WO2018143135A1

WO2018143135A1 - Cross-flow-type blower and indoor unit of air conditioner provided with same

Info

Publication number: WO2018143135A1
Application number: PCT/JP2018/002798
Authority: WO
Inventors: 弘宣寺岡; 貴士柏原; 錦帆劉
Original assignee: ダイキン工業株式会社
Priority date: 2017-02-02
Filing date: 2018-01-29
Publication date: 2018-08-09
Also published as: CN210686350U; JP2018123775A

Abstract

A cross-flow-type blower (30), wherein the relationship between an angle θ when the position of a protrusion (71) relative to a volute tongue point (O) of a scroll wall part (37a) is represented by the center angle of a fan rotor (31) and the protruding height H of the protrusion (71) is designed to satisfy the relationship represented by H ≤ 2.2τθ.

Description

Cross flow type blower and indoor unit of air conditioner equipped with the blower

The present disclosure relates to a crossflow type blower and an indoor unit of an air conditioner including the blower, and particularly relates to a structure that suppresses surging in a crossflow type blower.

Conventionally, a cross-flow type blower is used in an indoor unit of an air conditioner (see, for example, Patent Document 1 below).

A cross-flow type blower includes a cylindrical fan rotor having a plurality of blades and rotating around a central axis, and a housing in which an air inlet and an outlet are formed and the fan rotor is accommodated. ing. In this cross-flow type blower, the air that is sucked into the housing from the suction port flows through the fan rotor toward the blower outlet when the fan rotor rotates around the central axis in the housing.

The crossflow type blower is disposed in an air passage formed in the casing of the indoor unit of the air conditioner. In addition, a heat exchanger that heats or cools the air is also arranged in the air passage of the casing by heat exchange between the refrigerant flowing inside and the air.

In the crossflow type blower, generally, the housing is provided with a scroll wall portion where the area of the air flow path gradually increases in a region where air flows from the fan rotor toward the outlet. The scroll enlarged area ratio τ is represented by τ = (A1 + A2) / A1 in FIG. Note that A1 = π × r02.

In the above equation, r0 is the length of a line segment connecting the start point of the curve formed by the enlarged flow path of the casing and the rotation center of the cross flow fan, A1 is a fan-shaped area with radius R0, and A2 is the fan center A straight line with an angle θ of 90 ° formed by the twisted line segment r0 is an area obtained by subtracting A1 from an area surrounded by a point Q that intersects the enlarged flow path curve (a portion enlarged with respect to A1).

In patent document 2, ventilation efficiency can be improved by setting it to 1.416 <= tau <= 1.466 with respect to expansion area ratio (tau) = 1.39 quoted as the prior art of this patent document 2. It is described.

Further, as means for suppressing the occurrence of surging (periodic fluctuations in pressure and discharge amount) due to the backflow of air from the scroll wall surface, Patent Document 3 describes that a plurality of protrusions are provided in the vicinity of the scroll start. It is described that a high surging suppression effect can be obtained by making the protrusion on the downstream side larger than the protrusion on the upstream side of the air flow.

JP 2008-275231 A Japanese Patent No. 5230814 Japanese Patent Laying-Open No. 2015-092073

By the way, when a cross-flow type blower is applied to an indoor unit in which a duct is connected to the air inflow side or the air outflow side of the casing, the external static pressure (pressure loss) during operation increases. Under the conditions, since the air volume decreases with respect to the rotational speed of the fan, there is a tendency that the flow velocity tends to be slow on the wall surface of the scroll wall portion, and a backflow of air is generated therefrom, and surging is likely to occur.

Therefore, in order to suppress the occurrence of surging in the cross-flow type blower, the scroll wall portion enlargement area ratio τ is made smaller than 1.39, the distance between the fan and the scroll is narrowed, and the scroll wall flow velocity is increased. By doing so, it is conceivable to suppress the occurrence of backflow.

However, the smaller the enlarged area ratio is, the closer the distance between the fan rotor and the scroll wall portion is, so that the loss is increased and the noise and power consumption may increase. That is, when the enlarged area ratio τ is smaller than 1.39, it is difficult to suppress noise and power consumption simply by providing a protrusion near the start of winding of the scroll wall.

The purpose of the present disclosure is to suppress an increase in loss and increase noise and power consumption when the distance between the fan rotor and the scroll wall is close when the scroll expansion area ratio τ is smaller than 1.39. This is to suppress the occurrence of surging.

The first aspect of the present disclosure includes a fan rotor (31) that has a plurality of blades (34) and rotates around a central axis (X), an air suction port (32a), and an air outlet (32b). And a housing (32) in which the fan rotor (31) is accommodated, and the housing (32) has a blowout flow path (F) from the fan rotor (31) toward the blowout port (32b). The blowout flow path (F) has an enlarged flow path (70) comprising a scroll wall portion (37a) in which the distance from the outer circumference of the fan rotor (31) gradually increases from the upstream to the downstream of the flow path. ) And at least one projection (71) projecting from the wall surface of the scroll wall (37a) toward the fan rotor (31) on the downstream side of the winding start point (O) of the scroll wall (37a). ) Is assumed to be a crossflow type blower.

In this cross flow type compressor, the expansion area ratio τ of the expansion flow path (70) is τ ≦ 1.39, and the protrusion with respect to the winding start point (O) of the scroll wall portion (37a). The relationship between the angle θ when the position of (71) is expressed by the central angle of the fan rotor (31) and the protrusion height H of the protrusion (71) is expressed as H ≦ 2.2τθ. It is characterized by satisfying.

In the first aspect, at least one projecting from the wall surface of the scroll wall (37a) toward the fan rotor (31) on the downstream side of the winding start point (O) of the scroll wall (37a) of the housing (32). In the cross flow fan in which the two protrusions (71) are formed, the expansion area ratio τ of the expansion flow path (70) is τ ≦ 1.39, and the position (angle) θ of the protrusion (71) and the protrusion height H Since the relationship is H ≦ 2.2τθ, the protrusion (71) can be prevented from becoming too large. If the protrusion (71) is large, the turbulence of the wind tends to occur. However, in the first aspect, the size of the protrusion (71) is regulated by the equation of H ≦ 2.2τθ. It is possible to suppress the occurrence of turbulence by interfering with the flow.

According to a second aspect of the present disclosure, in the first aspect, the height H (mm) of the protrusion (71) closest to the winding start point (O) of the scroll wall portion (37a) is H ≦ 0.7. It is characterized by being.

In the second mode, since the relationship of H ≦ 0.7 is satisfied, it is possible to suppress the protrusion (71) from becoming too large, and as a result, the protrusion (71) interferes with the flow of the wind and turbulence occurs. Can be suppressed.

The third aspect of the present disclosure is characterized in that, in the first or second aspect, the height H (mm) of the protrusion (71) is H ≧ 0.5.

In the third aspect, since the height H (mm) of the protrusion (71) is set to satisfy H ≧ 0.5, it is possible to suppress the protrusion (71) from becoming too small.

A fourth aspect of the present disclosure is an indoor unit of an air conditioner that adjusts the temperature of indoor air, a casing (20) in which an air inlet (21) and an outlet (22) are formed; The cross flow type blower (30) according to claim 1, 2 or 3, wherein the cross flow type blower (30) is provided in the casing (20) to form an air flow flowing from the inlet (21) to the outlet (22). A heat exchanger (40) provided on the upstream side of the air flow with respect to the cross-flow type blower (30) in the casing (20) to heat or cool the air. It is said.

In the fourth aspect, in the indoor unit of the air conditioner, it is possible to suppress the disturbance of the wind flow in the housing (32) of the crossflow type blower (30).

According to a fifth aspect of the present disclosure, in the fourth aspect, a duct (2) is connected to one or both of the inlet (21) and the outlet (22) of the casing (20). .

In the fifth aspect, the interior of the air conditioner where the external static pressure is increased by connecting the duct (2) to one or both of the inlet (21) and the outlet (22) of the casing (20). In the unit, it is possible to prevent the wind flow from being disturbed in the housing (32) of the crossflow type blower (30).

According to the first aspect of the present disclosure, on the downstream side of the winding start point (O) of the scroll wall portion (37a) of the housing (32), from the wall surface of the scroll wall portion (37a) to the fan rotor (31) side. In the cross flow fan in which at least one protrusion (71) protruding is formed, the expansion area ratio τ of the expansion flow path (70) is set to τ ≦ 1.39, and the position (angle) θ of the protrusion (71) and the protrusion height Since the relationship between the height H and H ≦ 2.2τθ can suppress the protrusion (71) from becoming too large, the protrusion (71) can be prevented from interfering with the wind flow and causing turbulence. . Therefore, when the enlarged area ratio τ of the scroll is made smaller than 1.39, the distance between the fan rotor (31) and the protrusion (71) is too close, unlike the case of merely providing the protrusion. Therefore, the increase in noise and power consumption can be suppressed, and the surging suppression effect can be enhanced.

According to the second aspect, by satisfying the relationship of H ≦ 0.7, it is possible to suppress the protrusion (71) from becoming too large, and thus the protrusion (71) interferes with the wind flow and generates turbulence. Therefore, the increase in noise and power consumption can be suppressed, and the surging suppression effect can be enhanced.

According to the third aspect, the height H (mm) of the protrusion (71) is set to H ≧ 0.5 to prevent the protrusion (71) from becoming too small, so that the scroll wall (73a ) Can easily form the protrusion (71).

According to the fourth aspect, in the indoor unit of the air conditioner, it is possible to suppress the disturbance of the wind flow in the housing (32) of the crossflow type blower (30), and to increase noise and power consumption. While suppressing, a surging suppression effect is also heightened.

According to the fifth aspect, the air conditioner in which the external static pressure is increased by connecting the duct (2) to one or both of the inlet (21) and the outlet (22) of the casing (20). In this indoor unit, the disturbance of the wind flow in the housing (32) of the crossflow type blower (30) is suppressed, noise and power consumption are suppressed, and the surging suppression effect is enhanced.

Drawing 1 is a side sectional view showing the installation state of the indoor unit of the air harmony device concerning an embodiment. FIG. 2 is a side sectional view of the indoor unit of the air conditioner of FIG. FIG. 3 is an enlarged perspective view showing a fan rotor of a crossflow type blower provided in the indoor unit of FIG. 1. FIG. 4 is an enlarged view of a main part of FIG. FIG. 5 is an enlarged view showing the size (radius) of the first protrusion and the second protrusion of the example and the comparative example. FIG. 6 is an enlarged view showing positions (angles) of the first protrusion and the second protrusion of the example and the comparative example. FIG. 7 is a table showing the position (angle) and size (radius) of the first protrusion and the second protrusion of the example and the comparative example. FIG. 8 is a table showing the rotational speed, blowing noise, motor input, and maximum static pressure outside the examples and comparative examples.

Hereinafter, the indoor unit of the air conditioning apparatus according to the embodiment will be described with reference to the drawings. The following embodiments are essentially preferable examples, and are not intended to limit the scope of the present disclosure, applied products, or uses thereof.

As shown in FIG. 1, the indoor unit (10) is installed in a falling ceiling (1) in which the ceiling surface of the indoor space (S) is lowered by one step. The indoor unit (10) includes a casing (20), a cross-flow blower (30), a heat exchanger (40), a drain pan (50), and an electrical component box (60). The cross-flow blower (30), heat exchanger (40), drain pan (50), and electrical component box (60) are connected to the air passage (P) (see FIG. 2) formed in the casing (20). is set up.

The casing (20) is formed of a substantially rectangular parallelepiped box. Specifically, in FIG. 1, the casing (20) is a vertically long and thin box whose longitudinal direction (front and back direction in the drawing) is longer than the lateral direction (left and right direction) and whose height is lower than the lateral length in plan view. Constructed in the body. In the casing (20), an inflow port (21) is formed on one side surface (right side surface in FIG. 1) and an outflow port (22) is formed on the other side surface (left side surface in FIG. 1). Has been. The other end of the suction duct (2) whose one end opens in the indoor space (S) is connected to the inflow port (21). The outlet (22) is formed in a duct shape and passes through the side surface (1a) of the falling ceiling (1) and opens in the indoor space (S).

The cross-flow blower (30) has a fan rotor (impeller) (31), a housing (32), and a motor (not shown). The crossflow type blower (30) is formed long in the vertical direction.

The heat exchanger (40) is provided in the casing (20) on the suction side of the cross-flow blower (30). As shown in FIG. 2, the heat exchanger (40) has three heat exchanging parts, ie, first to third heat exchanging parts (41 to 43). The first to third heat exchanging parts (41 to 43) are formed long in the vertical direction, similarly to the cross-flow type blower (30). The first to third heat exchanging sections (41 to 43) are arranged at different angles so as to surround the suction side of the crossflow type blower (30).

The drain pan (50) is provided below the heat exchanger (40) in the casing (20) so as to receive dew condensation water generated on the surface of the heat exchanger (40). The drain pan (50) is formed so that the length in the vertical direction and the length in the horizontal direction are longer than the respective lengths of the heat exchanger (40) in plan view, so that the condensed water received is not leaked. Rises upward to form an outer peripheral wall. The drain pan (50) is installed on the bottom plate of the casing (20). The condensed water received by the drain pan (50) is discharged to the outside through a drain hose (not shown).

The electrical component box (60) is provided on the bottom plate at the end on the inlet (21) side in the lateral direction where the inlet (21) and the outlet (22) in the casing (20) face each other. That is, the electrical component box (60) is disposed upstream of the heat exchanger (40) that generates condensed water and the drain pan (50) that receives the condensed water in the air passage (P). The electrical component box (60) is disposed so as to be spaced from the outer peripheral wall of the drain pan (50), and is formed so that the height is lower than the height of the drain pan (50).

As described above, the cross-flow blower (30) has a fan rotor (impeller) (31), a housing (32), and a motor (not shown).

As shown in FIGS. 2 and 3, the fan rotor (31) includes ten disk-shaped partition plates (33), a number of airfoil blades (34), and two shaft portions (35). have. The ten partition plates (33) are provided at intervals so that the centers are aligned on the same straight line. The straight line connecting the centers is the central axis (rotating axis) (X) of the fan rotor (31). The two shaft portions (35) are formed so as to protrude outward from the center portions of the partition plates (33) at both ends provided at the ends of the ten partition plates (33). One shaft portion (35) of the two shaft portions (35) is rotatably supported by a side wall portion (38) described later of the housing (32), and a motor (not shown) is mounted on the other shaft portion (35). It is connected.

A large number of blades (34) are spanned around the outer periphery of a pair of opposing partition plates (33) between each of ten partition plates (33). A large number of blades (34) are arranged at intervals in the circumferential direction. Each blade (34) is curved so as to bulge to the opposite side of the rotational direction (the direction indicated by the arrow in FIG. 2) in the circumferential direction of the fan rotor (31), and the radial direction of the fan rotor (31). Are arranged in a posture inclined with respect to the radial direction so as to be located on the opposite side to the rotational direction in the circumferential direction.

In the present embodiment, the fan rotor (31) has a series formed by a pair of partition plates (33) facing each other and a plurality of blades (34) provided to connect the outer peripheral portions of each other. Nine are connected in the axial direction.

As shown in FIG. 2, the housing (32) has an air inlet (32a) and an air outlet (32b), and is formed in a bowl shape so that the fan rotor (31) is accommodated therein. Yes. The housing (32) includes a lower wall portion (36) provided below the fan rotor (31), an upper wall portion (37) provided above the fan rotor (31), and a shaft of the fan rotor (31). And two side wall portions (38) provided at both ends in the direction.

The lower wall portion (36) is formed longer in the axial direction of the fan rotor (31) below the center axis (X) of the fan rotor (31) and on the outlet (32b) side. The lower wall portion (36) includes a tongue portion (36a), a lower extension portion (first wall portion) (36b), and a seal portion (36c).

The tongue portion (36a) is opposed to the portion below the central axis (X) of the fan rotor (31) and close to the outlet (32b) side, and extends in the axial direction of the fan rotor (31). . The lower end of the tongue (36a) forms a suction port (32a).

The lower extension (36b) is formed to be continuous with the upper end of the tongue (36a) and bend in a substantially L shape from the upper end of the tongue (36a). The lower extension (36b) extends obliquely downward from the upper end of the tongue (36a) and extends to the air outlet (32b). That is, the lower end of the lower extension (36b) forms a blower outlet (32b).

The seal part (36c) extends substantially parallel to the tongue part (36a) from the lower surface of the lower extension part (36b). The lower end of the seal portion (36c) is in contact with the first heat exchange portion (41), and the air flowing into the casing (20) from the inlet (21) bypasses the heat exchanger (40) and crosses it. The gap between the suction port (32a) and the heat exchanger (40) is sealed so as not to be sucked into the flow type blower (30).

The upper wall (37) is formed longer in the axial direction of the fan rotor (31) above the central axis (X) of the fan rotor (31), and widely covers the upper outer peripheral surface. The upper wall portion (37) has a scroll wall portion (37a), an upper extension portion (second wall portion) (37b), and a seal portion (37c).

The scroll wall portion (37a) is a wall portion formed in a spiral shape except for one end portion, and in the axial direction of the fan rotor (31) above the central axis (X) of the fan rotor (31). It extends long and covers the outer peripheral surface of the fan rotor (31). In the scroll wall (37a), one end on the suction side (right side in FIG. 2) forms a suction port (32a), and the one end including the suction port (32a) increases toward the downstream side from the upstream side. It is formed so as to be close to (31). The scroll wall (37a) is located on the downstream side of the adjacent portion closest to the fan rotor (31) (the scroll start point (O): the scroll-shaped starting point where the distance from the fan rotor (31) increases). It forms so that it may leave | separate from a fan rotor (31), so that it goes to an exit (32b side). The scroll wall (37a) extends to a position directly above the upper end of the tongue (36a). Further, the proximity portion of the scroll wall portion (37a) and the proximity portion of the tongue portion (36a) are located on opposite sides of the central axis (X) of the fan rotor (31).

The upper extension (37b) is formed so as to be smoothly continuous with the scroll wall (37a) at a position directly above the upper end of the tongue (36a). The upper extension (37b) extends substantially parallel to the lower extension (36b) so as to face the lower extension (36b), and extends to the outlet (32b). That is, the lower end of the upper extension (37b) forms a blower outlet (32b).

The seal part (37c) extends obliquely upward from the upper surface of one end of the scroll wall part (37a) toward the top plate of the casing (20). The lower surface of the seal portion (37c) is in contact with the third heat exchange portion (43), and the air flowing into the casing (20) from the inlet (21) bypasses the heat exchanger (40) and crosses it. The gap between the suction port (32a) and the heat exchanger (40) is sealed so as not to be sucked into the flow type blower (30).

The two side wall portions (38) are provided at both end portions in the axial direction of the fan rotor (31). The two side wall portions (38) are formed such that the lower end portions are along the upper end surface of the heat exchanger (40), and the upper end portions are formed so as to correspond to the upper end portions of the scroll wall portion (37a). . The two side wall portions (38) are formed with insertion holes for the shaft portion (35) of the fan rotor (31), and the shaft portion (35) is inserted therethrough. The two side wall portions (38) are arranged between the air inlet (32a) and the air outlet (32) between the lower wall portion (36) and the upper wall portion (37) in the air passage (P) of the casing (20). The air flow path toward 32b) is formed. Further, the two side wall portions (38) are arranged between the fan rotor (31) between the lower extension portion (36b) of the lower wall portion (36) and the upper extension portion (37b) of the upper wall portion (37). The blowout flow path (F) which guides the blown-out blown air to the blowout outlet (32b) is formed.

The air flow path (F) of the housing (32) is enlarged by the scroll wall (37a) in which the distance from the outer peripheral circle of the fan rotor (31) gradually increases from the upstream to the downstream of the flow path. A flow path (70) is formed. And two protrusions (71, 72) projecting from the wall surface of the scroll wall (37a) toward the fan rotor 831) are formed on the downstream side of the winding start point (O) of the scroll wall (37a). Has been. These two protrusions (71, 72) are formed such that the protrusion closer to the winding start point (O) is the first protrusion (71), and the protrusion farther from the winding start point (O) is the second protrusion (72). That's it.

FIG. 4 is an enlarged view of the main part of FIG. In the present embodiment, the expansion area ratio τ of the expansion flow path (70) is τ ≦ 1.39. Further, the angle θ (°) representing the position of the protrusion (71, 72) relative to the winding start point (O) of the scroll wall portion (37a) with the central angle of the fan rotor (31), and the protrusion (71 , 72) satisfies the relationship represented by H (Hmax) ≦ 2.2τθ.

Here, the enlarged area ratio τ is represented by τ = (A1 + A2) / A1 in FIG. Further, A1 = π × r02.

In the above equation, r0 is the length of the line segment connecting the start point of the curve formed by the enlarged flow path of the casing and the rotation center of the cross flow fan, and A1 is R0 (from point (X) to point (O ) Is a 90 ° fan-shaped area partitioned by an arc C having a radius r0), and the angle θ between the center (X) of the fan rotor (31) and the line segment r0 is 90 °. The area obtained by subtracting A1 from the area surrounded by the point Q where the straight line L intersects the enlarged flow path curve (the area of the part enlarged with respect to A1).

In the present embodiment, the height H (mm) of the first protrusion (71) is H = 0.5. Specifically, the height H (mm) of the first protrusion (71) may be 0.5 ≦ H ≦ 0.7. The height H (mm) of the second protrusion (72) is H = 0.75.

-Driving operation-
In the indoor unit (10) of the air conditioner, the air flow in the air passage (P) from the inlet (21) to the outlet (22) in the casing (20) is activated by the activation of the cross flow blower (30). Is formed. Thereby, indoor air in the indoor space (S) flows into the casing (20) through the suction duct (2). The air flowing into the casing (20) from the inlet (21) exchanges heat with the refrigerant when passing through the heat exchanger (40), and the temperature is adjusted (heated or cooled). The temperature-adjusted air is sucked into the blower (30), flows through the air flow path formed in the housing (32), and is blown out from the outlet (32b). The air blown out from the blower (30) is supplied from the outlet (22) to the indoor space (S). The temperature of the indoor air in the indoor space (S) is adjusted by this air.

<Air flow in the blower>
In the cross-flow type blower (30), when the fan rotor (31) rotates, an air flow passing through the fan rotor (31) is formed in the housing (32) (see the white arrow in FIG. 2). This air flow becomes a substantially S-shaped flow due to the curved shape of the blades (34) of the fan rotor (31). The blown air blown out from the fan rotor (31) flows into the blowout flow path (F). The blown air flowing through the blowout flow path (F) reaches the blowout port (32b) and is blown out from the blowout port (32b).

<Contrast of Examples and Comparative Examples>
Next, with reference to FIGS. 5 to 8, an example in which the protrusions (71, 72) of this embodiment are formed and a comparative example in which protrusions (71 ′, 72 ′) having different dimensions of θ and H are formed. A comparison will be made.

As shown in FIG. 7, in the embodiment, the first protrusion (71) is formed with θ = 13.6, H = 0.5, and the second protrusion (72) is θ = 16.4, H =. It is formed at 0.75. In this case, Hmax is 0.7 and 0.8 for the first protrusion (71) and the second protrusion (72), respectively, and H <Hmax.

On the other hand, in the comparative example, the first protrusion (71 ′) is formed with θ = 21.2 and H = 1.15, and the second protrusion (72 ′) is θ = 26.4, H = 1.75. It is formed with. In this case, Hmax is 1.0 and 1.3, respectively, and H> Hmax, contrary to the embodiment.

Further, as shown in FIG. 8, during rated operation of the blower (30), in the example, the blowing sound and motor input are suppressed, and the maximum static pressure outside the machine is high (wind speed is slow), whereas in the comparative example, Since the protrusion is larger than the value of H (Hmax) ≦ 2.2τθ, the maximum static pressure outside the machine is low (the wind speed is high), the blowing sound is increased and the motor input is also increased. This is because, in the embodiment, the protrusions (71 ′, 72 ′) are large, the space between the fan rotor (34) is narrowed and the flow velocity becomes too fast, and the protrusions interfere with the wind flow and are disturbed. As a result, the noise increases and the surging suppression effect also decreases.

-Effects of the embodiment-
According to this embodiment, on the downstream side of the winding start point (O) of the scroll wall portion (37a) of the housing (32), a protrusion (from the wall surface of the scroll wall portion (37a) to the fan rotor (31) side ( 71, 72) In the crossflow type blower (30) in which the enlarged flow path (70) is formed, the enlarged area ratio τ is set to τ ≦ 1.39, and the position (angle) θ of the first protrusion (71) is Since the relationship with the protrusion height H is H ≦ 2.2τθ (specifically, H ≦ 0.7), the first protrusion (71) can be prevented from becoming too large. It is possible to prevent the protrusion (71) from interfering with the wind flow and generating turbulence.

Therefore, according to this embodiment, when the enlarged area ratio τ of the scroll wall portion (37a) is made smaller than 1.39, the distance between the fan rotor (31) and the scroll wall portion (37a) is too close. Increase in loss can be suppressed. As described above, according to the present embodiment, the duct (2) is connected to the inlet of the casing (20), and the cross-flow type blower is used in the indoor unit (10) of the air conditioner with high external static pressure. It suppresses the disturbance of the wind flow in the housing (32) of (30), suppresses the increase in noise and power consumption, and enhances the surging suppression effect.

In addition, according to the present embodiment, the height H (mm) of the protrusion is set to H ≧ 0.5 to suppress the protrusion from becoming too small, so that the protrusion can be easily formed on the scroll wall portion (37a). There is also an effect that can be formed.

<< Other Embodiments >>
About the said embodiment, it is good also as the following structures.

In the above-described embodiment, the example in which the crossflow blower (30) according to the present disclosure is applied to the indoor unit (10) installed in the ceiling has been described. However, the crossflow blower (30) according to the present disclosure is described. The configuration of the indoor unit (10) to which is applied is not limited to the above. It may be installed in an indoor space.

Moreover, in the said embodiment, although an indoor unit (10) is comprised so that the inflow port (21) and the outflow port (22) may be provided with the casing (20) formed in two side surfaces, The positions of the inlet (21) and the outlet (22) in the casing (20) are not limited to those described above. For example, the inlet (21) may be formed on the lower surface of the casing (20), and the outlet (22) may be formed on one side surface.

In the above embodiment, the configuration in which the suction duct (2) is connected only to the inlet (21) of the casing (20) has been described. However, the present disclosure describes the inlet (21) and the inlet of the casing (20) The present invention is also applicable to the indoor unit (10) in which a duct is connected to both the outlet (22) or only to the outlet (22).

Furthermore, the cross flow type blower (30) of the present disclosure is not intended for installation only on the high static pressure outdoor unit (10), and a large air volume that is not connected to a flow path resistance such as a duct. It may be provided in the outdoor unit.

As described above, the present disclosure is useful for a structure that suppresses surging of a crossflow type blower used for an indoor unit.

2 Suction duct 10 Indoor unit 20 Casing 21 Inlet 22 Outlet 30 Cross-flow blower 31 Fan rotor (impeller)
32 Housing

32a Suction port

32b Air outlet 34 Blade 37a Scroll wall 40 Heat exchanger 70 Enlarged flow channel 71 Winding start point 71 1st projection 72 2nd projection F Outflow channel H Projection height X Center axis (rotating shaft)
θ Center angle τ Expansion area ratio

Claims

A fan rotor (31) having a plurality of blades (34) and rotating about a central axis (X);
A housing (32) in which an air inlet (32a) and an air outlet (32b) are formed, and the fan rotor (31) is accommodated;
The housing (32) has a blowout flow path (F) from the fan rotor (31) to the blowout outlet (32b), and an outer peripheral circle of the fan rotor (31) is provided in the blowout flow path (F). And an enlarged flow path (70) composed of a scroll wall portion (37a) in which the distance between and the flow path gradually increases from the upstream to the downstream of the flow path,
At least one projection (71) projecting from the wall surface of the scroll wall (37a) toward the fan rotor (31) is formed on the downstream side of the winding start point (O) of the scroll wall (37a). A cross flow type blower,
The expansion area ratio τ of the expansion channel (70) is τ ≦ 1.39,
The angle θ when the position of the protrusion (71) with respect to the winding start point (O) of the scroll wall (37a) is expressed by the central angle of the fan rotor (31), and the protrusion height of the protrusion (71) The relationship with H
H ≦ 2.2τθ
A crossflow type blower characterized by satisfying the relationship represented by:
In claim 1,
The height H (mm) of the protrusion (71) closest to the winding start point (O) of the scroll wall (37a) is
H ≦ 0.7
A cross-flow type blower characterized by being.
In claim 1 or 2,
The height H (mm) of the protrusion (71) is H ≧ 0.5
A cross-flow type blower characterized by being.
An indoor unit of an air conditioner that adjusts the temperature of indoor air,
A casing (20) formed with an air inlet (21) and an outlet (22);
The cross flow type blower (30) according to claim 1, 2 or 3, wherein the cross flow type blower (30) is provided in the casing (20) to form an air flow flowing from the inlet (21) to the outlet (22).
A heat exchanger (40) provided on the upstream side of the air flow with respect to the cross-flow type blower (30) in the casing (20) to heat or cool the air. An indoor unit of an air conditioner.
In claim 4,
An indoor unit of an air conditioner, wherein a duct (2) is connected to one or both of an inlet (21) and an outlet (22) of the casing (20).