WO2015063851A1

WO2015063851A1 - Cross-flow fan and air conditioner

Info

Publication number: WO2015063851A1
Application number: PCT/JP2013/079217
Authority: WO
Inventors: 池田　尚史; 平川　誠司; 代田　光宏
Original assignee: 三菱電機株式会社
Priority date: 2013-10-29
Filing date: 2013-10-29
Publication date: 2015-05-07
Also published as: JPWO2015063851A1; EP3064776A1; EP3064776A4; EP3064776B1

Abstract

An impeller (8a) in a cross-flow fan (8) has a plurality of support plates (8b) and a plurality of blades (8c). Each outer circumferential side end section (15a) and inner circumferential side end section (15b) in each blade (8c) have a shape whereby same retreat in the rotation direction, from one corresponding support plate towards the other corresponding support plate, then again advance in the rotation direction, or have a shape whereby same advance in the rotation direction, then retreat in the rotation direction again.

Description

Cross-flow fan and air conditioner

The present invention relates to a cross-flow fan and an air conditioner using the cross-flow fan.

Patent Document 1 discloses a cross-flow fan in which each blade is inclined at a predetermined angle with respect to the fan shaft, and the blade mounting pitch is set at unequal intervals. In this cross flow fan, the blades are thin in the longitudinal direction of the impeller.

Patent Document 2 discloses an axial fan in which a blade cross section orthogonal to a rotation axis is formed so as to become smaller from a root portion of a blade portion continuously provided on a main surface toward a tip portion. Further, in such an axial fan, the center of the blade cross section orthogonal to the rotation axis is displaced toward the front side or the rear side in the rotation direction about the rotation axis as it goes from the root part of the blade part toward the tip part. Further, the blade cross section is curved outward in the radial direction.

Furthermore, Patent Document 3 discloses a fan configured by alternately stacking first component parts in which the blade tip is inclined in the rotation direction from the root and second component parts in the counter-rotation direction. Is disclosed.

Japanese Patent No. 3107711 Japanese Patent No. 4549416 JP-A-9-158890

However, in the cross-flow fan, when viewed between the pair of rings, a relatively large flow tends to be blown out from the vicinity of the center between the pair of rings apart from the pair of rings. There is a problem of non-uniformity. In addition, the conventional fans disclosed in Patent Documents 1 to 3 described above can generate a component of the flow from one ring to the other ring, but the flow between the pair of rings described above is not good. It is difficult to alleviate the problem of uniformity.

The present invention has been made in view of the above, and an object of the present invention is to provide a cross-flow fan that can alleviate uneven flow between a pair of support plates.

In order to achieve the above-described object, the cross-flow fan of the present invention is a cross-flow fan including an impeller and a shaft that rotatably supports the impeller, the impeller corresponding to a plurality of support plates. A plurality of wings arranged at intervals in the circumferential direction between the pair of supporting plates, and each of the plurality of wings has an inner peripheral side end portion corresponding to the other supporting plate from the corresponding one supporting plate. It has a shape that retreats in the rotation direction and then moves forward again in the rotation direction toward the support plate, or a shape that moves forward in the rotation direction and then retreats again in the rotation direction. However, it may be configured so that it moves backward from the corresponding one support plate to the corresponding other support plate in the rotational direction and then advances again in the rotational direction, or advances forward in the rotational direction and then again in the rotational direction. It has a retreating shape.
Further, each of the plurality of blades may have a pair of ring side portions extending along the rotation axis direction without moving forward or backward in the rotation direction.
In order to achieve the same object, the air conditioner of the present invention is disposed between a stabilizer that divides the suction side air passage and the blowout side air passage in the main body, and the suction side air passage and the blowout side air passage. A cross flow fan, a ventilation resistor disposed in the main body, and a guide wall for guiding the air discharged from the cross flow fan to the outlet of the main body. This is a once-through fan.

According to the present invention, it is possible to mitigate the non-uniform flow between the pair of support plates.

It is a figure which shows the installation state when it sees from the room regarding the air conditioner which shows Embodiment 1 of this invention. It is a longitudinal cross-sectional view of the air conditioner of FIG. It is a figure which shows the front and side of the impeller of a once-through fan mounted in the air conditioner of FIG. It is the perspective view seen from the impeller rotation direction side surface (blade pressure surface) regarding one blade of the impeller of the once-through fan. FIG. 4 is a view showing a side surface shape of a blade taken along line AA in FIG. 3 and a side surface shape of the blade taken along line BB. It is sectional drawing regarding the rotating shaft direction center part of a pair of ring in the blade | wing of a crossflow fan. It is sectional drawing regarding the rotating shaft direction center part of a pair of ring in the blade | wing of a crossflow fan. It is sectional drawing regarding the rotating shaft direction center part of a pair of ring in the blade | wing of a crossflow fan. It is a figure of the same aspect as FIG. 3 regarding Embodiment 2 of this invention. It is a figure of the same aspect as FIG. 5 regarding Embodiment 2 of this invention. It is a figure of the same aspect as FIG. 3 regarding Embodiment 3 of this invention. It is a figure of the same aspect as FIG. 4 regarding Embodiment 3 of this invention. It is a figure of the same aspect as FIG. 5 regarding Embodiment 3 of this invention. It is a figure of the same aspect as FIG. 4 regarding Embodiment 4 of this invention.

Hereinafter, embodiments of an air conditioner according to the present invention will be described with reference to the accompanying drawings. In the drawings, the same reference numerals indicate the same or corresponding parts.

Embodiment 1 FIG.
FIG. 1 is an installation schematic diagram when viewed from a room of an air conditioner equipped with a cross-flow fan according to Embodiment 1 of the present invention, FIG. 2 is a longitudinal sectional view of the air conditioner of FIG. 1, and FIG. It is a figure which shows the front and side of the impeller of a once-through fan mounted in the air conditioner of FIG.

As shown in FIG. 1, the air conditioner (indoor unit) 100 includes a main body 1 and a front panel 1 b provided on the front surface of the main body 1, so that an outline of the air conditioner 100 is configured. Here, in FIG. 1, the air conditioner 100 is installed in the wall 11a of the room 11 which is an air-conditioning target space. That is, FIG. 1 illustrates an example in which the air conditioner 100 is a wall-hanging type, but the present invention is not limited to such an embodiment, and may be, for example, a ceiling-embedded type. Moreover, the air conditioner 100 is not limited to being installed in the room 11, and may be installed in a room of a building or a warehouse, for example.

As shown in FIG. 2, a suction grill 2 for sucking room air into the air conditioner 100 is formed in the upper part 1 a constituting the upper part of the main body 1. An air outlet 3 for supplying the air to the room is formed, and a guide wall 10 for guiding air discharged from a cross-flow fan 8 described later to the air outlet 3 is formed.

As shown in FIG. 2, the main body 1 generates conditioned air by transmitting to the air a filter (ventilation resistor) 5 that removes dust and the like in the air sucked from the suction grill 2 and the heat or cold of the refrigerant. Arranged between the heat exchanger (ventilation resistor) 7, the stabilizer 9 that partitions the suction side air passage E1 and the blowout side air passage E2, and the suction side air passage E1 and the blowout side air passage E2, A cross-flow fan 8 that sucks in air and blows out air from the air outlet 3, and a vertical wind vane 4 a and a left-right wind vane 4 b that adjust the direction of the air blown from the cross-flow fan 8 are provided.

The suction grill 2 is an opening for forcibly taking room air into the air conditioner 100 by the cross-flow fan 8. The suction grill 2 has an opening formed on the upper surface of the main body 1. The blower outlet 3 is an opening through which the air passes when the air sucked from the suction grill 2 and passed through the heat exchanger 7 is supplied into the room. The blower outlet 3 is formed as an opening in the front panel 1b. The guide wall 10 constitutes the blowing side air passage E2 in cooperation with the lower surface side of the stabilizer 9. The guide wall 10 forms a spiral surface from the cross-flow fan 8 to the outlet 3.

The filter 5 is formed in a mesh shape, for example, and removes dust in the air sucked from the suction grill 2. The filter 5 is provided on the downstream side of the suction grille 2 and on the upstream side of the heat exchanger 7 in the air path from the suction grille 2 to the air outlet 3 (center portion inside the main body 1).

The heat exchanger 7 (indoor heat exchanger) functions as an evaporator during cooling operation to cool air, and functions as a condenser (heat radiator) during heating operation to heat the air. is there. The heat exchanger 7 is provided on the downstream side of the filter 5 and on the upstream side of the cross-flow fan 8 in the air path from the suction grill 2 to the blower outlet 3 (center portion inside the main body 1). In FIG. 2, the shape of the heat exchanger 7 is a shape that surrounds the front surface and the upper surface of the cross-flow fan 8, but is merely an example and is not particularly limited.

It is assumed that the heat exchanger 7 is connected to an outdoor unit that may be a well-known embodiment having a compressor, an outdoor heat exchanger, a throttling device, and the like and constitutes a refrigeration cycle. Further, as the heat exchanger 7, for example, a cross fin type fin-and-tube heat exchanger composed of a heat transfer tube and a large number of fins is used.

The stabilizer 9 divides the suction side air passage E1 and the blowout side air passage E2, and is provided on the lower side of the heat exchanger 7 as shown in FIG. Located on the upper surface side of the stabilizer 9, the blowing side air passage E <b> 2 is located on the lower surface side of the stabilizer 9. The stabilizer 9 has a drain pan 6 that temporarily stores the condensed water adhering to the heat exchanger 7.

The cross-flow fan 8 is for sucking room air from the suction grill 2 and blowing air-conditioned air from the outlet 3. The cross-flow fan 8 is provided on the downstream side of the heat exchanger 7 and on the upstream side of the air outlet 3 in the air path from the suction grill 2 to the air outlet 3 (the central portion inside the main body 1).

As shown in FIG. 3, the cross-flow fan 8 includes an impeller 8a made of a thermoplastic resin such as AS resin (Styrene-AcryloNitrile copolymer) containing glass fiber, and a motor 12 for rotating the impeller 8a. And the motor shaft 12a for transmitting the rotation of the motor 12 to the impeller 8a, and the impeller 8a itself rotates to suck indoor air from the suction grill 2 and send conditioned air to the blowout port 3. .

The impeller 8a is configured by connecting a plurality of impeller units 8d, and each impeller unit 8d has a plurality of blades 8c and at least one ring fixed to the end side of the plurality of blades 8c. (Support plate) 8b. That is, in the impeller single unit 8d, each of the plurality of blades 8c extends from the outer peripheral side surface of the disk-shaped ring 8b so as to be substantially perpendicular to the side surface, and the plurality of blades 8c are connected to the ring 8b. The impeller 8a is formed by welding a plurality of such impellers 8d and connecting them together.

The impeller 8a has a fan boss 8e protruding toward the inside (center) side of the impeller 8a. The fan boss 8e is fixed to the motor shaft 12a with a screw or the like. In the impeller 8a, one side of the impeller 8a is supported by the motor shaft 12a via the fan boss 8e, and the other side of the impeller 8a is supported by the fan shaft 8f. Thereby, the impeller 8a rotates in the rotation direction RO around the impeller rotation center O of the impeller 8a in a state where both ends are supported, sucks room air from the suction grille 2, and conditioned air into the outlet 3 Can be sent in. The impeller 8a will be described in detail later.

The up-and-down airflow direction vane 4a adjusts the vertical direction of the air blown from the cross-flow fan 8, and the left-right wind direction vane 4b adjusts the left-right direction of the air blown from the cross-flow fan 8. is there. The up / down wind direction vane 4a is provided on the downstream side of the left / right wind direction vane 4b. Note that the vertical direction in the description corresponds to the vertical direction in FIG. 2, and the horizontal direction in the description corresponds to the front and back direction of the paper surface in FIG.

FIG. 4 is a perspective view of one blade of a cross-flow fan impeller viewed from the impeller rotation direction side surface (blade pressure surface). FIG. 5 is a diagram showing the side shape of the wing taken along line AA in FIG. 3 and the side shape of the wing taken along line BB.

As shown in FIGS. 4 and 5, each of the plurality of blades 8 c has the inner peripheral side end portion 15 b retreated in the rotation direction from the corresponding one ring toward the corresponding other ring, and then again, It has a shape that advances in the rotational direction, and the outer peripheral side end portion 15a also moves backward from the corresponding one ring toward the other corresponding ring and then advances again in the rotational direction. It is comprised so that it may have a shape. In other words, as shown in FIG. 3 and FIG. 4, when the pressure surface of the blade 8 c is projected, the plurality of blades 8 c have the inner peripheral end 15 b and the outer peripheral end 15 a respectively up and down. It has an inverted V shape. Therefore, as for each of the inner peripheral side edge part 15b and the outer peripheral side edge part 15a, the center part of the rotation axis direction of a pair of rings is most retracted in the rotation direction. Moving forward in the direction of rotation. Further, as shown in FIG. 5, the blade 8c has a constant cross-section (cross-section in the direction orthogonal to the rotation axis) over the rotation axis direction, but faces the center portion of the rotation axis direction and the ring. It is deviated from the portion by an angle δ.

Further, as shown in FIG. 5, each of the plurality of blades 8c has an outer diameter (a distance between an outer peripheral side end portion 15a described later and a rotation axis O) and an outer diameter (described later) over the rotation axis direction. The distance between the inner peripheral side end 15b and the rotation axis O is kept the same, and the cross-sectional area shape of the blade 8c is also kept the same in the direction of the rotation axis. That is, each of the plurality of blades 8c is formed in a three-dimensional shape such that the blade cross section orthogonal to the impeller rotation axis remains the same, and moves forward or backward with respect to the impeller rotation direction.

Next, details of the cross-sectional shape in the direction orthogonal to the rotation axis of the blade 8c will be described. FIG. 6 to FIG. 8 are cross-sectional views of the pair of rings in the central portion in the rotational axis direction of the blades of the cross-flow fan.

As shown in FIGS. 6 to 8, the outer peripheral end 15a and the inner peripheral end 15b of the blade 8c are each formed in an arc shape. The blade 8c is formed so that the outer peripheral end 15a side is inclined forward in the impeller rotation direction RO with respect to the inner peripheral end 15b side. That is, when the blade 8c is viewed in a longitudinal section, the blade pressure surface 13a and the blade negative pressure surface 13b of the blade 8c are moved from the impeller rotation center (rotary axis) O of the impeller 8a toward the outside of the blade 8c. Curved in the vehicle rotation direction RO.

The center of the circle corresponding to the arc shape formed on the outer peripheral end 15a is P1 (also referred to as arc center P1), and the center of the circle corresponding to the arc shape formed on the inner peripheral end 15b is P2 (arc Also referred to as center P2. Further, if a line segment connecting the arc centers P1 and P2 is a chord line (chord) L, the chord line L has a length Lo as shown in FIG. 8 (hereinafter also referred to as a chord length Lo). ).

The blade 8c has a blade pressure surface 13a that is a surface on the rotational direction RO side of the impeller 8a and a blade negative pressure surface 13b that is a surface on the opposite side of the rotational direction RO of the impeller 8a. The vicinity of the center of the line L has a concave shape curved in a direction from the blade pressure surface 13a toward the blade suction surface 13b.

In the blade 8c, the radius of the circle corresponding to the arc shape on the blade pressure surface 13a side is different between the outer peripheral side of the impeller 8a and the inner peripheral side of the impeller 8a. That is, as shown in FIG. 7, the surface on the blade pressure surface 13a side of the blade 8c has an outer peripheral curved surface Bp1 whose radius (arc radius) corresponding to the arc shape on the outer peripheral side of the impeller 8a is Rp1, and the impeller A radius (arc radius) corresponding to the arc shape on the inner peripheral side of 8a has an inner peripheral curved surface Bp2 whose radius is Rp2, and is a multiple arc curved surface. Further, the blade pressure surface 13a side surface of the blade 8c has a flat surface Qp that is connected to the inner peripheral end of the inner peripheral curved surface Bp2 and has a planar shape.

Thus, the surface on the blade pressure surface 13a side of the blade 8c is configured by continuously connecting the outer peripheral curved surface Bp1, the inner peripheral curved surface Bp2, and the plane Qp. Note that when the blade 8c is viewed in a longitudinal section, the straight line forming the plane Qp is a tangent line at a point where the straight line is connected to the arc forming the inner peripheral curved surface Bp2.

On the other hand, the surface on the blade suction surface 13b side of the blade 8c is a surface corresponding to the surface on the blade pressure surface 13a side. Specifically, the surface of the blade 8c on the blade suction surface 13b side includes an outer peripheral curved surface Bs1 whose radius (arc radius) corresponding to the arc shape on the outer peripheral side of the impeller 8a is Rs1, and the inner periphery of the impeller 8a. And an inner circumferential curved surface Bs2 whose radius (arc radius) corresponds to the arc shape on the side is Rs2. Further, the surface of the blade 8c on the blade suction surface 13b side has a flat surface Qs that is connected to the inner peripheral end of the end portions of the inner peripheral curved surface Bs2 and has a planar shape.

As described above, the surface on the blade suction surface 13b side of the blade 8c is configured by continuously connecting the outer circumferential surface curved surface Bs1, the inner circumferential surface curved surface Bs2, and the plane Qs. Note that when the blade 8c is viewed in a longitudinal section, the straight line that forms the plane Qs is a tangent line at the point that it is connected to the arc that forms the inner peripheral curved surface Bs2.

Next, the blade thickness will be explained. When the diameter of a circle inscribed in the blade surface when the blade 8c is viewed in a longitudinal section is a blade thickness (thickness) t, as shown in FIG. 7, the blade thickness (thickness) t1 of the outer peripheral end 15a is shown in FIG. Is thinner than the blade thickness (wall thickness) t2 of the inner peripheral end 15b. The blade thickness t1 corresponds to the radius R1 × 2 of the circle that forms the arc of the outer peripheral side end portion 15a, and the blade thickness t2 corresponds to the radius R2 × 2 of the circle that forms the arc of the inner peripheral side end portion 15b. Correspond.

That is, when the diameter of a circle inscribed in the blade pressure surface 13a and the blade suction surface 13b of the blade 8c is defined as the blade thickness, the blade thickness is smaller at the outer peripheral end 15a than at the inner peripheral end 15b. It is formed so as to gradually increase from the portion 15a toward the center, become maximum at a predetermined position near the center, gradually become thinner toward the inside, and have the same thickness at the straight portion Q.

More specifically, the blade thickness t of the blade 8c is determined by the outer peripheral curved surface Bp1 and the inner peripheral curved surface formed by the blade pressure surface 13a and the blade negative pressure surface 13b, excluding the outer peripheral end 15a and the inner peripheral end 15b. In the range of Bp2, the outer peripheral curved surface Bs1, and the inner peripheral curved surface Bs2, it gradually increases from the outer peripheral end 15a toward the center of the blade 8c, and reaches the maximum thickness t3 at a predetermined position near the center of the chord line L. Then, the thickness gradually decreases toward the inner peripheral end 15b. The blade thickness t is an inner peripheral side end thickness t2 that is a substantially constant value in the range of the straight portion Q, that is, the range between the plane Qp and the plane Qs.

Here, a portion of the blade 8c having the planes Qp and Qs of the inner peripheral end 15b as the surface is referred to as a straight portion Q. That is, the blade negative pressure surface 13b of the blade 8c is formed by multiple arcs and straight portions Q from the outer peripheral side to the inner peripheral side of the impeller.

In the cross-flow fan having the above configuration and the air conditioner equipped with the same, the following effects can be obtained.

First, when each of the plurality of blades 8c sucks air from the outside to the inside of the cross-flow fan 8 (that is, in the case of the flow in the blade 8c at the upper left side in FIG. In the case of the flow in the blade 8c when located on the side air passage E1 side, air flows from the outer peripheral side end portion 15a toward the inner peripheral side end portion 15b as shown by a dotted arrow in FIG. . Therefore, the air flowing out from the inner peripheral end 15b toward the inside of the cross-flow fan 8 flows so as to spread toward the corresponding pair of rings 8b. Therefore, in the cross-flow fan in which a relatively large amount of flow tends to be blown out from the vicinity of the center between the pair of rings apart from the pair of rings when viewed between the pair of rings, the vicinity of the pair of rings is also positive. Therefore, the flow can be directed and the flow can be made uniform between the pair of rings.

On the other hand, when air is blown from the inside of the once-through fan 8 to the outside (that is, in the case of the flow at the blade 8c located at the lower right side of the cross-flow fan 8 in FIG. In the case of the flow in the blade 8c when positioned, air flows from the inner peripheral side end portion 15b toward the outer peripheral side end portion 15a as shown by a solid arrow in FIG. Therefore, when the air flows through the inner peripheral side end 15b, the air flows along the blade 8c as a flow with a blade tip vortex having the inner peripheral side end 15b as an end and the separation is suppressed. By suppressing the separation in this way, the maintenance of a uniform flow is promoted.

In addition, the following effects can be obtained.
(1) Since the negative pressure surface 13b of the blade 8c is formed of multiple arcs and straight portions Q from the outer peripheral side to the inner peripheral side of the impeller, the flow of the blade surface when the blade 8c passes through the suction side air passage E1. Is peeled off at the outer peripheral curved surface Bs1, the flow is reattached by the inner peripheral curved surface Bs2 having a different arc radius.

(2) Further, since the blade 8c has a flat surface Qs and a negative pressure is generated, even if the flow starts to peel off on the inner peripheral curved surface Bs2, it reattaches.

(3) Further, since the blade thickness t increases on the inner peripheral side of the impeller compared to the outer peripheral side of the impeller, the distance between the adjacent blades 8c is reduced.

(4) Furthermore, since the flat surface Qs is flat, the blade thickness t does not increase rapidly toward the outer periphery of the impeller as compared with the curved surface, so that the frictional resistance can be suppressed.

(5) The pressure surface 13a of the blade 8c is also formed by multiple arcs and straight portions (planes) from the outer peripheral side to the inner peripheral side of the impeller. For this reason, when the air flows from the outer peripheral curved surface Bp1 to the inner peripheral curved surface Bp2 having a different arc radius, the flow is gradually accelerated and a pressure gradient is generated on the negative pressure surface 13b. do not do.

(6) Further, the downstream plane Qp is tangent to the inner circumferential curved surface Bs2. In other words, since the blade 8c has the downstream plane Qp, it has a shape bent by a predetermined angle with respect to the rotation direction RO. For this reason, compared with the case where there is no straight surface (plane Qp), even if the blade thickness t2 of the inner peripheral side end portion 15b is thick, the flow can be directed to the suction surface 13b. The wake vortex when flowing into the impeller from the end 15b can be suppressed.

(7) The blade 8c has a thick inner end 15b and is difficult to separate in various inflow directions in the blowout air passage E2.

(8) Further, the blade 8c has the maximum thickness near the center of the chord, which is the downstream side of the plane Qs. For this reason, if the flow is about to peel after passing through the plane Qs, the blade thickness t gradually increases toward the center of the chord on the inner circumferential curved surface Bs2, and therefore the separation can be suppressed along the flow.

(9) Furthermore, since the blade 8c has the inner peripheral curved surface Bs1 having a different arc radius on the downstream side of the inner peripheral curved surface Bs2, the separation of the flow is suppressed, and the effective blowing side air passage from the impeller is expanded. It is possible to reduce and equalize the blown wind speed, and to reduce the load torque applied to the blade surface.

Furthermore, in the present embodiment, advantageous effects are obtained even with respect to the conventional configurations disclosed in Patent Documents 1 to 3 described above. First, in the configuration disclosed in Patent Document 1, the blade is thinned according to the position of the impeller in the rotation axis direction. Further, in the configuration disclosed in Patent Document 2, the outer diameter is reduced and the inner diameter is increased as it extends from the root of the blade on the ring side, and the blade tip is further inclined in the rotation axis direction. The blade outer diameter changes in the longitudinal direction of the impeller. For this reason, the flow of the impeller rotating shaft direction which goes to the other ring from one ring will generate | occur | produce. In addition, since the gap between the stabilizer and the casing facing the impeller is enlarged in the direction of the rotation axis, the leakage loss of the flow increases, and the gap changes in the direction of the impeller rotation axis, so that the gap is wide from a narrow region. The flow flows out into the area and leakage loss increases. Furthermore, the motor power consumption increases due to the deterioration of efficiency. Furthermore, the configuration disclosed in Patent Document 3 requires two components. In addition, since the direction of the blade inclination is changed alternately for each impeller, a region where the flow is concentrated near the ring and a region where the flow is separated from the vicinity of the ring are alternately generated for each ring. Roughness becomes wide with every single ring, and dust accumulates on the filter installed at the air inlet of the air conditioner and pressure loss increases, resulting in conspicuous density and the worst reverse flow in a wide rough area. For this reason, condensation occurs when high-humidity air flows backward during cooling, and condensed water may be discharged to the outside.

(10) In relation to these problems, in the present embodiment, the blade 8c has the same blade cross section orthogonal to the impeller rotation axis, and the central portion between the blade rings in the impeller rotation direction with respect to the impeller rotation direction. In contrast, the clearance with the stabilizer 9 facing the impeller is the same, and the leakage flow caused by the circulating vortex g1 is increased due to the difference in the longitudinal direction, which was a problem in the conventional configuration. Therefore, the efficiency can be increased and the motor power to be driven can be reduced.

(11) Since the blade has a region where the blade moves backward with respect to the rotation direction of the impeller and the blade end portion is inclined with respect to the rotation shaft of the impeller, when the blade passes around the stabilizer 9 facing the impeller, the blade Since it is dispersed without being subjected to pressure fluctuations in the entire region of the blade tip in the longitudinal direction of the vehicle, an annoying rotational sound (NZ sound) resulting from the rotational speed and the number of blades can be reduced, and noise can be reduced. As a result, since flow separation on the blade surface can be suppressed on the impeller suction side and the blowout side, noise can be reduced, and power consumption of the fan motor can be reduced. That is, the indoor unit 100 equipped with the quiet and energy-saving once-through fan 8 can be obtained.

Embodiment 2. FIG.
Next, Embodiment 2 of the present invention will be described with reference to FIGS. 9 and FIG. 10 are views of the same mode as FIG. 3 and FIG. 5, respectively, regarding the second embodiment of the present invention. The configuration of the second embodiment is the same as that of the first embodiment described above except for the parts described below.

In short, in the present second embodiment, the above-described first embodiment and the above-described V-shaped form are opposite to each other. In the second embodiment, each of the plurality of blades 108c has its inner peripheral side end portion 15b advanced in the rotational direction from the corresponding one ring toward the corresponding other ring, and then again in the rotational direction. The outer peripheral side end portion 15a also has a shape that moves forward from the corresponding one ring toward the other corresponding ring and then moves back in the rotational direction again. It is configured to be. In other words, when the pressure surface of the blade 8c is viewed in a projection manner, each of the plurality of blades 8c has an inner peripheral end 15b and an outer peripheral end 15a each having a V shape. Therefore, as for each of the inner peripheral side edge part 15b and the outer peripheral side edge part 15a, the center part of the rotation axis direction of a pair of rings has advanced most in the rotation direction, and in the part of the both sides, as it approaches a ring, Retracted in the direction of rotation.

In the second embodiment configured as described above, the same operation as that of the first embodiment is obtained with respect to the air flow. That is, when each of the plurality of blades 108c sucks air from the outside of the cross-flow fan 8 into the inside, the blade tip vortex having the outer end 15a as the end when the air flows through the outer end 15a. Therefore, the flow of the blade 108c flows as a flow in which separation is suppressed, and the maintenance of a uniform flow is promoted. In addition, when air is blown from the inside of the cross-flow fan 8 to the outside, the air flowing out from the outer peripheral side end portion 15a toward the outside of the cross-flow fan 8 spreads toward the corresponding pair of rings 8b. The flow can be actively directed to the vicinity of the pair of rings, and the flow can be made uniform between the pair of rings.

Embodiment 3 FIG.
Next, Embodiment 3 of the present invention will be described with reference to FIG. 11, FIG. 12, and FIG. 11, FIG. 12 and FIG. 13 are views of the same mode as FIG. 3, FIG. 4 and FIG. The configuration of the third embodiment is the same as that of the first embodiment described above except for the portions described below.

Briefly, the third embodiment is a wing having a V-shaped configuration similar to that of the first embodiment described above, and further, a portion in the vicinity of the corresponding pair of rings in the wing (ring side portion). Extends along the direction of the axis of rotation (does not advance or retract in the direction of rotation). That is, as best shown in FIG. 12, each of the plurality of wings 208c is arranged in the vicinity of the corresponding pair of rings as a part in a predetermined range from the ring in the rotational axis direction without moving forward or backward in the rotational direction. It has a ring side portion 220 extending along.

In the third embodiment configured as described above, the same operation as that of the first embodiment is obtained with respect to the air flow. Further, in the third embodiment, each of the plurality of blades has a pair of ring side portions extending along the rotation axis direction without moving forward or backward in the rotation direction, and thus has the following advantages. Has been obtained. That is, when laminating a plurality of impellers, when the blades of one impeller are welded to the ring of another impeller, the blade tip is upright so that it touches the ring surface upright. Workability is good and weldability is also improved. Further, since the inclination is eliminated at the blade parallel portions (ring side portions) at both ends, the concentration or dispersion of the flow on the ring surface is suppressed, and the flow near the ring is stabilized. As a result, even if dust or the like accumulates on the filter installed at the suction port of the air conditioner and the pressure loss increases, the wind speed distribution is made uniform and backflow can be prevented. Therefore, a high-quality air conditioner can be obtained without condensation even during cooling.

In addition, although the said description in this Embodiment 3 was illustrated as a combination with Embodiment 1, this Embodiment 3 can also be implemented in combination with Embodiment 2. FIG. That is, in the wing 108c of the second embodiment, a ring side portion 220 extending along the rotation axis direction without moving forward or backward in the rotation direction is formed in the vicinity of the corresponding pair of rings. It may be carried out as described above.

Embodiment 4 FIG.
Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 14 is a diagram of the same mode as FIG. 4 regarding the third embodiment of the present invention. The configuration of the fourth embodiment is the same as that of the first embodiment described above except for the portions described below.

In the above-described first to third embodiments, the inner end and the outer end of each of the plurality of blades may be set in such a manner that after retreating in the rotational direction and then moving forward again in the rotational direction, The set mode of moving forward again in the rotation direction after retreating is provided, but the present invention is not limited to this, and one or both of the inner peripheral end and the outer peripheral end are provided. A plurality of the above set aspects may be provided. FIG. 14 is an example of such a fourth embodiment.

In the wing 308c of FIG. 14 which is an example of the fourth embodiment, the inner peripheral side end portion 15b is provided with only one set mode in which it moves backward in the rotational direction and then moves forward again in the rotational direction. That is, it is formed in the same manner as the inner peripheral side end portion of the blade of the first embodiment. On the other hand, the outer peripheral side end portion 15a of the wing 308c is provided with a plurality of the above set modes. Note that both the wings in the illustrated example of the fourth embodiment and the wings in the illustrated examples of the first to third embodiments are symmetrical on both sides with respect to the center in the rotational axis direction between the pair of rings. It is comprised so that it may become.

Also in the fourth embodiment, the same effects as those of the first to third embodiments described above can be obtained at the corresponding portions at the inner peripheral side end and the outer peripheral side end of the blade.

The illustrated example of the fourth embodiment has been described assuming that the features of the fourth embodiment are applied to the upside down V-shaped wing referred to in the first embodiment. It is also possible to apply the characteristics of the fourth embodiment to a wing shaped like a blade.

Although the contents of the present invention have been specifically described with reference to the preferred embodiments, various modifications can be made by those skilled in the art based on the basic technical idea and teachings of the present invention. It is self-explanatory.

1 body, 8 cross-flow fan, 8a impeller, 8b ring (support plate), 8c, 108c, 208c, 308c wing, 9 stabilizer, 15a outer peripheral end, 15b inner peripheral end, 100 air conditioner.

Claims

A cross-flow fan comprising an impeller and a shaft that rotatably supports the impeller,
The impeller has a plurality of support plates, and a plurality of blades arranged in the circumferential direction between a pair of corresponding support plates,
Each of the plurality of blades has a shape in which the inner peripheral side end portion retreats in the rotation direction from one corresponding support plate toward the other support plate, and then advances again in the rotation direction, or After moving forward in the rotational direction, it has a shape that retreats again in the rotational direction, and after the outer peripheral side end retreats in the rotational direction from the corresponding one support plate to the other corresponding support plate , Again having a shape that advances in the rotational direction, or after moving forward in the rotational direction, again has a shape that retreats in the rotational direction,
Cross-flow fan.
Each of the plurality of blades has a pair of ring side portions extending along the rotation axis direction without moving forward or backward in the rotation direction.
The once-through fan according to claim 1.
A stabilizer that partitions the suction-side air passage and the blow-out air passage in the body,
A once-through fan disposed between the suction side air passage and the outlet side air passage;
A ventilation resistor disposed in the body;
An air conditioner comprising a guide wall for guiding the air discharged from the cross-flow fan to the outlet of the main body,
The cross-flow fan is the cross-flow fan according to claim 1 or 2.
Air conditioner.