall and periphery of rotor increases up to a value a., which is greater than a by about 20 35 percent of the radius of the rotor.
  • the distance increases again up to a value a which is greater by about 20 50 percent of the radius of the rotor than the value a,
  • the guide wall 3 deviates outwardly from the spiral, that is, it runs either in the direction of the tangent 10 to the end of the spiral (FIG. 1) or along a curve 11 (FIG. 2), the point of infection of which lies in the area of the end of the spiral.
  • a spiral form composed of circular arcs with different radii which are described with centers situated on a circular or elliptical curve which is described about the longitudinal middle axis of the rotor.
  • the different radii associated to the different circular arcs increase gradually as seen from the beginning of the guide wall and than diminish gradually before the maximal distance between the periphery of the rotor and the guide wall has been reached. Finally, they diminish down to the value corresponding to that within the area of the beginning of the guide wall.
  • the curve is composed of circular arcs described with radii which are by about 40 100 percent greater than the radius of the associated rotor.
  • the vortex forming tongue is constructed as a wedge-shaped body the leg 6 of which on the suction side encloses with the leg 7 on the pressure side an angle of about 10 60, the tip or apex of the said tongue being directed towards the periphery of the rotor.
  • a gap 13 which narrows towards the vortex forming tongue and against the direction of rotation according to arrow 4.
  • the distance b between the point 14 of the vortex forming tongue nearest to the periphery of the rotor and the periphery of the rotor corresponds to approximatively 5 15 percent of the outer diameter of the rotor.
  • the tangent 15 to the periphery of the rotor on the point thereof nearest to the vortex forming tongue encloses with the leg 6 on the suction side an angle of about 15 45.
  • the leg 6 on the suction side of the vortex forming tongue is connected with the leg 7 on the pressure side by a rounded surface which extends along an arc of circle described with a radius corresponding to 5 25 percent of the radius of the associated rotor.
  • the arrangement is such that the central angle on the suction side between the beginning 9 of the spiral and the point where the periphery of the rotor and the vortex forming tongue (point 18) are nearest to one another corresponds to approximatively
  • the effective length of the leg 6 of the vortex forming tongue on the suction side corresponds thereby to at least 15 percent of the radius r of the associated rotor.
  • the leg 7' of the vortex forming tongue 2 on the pressure side encloses with the guide sheet 3 an outlet channel 19 which narrows beginning with the area of the issuing flow leaving the blower and thereby accelerates the issuing flow.
  • This narrowing portion of the outlet channel 19 has a length l which corresponds to approximatively 0.75 1.25 of the radius r of the rotor, whereby the arrangement is such that the final speed of the flow issuing from the convergent portion of the outlet channel is greater than that of the flow entering it by about at least 20 percent.
  • the ratio between the smallest distance from the pressure side leg 7 or 7' of the vortex forming tongue 2 or 2' to the guide wall 3 within the outlet area and the radius r of the associated rotor 1 corresponds to approximatively a value between 0.75:1 and 1.50:1 whereas the greatest distance between the pressure side'leg 7 or 7' of the vortex forming tongue 2 or 2' and the guide wall 3 within the out-let area on the one hand and the radius r of the associated rotor 1 on the other hand are in a ratio of between 2:1 and 1:1.
  • At least the leg of the vortex forming tongue on the pressure side is designed as a curve with its concavity facing away from the inlet whereby it runs along a curve which is described with a radius which corresponds to two or three times the radius of the associated rotor.
  • the rotor 1", the vortex forming tongue 2" and the guide wall 3" are associated or arranged with respect to one another according to the invention in such a manner that there results a speed distribution of the incoming flow 25 as shown in the drawings, whereby the high speed streamlines are situated in the area facing towards the vortex forming tongue, whereas with the outlet speed 26 there is obtained a speed distribution with which again the high speed streamlines are directed towards the vortex forming tongue.
  • the construction of the guide wall and of the vortex forming tongue according to the invention promotes such a speed distribution of the flow in optimal manner. Within the rotor the flow is deflected as indicated by the streamline 27.
  • the pressure side leg 30b of the vortex forming tongue may consist, for example, also of a fine-pored wall permeable by air.
  • a partial flow of finely divided and distributed energy containing air flows from the pressure side to the suction side of the blower.
  • the generation of a boundary layer of the oncoming flow is prevented.
  • This filtering sub stance produces pressure losses and has also a sound silencing effect.
  • a cross flow blower having a bladed rotor and a wedge-shaped vortex forming tongue to separate the incoming flow from the issuing flow and having, further, a guide wall to guide the flow, the said guide wall deviating immediately after the inlet from the blading of the rotor whereby the distance from said guide wall to the periphery of the rotor increases gradually from the inlet up to a spiral form, the said vortex forming tongue having the shape of a wedge-like body the apex of which is directed towards the periphery of the rotor, the leg on the suction side and the leg on the pressure side of the said wedge-like body enclosing between them an angle of to 60 and the leg on the suction side of the said tongue enclosing with the periphery of the rotor a gap narrowing towards the vortex and in a direction opposite to the direction of the rotation, wherein the said guide wall extends along a spiral curve the distances of which from the periphery of the rotor
  • suction side leg of the vortex forming tongue and the pressure side leg thereof are connected by a round surface running approximately along an arc of a circle with a radius with corresponds to 5 25 percent of the radius of the rotor.
  • suction side leg of the vortex forming tongue comprises a finely-pored wall pervious to air through which wall finely distributed and energy containing air passes to the suction side of the blower, the said air entering from the pressure side of the blower through openings in the pressure side legs, said air flowing into the suction area preventing thereby the formation of a boundary layer by the oncoming flow.
US79453A 1969-10-10 1970-10-09 Cross flow blower Expired - Lifetime US3695775A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691951115 DE1951115B2 (de) 1969-10-10 1969-10-10 Querstromgeblaese

Publications (1)

Publication Number Publication Date
US3695775A true US3695775A (en) 1972-10-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
US79453A Expired - Lifetime US3695775A (en) 1969-10-10 1970-10-09 Cross flow blower

Country Status (5)

Country Link
US (1) US3695775A (de)
CH (1) CH529925A (de)
DE (1) DE1951115B2 (de)
FR (1) FR2065979A5 (de)
GB (1) GB1318986A (de)

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3809503A (en) * 1971-08-04 1974-05-07 Papst Motoren Kg Fan construction
US4014625A (en) * 1973-08-20 1977-03-29 Teruo Yamamoto Transverse flow fan
US4078870A (en) * 1976-06-16 1978-03-14 International Standard Electric Corporation Tangential blower
US4128364A (en) * 1972-11-23 1978-12-05 Papst-Motoren Kg Radial flow fan with motor cooling and resilient support of rotor shaft
US4705453A (en) * 1983-07-23 1987-11-10 Alcatel N.V. Tangential blower
US4712976A (en) * 1984-05-16 1987-12-15 Standard Elektrik Lorenz Ag Tangential blower
US5094586A (en) * 1989-06-23 1992-03-10 Hitachi, Ltd. Air conditioner employing cross-flow fan
US5484259A (en) * 1994-06-13 1996-01-16 Emerson Electric Co. Low noise centrifugal blower
US5655874A (en) * 1996-06-06 1997-08-12 Carrier Corporation Elliptical vortex wall for transverse fans
WO1998050702A1 (en) * 1997-05-02 1998-11-12 American Standard Inc. Tangential fan cutoff
US5924923A (en) * 1996-08-23 1999-07-20 Mitsubishi Denki Kabushiki Kaisha Air conditioner indoor unit
EP0930472A2 (de) * 1998-01-19 1999-07-21 Mitsubishi Denki Kabushiki Kaisha Querstromlüfter
US5943878A (en) * 1998-05-22 1999-08-31 American Standard Inc. Tangential fan scroll and discharged diffuser design
EP0943876A1 (de) * 1998-03-19 1999-09-22 Electricite De France Wärmetauscher oder Wärmepumpe mit Querstromlüfter
US20070266728A1 (en) * 2006-05-19 2007-11-22 Lg Electronics Inc. Refrigerator
US20100040456A1 (en) * 2008-08-13 2010-02-18 Furui Precise Component (Kunshan) Co., Ltd. Centrifugal fan
US20100126207A1 (en) * 2007-04-04 2010-05-27 Jun Ho Bae Ventilating device and the refrigerator having the same
RU2454698C2 (ru) * 2007-09-07 2012-06-27 Нью Инвайронментал Текнолоджи Гмбх Способ и устройство для непрерывной обработки загрязненных жидкостей
CN103185039A (zh) * 2011-12-29 2013-07-03 富瑞精密组件（昆山）有限公司 薄型风扇
US20130170968A1 (en) * 2011-12-29 2013-07-04 Chih-Jen Liu Heat dissipating fan with lateral air inlet and outlet
US20150354585A1 (en) * 2014-06-05 2015-12-10 Asia Vital Components Co., Ltd. Slim fan structure
CN105526193A (zh) * 2016-02-29 2016-04-27 宁波方太厨具有限公司 一种用于吸油烟机的风机蜗壳
CN106351882A (zh) * 2016-11-10 2017-01-25 华中科技大学 一种蜗舌结构的贯流风机
CN109790842A (zh) * 2016-09-30 2019-05-21 大金工业株式会社 横流式风机及包括该横流式风机的空调装置的室内机组
US10415601B2 (en) * 2017-07-07 2019-09-17 Denso International America, Inc. Blower noise suppressor
CN112283806A (zh) * 2020-10-09 2021-01-29 海信（广东）空调有限公司 空调器
US11002286B2 (en) * 2018-05-04 2021-05-11 Ningbo Fotile Kitchen Ware Co., Ltd. Volute mechanism of a centrifugal fan
CN113859578A (zh) * 2021-10-13 2021-12-31 西北工业大学 一种可减弱地面涡的工艺进气道及其设计方法

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5548154Y2 (de) * 1974-06-19 1980-11-11
JPS5524555A (en) * 1978-08-09 1980-02-21 Matsushita Electric Ind Co Ltd Electrical dust precipitator
DE3016438C2 (de) * 1980-04-29 1985-12-19 Standard Elektrik Lorenz Ag, 7000 Stuttgart Querstromlüfter
DE3048571A1 (de) * 1980-12-22 1982-07-22 Ltg Lufttechnische Gmbh, 7000 Stuttgart Querstromventilator
DE3343594C2 (de) * 1983-12-02 1985-10-03 Rudolf 5982 Neuenrade Bültmann Rohrziehmaschine für nahtlose Rohre
SE444975B (sv) * 1984-03-21 1986-05-20 Bahco Ventilation Ab Luftridaenhet
FR2619422B1 (fr) * 1987-08-13 1989-12-08 Onera (Off Nat Aerospatiale) Ventilateur a courant transversal
GB2234012A (en) * 1989-07-14 1991-01-23 Ibm Dc motor driven centrifugal fan
GB2241118A (en) * 1990-02-15 1991-08-21 Ibm Electrical apparatus with forced air cooling
GB2263502A (en) * 1992-01-17 1993-07-28 Parker Mark & Associates Limit Blower unit.
US6050773A (en) * 1997-06-23 2000-04-18 Carrier Corporation Flow stabilizer for transverse fan

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB980684A (en) * 1960-02-11 1965-01-20 Firth Cleveland Ltd Improvements relating to flow machines for example blowers of the cross flow type
US3398882A (en) * 1965-03-30 1968-08-27 Zenkner Kurt Crossflow blower
US3446426A (en) * 1967-04-03 1969-05-27 Torrington Mfg Co Transverse flow blower for discharging fluid in a path defined by a surface
US3559298A (en) * 1968-09-05 1971-02-02 Horst Theilemann Method for drying or heating or cooling a process material and a device for conducting such method

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB980684A (en) * 1960-02-11 1965-01-20 Firth Cleveland Ltd Improvements relating to flow machines for example blowers of the cross flow type
US3398882A (en) * 1965-03-30 1968-08-27 Zenkner Kurt Crossflow blower
US3446426A (en) * 1967-04-03 1969-05-27 Torrington Mfg Co Transverse flow blower for discharging fluid in a path defined by a surface
US3559298A (en) * 1968-09-05 1971-02-02 Horst Theilemann Method for drying or heating or cooling a process material and a device for conducting such method

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3809503A (en) * 1971-08-04 1974-05-07 Papst Motoren Kg Fan construction
US4128364A (en) * 1972-11-23 1978-12-05 Papst-Motoren Kg Radial flow fan with motor cooling and resilient support of rotor shaft
US4014625A (en) * 1973-08-20 1977-03-29 Teruo Yamamoto Transverse flow fan
US4078870A (en) * 1976-06-16 1978-03-14 International Standard Electric Corporation Tangential blower
US4705453A (en) * 1983-07-23 1987-11-10 Alcatel N.V. Tangential blower
US4712976A (en) * 1984-05-16 1987-12-15 Standard Elektrik Lorenz Ag Tangential blower
US5094586A (en) * 1989-06-23 1992-03-10 Hitachi, Ltd. Air conditioner employing cross-flow fan
US5484259A (en) * 1994-06-13 1996-01-16 Emerson Electric Co. Low noise centrifugal blower
AU707611B2 (en) * 1996-06-06 1999-07-15 Carrier Corporation Elliptical vortex wall for transverse fans
US5655874A (en) * 1996-06-06 1997-08-12 Carrier Corporation Elliptical vortex wall for transverse fans
US5924923A (en) * 1996-08-23 1999-07-20 Mitsubishi Denki Kabushiki Kaisha Air conditioner indoor unit
EP1321678A1 (de) * 1997-05-02 2003-06-25 American Standard Inc. Schalldämpfer für Tangentialgebläse
WO1998050702A1 (en) * 1997-05-02 1998-11-12 American Standard Inc. Tangential fan cutoff
EP0930472A2 (de) * 1998-01-19 1999-07-21 Mitsubishi Denki Kabushiki Kaisha Querstromlüfter
US6086324A (en) * 1998-01-19 2000-07-11 Mitsubishi Denki Kabushiki Kaisha Cross flow fan
EP0930472A3 (de) * 1998-01-19 2002-09-18 Mitsubishi Denki Kabushiki Kaisha Querstromlüfter
EP0943876A1 (de) * 1998-03-19 1999-09-22 Electricite De France Wärmetauscher oder Wärmepumpe mit Querstromlüfter
FR2776369A1 (fr) * 1998-03-19 1999-09-24 Electricite De France Emetteur de chaud ou de froid ou pompe a chaleur a ventilateur tangentiel
US5943878A (en) * 1998-05-22 1999-08-31 American Standard Inc. Tangential fan scroll and discharged diffuser design
US20070266728A1 (en) * 2006-05-19 2007-11-22 Lg Electronics Inc. Refrigerator
US7762100B2 (en) * 2006-05-19 2010-07-27 Lg Electronics Inc. Refrigerator
US20100126207A1 (en) * 2007-04-04 2010-05-27 Jun Ho Bae Ventilating device and the refrigerator having the same
RU2454698C2 (ru) * 2007-09-07 2012-06-27 Нью Инвайронментал Текнолоджи Гмбх Способ и устройство для непрерывной обработки загрязненных жидкостей
US20100040456A1 (en) * 2008-08-13 2010-02-18 Furui Precise Component (Kunshan) Co., Ltd. Centrifugal fan
US8083477B2 (en) * 2008-08-13 2011-12-27 Furui Precise Component (Kunshan) Co., Ltd. Centrifugal fan
CN103185039A (zh) * 2011-12-29 2013-07-03 富瑞精密组件（昆山）有限公司 薄型风扇
US20130170968A1 (en) * 2011-12-29 2013-07-04 Chih-Jen Liu Heat dissipating fan with lateral air inlet and outlet
US9388826B2 (en) * 2011-12-29 2016-07-12 Foxconn Technology Co., Ltd. Heat dissipating fan with lateral air inlet and outlet
TWI548814B (zh) * 2011-12-29 2016-09-11 鴻準精密工業股份有限公司 薄型風扇
CN103185039B (zh) * 2011-12-29 2016-11-23 富瑞精密组件（昆山）有限公司 薄型风扇
US20150354585A1 (en) * 2014-06-05 2015-12-10 Asia Vital Components Co., Ltd. Slim fan structure
US9655278B2 (en) * 2014-06-05 2017-05-16 Asia Vital Components Co., Ltd. Slim fan structure
CN105526193B (zh) * 2016-02-29 2019-02-26 宁波方太厨具有限公司 一种用于吸油烟机的风机蜗壳
CN105526193A (zh) * 2016-02-29 2016-04-27 宁波方太厨具有限公司 一种用于吸油烟机的风机蜗壳
CN109790842A (zh) * 2016-09-30 2019-05-21 大金工业株式会社 横流式风机及包括该横流式风机的空调装置的室内机组
EP3505766A4 (de) * 2016-09-30 2020-04-08 Daikin Industries, Ltd. Querstromgebläse und innenraumeinheit einer klimaanlage damit
US11396879B2 (en) * 2016-09-30 2022-07-26 Daikin Industries, Ltd. Cross-flow blower and indoor unit of air-conditioning device equipped with same
CN106351882B (zh) * 2016-11-10 2018-01-02 华中科技大学 一种具有蜗舌结构的贯流风机
CN106351882A (zh) * 2016-11-10 2017-01-25 华中科技大学 一种蜗舌结构的贯流风机
US10415601B2 (en) * 2017-07-07 2019-09-17 Denso International America, Inc. Blower noise suppressor
US11002286B2 (en) * 2018-05-04 2021-05-11 Ningbo Fotile Kitchen Ware Co., Ltd. Volute mechanism of a centrifugal fan
CN112283806A (zh) * 2020-10-09 2021-01-29 海信（广东）空调有限公司 空调器
CN113859578A (zh) * 2021-10-13 2021-12-31 西北工业大学 一种可减弱地面涡的工艺进气道及其设计方法

Also Published As

Publication number Publication date
FR2065979A5 (de) 1971-08-06
GB1318986A (en) 1973-05-31
DE1951115A1 (de) 1971-04-22
CH529925A (de) 1972-10-31
DE1951115B2 (de) 1976-10-21

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