EP0303543B1 - Ventilateur à courant transversal - Google Patents

Ventilateur à courant transversal Download PDF

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Publication number
EP0303543B1
EP0303543B1 EP88402086A EP88402086A EP0303543B1 EP 0303543 B1 EP0303543 B1 EP 0303543B1 EP 88402086 A EP88402086 A EP 88402086A EP 88402086 A EP88402086 A EP 88402086A EP 0303543 B1 EP0303543 B1 EP 0303543B1
Authority
EP
European Patent Office
Prior art keywords
impeller
cross
axis
upstream
leading edge
Prior art date
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
EP88402086A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0303543A1 (fr
Inventor
Jean-Pierre Guezou
Gilles Heid
Pierre Bailleux
Marc Pruvost
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.)
Direction General pour lArmement DGA
Office National dEtudes et de Recherches Aerospatiales ONERA
Original Assignee
Direction General pour lArmement DGA
Office National dEtudes et de Recherches Aerospatiales ONERA
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
Application filed by Direction General pour lArmement DGA, Office National dEtudes et de Recherches Aerospatiales ONERA filed Critical Direction General pour lArmement DGA
Publication of EP0303543A1 publication Critical patent/EP0303543A1/fr
Application granted granted Critical
Publication of EP0303543B1 publication Critical patent/EP0303543B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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

Definitions

  • the technical sector of the present invention is that of transverse current fans applied to the ventilation of a room or a machine or else to the support of an air cushion vehicle, for example a surface effect vessel. .
  • This type of ventilator is well known and was first proposed in 1892 by MORTIER for the ventilation of coal mines.
  • the main feature of this fan is that it has a hunchback type pressure-flow characteristic, the increasing part of which represents between 50 and 75% of the maximum range (or excursion) accessible in flow.
  • the second feature is to present a pressure at zero flow other than zero.
  • Another characteristic of this fan lies in the simultaneous supply of high flow and pressure coefficients, compared to the centrifugal fan which provides, at equal size, only a high pressure coefficient with low flow coefficient and to the axial fan which does not provides on the other hand, at equal size, that a high flow coefficient with a low pressure coefficient.
  • the weak point of this fan traditionally resides in the efficiency obtained which can be improved by playing on the stator shapes.
  • patent DE-A-1 428 071 is known relating to a transverse fan having a characteristic characteristic of stable air flow and being very noisy.
  • Patent DE-A-2 545 036 is also known, improving the fan of the previous patent by a complex system of guide walls and porous walls placed on the path of the fluid to reduce noise.
  • this advantage can be compromised by the fouling of the porous walls after a certain period of use.
  • Patent FR-A-2 481 378 is also known, which aims to reduce the noise level and to provide an increased air flow for the same rotor speed by a particular rounded shape of the downstream volute and volute nozzles and lacrosse.
  • the flow properties of the transverse fan are mainly used and no attempt has ever been made to improve the shapes of the upstream collector and the downstream diffuser to simultaneously obtain a high flow and pressure, while aiming for high efficiency.
  • the aim of the present invention is therefore to define, for the first time, a transverse fan whose characteristics are provided in advance, in order to simultaneously obtain in a technical installation coefficients of flow and pressure which can reach respectively 2.5 to 3 approximately, while controlling the stability of the operating point over the entire flow range and in particular over the increasing part of the pressure-flow characteristic on which it is known that a pumping phenomenon can arise. It is known that such a pumping phenomenon results in periodic pulses in flow and pressure in the downstream circuit, characterized by a pumping frequency and amplitude, which makes the machine unusable in an industrial application.
  • the stock element has between its upstream and downstream nozzles a thickness of between 1 and 40% of the outside diameter De of the wheel.
  • the thickness of the stock element is 16% of the outside diameter De of the wheel.
  • the stock-wheel face is flat and inclined with respect to the ordinate axis at an angle between _20 and 60 °.
  • the stock / wheel face is hollow and produced in the form of an arc of a circle passing through the upstream and downstream beaks of stock element, both placed on a parallel to the Y axis, such that the tangent to the upstream beak delimits an angle with said parallel to the ordinate axis varying between 0 to 60 °.
  • the length (1) of the upstream face of the butt projected onto the abscissa axis is between 90 and 100% of the outside diameter De of the wheel.
  • the upstream face of the butt consists of a flat surface inclined at an angle between 25 and 80 ° relative to the axis of the abscissa.
  • the angle of inclination is equal to 26 ° and the length (1) to 95% of the outside diameter De of the wheel.
  • the upstream stock face consists of an arc of a circle open towards the wheel whose tangent to the upstream stock spout defines with respect to the radius passing through the upstream spout an angle of between 25 and 80 °.
  • the downstream volute is extended by a divergent delimiting an angle of 7 ° relative to the abscissa axis from a point located on a parallel to the ordinate axis passing through the downstream butt stock at a distance from that -this between 60 and 90% of the outside diameter De of the wheel.
  • the downstream volute is delimited in section by a first arc of a circle concentric with the wheel and a second arc of circle connecting the first arc of circle to the divergent.
  • the downstream volute passes through an axis situated on a parallel to the X axis passing through the downstream butt of the butt, at a distance from the latter between 60 and 120% of the external diameter De of the wheel.
  • This distance is equal to 59% of the outside diameter De of the wheel.
  • the wheel is of the type with sharp blades, the internal diameter of which is between 70 and 80% of its external diameter, and each blade has, depending on the external diameter De of the wheel, a radius of curvature of between 10 and 15% , a rope between 10 and 15% and an elongation between 1 and 5.
  • the blades are twisted longitudinally with a helix angle of less than 10 °.
  • the wheel is twisted by rotation of the end plates relative to one another.
  • the butt end element is twisted with a helix angle of less than 10 °.
  • a result of the present invention lies in obtaining a high yield which reaches 70 to 80%.
  • Another result lies in taking advantage of the intrinsic characteristics of the transverse fan to obtain a sheet flow or an air curtain; the flow rate being therefore proportional to the length of the wheel, at constant speed, the value of the reduced aeraulic coefficients is kept.
  • Another result is the increase in the pumping margin.
  • Another result lies in the accessibility to powers of the order of megawatts, while retaining a minimum size compared to that of conventional machines of the same power.
  • the characteristics of a fan are usually defined by the dimensionless coefficients of flow Cd, pressure Cp and efficiency ⁇ according to the relationships: where L is the length of the wheel (m), ⁇ the speed of rotation of the wheel (rd / s), R the radius of the wheel, ⁇ the density of the air (Kg / m3), Qv the flow of the fan (m3 / s) and ⁇ P the pressure variation (Pa).
  • FIG 1 there is shown an embodiment of a transverse fan comprising a wheel 1, rotating in the direction of the arrow F, a stock member 2 and a scroll element 3.
  • the scroll and butt elements constitute the stator of the rotary machine and delimit an upstream part of converging section and a downstream part 4a of diverging section, the latter being followed by a use circuit 4b partially shown.
  • the stock element 2 comprises an upstream face 5 or upstream volute, an upstream spout 6, a wheel-stock face 7, a spout downstream 8 and a downstream face 9.
  • the scroll element 3 comprises an upstream face 10, a scroll beak 11 and a downstream scroll 12.
  • the upstream butt 6 of the butt is placed at a distance from the wheel 1 called the butt 13 of the butt (ECR).
  • the volute nozzle 11 is also placed at a distance from the wheel 1 called volute nozzle air gap 14 (EVR).
  • the position of the upstream spout 6 of the butt is defined, in accordance with FIG. 2, by the angle A BCAM between the axis X and the radius D of the wheel 1 passing through this spout.
  • This angle can be between 290 and 330 °.
  • this angle is 309 ° with zero air gap.
  • the dimension of the air gap 13 is between 2 and 8% of the outside diameter De of the wheel and more particularly between 2 and 3%.
  • the thickness Ec of the stock and its inclination A FRC with respect to the parallel 15 to the axis Y passing through the upstream nozzle 6 of the stock has been shown diagrammatically as the gap ECR zero.
  • the thickness Ec is counted between the planar downstream face 9 and the plane 16 parallel to this face passing through the spout 6.
  • the thickness Ec is between 0.1 and 40% of the external diameter De of the wheel 1 and advantageously between 14 and 18%.
  • the face 7 of the wheel-stock can be either flat or hollow, in order to organize the internal flow of air as a function of the envisaged application.
  • the butt-wheel face 7a shown in FIG. 3, is flat and wedged at an angle A FRC , with respect to the parallel 15, between _30 and + 60 ° and more particularly between _10 and + 10 °.
  • the butt-wheel face 7b represented in FIG. 4, is hollow, in an arc of a circle, the upstream spout 6 and the downstream spout 8 of the butt being in this configuration aligned on the parallel 17 to the axis Y.
  • the center B of curvature of this arc of circle is located on the perpendicular bisector of the cord 18 joining the beaks 6 and 8 and the angle A FRC is determined by the tangent 19 passing through the beak 6 and the cord 18. This angle is between 0 and 60 ° and advantageously between 10 and 25 °. Note that when the angle A FRC is zero, the face 7b is plane.
  • the upstream face 5 of the stock can be either flat 5a (FIG. 5) or hollow 5b (FIG. 6). It extends between the upstream nozzle 6 of the butt and a point M FAC .
  • the face 5a is defined by its angular position relative to the axis X and by its length projected on this same axis.
  • the angle A FAC is between 25 and 80 ° and its projected length (1) is between 90 and 100% of the outside diameter De of the wheel 1.
  • the hollow face 5b is defined by the angle A ′ FAC between the radius of the wheel passing through the upstream nozzle 6 of the stock and the tangent at this point to the shape studied.
  • the angle A ′ FAC is between 25 and 80 ° as above and more particularly between 60 and 78 °.
  • the center C of curvature is located on the perpendicular bisector of the cord 20 passing the beak 6 and the point M FAC .
  • the length (1) of the hollow face projected on an axis parallel to the axis X is between 90 and 100% of the external diameter De of the wheel 1.
  • the volute beak 11 the position of which is shown diagrammatically in FIG. 7, is located on a circular arc 21, at a distance or air gap 14 (EVR) of between 2 and 8% of the external diameter De of the wheel 1.
  • EMR air gap 14
  • L 'arc of a circle 21 is delimited by the angle A BC between 76 and 112 °.
  • This figure also shows the upstream face 10 of the volute beak inclined by the angle A FABV relative to the radius passing through the volute beak 11.
  • the angle A FABV is between 0 and 70 °. These two angles are chosen so as to ensure an optimal supply compatible with the nominal point sought.
  • FIG. 8 represents the downstream volute 12 which is consisting of three parts 21, 22 and 23.
  • Part 21 is an arc always concentric with the wheel 1 and exists when the angle A BC is less than 112 °.
  • the two parts 22 and 23 are defined from the stock element 2 by delimiting a first section denoted SHBCAV (horizontal section of downstream stock tip) parallel to the axis X, such that its length is between 80 and 100 % of the outside diameter De of the wheel 1, and a second section denoted SBCAV (vertical section of downstream butt stock), such that its length is between 60 and 90% of the outside diameter Of the wheel 1.
  • SHBCAV horizontal section of downstream stock tip
  • SBCAV vertical section of downstream butt stock
  • the volute is finally connected to the divergent plane 24 by the planar part 23 extending the latter.
  • the divergent 4b is delimited by a flat surface extending the downstream face 9 of the butt and the flat part 24 making an angle of 7 ° with the axis X. This leads to a fan divergent at 7 °, a value commonly accepted in mechanical mechanics. fluids with regard to obtaining a minimum pressure drop.
  • the wheel of a transverse fan is defined in a known manner by the following parameters: outside and inside diameters, length, number of blades, radius of curvature of the blade, chord of the blade, angles of entry and exit of the blade , flange diameter.
  • outside and inside diameters outside and inside diameters
  • length length
  • number of blades radius of curvature of the blade
  • chord of the blade chord of the blade
  • angles of entry and exit of the blade flange diameter
  • the wheel 1 can be twisted as shown in FIG. 10 by rotation of the flanges 26 and 27 relative to each other by a helix angle A H.
  • the leading edge 28 of each blade 25 then defines a curve having a helix angle A H less than 10 °. This achievement makes it possible, among other things, to reduce the noise and the amplitude of the vibrations.
  • the line described by the volute beak 11 and / or the upstream beak 6 of the butt can be twisted according to the same law.
  • E C / De 16.25%
  • a FRC 0 °
  • a FAC with minimum air gap 40 °
  • Radius of curvature of the upstream stock volute 251 mm
  • a FABV with minimum air gap 40 °
  • S HBCAV with minimum air gap 166 mm or 58.64% of De
  • S VBCAV with minimum air gap 220 mm or 77.73% of De
  • the power obtained is approximately 2 KWatt for a fan 420 mm long, while obtaining a power equivalent using an axial or centrifugal fan would require a diameter and a length of at least 2 to 3 times larger.
  • the ⁇ P and Qv values are measured at the fan outlet.
  • Curve P represents the pressure variation and curve R the efficiency.
  • this fan has an increased pumping margin ⁇ Q compared to conventional machines with a hunchback curve and can be used in a range of flow excursion free of pumping risks.
  • this margin ⁇ Q is of the order of 1 m3 / s. This type of ventilator can therefore be used in particular in the lifting of surface effect vessels.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
EP88402086A 1987-08-13 1988-08-11 Ventilateur à courant transversal Expired - Lifetime EP0303543B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8711522 1987-08-13
FR8711522A FR2619422B1 (fr) 1987-08-13 1987-08-13 Ventilateur a courant transversal

Publications (2)

Publication Number Publication Date
EP0303543A1 EP0303543A1 (fr) 1989-02-15
EP0303543B1 true EP0303543B1 (fr) 1991-05-08

Family

ID=9354165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88402086A Expired - Lifetime EP0303543B1 (fr) 1987-08-13 1988-08-11 Ventilateur à courant transversal

Country Status (8)

Country Link
US (1) US4836743A (es)
EP (1) EP0303543B1 (es)
JP (1) JP2767747B2 (es)
CA (1) CA1337984C (es)
DE (1) DE3862709D1 (es)
ES (1) ES2023267B3 (es)
FR (1) FR2619422B1 (es)
NO (1) NO169360C (es)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4906219A (en) * 1988-08-15 1990-03-06 J. I. Case Company Cleaning system for a combine
KR960703203A (ko) * 1994-04-28 1996-06-19 시게후치 마사토시 다익(多翼) 레이디얼 팬의 설계 방법 및 그 다익 레이디얼 팬(multivane radial fan designing method and multivane radial fan)
JP3632789B2 (ja) * 1995-08-28 2005-03-23 東陶機器株式会社 多翼遠心ファンの設計方法及び多翼遠心ファン
KR0141763B1 (ko) * 1995-12-19 1998-07-01 구자홍 횡류형 송풍기의 리어가이더
JP3649567B2 (ja) * 1998-01-12 2005-05-18 三菱電機株式会社 貫流送風機
US6146092A (en) * 1998-07-13 2000-11-14 Ford Motor Company Centrifugal blower assembly with a diffuser
US6261051B1 (en) * 1998-09-02 2001-07-17 Gordon A. Kolacny Fan duct combination unit
KR100731366B1 (ko) * 2005-11-04 2007-06-21 엘지전자 주식회사 평면 디스플레이 기기의 냉각 장치 및 그 장치의 횡류팬
EP2472190B1 (en) * 2009-08-25 2018-12-05 Mitsubishi Electric Corporation Fan unit and air conditioner equipped with fan unit
WO2011112928A2 (en) * 2010-03-12 2011-09-15 Vornado Air, Llc Spiral tower fan
TWI479083B (zh) * 2012-06-21 2015-04-01 Sunonwealth Electr Mach Ind Co 水平對流扇及其扇框
TWI624589B (zh) * 2016-07-21 2018-05-21 Lai Rong Yi Low head large flow channel turbine

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB757543A (en) * 1953-07-17 1956-09-19 H A Saunders Ltd Improvements relating to hand scoops incorporating weighing mechanism
GB830362A (en) * 1956-05-08 1960-03-16 Machinenfabrik Benninger A G Improvements in transverse flow blowers
US3305665A (en) * 1959-11-17 1967-02-21 Laing Vortex Inc Forced circulation electric heater employing cross-flow type fan
DE1503668B2 (de) * 1963-05-02 1971-02-18 Zenkner, Kurt, Dr Ing , 7500 Karls ruhe Gehaeuse fuer ein querstromgeblaese
GB1102091A (en) * 1964-02-05 1968-02-07 Firth Cleveland Ltd Improvements relating to machines of the cross-flow type for inducing flow of fluid
US3385511A (en) * 1966-08-19 1968-05-28 Lau Blower Co Blower
US3459365A (en) * 1967-12-01 1969-08-05 Torrington Mfg Co Transverse flow blower unit having cavity with restricted opening adjacent cut-off section
DE1951115B2 (de) * 1969-10-10 1976-10-21 Böhler-Zenkner GmbH & Co KG Strömungstechnik, 4005 Meerbusch Querstromgeblaese
AU467912B2 (en) * 1973-08-20 1975-12-18 Yamamoto Teruo Cross-flow fan
DE2545036B2 (de) * 1975-10-08 1979-08-23 Kurt Dr.-Ing. 7505 Ettlingen Zenkner Gehäuse für ein Querstromgebläse
DE8034229U1 (de) * 1980-12-22 1986-07-03 Ltg Lufttechnische Gmbh, 7000 Stuttgart Querstromventilator
DE3326651A1 (de) * 1983-07-23 1985-01-31 Standard Elektrik Lorenz Ag, 7000 Stuttgart Querstromluefter

Also Published As

Publication number Publication date
ES2023267B3 (es) 1992-01-01
FR2619422A1 (fr) 1989-02-17
DE3862709D1 (de) 1991-06-13
US4836743A (en) 1989-06-06
JP2767747B2 (ja) 1998-06-18
NO883600D0 (no) 1988-08-12
CA1337984C (fr) 1996-01-23
NO169360C (no) 1992-06-10
JPH01195991A (ja) 1989-08-07
NO169360B (no) 1992-03-02
EP0303543A1 (fr) 1989-02-15
NO883600L (no) 1989-02-14
FR2619422B1 (fr) 1989-12-08

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