EP2172655A1 - Dual reversal-rotating type axial blower - Google Patents
Dual reversal-rotating type axial blower Download PDFInfo
- Publication number
- EP2172655A1 EP2172655A1 EP08790949A EP08790949A EP2172655A1 EP 2172655 A1 EP2172655 A1 EP 2172655A1 EP 08790949 A EP08790949 A EP 08790949A EP 08790949 A EP08790949 A EP 08790949A EP 2172655 A1 EP2172655 A1 EP 2172655A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- support frame
- half portion
- main body
- housing
- motor
- 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.)
- Granted
Links
- 230000009977 dual effect Effects 0.000 title 1
- 239000006260 foam Substances 0.000 claims description 23
- NIXOWILDQLNWCW-UHFFFAOYSA-N acrylic acid group Chemical group C(C=C)(=O)O NIXOWILDQLNWCW-UHFFFAOYSA-N 0.000 claims description 21
- 230000008878 coupling Effects 0.000 claims description 17
- 238000010168 coupling process Methods 0.000 claims description 17
- 238000005859 coupling reaction Methods 0.000 claims description 17
- 229910052782 aluminium Inorganic materials 0.000 claims description 8
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 8
- 239000000463 material Substances 0.000 claims description 8
- 229920003002 synthetic resin Polymers 0.000 claims description 4
- 239000000057 synthetic resin Substances 0.000 claims description 4
- 230000001133 acceleration Effects 0.000 description 35
- 230000000052 comparative effect Effects 0.000 description 19
- 238000005259 measurement Methods 0.000 description 15
- 230000002093 peripheral effect Effects 0.000 description 12
- 230000000694 effects Effects 0.000 description 7
- 239000002985 plastic film Substances 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 239000007769 metal material Substances 0.000 description 3
- 229910001369 Brass Inorganic materials 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 239000010951 brass Substances 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 230000001629 suppression Effects 0.000 description 1
Images
Classifications
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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
- 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
Abstract
Description
- The present invention relates to a counter-rotating axial flow fan for use to cool the inside of an electric device and the like.
- Japanese Unexamined Patent Application Publication No.
2004-278370 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. In the counter-rotating axial flow fan, 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. Also, 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. In the counter-rotating axial flow fan, 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. - [Patent Document 1] Japanese Unexamined Patent Application Publication No.
2004-278370 - [Patent Document 2]
US Patent No. 7,156,611 - In the counter-rotating axial flow fan according to the related art, however, 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 including a housing, a first impeller, a first motor, a second impeller, and a second motor. The housing includes 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. The first impeller is disposed in a first space defined in the housing between the motor support frame and the suction port, and includes a plurality of blades. The first motor includes a first rotary shaft to which the first impeller is fixed to rotate the first impeller in a first rotational direction in the first space. The second impeller is disposed in a second space defined in the housing between the motor support frame and the discharge port, and includes a plurality of blades. The second motor includes a second rotary shaft to which the second impeller is fixed to rotate the second impeller in a second rotational direction opposite the first rotational direction in the second space.
- The motor support frame includes a support frame main body located at the center portion of the air channel and a plurality of webs disposed between the support frame main body and the housing main body at predetermined intervals in a circumferential direction of the rotary shafts to couple the support frame main body and the housing main body.
- The housing includes a first split housing unit and a second split housing unit coupled to each other by a mechanical coupling structure. The first split housing unit includes a first housing main body half portion including a first cylindrical air channel half portion having the suction port at one end and 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 a 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 the discharge port at one end and 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 split plane.
- The coupling structure adopted in the present invention includes a plurality of engaging portions integrally formed with the first housing main body half portion and disposed at intervals in the circumferential direction, and a plurality of engaged portions integrally formed with the second housing main body half portion and disposed at intervals in the circumferential direction to be engaged with the plurality of engaging portions. The coupling structure and the first and second split housing units are configured such that an opposed surface of the first support frame half portion and an opposed surface of the second support frame half portion entirely contact each other when the plurality of engaging portions and the plurality of engaged portions are completely engaged with each other. The phrase "opposed surfaces entirely contact each other" as used herein means that opposed surfaces contact each other through a large number of point contacts as seen from a microscopic point of view.
- In the present invention, in particular, a soft cushioning member is disposed between the first support frame half portion and the second support frame half portion, the cushioning member being compressed when the plurality of engaging portions and the plurality of engaged portions are completely engaged with each other. 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. If 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. As a result, according to the present invention, 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 compared to the related art.
- 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.
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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 according to the embodiment of the present invention. -
Figs. 3A and3B are graphs showing the results of vibration measurements performed to verify the effect of the present invention. -
Figs. 4A and4B are graphs showing the results of vibration measurements performed to verify the effect of the present invention. -
Fig. 5 is a graph showing the detailed results of vibration measurements performed to verify the effect of the present invention. - An embodiment of the present invention will be described in detail below with reference to the drawings.
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. As shown in the drawings, the counter-rotating axial flow fan according to the embodiment includes ahousing 1, afirst motor 3, afirst impeller 5, asecond motor 7, and asecond impeller 9. Thefirst impeller 5 is disposed in a first space S1 defined in thehousing 1 between a motor support frame (23, 53) to be discussed later and a suction port 11a, and includes a plurality ofblades 6. Thefirst motor 3 includes a firstrotary shaft 4 to which thefirst impeller 5 is fixed to rotate thefirst impeller 5 in a first rotational direction in thefirst space S 1. Thesecond impeller 9 is disposed in a second space S2 defined in thehousing 1 between the motor support frame (23, 53) and thedischarge port 13b, and includes a plurality ofblades 10. Thesecond motor 7 includes a secondrotary shaft 8 to which thesecond impeller 9 is fixed to rotate thesecond 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 firstsplit housing unit 11 and a secondsplit housing unit 13 via a coupling structure. The firstsplit housing unit 11 is formed from a synthetic resin material or a metal material such as aluminum. As shown inFig. 1 , the firstsplit housing unit 11 includes a first housing mainbody half portion 15 and a first support frame half portion 17 integrally formed with each other. The first housing mainbody half portion 15 includes first andsecond flange portions channel half portion 21. Thefirst flange portion 19 includes first tofourth 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 andsecond motors first flange portion 19 includes the suction port 11a at one end in the direction of the common axis A. Fourhole portions 19e are respectively formed at the four corners of the first flange portion 19 (the first tofourth corners 19a to 19d) to serve as engaged portions for use in forming a coupling structure with the secondsplit housing unit 13. The details of the shape of thehole portions 19e and the details of the engagement relationship between thehole portions 19e and thehook 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. Thesecond flange portion 20 is formed with throughholes 20a through which mounting members for mounting the counter-rotating axial flow fan to an electric device are to be inserted. The first andsecond flange portions channel half portion 21. The first cylindrical airchannel half portion 21 extends in an axial direction of therotary 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 thefirst motor 3 is fixed and three firstweb half portions 25. The first support frame mainbody half portion 23 includes acircular plate portion 23b having acylindrical boss portion 23a at a center portion thereof, and aperipheral wall portion 23c extending in the axial direction from the outer peripheral portion of thecircular plate portion 23b. A firstmetallic bearing holder 27 made of brass is fixedly fitted in theboss portion 23a. Abase plate 29 of a stator of thefirst motor 3 is disposed to block a space surrounded by thecircular plate portion 23b and theperipheral wall portion 23c. Astator core 33 including a plurality of windingportions 31 is fitted with the bearingholder 27. - The three first
web half portions 25 are disposed between theperipheral wall portion 23c of the first support frame mainbody half portion 23 and an inner peripheral surface of the first housing mainbody half portion 15 at predetermined intervals in the circumferential direction to couple the first support frame mainbody half portion 23 and the first housing mainbody half portion 15. - A cup-shaped
member 35 made of a magnetically permeable material is fixed to one end of therotary shaft 4 to support theimpeller 5 including the plurality ofblades 6. A plurality ofpermanent magnets 37 are fixed to the inner peripheral portion of the cup-shapedmember 35. - The second
split housing unit 13 is also formed from a synthetic resin material or a metal material such as aluminum. As shown inFig. 1 , the secondsplit housing unit 13 includes a second housing mainbody half portion 39 and a second supportframe half portion 41 integrally formed with each other. The second housing mainbody half portion 39 includes first andsecond flange portions channel half portion 47. Thefirst flange portion 43 includes four corners, namely first tofourth 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 andsecond motors hook portions 49 and fourprojections 51 are respectively integrally formed with the four corners of the first flange portion 43 (the first tofourth corners 43a to 43d) to serve as engaging portions for use in forming a coupling structure with the firstsplit housing unit 11. The details of the engagement relationship of thehook portions 49 and theprojections 51 with thehole 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 2004-278370 US Patent No. 7,156,611 ), thehook portions 49 are partly fitted in thehole portions 19e, and the secondsplit housing unit 13 is rotated by a predetermined angle about the common axis A. Then, theprojections 51 are fitted in fitting recesses (not shown) formed in an end surface of thefirst flange portion 19 of the firstsplit housing unit 11. As a result, the secondsplit housing unit 13 is prevented from rotating. Also, engagement between thehook portions 49 and edge portions around thehole portions 19e prevents the secondsplit housing unit 13 from separating from the firstsplit housing unit 11 in the axial direction. Thesecond flange portion 45 is formed with throughholes 45a through which mounting members for mounting the counter-rotating axial flow fan to an electric device are to be inserted. The first andsecond flange portions channel half portion 47. The second cylindrical airchannel half portion 47 extends in the axial direction (the axial direction of therotary shafts - The second support
frame half portion 41 includes a second support frame mainbody half portion 53 to which thesecond motor 7 is fixed and three secondweb half portions 55. The second support frame mainbody half portion 53 includes acircular plate portion 53b having acylindrical boss portion 53a at a center portion thereof, and aperipheral wall portion 53c extending in the axial direction from the outer peripheral portion of thecircular plate portion 53b. A secondmetallic bearing holder 57 made of brass is fixedly fitted in theboss portion 53a. Abase plate 59 of a stator of thesecond motor 7 is disposed to block a space surrounded by thecircular plate portion 53b and theperipheral wall portion 53c. Astator core 63 including a plurality of windingportions 61 is fitted with the bearingholder 57. - The three second
web half portions 55 are disposed between theperipheral wall portion 53c of the second support frame mainbody half portion 53 and an inner peripheral surface of the second housing mainbody half portion 39 at predetermined intervals in the circumferential direction to couple the second support frame mainbody half portion 53 and the second housing mainbody half portion 39. Of the threeweb half portions 55, one web half portion has agroove 55A formed for receiving lead wires. - A cup-shaped
member 65 made of a magnetically permeable material is fixed to one end of therotary shaft 8 to support theimpeller 9 including the plurality ofblades 10. A plurality ofpermanent magnets 67 are fixed to the inner peripheral portion of the cup-shapedmember 65. - In the embodiment, the first and second support
frame half portions 17 and 41 are assembled to form the motor support frame (23, 53). In other words, the first and second supportframe 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. With this configuration of the embodiment, the coupling structure and the first and secondsplit housing units frame half portion 41 entirely contact each other when the four engaging portions (the four hook portions 49) and the four engaged portions (the fourhole portions 19e) are completely engaged with each other. - In the embodiment, 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 supportframe half portion 41, specifically between thecircular plate portion 23b of the first support frame mainbody half portion 23 and thecircular plate portion 53b of the second support frame mainbody half portion 53. As thesoft cushioning member 71, preferably, an acrylic foam sheet may be used. The cushioningmember 71 is disposed as it is compressed with the fourhook portions 49 forming the plurality of engaging portions and the fourhole portions 19e forming the plurality of engaged portions completely engaged with each other. When the cushioningmember 71 with a plurality of independent air bubbles dispersed therein is compressed, the cushioningmember 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. As a result, 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 fourhole portions 19e) is strengthened, which prevents generation of a large gap between the first and secondsplit housing units member 71 also serves a function of absorbing vibration produced between the first support frame half portion 17 and the second supportframe 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. - In the above embodiment, the
soft cushioning member 71 is disposed only between thecircular plate portion 23b of the first support frame mainbody half portion 23 and thecircular plate portion 53b of the second support frame mainbody half portion 53 to obtain favorable results. However, an enhanced vibration suppression effect is obtained by disposing a soft cushioning member also between the firstweb half portions 25 and the secondweb half portions 55. - Vibration measurement tests were performed as described below to verify the effect of the present invention.
Figs. 3 to 5 are each a graph showing the results of vibration measurement tests. In the vibration measurement tests, the vibration acceleration (m/s2) at a measurement location M1 (a portion of thefirst flange portion 43 of the second split housing unit 13) in the circumferential direction and the vibration acceleration (m/s2) at a measurement location M2 (near a throughhole 20a of thesecond 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/s2) 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. InFig. 3A , X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a soft cushioning member 71 (Embodiment 1), and Y indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with no cushioning member 71 (Comparative Example 1). As the soft cushioning member, 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 inFig. 3A , and when the present invention is not applied thereto. InFig. 3B , X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member 71 (Embodiment 2), and 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 inFig. 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. InFig. 4A , X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member 71 (Embodiment 3), and 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 inFig. 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. - Like
Fig. 4A ,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. InFig. 4B , X indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with a cushioning member 71 (Embodiment 4), and 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 inFig. 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. - As a result of the above vibration measurements (
Figs. 3 and4 ), it was found that favorable results were obtained by using an acrylic-foam cushioning member with independent air bubbles. Further, a preferable thickness range of the acrylic-foam cushioning member was confined and it was verified whether or not materials other than the acrylic foam were suitable for use as 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 inFig. 3 under the same measurement conditions as inFig. 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. - In
Fig. 5 , the "dotted line" indicates changes in vibration acceleration of a counter-rotating axial flow fan provided with thesoft 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 cushioningmember 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 mainbody 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 measurement results are described below. When no cushioning member was used (Comparative Example 5), a plurality of resonance points (peaks) appeared in the vibration acceleration. In particular, a very high peak was exhibited in the vibration acceleration in a high rotational speed range around 14000 [rpm]. When an aluminum sheet was used as the cushioning member (Comparative Example 7) and when a plastic sheet was used as the cushioning member (Comparative Example 8), the plurality of resonance points (peaks) in the vibration acceleration in a high rotational speed range were slightly decreased. However, the resonance point (peak) in the vibration acceleration around 14000 [rpm] remained relatively high, although it was not as high as when no cushioning
member 71 was used (Comparative Example 5). - In contrast, when an acrylic foam sheet having a thickness of 0.4 mm was used as the cushioning member 71 (Embodiment 5), the plurality of peaks in the vibration acceleration in a high rotational speed range were decreased, and in addition, the peak in the vibration acceleration around 14000 [rpm] was reduced by 40% with respect to when no cushioning
member 71 was used (Comparative Example 5), and reduced by 30% with respect to when an aluminum sheet and a plastic sheet were used as the cushioning member 71 (Comparative Examples 7 and 8). Also, when an acrylic foam sheet having a thickness of 0.8 mm was used as the cushioning member 71 (Embodiment 6), the plurality of peaks in the vibration acceleration in a high rotational speed range were decreased, and in addition, the peak in the vibration acceleration around 14000 [rpm] was reduced by 60% with respect to when no cushioningmember 71 was used (Comparative Example 5), and reduced by 50% with respect to when an aluminum sheet and a plastic sheet were used as the cushioning member 71 (Comparative Examples 7 and 8). When an acrylic foam sheet having a thickness of 0.8 mm was used (Embodiment 6), the peak in the vibration acceleration around 14000 [rpm] was reduced by 30% with respect to when an acrylic foam sheet having a thickness of 0.4 mm was used (Embodiment 5). - When a gap of 0.2 mm was provided without using a cushioning member (Comparative Example 6), a peak higher than the highest peak that appeared when no cushioning
member 71 was used (Comparative Example 5) was exhibited in the vibration acceleration around 12000 [rpm] although no high peak was exhibited in the vibration acceleration around 14000 [rpm]. Moreover, the number of peaks in the vibration acceleration that were relatively high was increased compared to when no cushioningmember 71 was used (Comparative Example 5). Consequently, it is found that generation of vibration cannot be reduced in a wide rotational speed range from a low rotational speed range to a high rotational speed range by simply providing a gap with no cushioning member disposed therein, although vibration can be suppressed in a high rotational speed range by transferring high peaks in the vibration acceleration to a lower rotational speed range (by causing a shift phenomenon). - As can be seen from the above results, it is possible to not only suppress significant vibration that is produced in a high rotational speed range but also generally suppress an increase in vibration over a wide rotational speed range by setting 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. - In the above embodiment, the cushioning
member 71 is disposed only between thecircular plate portion 23b of the first support frame mainbody half portion 23 and thecircular plate portion 53b of the second support frame mainbody half portion 53. However, it is a matter of course that the cushioningmember 71 may also be disposed between the firstweb half portions 25 and the secondweb half portions 55. - According to the present invention, 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.
Claims (6)
- A counter-rotating axial flow fan comprising: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 disposed in a first space defined in the housing between the motor support frame and the suction port and including a plurality of blades;a first motor including a first rotary shaft to which the first impeller is fixed to rotate the first impeller in a first rotational direction in the first space;a second impeller disposed in a second space defined in the housing between the motor support frame and the discharge port and including a plurality of blades; anda second motor including a second rotary shaft to which the second impeller is fixed to rotate the second impeller in a second rotational direction opposite the first rotational direction in the second space,the motor support frame including a support frame main body located at the center portion of the air channel and a plurality of webs disposed between the support frame main body and the housing main body at predetermined intervals in a circumferential direction of the rotary shafts to couple the support frame main body and the housing main body,the housing including a first split housing unit and a second split housing unit coupled to each other by a mechanical coupling structure,the first split housing unit including a first housing main body half portion including a first cylindrical air channel half portion having the suction port at one end and 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 a split plane extending in a radial direction perpendicular to the axial direction,the second split housing unit including a second housing main body half portion including a second cylindrical air channel half portion having the discharge port at one end and 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 split plane,the coupling structure including a plurality of engaging portions integrally formed with the first housing main body half portion of the first split housing unit and disposed at intervals in the circumferential direction, and a plurality of engaged portions integrally formed with the second housing main body half portion of the second split housing unit and disposed at intervals in the circumferential direction to be engaged with the plurality of engaging portions,the coupling structure and the first and second split housing units being configured such that an opposed surface of the first support frame half portion and an opposed surface of the second support frame half portion entirely contact each other when the plurality of engaging portions and the plurality of engaged portions are completely engaged with each other,the first support frame half portion including a first support frame main body half portion to which the first motor is fixed and a plurality of first web half portions, andthe second support frame half portion including a second support frame main body half portion to which the second motor is fixed and a plurality of second web half portions,wherein a soft cushioning member with a plurality of independent air bubbles dispersed therein is disposed between the first support frame main body half portion and the second support frame main body half portion, the cushioning member being compressed when the plurality of engaging portions and the plurality of engaged portions are completely engaged with each other.
- A counter-rotating axial flow fan comprising: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 disposed in a first space defined in the housing between the motor support frame and the suction port and including a plurality of blades;a first motor including a first rotary shaft to which the first impeller is fixed to rotate the first impeller in a first rotational direction in the first space;a second impeller disposed in a second space defined in the housing between the motor support frame and the discharge port and including a plurality of blades; anda second motor including a second rotary shaft to which the second impeller is fixed to rotate the second impeller in a second rotational direction opposite the first rotational direction in the second space,the motor support frame including a support frame main body located at the center portion of the air channel and a plurality of webs disposed between the support frame main body and the housing main body at predetermined intervals in a circumferential direction of the rotary shafts to couple the support frame main body and the housing main body,the housing including a first split housing unit and a second split housing unit coupled to each other by a mechanical coupling structure,the first split housing unit including a first housing main body half portion including a first cylindrical air channel half portion having the suction port at one end and 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 a split plane extending in a radial direction perpendicular to the axial direction,the second split housing unit including a second housing main body half portion including a second cylindrical air channel half portion having the discharge port at one end and 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 split plane,the coupling structure including a plurality of engaging portions integrally formed with the first housing main body half portion of the first split housing unit and disposed at intervals in the circumferential direction, and a plurality of engaged portions integrally formed with the second housing main body half portion of the second split housing unit and disposed at intervals in the circumferential direction to be engaged with the plurality of engaging portions, andthe coupling structure and the first and second split housing units being configured such that opposed surfaces of the first and second support frame half portions entirely contact each other when the plurality of engaging portions and the plurality of engaged portions are completely engaged with each other,wherein a soft cushioning member with a plurality of independent air bubbles dispersed therein is disposed between the first support frame half portion and the second support frame half portion, the cushioning member being compressed when the plurality of engaging portions and the plurality of engaged portions are completely engaged with each other.
- The counter-rotating axial flow fan according to claim 2, wherein
the first support frame half portion includes a first support frame main body half portion to which the first motor is fixed,
the second support frame half portion includes a second support frame main body half portion to which the second motor is fixed, and
the cushioning member is disposed between the first support frame main body half portion and the second support frame main body half portion. - The counter-rotating axial flow fan according to claim 1 or 2, wherein
the first and second split housing units are formed from a synthetic resin material. - The counter-rotating axial flow fan according to claim 1 or 2, wherein
the first and second split housing units are formed from aluminum. - The counter-rotating axial flow fan according to claim 1 or 2, wherein
the cushioning member is an acrylic foam sheet with a thickness of not less than 0.4 mm and not more than 0.8 mm.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007183756 | 2007-07-12 | ||
PCT/JP2008/062312 WO2009008415A1 (en) | 2007-07-12 | 2008-07-08 | Dual reversal-rotating type axial blower |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2172655A1 true EP2172655A1 (en) | 2010-04-07 |
EP2172655A4 EP2172655A4 (en) | 2017-04-05 |
EP2172655B1 EP2172655B1 (en) | 2018-10-24 |
Family
ID=40228585
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08790949.5A Active EP2172655B1 (en) | 2007-07-12 | 2008-07-08 | Dual reversal-rotating type axial blower |
Country Status (6)
Country | Link |
---|---|
US (1) | US20100189544A1 (en) |
EP (1) | EP2172655B1 (en) |
JP (1) | JP5386353B2 (en) |
CN (1) | CN101755130B (en) |
TW (1) | TW200918760A (en) |
WO (1) | WO2009008415A1 (en) |
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WO2013059437A1 (en) | 2011-10-19 | 2013-04-25 | Mars, Incorporated | Inhibitors of arginase and their therapeutic applications |
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CN104806545B (en) * | 2014-01-25 | 2017-05-10 | 深圳兴奇宏科技有限公司 | Serial fan combining method |
WO2016044945A1 (en) * | 2014-09-25 | 2016-03-31 | Nuhn Industries Ltd. | Fluid pump with multiple pump heads |
CN104454592A (en) * | 2014-11-28 | 2015-03-25 | 德清振达电气有限公司 | High-power axial fan |
US9739291B2 (en) * | 2015-04-13 | 2017-08-22 | Minebea Mitsumi Inc. | Cooling fan |
AU2016281620B2 (en) | 2015-06-23 | 2021-07-22 | Calithera Biosciences, Inc. | Compositions and methods for inhibiting arginase activity |
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TWI667413B (en) * | 2017-12-14 | 2019-08-01 | 建準電機工業股份有限公司 | Ventilation fan |
JP7119635B2 (en) * | 2018-06-22 | 2022-08-17 | 日本電産株式会社 | axial fan |
CN109520083B (en) * | 2018-11-15 | 2020-06-23 | 广东美的制冷设备有限公司 | Control method of air conditioner, air conditioner and computer readable storage medium |
CN109737085B (en) * | 2018-12-24 | 2020-10-16 | 宁波生久散热科技有限公司 | Combined radiating fan |
JP2023046766A (en) * | 2021-09-24 | 2023-04-05 | 山洋電気株式会社 | Axial flow blower |
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- 2008-07-08 EP EP08790949.5A patent/EP2172655B1/en active Active
- 2008-07-08 JP JP2009522647A patent/JP5386353B2/en active Active
- 2008-07-08 CN CN2008800242361A patent/CN101755130B/en active Active
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Also Published As
Publication number | Publication date |
---|---|
JP5386353B2 (en) | 2014-01-15 |
WO2009008415A1 (en) | 2009-01-15 |
JPWO2009008415A1 (en) | 2010-09-09 |
CN101755130B (en) | 2012-10-17 |
CN101755130A (en) | 2010-06-23 |
US20100189544A1 (en) | 2010-07-29 |
EP2172655B1 (en) | 2018-10-24 |
EP2172655A4 (en) | 2017-04-05 |
TW200918760A (en) | 2009-05-01 |
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