Patent Application
20110171004
The present invention relates to a cross-flow fan, a blower and a molding machine for an impeller, and particularly to a cross-flow fan formed by stacking a plurality of impellers, a blower including the cross-flow fan, and a molding machine for an impeller.
Indoor fans for air conditioners designed in various ways for the purpose of reducing noise and improving the efficiency have been proposed.
Japanese Patent Laying-Open No. 11-264394 for example discloses a transverse fan formed by axially stacking a plurality of multi-blade impellers. Each multi-blade impeller is formed by being injection-molded in a mold, and removed from the mold while rotated about its rotational axis in the direction of inclination of each blade.
This transverse fan aims to reduce rotation sound of the transverse fan by successively varying the pressure generated between the transverse fan, a nose and a fan casing.
A transverse fan disclosed in Japanese Patent Laying-Open No. 10-148196 is also formed by axially stacking a plurality of multi-blade impellers. Each multi-blade impeller includes a partition plate and a plurality of blades provided integrally and standing on a surface of the partition plate, and the blades are arranged annularly and inclined by a predetermined angle.
This transverse fan also aims to reduce rotation sound, similarly to the transverse fan disclosed in Japanese Patent Laying-Open No. 11-264394.
In a molding process for the conventional transverse fans as described above, a resin molded product has to be rotated along blade molding holes in a cavity of a mold for removing the molded product from the mold. At this time, it is difficult to precisely match the angle of inclination of the blade molding holes with the angle at which the molded product is rotated for removing the product. Thus, the blade molding holes and the blades of the molded product more or less interfere with each other. Accordingly, friction is generated where the interference occurs, and a crack is opened from a portion where excessive stress is applied due to the friction. In particular, a radially inner portion of a blade is likely to be influenced by the stress, and a crack opened at this portion results in a crack of the whole blade
The above-referenced documents disclose that a conventional transverse fan is designed such that each blade is inclined by a predetermined angle, and also disclose that multi-blade impellers axially adjacent to each other are displaced by a predetermined angle in the direction of rotation about the axis. From the transverse fan designed in the above-described manner, blade passing sounds, which are generated when the blades of the transverse fan pass near a nose, are generated at respective portions in the axial direction of the fan in different cycles. Therefore, a large peak noise (nZ noise) of the conventional transverse fans as described above can be suppressed. The peak noise refers to noise that is generated when the blade passing sounds of the whole fan occur simultaneously. However, when an angular displacement between the multi-blade impellers about the axis is excessively large, a phase shift between a flow between blades on one side of the partition plate and a flow between blades on the other side thereof causes a secondary flow, resulting in excessive pulsation of forced vortex, and generation of abnormal noise (bubbling noise). Further, the abnormal noise (bubbling noise) is transmitted to a casing of an indoor unit to cause further vibrations and noise. If the multi-blade impellers are arranged without angular displacement therebetween about the axis for the purpose of suppressing the abnormal noise, respective blades of multi-blade impellers pass near the nose in the same cycle, and accordingly a large peak noise (nZ noise) is generated.
If a blade inclined relative to the axial direction (skew blade) like that of the above-described conventional transverse fans is employed, the air blowing performance is deteriorated and the power consumption increases. In addition, resin molding with a mold as described above is difficult.
An object of the present invention is to provide a cross-flow fan and a blower that can simultaneously suppress the peak noise and the abnormal noise and reduce the power consumption without deterioration in performance even if blades are inclined, and facilitate resin molding with a mold, and to provide a molding machine capable of forming impellers constituting the cross-flow fan.
According to an aspect of the present invention, a cross-flow fan is formed by stacking a plurality of impellers in a direction of a central axis line, the impellers each including a support having a main surface and a plurality of blades spaced from each other on the main surface of the support, and arranged in order on the support such that the blades stand on the main surface, and respective heads of the blades of one impeller of the plurality of impellers and the support of another impeller adjacent to the one impeller being connected with each other to form the cross-flow fan. The blades are each formed such that a cross section of the blade perpendicular to the central axis line decreases from a bottom of the blade arranged in order on the main surface toward the head of the blade. A center of the cross section of the blade perpendicular to the central axis line is displaced frontward or backward in a direction of rotation about the central axis line, and displaced radially outward, from the bottom of the blade arranged in order on the main surface toward the head of the blade.
According to another aspect of the present invention, a cross-flow fan is formed by stacking a plurality of impellers in a direction of a central axis line, the impellers each including a support having a main surface and a plurality of blades spaced from each other on the main surface of the support, and arranged in order on the support such that the blades stand on the main surface, and respective heads of the blades of one impeller of the plurality of impellers and the support of another impeller adjacent to the one impeller being connected with each other to form the cross-flow fan. The blades are each formed such that a cross section of the blade perpendicular to the central axis line decreases from a bottom of the blade arranged in order on the main surface toward the head of the blade. A center of the cross section of the blade perpendicular to the central axis line is displaced frontward or backward in a direction of rotation about the central axis line, from the bottom of the blade arranged in order on the main surface toward the head of the blade. A cross angle defined by a radially inner side of the blade and the support is smaller than a cross angle defined by a radially outer side of the blade and the support.
According to still another aspect of the present invention, a cross-flow fan is formed by stacking a plurality of impellers in a direction of a central axis line, the impellers each including a support having a main surface and a plurality of blades spaced from each other on the main surface of the support, and arranged in order on the support such that the blades stand on the main surface, and respective heads of the blades of one impeller of the plurality of impellers and the support of another impeller adjacent to the one impeller being connected with each other to form the cross-flow fan. The blades are each formed such that a cross section of the blade perpendicular to the central axis line decreases from a bottom of the blade arranged in order on the main surface toward the head of the blade. A center of the cross section of the blade perpendicular to the central axis line is displaced frontward or backward in a direction of rotation about the central axis line, from the bottom of the blade arranged in order on the main surface toward the head of the blade. A radially inner side of the blade extends radially outward from the bottom of the blade arranged in order on the main surface toward the head of the blade. A radially outer side of the blade extends radially inward from the bottom of the blade arranged in order on the main surface toward the head of the blade. A distance between a radially inner end of the head of the blade and a radially inner end of the bottom of the blade is larger than a distance between a radially outer end of the head of the blade and a radially outer end of the bottom of the blade.
Preferably, where a cross section of the bottom of the blade perpendicular to the central axis line is a first reference plane, where a cross section of the head of the blade is a second reference plane, where a rotational angle by which the second reference plane is displaced from the first reference plane about the central axis line is rotational angle W, where a length of the blade in the direction of the central axis line is length L, where a distance by which the second reference plane is displaced radially outward from the first reference plane is distance r, where a central point and a central line of the first reference plane are made coincident with a central point and a central line of the second reference plane respectively, an outer periphery of the second reference plane and an outer periphery of the first reference plane are spaced by a constant distance over respective whole outer peripheries of the first reference plane and the second reference plane, and where the constant distance is distance e, W/L is not more than 0.15, and r/e is not less than 0.3 and not more than 1.5.
Preferably, the blades are spaced from each other, thereby forming a gap between the blades adjacent to each other in the direction of rotation, and the blades are arranged such that a width of at least one of a plurality of the gaps defined in the impeller is different from a width of other gaps.
Preferably, the impellers include a first impeller and a second impeller adjacent to head side of the blades of the first impeller, and the gap formed in the first impeller and the gap of the second impeller adjacent to the gap of the first impeller are different from each other in width. Preferably, where an arbitrary one of the plurality of blades provided to the first impeller is a first reference blade and a blade that is one of the plurality of blades provided to the second impeller and corresponds to the first reference blade is a second reference blade, the head of the first reference blade is connected to a first main surface of the support of the second impeller, and the blades of the second impeller are arranged in order on a second main surface located opposite to the first main surface, and the head of the first reference blade is adjacent to the bottom of a blade of the second impeller that is different from the second reference blade, and the bottom of the second reference blade is adjacent to the head of a blade of the first impeller that is different from the first reference blade. Preferably, the impellers include a first impeller and a second impeller adjacent to head side of the blades of the first impeller, and the gap formed in the first impeller and the gap of the second impeller adjacent to the gap of the first impeller are substantially identical to each other in width.
A blower according to the present invention includes the cross-flow fan as described above. Preferably, the blower further includes: a casing housing the cross-flow fan and having an outlet formed for allowing air forced to be delivered by the cross-flow fan to blow to outside; and a flap provided in the casing and serving as a partition between a supply region for supplying air to the cross-flow fan and an outflow region for supplying air from the cross-flow fan toward the outlet, and the flap is provided parallel to a rotational axis of the cross-flow fan.
A molding machine for an impeller according to the present invention includes a cavity formed with an inner surface formed to conform to an outer surface of an impeller of the cross-flow fan as described above.
The cross-flow fan and the blower of the present invention can be used to simultaneously suppress the peak noise and the abnormal noise while reducing the power consumption, and facilitate resin molding with a mold. With a molding machine for an impeller of the present invention, the cross-flow fan as described above can be formed.
With reference to
Casing 102 has a slit formed in any of a top surface, a front surface or a side surface. Through the slit, the outdoor air can be drawn into casing 102 by driving cross-flow fan 200. The indoor air is taken in through the slit by rotationally driving cross-flow fan 200. The intake indoor air undergoes heat exchanging by heat exchangers 110 and is thereafter forced by cross-flow fan 200 to be blown into the room through a wind path 131 provided in casing 102 and an outlet.
In casing 102, an upper wall 132 and a lower wall 133 are provided, and upper wall 132 and lower wall 133 define wind path 131. The outlet is formed at an end of wind path 131. Both of upper wall 132 and lower wall 133 are located lower than rotational central line O, while upper wall 132 is located higher than lower wall 133. Lower wall 133 is formed to extend from below cross-flow fan 200 to the rear side with respect to cross-flow fan 200 and to further extend higher than rotational central line O.
Upper wall 132 extends from the front side of casing 102 toward cross-flow fan 200 to be located close to cross-flow fan 200. Further, at an end of upper wall 132 on the cross-flow-fan 200 side, a flap 130 is formed.
In the space located around cross-flow fan 200, a region extending forward from flap 130 in rotational direction R to an upper end of lower wall 133 is a supply region 135 for supplying air into cross-flow fan 200. A region extending forward from an upper end of lower wall 133 in rotational direction R to reach flap 130 is an outflow region 136 where air flows out from cross-flow fan 200 into wind path 131. Flap 130 is located near cross-flow fan 200 and serves as a partition between outflow region 136 and supply region 135.
At the outlet, a wind guide plate 120 for freely changing the direction of airflow from the outlet is provided.
Impeller 226 is formed by injection molding, blades 224 and support plate 225 are integrally formed, and respective bottoms of blades 224 are arranged in order on the main surface of support plate 225. Respective heads of blades 224 are attached to be secured to another support plate 225 of another impeller 226 adjacent to impeller 226 having these blades 224 formed thereon, by, for example, ultrasonic crimping.
In
The bottom of blade 224 is usually provided with so-called “thickened” portion like a base R for reinforcement purpose. First reference plane 300 here, however, is defined as a cross section without this so-called thickened portion. Second reference plane 301 is defined as a cross section at the position corresponding to the attachment surface to be attached to another support plate when impellers are attached to each other. Therefore, even if the head of the blade is not parallel with a plane perpendicular to rotational central axis O, the cross section at the head of the blade at the position corresponding to the position of the attachment surface to be attached to another support plate may be regarded as the second reference plane.
The points where the outer perimeter of first reference plane 300 and first central line CL1 meet are an outer end Q1 and an inner end Q3. Outer end Q1 is located on the radially outer side and inner end Q3 is located on the radially inner side. A point on first central line CL1 where the distance from outer end Q1 to this point and the distance from inner end Q3 to this point are equal to each other is a first central point CP1 of first reference plane 300.
Likewise, a second central line CL2 is a central line (camber line) of second reference plane 301, and respective distances from the opposing sides of second reference plane 301 to second central line CL2 are equal to each other. The points where the outer perimeter of second reference plane 301 and second central line CL2 meet are an outer end Q2 and an inner end Q4. Outer end Q2 is located on the radially outer side and inner end Q4 is located on the radially inner side. A point on second central line CL2 where the distance from outer end Q2 to this point and the distance from inner end Q4 to this point are equal to each other is a second central point CP2 of second reference plane 301.
Second reference plane 301 is located away from first reference plane 300 in the direction of central rotational line O, and second reference plane 301 is located forward in rotational direction R relative to first reference plane 300 and located outward in the radial direction of support plate 225.
Specifically, second reference plane 301 is displaced from first reference plane 300 by a rotational angle θ1 with respect to rotational central line O, and second reference plane 301 is further displaced radially outward from first reference plane 300 by an outward displacement L4.
Rotational angle θ1 may be defined by a first virtual axis line D1 connecting outer end Q1 of first reference plane 300 and rotational central line O, and a second virtual axis line D2 connecting outer end Q2 of second reference plane 301 and rotational central line O. Rotational angle θ1 is a smaller one of cross angles defined by first virtual axis line D1 and second virtual axis line D2.
The way to define rotational angle θ1 is not limited to the above-described one. For example, this angle may be defined as a cross angle between a first chord D3 of first reference plane 300 and a second chord D4 of second reference plane 301. Here, first chord D3 is a virtual line segment connecting outer end Q1 and inner end Q3, and second chord D4 is a virtual line segment connecting outer end Q2 and inner end Q4.
Outward displacement L4 may be defined as radially outward displacement L4 between a virtual circle S1 centered at rotational central line O and passing first central point CP1, and a virtual circle S2 centered at rotational central line O and passing second central point CP2.
In
As seen from above, the area of second reference plane 301 is smaller than that of first reference plane 300, and blade 224 is formed so that the cross section perpendicular to rotational central line O decreases from the bottom side toward the head side.
In this way, blade 224 is formed so that the area of the cross section of blade 224 perpendicular to rotational central line O gradually decreases from first reference plane 300 toward second reference plane 301, and the center of the cross section of blade 224 perpendicular to rotational central line O is displaced forward in rotational direction R and radially outward about rotational central line O, from first reference plane 300 toward second reference plane 301.
In the present embodiment, inner side 310 is inclined radially outward from the main surface of support plate 225, and outer side 311 is inclined radially inward from the main surface of support plate 225. Here, outer side 311 may not necessarily be inclined radially inward and may be inclined radially outward depending on the case. In this case as well, cross angle θ3 is defined in the same manner as the one described above. It should be noted that, in the case where outer side 311 inclines radially inward, a relatively simpler mold may be used since so-called undercut is not provided when the blade is molded. Therefore, the outer side inclined radially inward is more preferable than the outer side inclined radially outward.
A radial distance L1 between inner end Q3 of first reference plane 300 and inner end Q4 of second reference plane 301 is longer than a radial distance L2 between outer end Q1 of first reference plane 300 and outer end Q2 of second reference plane 301.
In the example shown in
In this case, at the same height from the main surface of support plate 225, the cross angle between the tangent of inner side 310 and a virtual plane perpendicular to rotational central line O is smaller than the cross angle between the tangent of outer side 311 and a virtual plane perpendicular to rotational central line O.
The center of the cross section of blade 224 perpendicular to rotational central line O is displaced forward in rotational direction R and displaced radially outward, from the bottom of blade 224 toward the head of blade 224. Accordingly a central line P connecting respective centers of cross sections of blade 224 is inclined radially forward in rotational direction R and radially outward, from the bottom toward the head of blade 224.
The shape of blade 224 is defined in the above-described manner, so that respective sides of blades can be inclined outward. In this way, the surface pressure can be kept low that is applied to the radially inner side of blade 224 when the molded product of impeller 226 is removed from the mold while rotating the mold. Thus, when the molded product is removed from the mold, crack or break can be prevented from occurring on the radially inner side of blade 224 that is likely to crack in particular.
In the example shown in
Further, in the case where cross-flow fan 200 having blades 224 formed in the above-described manner is arranged parallel to flap 130 shown in
Impeller 226 having a plurality of blades 224 as described above is formed by an injection molding machine that is formed with the inner surface of a cavity extending to conform to the outer peripheral surfaces of blades 224 and impeller 226.
Table 1 below shows positive and negative differences in volume of air (m3/min) generated by cross-flow fan 200 with various parameters varied, with respect to a reference volume of air (m3/min) generated by a cross-flow fan having blades without skew and radial inclination where rotational angle θ1 is zero (deg) and outward displacement L4 is zero (mm).
In Table 1 below, “L” represents a length of the blade (mm) (height H in
Since the air volume of cross-flow fan 200 is proportional to each of the diameter, the length and the number of revolutions of the fan, the same data as that shown in the table is obtained for the positive and negative values in the table, regardless of the diameter, the length and number of revolutions of the fan.
−0.4
−0.4
−0.5
−0.6
−0.6
−0.7
−0.9
−1.1
−1.5
−2.1
−2.6
−0.2
−0.4
−0.5
−0.5
−0.5
−0.6
−0.7
−0.9
−1.4
−1.8
−2.5
−0.1
−0.1
−0.2
−0.3
−0.3
−0.4
−0.5
−0.8
−1.2
−1.8
−2.5
−0.1
−0.1
−0.2
−0.3
−0.4
−0.7
−1.2
−1.7
−2.4
−0.1
−0.1
−0.2
−0.2
−0.6
−1.0
−1.6
−2.2
−0.2
−0.4
−0.6
−1.3
−1.9
−0.2
−0.6
−1.2
−1.7
−0.2
−0.8
−1.5
−0.1
−0.6
−1.1
−1.7
−0.2
−0.5
−0.9
−1.5
−2.0
−0.1
−0.1
−0.2
−0.3
−0.4
−0.7
−1.1
−1.6
−2.2
It is seen from above Table 1 that the air volume is larger than that of the reference cross-flow fan in the case where w/L is not larger than 0.15 and r/e is not smaller than 0.3 and not larger than 1.5.
As shown in Table 1, as r/e is closer to 1.0, the outer side of the blade is closer to parallel with the rotational axis, and the air volume is larger. As r/e is too large, the angle with the rotational axis is large as well, and accordingly the air volume tends to be smaller.
It is further seen from Table 1 that, as w/L is larger, basically the air volume tends to be smaller. In the case where r (outward displacement (mm) of the blade cross section from the bottom toward the head of the blade (outward displacement L4 in
As shown in
In this way, pulsation of forced vortex accompanying the secondary flow near each support plate 225 can also be suppressed, and abnormal noise (bubbling noise) can be alleviated.
While
Thus, blades 224A to 224E can be attached at different intervals to reduce nZ noise (peak noise) generated when cross-flow fan 200 is rotated. In the example shown in
In the example shown in
Specifically, respective heads of blades 224 of impeller 226A are fit in and attached to a groove formed in the top surface (another main surface) of support plate 225 of impeller 226B.
Gap 227 formed in impeller 226A and gap 227 of impeller 226B that is adjacent to gap 227 of impeller 226A in the direction in which blade 224 extends are different in width.
Thus, impellers 226A and 226B axially adjacent to each other have respective blades 224 that are circumferentially displaced from each other, so that respective acoustic waves of impellers 226 have a phase difference therebetween and the acoustic waves cancel each other. In this way, the noise generated while cross-flow fan 200 is rotating can be reduced.
Specifically, impeller 226A and impeller 226B are identical in shape, while impeller 226B is secured (attached) to impeller 226A in the state where impeller 226B is rotated backward in rotational direction R about rotational central line O, relative to impeller 226A.
The blade of impeller 226B that is adjacent to blade 224B (first reference blade) of impeller 226A is blade 224A located forward in rotational direction R relative to corresponding blade 224B of impeller 226B, and blade 224B of impeller 226A and blade 224A of impeller 226B are adjacent to each other in the vicinity of support plate 225. Thus, impeller 226B is placed in the state where impeller 226B is rotated relative to impeller 226A, so that gap 227 of impeller 226A and adjacent gap 227 of impeller 226B are different from each other.
Therefore, gap 227 extends from one end to the other end of cross-flow fan 200 with a constant width, and respective widths of gaps 227 circumferentially adjacent to each other are different from each other. In other words, at the head of blade 224 of impeller 226A, the bottom of corresponding blade 224 of impeller 226B is located, and each of blades 224 arranged at different intervals in the circumferential direction extends linearly from one end to the other end of cross-flow fan 200.
A difference between this another modification illustrated in
In this way, a plurality of impellers 226 are stacked on each other, so that pulsation of forced vortex accompanying the secondary flow near support plate 225 can be suppressed and abnormal noise (bubbling noise) can be alleviated. Further, because of the inclination of blades 224 and gaps 227, the blade passing sounds do not simultaneously occur, and thus peak noise (nZ noise) can be suppressed at the same time. Accordingly, the rotational speed of the fan can be increased as compared with the conventional fan, under the condition that respective noise levels are substantially identical, and the available upper limit of the rotational speed of the fan can be increased as compared with the conventional fan. Thus, the blowing ability of the fan can be further improved.
While embodiments of the present invention have been described, it should be construed that the embodiments disclosed herein are by way of illustration in all respects, not by way of limitation. It is intended that the scope of the present invention is defined by claims, not by the above description of the embodiments, and includes all modifications and variations equivalent in meaning and scope to the claims. Numerical values referenced above are also examples and the invention is not limited to the numerical values and the range thereof.
The present invention is applicable to a cross-flow fan, a blower and a molding machine for an impeller, and particularly suitable for a cross-flow fan formed by stacking a plurality of impellers, a blower including this cross-flow fan, and a molding machine for the impellers.
100 air conditioner, 102 casing, 110 heat exchanger, 120 wind guide plate, 130 flap, 200 cross-flow fan, 222, 223, 225 support plate, 224 blade, 226 impeller, 227 gap, 300, 301 reference plane, 310 inner side, 311 outer side, CL1, CL2, P central line, CP1, CP2 central point, D1, D2 virtual axis line, D3, D4 blade chord, e, L1, L2, r distance, L3 reduction, L4 outward displacement, O rotational central line, Q1, Q2 outer end, Q3, Q4 inner end, R rotational direction, S1, S2 virtual circle, W, θ1 rotational angle, θ2, θ3 cross angle
| Number | Date | Country | Kind |
|---|---|---|---|
| 2008-272255 | Oct 2008 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2009/067658 | 10/9/2009 | WO | 00 | 3/18/2011 |
