EP2172655B1 - Doppelt-Axialgebläse mit gegenläufig drehenden Rotoren - Google Patents

Doppelt-Axialgebläse mit gegenläufig drehenden Rotoren Download PDF

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Publication number
EP2172655B1
EP2172655B1 EP08790949.5A EP08790949A EP2172655B1 EP 2172655 B1 EP2172655 B1 EP 2172655B1 EP 08790949 A EP08790949 A EP 08790949A EP 2172655 B1 EP2172655 B1 EP 2172655B1
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EP
European Patent Office
Prior art keywords
support frame
half portion
main body
housing
cushioning member
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EP08790949.5A
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English (en)
French (fr)
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EP2172655A4 (de
EP2172655A1 (de
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designation of the inventor has not yet been filed The
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Sanyo Electric Co Ltd
Sanyo Denki Co Ltd
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Sanyo Electric Co Ltd
Sanyo Denki Co Ltd
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Publication of EP2172655A1 publication Critical patent/EP2172655A1/de
Publication of EP2172655A4 publication Critical patent/EP2172655A4/de
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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
    • F04D19/00—Axial-flow pumps
    • F04D19/007—Axial-flow pumps multistage fans
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/64—Mounting; Assembling; Disassembling of axial pumps
    • F04D29/644—Mounting; Assembling; Disassembling of axial pumps especially adapted for elastic fluid pumps
    • F04D29/646—Mounting or removal of fans
    • 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
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations

Definitions

  • the present invention relates to a counter-rotating axial flow fan for use to cool the inside of an electric device and the like.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 2004-278370 (Patent Document 1) and US Patent No. 7,156,611 (Patent Document 2) each disclose a counter-rotating axial flow fan including a housing including a housing main body having defined therein an air channel having a suction port at one end in an axial direction and a discharge port at the other end in the axial direction, and a motor support frame disposed at a center portion of the air channel.
  • a first impeller rotated by a first motor is disposed in a first space in the housing between the motor support frame and the suction port.
  • a second impeller rotated by a second motor is disposed in a second space in the housing between the motor support frame and the discharge port.
  • the first impeller rotates in the opposite direction to the second impeller.
  • the housing includes a first split housing unit and a second split housing unit coupled to each other by a coupling structure.
  • the first split housing unit includes a first housing main body half portion including a first cylindrical air channel half portion having defined therein a main portion of the first space, and a first support frame half portion which is one of two pieces obtained by splitting the motor support frame along an imaginary reference split plane extending in a radial direction perpendicular to the axial direction.
  • the second split housing unit includes a second housing main body half portion including a second cylindrical air channel half portion having defined therein a main portion of the second space, and a second support frame half portion which is the other of the two pieces obtained by splitting the motor support frame along the imaginary reference split plane.
  • vibration increases in a plurality of rotational speed ranges (resonance ranges) as the rotational speeds of the first and second motors are increased. If the counter-rotating axial flow fan is used within any of such rotational speed ranges with increased vibration, the counter-rotating axial flow fan may produce significant vibration, which may result in significant noise.
  • An object of the present invention is to provide a counter-rotating axial flow fan in which vibration generation may be reduced more than ever in a wide rotational speed range.
  • the present invention provides a counter-rotating axial flow fan having the characterizing features of claim 1.
  • opposite surfaces entirely contact each other means that opposed surfaces contact each other through a large number of point contacts as seen from a microscopic point of view.
  • a plurality of independent air bubbles are dispersed in the soft cushioning member adopted in the present invention.
  • the independent air bubbles may include not only individual air bubbles but also large independent air bubbles formed by incorporating a plurality of air bubbles. When such a cushioning member is used, it is possible to generally suppress an increase in vibration over a wide rotational speed range from a low rotational speed range to a high rotational speed range.
  • Specific preferred embodiments of the soft cushioning member with a plurality of independent air bubbles dispersed therein include an acrylic foam sheet. If an acrylic foam sheet is used as the soft cushioning member, the thickness of the acrylic foam sheet is preferably not less than 0.4 mm and not more than 0.8 mm.
  • the thickness of the acrylic foam sheet is less than 0.4 mm, the thickness of the cushioning member itself is too small to provide a sufficient vibration absorption effect. If the thickness of the acrylic foam sheet is more than 0.8 mm, it is necessary to separately provide a gap in which the acrylic foam sheet is to be disposed between the first support frame half portion and the second support frame half portion. However, providing such a gap is not preferred because it changes the resonance frequencies of vibration and thus complicates measures taken against the vibration.
  • the specific soft cushioning member used in the present invention also serves a function of reducing vibration produced between the first support frame half portion and the second support frame half portion.
  • the soft cushioning member may be entirely disposed between the first support frame half portion and the second support frame half portion.
  • the first and second split housing units may be formed from a synthetic resin material, or may be formed from a metal material such as aluminum.
  • Fig. 1 is an exploded cross-sectional view of a half portion of a counter-rotating axial flow fan according to an embodiment of the present invention.
  • Fig. 2 is an exploded perspective view of the counter-rotating axial flow fan.
  • the counter-rotating axial flow fan according to the embodiment includes a housing 1, a first motor 3, a first impeller 5, a second motor 7, and a second impeller 9.
  • the first impeller 5 is disposed in a first space S1 defined in the housing 1 between a motor support frame (23, 53) to be discussed later and a suction port 11a, and includes a plurality of blades 6.
  • the first motor 3 includes a first rotary shaft 4 to which the first impeller 5 is fixed to rotate the first impeller 5 in a first rotational direction in the first space S1.
  • the second impeller 9 is disposed in a second space S2 defined in the housing 1 between the motor support frame (23, 53) and the discharge port 13b, and includes a plurality of blades 10.
  • the second motor 7 includes a second rotary shaft 8 to which the second impeller 9 is fixed to rotate the second impeller 9 in a second rotational direction opposite the first rotational direction in the second space S2.
  • the housing 1 is configured by assembling a first split housing unit 11 and a second split housing unit 13 via a coupling structure.
  • the first split housing unit 11 is formed from a synthetic resin material or a metal material such as aluminum.
  • the first split housing unit 11 includes a first housing main body half portion 15 and a first support frame half portion 17 integrally formed with each other.
  • the first housing main body half portion 15 includes first and second flange portions 19 and 20 and a first cylindrical air channel half portion 21.
  • the first flange portion 19 includes first to fourth corners 19a to 19d arranged in a circumferential direction of the rotary shaft 4 (hereinafter simply referred to as "circumferential direction") arranged on a common axis A of the first and second motors 3 and 7.
  • the second flange portion 20 includes the suction port 11a at one end in the direction of the common axis A.
  • Four hole portions 19e are respectively formed at the four corners of the first flange portion 19 (the first to fourth corners 19a to 19d) to serve as engaged portions for use in forming a coupling structure with the second split housing unit 13.
  • the details of the shape of the hole portions 19e and the details of the engagement relationship between the hole portions 19e and the hook portions 49 forming engaging portions to be discussed later are the same as the relationship between hole portions and hook portions forming a coupling structure disclosed in Japanese Unexamined Patent Application Publication No. 2004-278370 ( US Patent No. 7,156,611 ), and therefore are not described herein.
  • the second flange portion 20 is formed with through holes 20a through which mounting members for mounting the counter-rotating axial flow fan to an electric device are to be inserted.
  • the first and second flange portions 19 and 20 are integrally formed with both ends of the first cylindrical air channel half portion 21.
  • the first cylindrical air channel half portion 21 extends in an axial direction of the rotary shafts 4 and 8 (hereinafter simply referred to as "axial direction") arranged on the common axis A.
  • the first support frame half portion 17 includes a first support frame main body half portion 23 to which the first motor 3 is fixed and three first web half portions 25.
  • the first support frame main body half portion 23 includes a circular plate portion 23b having a cylindrical boss portion 23a at a center portion thereof, and a peripheral wall portion 23c extending in the axial direction from the outer peripheral portion of the circular plate portion 23b.
  • a first metallic bearing holder 27 made of brass is fixedly fitted in the boss portion 23a.
  • a base plate 29 of a stator of the first motor 3 is disposed to block a space surrounded by the circular plate portion 23b and the peripheral wall portion 23c.
  • a stator core 33 including a plurality of winding portions 31 is fitted with the bearing holder 27.
  • the three first web half portions 25 are disposed between the peripheral wall portion 23c of the first support frame main body half portion 23 and an inner peripheral surface of the first housing main body half portion 15 at predetermined intervals in the circumferential direction to couple the first support frame main body half portion 23 and the first housing main body half portion 15.
  • a cup-shaped member 35 made of a magnetically permeable material is fixed to one end of the rotary shaft 4 to support the impeller 5 including the plurality of blades 6.
  • a plurality of permanent magnets 37 are fixed to the inner peripheral portion of the cup-shaped member 35.
  • the second split housing unit 13 is also formed from a synthetic resin material or a metal material such as aluminum. As shown in Fig. 1 , the second split housing unit 13 includes a second housing main body half portion 39 and a second support frame half portion 41 integrally formed with each other.
  • the second housing main body half portion 39 includes first and second flange portions 43 and 45 and a second cylindrical air channel half portion 47.
  • the first flange portion 43 includes four corners, namely first to fourth corners 43a to 43d, arranged in a circumferential direction of the rotary shaft 8 (hereinafter simply referred to as "circumferential direction") arranged on the common axis A of the first and second motors 3 and 7.
  • hook portions 49 and four projections 51 are respectively integrally formed with the four corners of the first flange portion 43 (the first to fourth corners 43a to 43d) to serve as engaging portions for use in forming a coupling structure with the first split housing unit 11.
  • the details of the engagement relationship of the hook portions 49 and the projections 51 with the hole portions 19e are the same as the relationship between hole portions and hook portions forming a coupling structure disclosed in Japanese Unexamined Patent Application Publication No. 2004-278370 .
  • the hook portions 49 are partly fitted in the hole portions 19e, and the second split housing unit 13 is rotated by a predetermined angle about the common axis A.
  • the second flange portion 45 is formed with through holes 45a through which mounting members for mounting the counter-rotating axial flow fan to an electric device are to be inserted.
  • the first and second flange portions 43 and 45 are integrally formed with both ends of the second cylindrical air channel half portion 47.
  • the second cylindrical air channel half portion 47 extends in the axial direction (the axial direction of the rotary shafts 4 and 8 arranged on the common axis A).
  • the second support frame half portion 41 includes a second support frame main body half portion 53 to which the second motor 7 is fixed and three second web half portions 55.
  • the second support frame main body half portion 53 includes a circular plate portion 53b having a cylindrical boss portion 53a at a center portion thereof, and a peripheral wall portion 53c extending in the axial direction from the outer peripheral portion of the circular plate portion 53b.
  • a second metallic bearing holder 57 made of brass is fixedly fitted in the boss portion 53a.
  • a base plate 59 of a stator of the second motor 7 is disposed to block a space surrounded by the circular plate portion 53b and the peripheral wall portion 53c.
  • a stator core 63 including a plurality of winding portions 61 is fitted with the bearing holder 57.
  • the three second web half portions 55 are disposed between the peripheral wall portion 53c of the second support frame main body half portion 53 and an inner peripheral surface of the second housing main body half portion 39 at predetermined intervals in the circumferential direction to couple the second support frame main body half portion 53 and the second housing main body half portion 39.
  • one web half portion has a groove 55A formed for receiving lead wires.
  • a cup-shaped member 65 made of a magnetically permeable material is fixed to one end of the rotary shaft 8 to support the impeller 9 including the plurality of blades 10.
  • a plurality of permanent magnets 67 are fixed to the inner peripheral portion of the cup-shaped member 65.
  • the first and second support frame half portions 17 and 41 are assembled to form the motor support frame (23, 53).
  • the first and second support frame half portions 17 and 41 are formed by splitting the motor support frame (23, 53) into two pieces along a split plane extending in a radial direction perpendicular to the axial direction in which the common axis A extends.
  • the coupling structure and the first and second split housing units 11 and 13 are configured such that an opposed surface of the first support frame half portion 17 and an opposed surface of the second support frame half portion 41 entirely contact each other when the four engaging portions (the four hook portions 49) and the four engaged portions (the four hole portions 19e) are completely engaged with each other.
  • a soft disk-like cushioning member 71 with a plurality of independent air bubbles dispersed therein is disposed between the first support frame half portion 17 and the second support frame half portion 41, specifically between the circular plate portion 23b of the first support frame main body half portion 23 and the circular plate portion 53b of the second support frame main body half portion 53.
  • an acrylic foam sheet may be used as the soft cushioning member 71.
  • the cushioning member 71 is disposed as it is compressed with the four hook portions 49 forming the plurality of engaging portions and the four hole portions 19e forming the plurality of engaged portions completely engaged with each other.
  • the cushioning member 71 When the cushioning member 71 with a plurality of independent air bubbles dispersed therein is compressed, the cushioning member 71 produces a restoring force substantially evenly from its entirety to return from a compressed state to an original state.
  • the restoring force acts in a direction to release the engagement between the plurality of engaging portions (the four hook portions 49) and the plurality of engaged portions.
  • the coupling force between the plurality of engaging portions (the four hook portions 49) and the plurality of engaged portions (the edge portions around the four hole portions 19e) is strengthened, which prevents generation of a large gap between the first and second split housing units 11 and 13 which will cause vibration therebetween, and to reduce vibration that is actually produced.
  • the cushioning member 71 also serves a function of absorbing vibration produced between the first support frame half portion 17 and the second support frame half portion 41 to reduce such vibration. As a result, according to the present invention, it is possible to generally suppress an increase in vibration within a wide rotational speed range compared to the related art.
  • the soft cushioning member 71 is disposed only between the circular plate portion 23b of the first support frame main body half portion 23 and the circular plate portion 53b of the second support frame main body half portion 53 to obtain favorable results.
  • an enhanced vibration suppression effect is obtained by disposing a soft cushioning member also between the first web half portions 25 and the second web half portions 55.
  • Figs. 3 to 5 are each a graph showing the results of vibration measurement tests.
  • the vibration acceleration (m/s 2 ) at a measurement location M1 a portion of the first flange portion 43 of the second split housing unit 13) in the circumferential direction and the vibration acceleration (m/s 2 ) at a measurement location M2 (near a through hole 20a of the second flange portion 20 of the first split housing unit 11) at the discharge port in the axial direction were measured, and the obtained vibration accelerations (m/s 2 ) were synthesized and plotted on a graph.
  • FIG. 3A is a graph showing the results of measuring the relationship between the rotational speed (the rotational speed of the second motor rotating at high speeds) and the vibration acceleration of vibration produced when the present invention is applied to a counter-rotating axial flow fan available from the applicant (Sanyo Denki Co., Ltd.) under the product number 9CRA0412P5J03, and when the present invention is not applied thereto.
  • X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a soft cushioning member 71 (Embodiment 1)
  • Y indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with no cushioning member 71 (Comparative Example 1).
  • a cushioning member commercially available from Sumitomo 3M Limited under the product name Y-4615 was used. From the measurement results, it is found that generation of vibration was suppressed in a wide rotational speed range from a low rotational speed range to a high rotational speed range by using the cushioning member.
  • Fig. 3B is a graph showing the results of measuring the relationship between the rotational speed (the rotational speed of the second motor rotating at high speeds) and the vibration acceleration of vibration produced when the present invention is applied to another type of counter-rotating axial flow fan also available from the applicant (Sanyo Denki Co., Ltd.) but under a different product number 9CRA0412P4J03 and of different dimensions from the counter-rotating axial flow fan used in Fig. 3A , and when the present invention is not applied thereto.
  • Fig. 3B is a graph showing the results of measuring the relationship between the rotational speed (the rotational speed of the second motor rotating at high speeds) and the vibration acceleration of vibration produced when the present invention is applied to another type of counter-rotating axial flow fan also available from the applicant (Sanyo Denki Co., Ltd.) but under a different product number 9CRA0412P4J03 and of different dimensions from the counter-rotating axial flow fan used in Fig. 3A , and when the present invention is not applied thereto.
  • X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member 71 (Embodiment 2)
  • Y indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with no cushioning member 71 (Comparative Example 2).
  • the soft cushioning member used was the same as that used in Fig. 3A . Also from the measurement results of these embodiments, it is found that generation of large vibration was significantly suppressed in a wide rotational speed range from a low rotational speed range to a high rotational speed range by using the cushioning member.
  • Fig. 4A is a graph showing the results of measuring the relationship between the rotational speed (the rotational speed of the second motor rotating at high speeds) and the vibration acceleration of vibration produced when the present invention is applied to a counter-rotating axial flow fan produced by and available from a manufacturer other than the applicant, and when the present invention is not applied thereto.
  • X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member 71 (Embodiment 3)
  • Y indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with no cushioning member 71 (Comparative Example 3).
  • the cushioning member used was the same as that used in Fig. 3A . From the measurement results, it is found that generation of vibration was generally suppressed through the entire rotational speed range by using the cushioning member.
  • Fig. 4B is a graph showing the results of measuring the relationship between the rotational speed (the rotational speed of the second motor rotating at high speeds) and the vibration acceleration of vibration produced when the present invention is applied to another type of counter-rotating axial flow fan produced by and available from a manufacturer other than the applicant, and when the present invention is not applied thereto.
  • X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member 71 (Embodiment 4)
  • Y indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with no cushioning member 71 (Comparative Example 4).
  • the cushioning member used was the same as that used in Fig. 3A . From the measurement results, it is found that generation of vibration was generally suppressed through the entire rotational speed range by using the cushioning member.
  • Fig. 5 is a graph showing the results of measuring the relationship between the rotational speed (the rotational speed of the second motor rotating at high speeds) and the vibration acceleration of vibration produced by the same counter-rotating axial flow fan as in Fig. 3 under the same measurement conditions as in Fig. 3 , where the thickness of the acrylic foam sheet was changed, a cushioning member made of a material other than the acrylic foam was used, no cushioning member was used, and a gap was positively provided in place of a cushioning member.
  • the "dotted line” indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with the soft cushioning member 71 formed by an acrylic foam sheet having a thickness of 0.4 mm (Embodiment 5).
  • the “broken line” indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with the cushioning member 71 formed by an acrylic foam sheet having a thickness of 0.8 mm (Embodiment 6).
  • the “thick solid line” indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with no cushioning member 71 (Comparative Example 5).
  • the "thick broken line” indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a gap of 0.2 mm positively provided between the first support frame main body half portion 23 and the second support frame main body half portion 53 (Comparative Example 6).
  • the normal “solid line” indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member formed by an aluminum sheet having a thickness of 0.46 mm (Comparative Example 7).
  • the “dash and dot line” indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member formed by a plastic sheet having a thickness of 0.5 mm (Comparative Example 8).
  • the thickness of the acrylic foam sheet used as the cushioning member 71 in a range from 0.4 mm to 0.8 mm. If the thickness of the acrylic foam sheet is less than 0.4 mm, it is expected that the thickness of the cushioning member itself is too small to provide a necessary and sufficient vibration absorption effect. If the thickness of the acrylic foam sheet is more than 0.8 mm, it is necessary to separately provide a gap in which the thick acrylic foam sheet is to be disposed between the first support frame half portion and the second support frame half portion. It is not preferable to positively provide a gap because the effect of the shift phenomenon, as discussed earlier when a gap of 0.2 mm was provided, appears.
  • the cushioning member 71 is disposed only between the circular plate portion 23b of the first support frame main body half portion 23 and the circular plate portion 53b of the second support frame main body half portion 53. However, it is a matter of course that the cushioning member 71 may also be disposed between the first web half portions 25 and the second web half portions 55.
  • a soft cushioning member with a plurality of independent air bubbles dispersed therein is disposed between a first support frame half portion and a second support frame half portion, the cushioning member being compressed when a plurality of engaging portions and a plurality of engaged portions are completely engaged with each other. Therefore, it is possible to generally suppress an increase in vibration over a wide rotational speed range compared to the related art.

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  • General Engineering & Computer Science (AREA)
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Claims (5)

  1. Gegenläufiger Axiallüfter, umfassend:
    ein Gehäuse (1), das einen Gehäusehauptkörper, der einen Luftkanal aufweist, der in demselben festgelegt ist und der an einem Ende in einer axialen Richtung einen Sauganschluss (11a) und an dem anderen Ende in der axialen Richtung einen Druckanschluss (13b) aufweist, und einen Motorstützrahmen (23, 53) aufweist, der an einem mittleren Abschnitt des Luftkanals angeordnet ist;
    ein erstes Laufrad (5), das in einem ersten Raum (S1) angeordnet ist, der in dem Gehäuse (1) zwischen dem Motorstützrahmen (23, 53) und dem Sauganschluss (11a) festgelegt ist, und eine Vielzahl von Schaufeln (6) umfasst;
    einen ersten Motor (3), der eine erste Drehwelle (4) aufweist, an der das erste Laufrad (5) befestigt ist, um das erste Laufrad in einer ersten Drehrichtung in dem ersten Raum zu drehen;
    ein zweites Laufrad (9), das in einem zweiten Raum (S2) angeordnet ist, der in dem Gehäuse (1) zwischen dem Motorstützrahmen (23, 53) und dem Druckanschluss (13b) festgelegt ist, und eine Vielzahl von Schaufeln (10) umfasst; und
    einen zweiten Motor (7), der eine zweite Drehwelle (8) aufweist, an der das zweite Laufrad (9) befestigt ist, um das zweite Laufrad in einer entgegengesetzt zu der ersten Drehrichtung verlaufenden zweiten Drehrichtung in dem zweiten Raum (S2) zu drehen,
    wobei der Motorstützrahmen (23, 53) einen Stützrahmenhauptkörper (17, 41), der sich an dem mittleren Abschnitt des Luftkanals befindet, und eine Vielzahl von Stegen (25, 55) umfasst, die zwischen dem Stützrahmenhauptkörper (17, 41) und dem Gehäusehauptkörper in vorgegebenen Abständen in einer Umfangsrichtung der Drehwellen angeordnet sind, um den Stützrahmenhauptkörper und den Gehäusehauptkörper (15, 39) zu koppeln,
    wobei das Gehäuse (1) eine erste geteilte Gehäuseeinheit (11) und eine zweite geteilte Gehäuseeinheit (13) umfasst, die durch eine mechanische Kopplungsstruktur miteinander gekoppelt sind,
    wobei die erste geteilte Gehäuseeinheit (11) einen ersten Gehäusehauptkörperhalbabschnitt (15), der einen ersten zylindrischen Halbabschnitt (21) des Luftkanals umfasst, der den Sauganschluss (11a) an einem Ende aufweist, und der einen Hauptabschnitt des ersten Raums (S1) aufweist, der in demselben festgelegt ist, und einen ersten Stützrahmenhalbabschnitt (17) umfasst, der einer von zwei Teilen ist, die dadurch erhalten werden, dass der Motorstützrahmen (23, 53) entlang einer Teilungsebene geteilt wird, die sich in einer rechtwinklig zu der axialen Richtung verlaufenden radialen Richtung erstreckt,
    wobei die zweite geteilte Gehäuseeinheit (13) einen zweiten Gehäusehauptkörperhalbabschnitt (39), der einen zweiten zylindrischen Halbabschnitt (47) des Luftkanals umfasst, der den Druckanschluss (13b) an einem Ende aufweist, und der einen Hauptabschnitt des zweiten Raums (S2) aufweist, der in demselben festgelegt ist, und einen zweiten Stützrahmenhalbabschnitt (41) umfasst, der der andere der zwei Teile ist, die dadurch erhalten werden, dass der Motorstützrahmen (23, 53) entlang der Teilungsebene geteilt wird,
    wobei die Kopplungsstruktur eine Vielzahl von Eingriffsabschnitten (49), die einstückig mit dem ersten Gehäusehauptkörperhalbabschnitt (15) der ersten geteilten Gehäuseeinheit (11) ausgebildet und in Abständen in der Umfangsrichtung angeordnet sind, und eine Vielzahl von eingreifbaren Abschnitten (19e) umfasst, die einstückig mit dem zweiten Gehäusehauptkörperhalbabschnitt (39) der zweiten geteilten Gehäuseeinheit (13) ausgebildet und in Abständen in der Umfangsrichtung angeordnet sind, um mit der Vielzahl von Eingriffsabschnitten (49) einzugreifen, und
    wobei die Kopplungsstruktur und die erste und die zweite geteilte Gehäuseeinheit (11 und 13) auf eine solche Weise ausgebildet sind, dass sich gegenüberliegende Flächen des ersten und des zweiten Stützrahmenhalbabschnitts (17 und 41) vollständig berühren, wenn die Vielzahl von Eingriffsabschnitten (49) und die Vielzahl von eingreifbaren Abschnitten (19e) vollständig miteinander eingreifen, dadurch gekennzeichnet, dass:
    ein weiches Dämpfungselement (71) mit einer Vielzahl von in demselben dispergierten unabhängigen Luftblasen zwischen dem ersten Stützrahmenhalbabschnitt (17) und dem zweiten Stützrahmenhalbabschnitt (41) angeordnet ist, wobei das Dämpfungselement (71) zusammengedrückt wird, wenn die Vielzahl von Eingriffsabschnitten (49) und die Vielzahl von eingreifbaren Abschnitten (19e) vollständig miteinander eingreifen.
  2. Gegenläufiger Axiallüfter nach Anspruch 1, wobei
    der erste Stützrahmenhalbabschnitt (17) einen ersten Stützrahmenhauptkörperhalbabschnitt (23) umfasst, an dem der erste Motor (3) befestigt ist,
    der zweite Stützrahmenhalbabschnitt (41) einen zweiten Stützrahmenhauptkörperhalbabschnitt (53) umfasst, an dem der zweite Motor (7) befestigt ist, und
    das Dämpfungselement (71) zwischen dem ersten Stützrahmenhauptkörperhalbabschnitt (23) und dem zweiten Stützrahmenhauptkörperhalbabschnitt (53) angeordnet ist.
  3. Gegenläufiger Axiallüfter nach Anspruch 1 oder 2, wobei
    die erste und die zweite geteilte Gehäuseeinheit (11 und 13) aus einem Kunstharzmaterial gebildet sind.
  4. Gegenläufiger Axiallüfter nach Anspruch 1 oder 2, wobei
    die erste und die zweite geteilte Gehäuseeinheit (11 und 13) aus Aluminium gebildet sind.
  5. Gegenläufiger Axiallüfter nach Anspruch 1 oder 2, wobei
    das Dämpfungselement (71) eine Akrylschaumplatte mit einer Dicke von mindestens 0,4 mm und höchstens 0,8 mm ist.
EP08790949.5A 2007-07-12 2008-07-08 Doppelt-Axialgebläse mit gegenläufig drehenden Rotoren Active EP2172655B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007183756 2007-07-12
PCT/JP2008/062312 WO2009008415A1 (ja) 2007-07-12 2008-07-08 二重反転式軸流送風機

Publications (3)

Publication Number Publication Date
EP2172655A1 EP2172655A1 (de) 2010-04-07
EP2172655A4 EP2172655A4 (de) 2017-04-05
EP2172655B1 true EP2172655B1 (de) 2018-10-24

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US (1) US20100189544A1 (de)
EP (1) EP2172655B1 (de)
JP (1) JP5386353B2 (de)
CN (1) CN101755130B (de)
TW (1) TW200918760A (de)
WO (1) WO2009008415A1 (de)

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Also Published As

Publication number Publication date
CN101755130A (zh) 2010-06-23
WO2009008415A1 (ja) 2009-01-15
EP2172655A4 (de) 2017-04-05
JPWO2009008415A1 (ja) 2010-09-09
US20100189544A1 (en) 2010-07-29
TW200918760A (en) 2009-05-01
CN101755130B (zh) 2012-10-17
JP5386353B2 (ja) 2014-01-15
EP2172655A1 (de) 2010-04-07

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