JP4896213B2 - Cross-flow fan and air conditioner equipped with the same - Google Patents

Description

  The present invention relates to a cross-flow fan used as a blowing means and an air conditioner equipped with the cross-flow fan.

As a conventional once-through fan, for example, one disclosed in Patent Document 1 is known. This is because the shape along the longitudinal line of the outer diameter side end of a large number of blades (blades) attached between the blade holding plates (rings) of the impeller alternates between a phase that advances in the rotational direction and a phase that moves backward The shape is such that the phase is changed. That is, the shape of the phase change in the longitudinal direction line at the outer diameter side end of the blade is formed in the order of advance-retreat-advance or reverse-advance-retreat in the rotation direction. As a result, the rotational sound primary and secondary are reduced, and the sound quality is good and the noise can be reduced.
In Patent Document 2, a cylindrical portion is intermittently provided at the blade tip on the outer peripheral side of the impeller at intervals in the longitudinal direction of the blade, and the outer diameter of the cylindrical portion is larger than the thickness of the blade. Is disclosed.

JP-A-9-250493 (page 3, FIGS. 1 and 2) Japanese Patent Laid-Open No. 2-115598 (2nd page, FIG. 1)

In the once-through fan described in Patent Document 1, since the blade position outer diameter changes, there is a portion where the gap is widened between the surface of the tongue that separates the blowing air passage and the suction air passage of the once-through fan, Since the leakage flow occurs, there is a problem that the loss is large and the rotational torque at the same air volume is increased. As a result, the power consumption of the fan motor is increased and the energy saving performance is inferior.
Also, in the cross-flow fan described in Patent Document 2, since a configuration with a cylindrical portion and a non-cylindrical portion are alternately provided on the outer peripheral side of the blade in the longitudinal direction of the blade, there is a gap between the tongue surface. There will be a part where the width becomes wider, and there is a problem similar to that of Patent Document 1. In addition, since there is a concern that the vortex of the airflow generated by the cylindrical portion grows greatly in the vicinity of the tongue, it is considered that the noise reduction effect cannot be expected so much.

The present invention has been made in view of the problems as described above, and reduces the ventilation resistance by equalizing the wind speed distribution in the blowout air passage, and also reduces the power consumption of the fan motor and saves energy. The purpose is to obtain.
Moreover, an object of this invention is to obtain an air conditioner with good energy saving property by mounting such a cross-flow fan.

The cross-flow fan according to the present invention is
At least two support plates spaced apart in the direction of the rotation axis;
In a cross-flow fan provided with an impeller having a plurality of blades spaced apart in the circumferential direction of the support plate between the support plates,
The outer diameters of the plurality of blades in the blade cross section perpendicular to the rotation axis of the impeller are substantially the same,
The longitudinal length of the wing is divided into a plurality of regions, a portion adjacent to the support plate is a first region, a central portion of the wing is a second region, and a portion between the first region and the second region is a third region. In the case of the region, the blade exit angle at the blade outer peripheral end of each region is characterized by increasing in the order of second region <first region <third region.

  Moreover, the air conditioner which concerns on this invention arrange | positions a heat exchanger in said wind path provided in the inside of a main body, and said cross-flow fan downstream from this heat exchanger.

As described above, the cross-flow fan mounted on the air conditioner of the present invention has a minimum blade exit angle in the second region, which is the blade central portion in the longitudinal direction, and therefore flows in the longitudinal central portion between the support plates. Since the blade exit angle is the largest in the third region, air is blown out in the radial direction relative to the other regions, and the distance between the blades is increased, so that the wind speed can be reduced. Further, in the first region where the speed is low, the blade exit angle is reduced and the distance between the blades is reduced, so that turbulence generation due to instability of the flow can be prevented and the wind speed can be increased. Therefore, the wind speed distribution in the blowout air passage is made uniform, and the high wind speed region is locally eliminated, so that the load torque can be reduced and the power consumption of the fan motor can be reduced. In addition, since the blade outer radius does not change in the circumferential and longitudinal directions and the gap with the tongue can be kept constant, the loss due to leakage flow is reduced, ventilation resistance is reduced, and load torque can be reduced. it can.
As a result, an energy-saving air conditioner can be obtained.

1 is an external perspective view of an air conditioner according to Embodiment 1 of the present invention. It is a longitudinal cross-sectional view of the air conditioner of FIG. FIG. 3A is a side view of the impeller, and FIG. 3B is a front view showing a half section of the impeller. FIG. 4 is a cross-sectional view of a blade in the AA cross section (first region) in FIG. 3. FIG. 4 is a cross-sectional view of a blade in a BB cross section (second region) in FIG. 3. FIG. 4 is a cross-sectional view of a blade in a CC cross section (third region) in FIG. 3. It is a perspective view of 1 blade | wing for showing a blade outer peripheral part. The noise value by the ratio L1 / L of the length L1 of the first region with respect to the distance L between the rings, and the noise value in the case of the blade shape in the vicinity of the ring (first region) in the full length in the longitudinal direction as a comparative example It is a figure which shows a difference. It is a figure which shows the relationship of difference (DELTA) (beta) 2 (= (beta) 2c- (beta) 2a)) between the blade exit angle (beta) 2c in the blade outer periphery edge part of 3rd area | region, and the blade exit angle (beta) 2a in the blade outer periphery edge part of 1st area | region, and a noise value difference.

Embodiment 1 FIG.
First, an outline of an air conditioner equipped with a cross-flow fan according to the present invention will be described. 1 is an external perspective view of a wall-mounted air conditioner according to Embodiment 1 of the present invention, and FIG. 2 is a longitudinal sectional view of the air conditioner of FIG. FIG. 2 also shows the wind speed distribution U1 when the conventional cross-flow fan is mounted and the wind speed distribution U2 when the cross-flow fan of the present invention is mounted as the wind speed distribution at the outlet.
In FIG.1 and FIG.2, the main body 1 of the air conditioner which concerns on this invention is installed in the wall of the room air-conditioned. The main body front surface 1a is covered with a removable front grille 6. The main body upper part 1b is provided with a suction port 2 for sucking room air, and the lower part of the main body is provided with a blower outlet 3 for blowing out air-conditioned air into the room. Up and down wind direction vanes 4a and left and right wind direction vanes 4b are rotatably attached to the air outlet 3 so that the direction of air flow into the room can be adjusted.

  Inside the main body 1, in the air passage 5 from the suction port 2 to the blowout port 3, an electric dust collector 7 that collects dust by applying static electricity to the dust in order from the upstream side, and a mesh-like shape that removes dust. A filter 8, a heat exchanger 9 for cooling and heating air, and a cross-flow fan 10 according to the present invention are mainly arranged. The heat exchanger 9 is a fin-tube heat exchanger, and is disposed on the front side and the upper side of the impeller 10a of the cross-flow fan 10 so as to cover the impeller 10a.

  The impeller 10a of the cross-flow fan 10 is between a tongue 11a that separates the suction-side air passage 5a and the blow-out air passage 5b and a guide wall (also referred to as a rear guide) 12 that forms a scroll wall on the back side of the main body. is set up. In addition, a stabilizer 11 having a drain pan 11b that temporarily receives water drops (drain water) dripping from the heat exchanger 9 is horizontally mounted inside the main body 1, and the tongue portion 11a is integrated with the tip of the drain pan 11b. Is formed. In the figure, O indicates the rotational center of the impeller 10a, and RO indicates the rotational direction of the impeller 10a.

  In this air conditioner, when the impeller 10a of the once-through fan 10 is rotationally driven, room air is sucked from the suction port 2 of the suction grill provided in the upper part of the main body. Dust and the like contained in the air are removed from the sucked room air by the electric dust collector 7 and the filter 8, and clean air passes through the heat exchanger 9 and is sucked into the impeller 10 a. At that time, the refrigerant flowing through the tubes of the heat exchanger 9 and the air passing between the fins and tubes of the heat exchanger 9 are subjected to heat exchange, and the air that has become cold air or warm air crosses the impeller 10a (throughflow). And air is blown out from the air outlet 3 into the room through the air outlet side air passage 5b.

  Next, the cross-flow fan 10 will be described in detail with reference to FIGS. 3 is a schematic view of the impeller of the cross-flow fan according to Embodiment 1 of the present invention, FIG. 3 (a) is a side view of the impeller, and FIG. 3 (b) is a front view showing a half section of the impeller. is there. 4, 5, and 6 are enlarged cross-sectional views of one blade in a cross section orthogonal to the rotation axis of the once-through fan, respectively, and FIG. 4 is an AA view in a first region in the blade longitudinal direction of FIG. 3. 5 is a cross-sectional view taken along the line BB in the second region in the blade longitudinal direction of FIG. 3, and FIG. 6 is a cross-sectional view taken along the line CC in the third region in the longitudinal direction of the blade of FIG. FIG. 7 shows a perspective view of one blade for representing the outer periphery of the blade. In FIG. 3, the wind speed distribution V1 of the conventional cross-flow fan and the wind speed distribution V2 of the cross-flow fan of the present invention are shown together.

  In FIG. 3, the impeller 10 a of the cross-flow fan 10 has one or more impeller units 10 c in the rotation axis direction X. The impeller 10c is used as at least two disc-shaped support plates arranged at a predetermined interval, for example, at a predetermined interval in the circumferential direction at the outer peripheral portion between the ring 10b and the two rings 10b. It is comprised from the some wing | blade 20 arrange | positioned. Both ends of the blade 20 are fixed to the ring 10 b and are arranged in parallel to the rotation axis direction X. The impeller single unit 10c is formed of, for example, a thermoplastic resin such as AS resin or ABS resin, and a plurality of impeller units 10c are connected and integrated in the rotation axis direction X by welding or the like, thereby having one or more impeller single units 10c. An impeller 10a is formed. A fan shaft 10d is attached to the ring 10b, which is one end plate at both ends of the impeller 10a, and a fan boss 10e is provided on the ring 10b, which is the other end plate, and a motor boss is provided on the fan boss 10e. The motor shaft 13a is attached by inserting 13 motor shafts 13a and fixing them with screws or the like. The impeller 10a configured as described above has the fan shaft 10d and the motor shaft 13a supported by both ends in the air passage 4 as shown in FIG. 2 via bearings (not shown), respectively. It can blow by rotating in the direction.

Here, the length of the blade 20 in the longitudinal direction is divided into five regions as shown in FIGS. 3 and 7, and the blade cross-sectional shape is formed as shown below.
A first region 20a indicated by a length L1 is a blade tip portion in the vicinity of the ring adjacent to the ring 10b. The second region 20b indicated by the length L2 is the central portion of the wing. And the 3rd field 20c shown by length L3 is between the 1st field 20a and the 2nd field 20b, ie, the middle part (inter-blade part) of a wing. The total length in the longitudinal direction of the blade 20 between the rings 10b is L, and in this example, L = 2 (L1 + L3) + L2.

  The blade 20 is formed in an airfoil shape as shown in FIGS. 4 to 6 in the sectional shape in each of the regions 20a, 20b, and 20c. The blade 20 is formed in an arc shape, and the blade outer peripheral end portion T1 and the blade inner peripheral end portion T2 are formed in a circular arc shape having roundness. The radius R01 of the straight line O-T1o that connects the arc center T1o of the blade outer peripheral end T1 and the impeller rotation center O is substantially the same radial dimension in the longitudinal direction in the blade sections of the regions 20a, 20b, and 20c. The impeller effective outer diameter, which is the diameter of the circumscribed circle of all the blades, is the same in the longitudinal direction. Accordingly, the gap between the effective outer diameter of the impeller and the surface of the tongue portion 11a is constant in each of the regions 20a, 20b, and 20c.

FIG. 4 shows the blade cross-sectional shape of the first region 20a. FIG. 4 also shows the blade cross-sectional shape of the third region 20c adjacent to the first region 20a for comparison with the blade cross-sectional shape of the first region 20a.
The blade cross-sectional shape of the first region 20a is such that the warp line S which is the thickness center line of the pressure surface 20p facing the rotation direction RO side of the blade 20 and the negative pressure surface 20s facing the counter-rotation side is the rotation of the impeller. With respect to a predetermined radius R03 from the center O, it is formed by two arcs of an outer peripheral warp line S1a having an outer predetermined radius Ra31 and an inner peripheral warp line S2a having an inner predetermined radius Ra32. However, the relationship between the curvature radii Ra31 and Ra32 of the two warp lines 31a and 32a is Ra31 <Ra32. Further, the pressure surface 20p is formed of two arcs of a radius of curvature Ra11 on the outer peripheral side and a radius of curvature Ra12 on the inner peripheral side with respect to the predetermined radius R03 from the impeller rotation center O. The relationship between Ra11 and Ra12 is Ra11 <Ra12. The suction surface 20s is formed of two arcs of a radius of curvature Ra21 on the outer peripheral side and a radius of curvature Ra22 on the inner peripheral side with respect to the predetermined radius R03 from the impeller rotation center O. The relationship with Ra22 is Ra21 <Ra22.

  A blade exit angle β2a, which is a narrow angle formed by a tangent of a circle centered on the impeller rotation center O at the arc center T1o of the blade outer peripheral end T1 of the blade 20 and a tangent of the blade outer peripheral sled line S1a, is predetermined. Wings 20 are formed to have an angle.

FIG. 5 shows the blade cross-sectional shape of the second region 20b. In FIG. 5, the blade cross-sectional shapes of the first region 20a and the third region 20c are also shown for comparison with the blade cross-sectional shape of the second region 20b.
The blade sectional shape of the second region 20b is such that the warp line S, which is the thickness center line of the pressure surface 20p facing the rotational direction RO side of the blade 20 and the negative pressure surface 20s facing the counter-rotation side, is the rotation of the impeller. With respect to a predetermined radius R03 from the center O, it is formed by two arcs of an outer peripheral warp line S1b of an outer predetermined radius Rb31 and an inner peripheral warp line S2b of an inner predetermined radius Rb32. However, the relationship between the curvature radii Rb31 and Rb32 of the two warp lines 31b and 32b is Rb31 <Rb32. The pressure surface 20p is formed of two arcs of a radius of curvature Rb11 on the outer peripheral side and a radius of curvature Rb12 on the inner peripheral side with respect to the predetermined radius R03 from the impeller rotation center O. The relationship between Rb11 and Rb12 is Rb11 <Rb12. The suction surface 20s is formed of two arcs of a radius of curvature Rb21 on the outer peripheral side and a radius of curvature Rb22 on the inner peripheral side with respect to a predetermined radius R03 from the impeller rotation center O. The relationship with Rb22 is Rb21 <Rb22.

  A blade exit angle β2b, which is a narrow angle formed by a tangent of a circle centering on the impeller rotation center O at the arc center T1o of the blade outer peripheral end T1 of the blade 20 and a tangent of the blade outer peripheral warp line S1b, is predetermined. Wings 20 are formed to have an angle.

FIG. 6 shows the blade cross-sectional shape of the third region 20c. In FIG. 6, the blade cross-sectional shape of the first region 20a adjacent to the third region 20c is also shown for comparison with the blade cross-sectional shape of the third region 20c.
The blade sectional shape of the third region 20c is such that the warp line S, which is the thickness center line of the pressure surface 20p facing the rotational direction RO side of the blade 20 and the negative pressure surface 20s facing the counter-rotation side, is the rotation of the impeller. With respect to a predetermined radius R03 from the center O, it is formed by two arcs of an outer peripheral warp line S1c of an outer predetermined radius Rc31 and an inner peripheral warp line S2c of an inner predetermined radius Rc32. However, the relationship between the curvature radii Rc31 and Rc32 of the two warp lines 31c and 32c is Rc31> Rc32. The pressure surface 20p is formed of two arcs of a radius of curvature Rc11 on the outer peripheral side and a radius of curvature Rc12 on the inner peripheral side with respect to the predetermined radius R03 from the impeller rotation center O. The relationship between Rc11 and Rc12 is Rc11> Rc12. The suction surface 20s is formed from two arcs of a radius of curvature Rc21 on the outer peripheral side and a radius of curvature Rc22 on the inner peripheral side with respect to a predetermined radius R03 from the impeller rotation center O. The relationship with Rc22 is Rc21> Rc22.

  A blade exit angle β2c, which is a narrow angle formed by a tangent of a circle centering on the impeller rotation center O at the arc center T1o of the blade outer peripheral end T1 of the blade 20 and a tangent of the blade outer peripheral warp line S1b, is predetermined. Wings 20 are formed to have an angle.

  In the blade cross-sectional shape of each region of the first region 20a to the third region 20c, a circle having a predetermined radius R03 from the impeller rotation center O is used as a reference for changing the shape of the blade outer peripheral side, and is within the predetermined radius R03. The peripheral blade cross-sectional shape is the same in the longitudinal direction. That is, in each region, the radius Ra32 = Rb32 = Rc32 of the sled line S2, the pressure surface inner radius Ra12 = Rb12 = Rc12 = R12, and the suction surface inner radius Ra22 = Rb22 = Rc22 = R22. Further, in the blade cross-sectional shape on the outer peripheral side from the predetermined radius R03, the radius Rb31 <Ra31 <Rc31 of the sled line S1, the pressure surface inner peripheral radius Rb11 <Ra11 <Rc11, and the suction pressure inner peripheral radius Rb21 <Ra21 <Rc21. It is formed to become. As a result, the blade exit angle increases in the order of β2b (second region) <β2a (first region) <β2c (third region). Therefore, as shown in FIG. 5, the blade outer peripheral end T1 of the second region 20b advances most in the rotational direction than the other regions, and the blade outer peripheral end of the third region 20c reverses most in the rotational direction. It has a blade cross-sectional shape. Therefore, the chord length is also shortened in the order of second region <first region <third region.

  FIG. 7 is a perspective view showing the shape of the blade outer peripheral portion 20d in each of the first region 20a to the third region 20c. As shown in FIG. 7, the wing 20 has a longitudinal direction, the first region 20a at two ends adjacent to the ring, the second region 20b at the central portion of the wing, and between the first region 20a and the second region 20b. Divided into five regions of the third region 20c of the two inter-blade portions, each is formed in a rectangular shape having a predetermined length L1, L2, L3 in the longitudinal direction, and an inclined surface is formed between the five regions. The blade shape connected by 20e is formed.

By forming the blade cross-sectional shape of each region 20a, 20b, 20c as described above, as shown in FIG. 2, in the case of a cross-flow fan having the same blade cross-sectional shape in the conventional longitudinal direction, the outlet height direction Like the wind speed distribution U1, the wind speed is fast at the center of the blade and is slow at the blade tip near the ring due to the friction loss on the ring surface. On the other hand, the wind velocity distribution U2 of the present invention has the smallest blade exit angle in the second region 20b (blade center), and the blade outer peripheral edge protrudes more forward than the blade outer peripheral edge in the other region in the impeller rotation direction. ), The flow does not concentrate too much at the center of the blade in the longitudinal direction between the rings, and the blade exit angle is the largest in the third region 20c (interblade portion), and the radius is relatively larger than in other regions. Since the air is blown out in the direction, the distance between the blades adjacent to each other in the rotation direction (inter-blade distance) is also increased, so that the wind speed can be reduced. In addition, in the first region 20a (blade tip near the ring), which has a low speed, the generation of turbulence due to instability of the flow can be prevented by reducing the blade exit angle and reducing the distance between the blades, and Wind speed can be increased.
Moreover, since the blade outer radius does not change in the circumferential direction and the longitudinal direction and the gap with the tongue portion 11a can be kept constant, loss due to leakage flow is reduced, ventilation resistance is reduced, and load torque is further reduced. Can do.

Further, the present invention has a different blade exit angle instead of diffusing the flow by suppressing the turbulence by diffusing the flow at the blade outer periphery end by forming the blade outer periphery end to be gradually curved in the longitudinal direction as in the prior art. Since the region has a rectangular shape with a predetermined width in the longitudinal direction, the wind speed distribution to the downstream outlet is made uniform by controlling the blowing direction of the impeller in the longitudinal direction.
In addition, since five regions having different blade exit angles are formed by inclined surfaces and are not substantially perpendicular steps, there is no sudden change in flow on the blade surface, so there is no disturbance due to steps.

Accordingly, the wind speed distribution is made uniform in the longitudinal direction of the blade, and the local high wind speed region is eliminated. Therefore, the load torque is reduced, so that the power consumption of the motor can be reduced. Further, since the local high-speed flow is not applied to the wind direction vanes disposed on the downstream side, the ventilation resistance can be reduced and the load torque can be further reduced.
Further, since the wind speed to the wind direction vanes is uniform and there is no locally high speed region, noise due to boundary layer disturbance on the wind direction vane surface can be reduced.
As a result, an energy-saving and low-noise air conditioner can be obtained.

The blade 20 is an airfoil blade that is thin on the inner peripheral side and outer peripheral side of the impeller and has a maximum thickness near the center, and has a predetermined radius centered on the impeller rotation center O on the outer peripheral side from the maximum thickness portion. The blade shape is changed on the outer peripheral side from R03, and the inner peripheral side is formed so as to have the same shape in the longitudinal direction of the impeller. In addition, since it is not twisted in the longitudinal direction, and even in the maximum wall thickness portion of the wing, it is not twisted in the longitudinal direction, so the torsional strength is high and it does not break.
Therefore, since such a once-through fan is mounted, a high-quality air conditioner can be obtained.

Further, in the order of blade exit angle β2b <β2a <β2c, the outer peripheral side of the second region 20b is advanced most in the rotational direction than the other regions, and the outer peripheral side of the third region 20c is conversely the most receded shape, The first region 20a, the second region 20b, and the third region 20c are formed in a substantially identical rectangular shape in the longitudinal direction between the predetermined lengths L1, L2, and L3 in the longitudinal direction, and the second region 20b is the second region 20b. The first region 20a protrudes in the rotational direction, and the second region 20b is formed to protrude in the rotational direction from the third region 20c.
Therefore, if the length L1 in the longitudinal direction of the first region 20a is too short, the flow in the vicinity of the ring is attracted to the third region 20c and the low speed region increases in the vicinity of the ring, resulting in a difference in wind speed distribution. On the other hand, if the length L1 of the first region 20a is too long, the length L3 of the third region 20c becomes short, the high-speed flow increases in the vicinity of the ring, and a difference in wind speed distribution occurs. Accordingly, there is an optimum range for the length L1 of the first region 20a and the inter-ring distance (the total length of the blade) L.

FIG. 8 shows a noise value based on the ratio L1 / L of the length L1 of the first region 20a with respect to the distance L between the rings and, as a comparative example, a blade shape in the vicinity of the ring (first region) in the entire length in the longitudinal direction. It is a figure which shows the difference with the noise value. In the graph of the figure, the vertical axis represents the noise value difference [dB], and the horizontal axis represents L1 / L [%].
From FIG. 8, it is at least low noise if L1 / L = 25% to 40%. If L1 / L is less than 25%, the length L1 of the first region 20a is too short, and the low speed region increases near the ring as described above. Therefore, the noise value of the comparative example tends to be rather large. On the other hand, when L1 / L is about 43% or more, the length L1 of the first region 20a is too long, and the difference in blade shape from the comparative example is almost eliminated, so that the noise value increases. Therefore, in order to reduce the noise level, the range of 25% ≦ L1 / L ≦ 40% is desirable as the range of L1 / L.

Further, FIG. 9 shows a difference Δβ2 (= β2c−β2a) between the blade outlet angle β2c at the blade outer peripheral end of the third region 20c and the blade outlet angle β2a at the blade outer peripheral end of the first region 20a, and the noise value difference. It is a figure which shows the relationship. In the graph of the figure, the vertical axis represents the noise value difference [dB], and the horizontal axis represents the exit angle difference Δβ2 [°].
As described above, the blade outlet angle β2b in the second region 20b <the blade outlet angle β2a in the first region 20a <the blade outlet angle β2c in the third region 20c is formed so as to increase in order. However, if the outlet angle difference Δβ2 between the blade outlet angle β2a in the first region 20a and the blade outlet angle β2c in the third region 20c is too large, the speed is increased between the first region 20a and the third region 20c. Since the difference is generated and the flow is disturbed, the noise reduction effect is reduced. On the contrary, if the exit angle difference Δβ2 is too small, there is no noise reduction effect.
Therefore, from FIG. 9, if the exit angle difference Δβ2 is at least 2 ° to 4 °, a noise reduction effect can be obtained.

  The cross-flow fan of the present invention is not limited to the air conditioner described above, but can be effectively used in car air conditioners, air purifiers, humidifiers, dehumidifiers, and the like.

  DESCRIPTION OF SYMBOLS 1 Main body, 1a Main body front, 1b Upper body, 2b Suction port, 3 Outlet, 4a Vertical wind vane, 4b Left and right wind vane, 5 Air channel, 5a Suction side air channel, 5b Outlet air channel, 6 Front grille, 7 Electric dust collector, 8 filter, 9 heat exchanger, 10 once-through fan, 10a impeller, 10b ring (support plate), 10c impeller alone, 10d fan shaft, 10e fan boss, 11 stabilizer, 11a tongue, 11b drain pan , 12 guide wall, 13 motor, 13a motor shaft, 20 impeller blades, 20a first region, 20b second region, 20c third region, 20d blade outer peripheral portion, 20e inclined surface, 20p pressure surface, 20s suction surface, L Total length of blade, L1 length of first region, L2 length of second region, L3 length of third region, O impeller R01, the radius of a straight line connecting the arc center T1o of the blade outer peripheral end T1 and the impeller rotation center O, the radius of a straight line connecting the arc center T2o of the inner peripheral end T2 of the blade and the impeller rotation center O, R03 Reference radius for changing blade shape, RO impeller rotation direction, S warp line, S1 blade outer periphery side warp line, S1a blade outer periphery side warp line, S1b second region blade outer periphery warp line, S1c 3rd region blade outer periphery warp line, S2 blade inner periphery warp wire, S2a first region blade inner warp line, S2b second region blade inner warp line, S2c third region blade Circumferential warp line, T1 blade outer peripheral end, T1o blade outer peripheral end arc center, T2 blade inner peripheral end, T2o blade inner peripheral end circular arc center, U1 Conventional wind speed distribution in the height direction of the outlet , U2 Wind velocity distribution in the outlet height direction in the present invention, V1 Conventional Longitudinal velocity distribution between roots wheel rings, longitudinal velocity distribution between the impeller rings in V2 present invention.

Claims (7)

At least two support plates spaced apart in the direction of the rotation axis;
In a cross-flow fan provided with an impeller having a plurality of blades spaced apart in the circumferential direction of the support plate between the support plates,
The outer diameters of the plurality of blades in the blade cross section perpendicular to the rotation axis of the impeller are substantially the same,
The longitudinal length of the wing is divided into a plurality of regions, a portion adjacent to the support plate is a first region, a central portion of the wing is a second region, and a portion between the first region and the second region is a third region. A cross-flow fan in which the blade outlet angle at the blade outer peripheral edge of each region increases in the order of the second region <first region <third region. The blade outer peripheral end of the second region advances in the rotational direction more than the blade outer peripheral end of the first region,
The cross-flow fan according to claim 1, wherein the blade outer peripheral end portion in the first region is formed with a blade so that the blade outer peripheral end portion in the third region advances in the rotational direction.   The blade is formed so that the blade cross-sectional shape of each region changes on the outer peripheral side from the maximum thickness portion, and the blade cross-sectional shape of each region is the same on the inner peripheral side from the maximum thickness portion. The once-through fan according to claim 1 or 2.   The length of the blade in the longitudinal direction is divided into five regions, and the outer peripheral portion of the blade in each region is formed in a rectangular shape in the longitudinal direction, and the regions are connected by inclined surfaces. The once-through fan according to any one of claims 1 to 3.   The flow-through according to any one of claims 1 to 4, wherein the blades are formed so that a ratio between a blade length of the first region and a blade total length between support plates is 25% to 40%. fan.   The blade is formed such that the difference between the blade outlet angle at the blade outer peripheral end of the third region and the blade outlet angle at the blade outer peripheral end of the first region is 2 ° to 4 °. The once-through fan according to any one of claims 1 to 5.   An air characterized in that a heat exchanger and a cross-flow fan according to any one of claims 1 to 6 are disposed downstream of the heat exchanger in an air passage through which air is provided. Harmony machine.

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