Patent Application
20100189544
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 (Patent Document 1) and U.S. Pat. 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] U.S. Pat. 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.
An embodiment of the present invention will be described in detail below with reference to the drawings.
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. As shown in
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
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. Of the three web half portions 55, 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.
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 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. With this configuration of the embodiment, 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.
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 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. As the soft cushioning member 71, preferably, an acrylic foam sheet may be used. 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. 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. 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 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.
In the above embodiment, 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. However, 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.
Vibration measurement tests were performed as described below to verify the effect of the present invention.
Like
As a result of the above vibration measurements (
In
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 cushioning member 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 cushioning member 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 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.
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.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2007-183756 | Jul 2007 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2008/062312 | 7/8/2008 | WO | 00 | 1/11/2010 |
