CN203926056U - Air conditioner - Google Patents

Abstract

Provided is an air conditioner capable of preventing indoor air from flowing back from the indoor to the inside of the air conditioner through an air outlet at both longitudinal direction end portions of the air outlet of an indoor unit of the air conditioner, and capable of suppressing an increase in energy loss, thereby realizing a reduction in power and noise. The length of the cross-flow fan (8) in the direction of the axis of rotation (AX) is longer than the length of the outlet (3) in the longitudinal direction, and the cross-flow fan (8) has fan extension sections (8a) that extend from both ends of the outlet (3) outward in the direction of the axis of rotation (AX). The indoor unit further comprises a collision wall (18) which is provided in the indoor unit main body and which collides with the outlet airflow blown out from the fan extension section (8 a). In addition, the facing surface (18a) is configured in such a manner that, in a cross section perpendicular to the rotation axis (17), the distance Mb between the rear guide side end (19b) of the facing surface (18a) and the fan outer peripheral portion (8b) is longer than the distance Ma between the stabilizer side end (19a) of the facing surface (18a) of the collision wall (18) and the fan outer peripheral portion (8 b).

Description

air conditioner

technical field

The utility model relates to an air conditioner, in particular to an indoor unit of a split type air conditioner with an indoor unit and an outdoor unit.

Background technique

The indoor unit of the air conditioner is installed in the air-conditioned room (indoors of houses, offices, etc.), and the indoor air sucked in from the suction port exchanges heat with the refrigerant circulating in the refrigeration cycle at the heat exchanger. In the heat operation, the indoor air is heated, and in the cooling operation, the indoor air is cooled, and the air is blown into the room again from the air outlet. For this purpose, a blower and a heat exchanger are housed inside the indoor unit main body.

There are various types of indoor units of air conditioners, but it is well known to use cross-flow fans (also called cross-flow fans, cross-flow fans) , cross-cut fan). With respect to the airflow from the suction port of the indoor unit of the air conditioner to the air outlet, a heat exchanger is arranged on the upstream side of the cross-flow fan, that is, a heat exchanger is arranged between the suction inlet and the cross-flow fan, and the air outlet is located at the through-flow fan. Downstream side of the flow fan. The length of the air outlet of the indoor unit in the longitudinal direction is approximately the same as the overall length of the cross-flow fan in the longitudinal direction (rotation axis direction), and a supporting cross-flow fan is arranged on the outside of both ends of the cross-flow fan in the longitudinal direction with a predetermined space. The support part of the rotating shaft of the fan, the drive motor, etc.

A cross-flow fan (hereinafter simply referred to as a fan) is constructed by connecting a plurality of impeller units in the direction of the axis of rotation. The above-mentioned impeller unit is formed in a concentric ring shape by inclining a plurality of blades whose cross section is curved in a substantially circular arc shape at a predetermined angle. It is fixed to an annular (ring-shaped) flat plate having an outer diameter and an inner diameter, that is, a support plate. In the direction of the rotation axis, a disc-shaped fan end plate with a rotating shaft supported by the bearing part of the main body of the indoor unit is fixed to the blade tip of the impeller unit at one end, and the impeller unit at the other end The body has a fan end plate with a bushing, which is different from the support plates of other parts, and has a bushing portion at the center to which the motor rotation shaft of the drive motor is mounted and fixed. Rotationally driven by the drive motor, the fan rotates around the center of the rotation shaft, that is, the rotation axis. The fins are inclined so that the front ends on the outer peripheral side are located forward in the direction of rotation.

Hereinafter, for the sake of description, the individual impellers connected in the direction of the rotation axis are referred to as a chain of fans. In addition, the impeller units located at both ends of the fan in the direction of the rotation axis are referred to as end units, respectively.

With the rotation of the fan, the indoor air is sucked into the main body of the indoor unit of the air conditioner from the suction port, becomes the conditioned air whose temperature is adjusted as described above when passing through the heat exchanger, and after crossing the fan, it flows from the fan in the direction of rotation. was blown out. After that, the conditioned air flows through the gradually expanding blowing air path formed between the stabilizer provided on the front side of the cross-flow fan and the rear guide part provided on the back side, and flows from the blowing port formed at the lower part of the indoor unit main body. was blown into the room.

When the cross-flow fan rotates, a plurality of vanes constituting the cross-flow fan pass through an upstream suction area and a downstream blow-out area of the cross-flow fan. In the structure of such a cross-flow fan, it is known that a vortex is generated near a stabilizer disposed on the front side with respect to the blowing direction of the air flow of the cross-flow fan and dividing the suction area and the blowing area.

When the inhaled indoor air passes through the heat exchanger, there is a ventilation resistance (pressure loss) in the air, and as mentioned above, when the fan rotates, a vortex is generated inside the fan. Therefore, the air pressure inside the indoor unit (hereinafter referred to as static pressure) Ps) becomes lower than the atmospheric pressure P0. On the other hand, the static pressure Ps adds the pressure obtained by converting the energy of the wind velocity into the energy of the pressure by accelerating the air flow by the fan, and the air flow with energy higher than the atmospheric pressure P0 is blown from the outlet. However, there are cases where the fan cannot supply enough energy to the airflow exceeding the atmospheric pressure P0, and although the fan supplies sufficient energy to the airflow, the airflow does not flow uniformly toward the outlet, and at the end of the air passage, due to the The friction of the side wall of the indoor unit causes the airflow to be turbulent, and the airflow cannot flow smoothly toward the air outlet. In these cases, the static pressure Ps near the air outlet in the indoor unit becomes lower than the atmospheric pressure P0, and the indoor air is sucked into the interior of the indoor unit through the air outlet due to the pressure difference between the two. This phenomenon is called suck back.

Such suck-back is likely to occur in the vicinity of both ends in the left-right direction and on the upper side in the vertical direction in the substantially rectangular air outlet extending in the left-right direction. The reason for this is as follows.

At both ends of the fan in the direction of the rotation axis, fan end plates (support plates) constituting the rotating body, that is, the impeller unit are provided, and on the outside of the fan end plate in the main body of the indoor unit, the fan end plate is opposed to the fan end plate. The side wall constituting the side surface of the air passage is arranged in such a manner. The distance between the fan end plate and the side wall of the main body of the indoor unit is, for example, about 5 mm, thereby preventing rotational friction due to contact between the two. However, the space formed between the fan end plate and the side wall facing the fan end plate is located outside the both ends of the fan in the direction of the rotation axis, and has a pressure lower than atmospheric pressure due to the pressure loss when the airflow passes through the heat exchanger. The pressure atmosphere of P0. Therefore, it is considered that suction is likely to occur in the vicinity of both ends of the air outlet due to the pressure difference from the atmospheric pressure P0 outside the indoor unit. Also, on the side of the air outlet connected to the stabilizer, the static pressure Ps is the lowest due to the above-mentioned vortex generated near the stabilizer, and the difference from the atmospheric pressure P0 is the largest. Therefore, compared with the side connected to the rear guide Suction is prone to occur.

If backdraft occurs, the air volume of the fan as a whole decreases due to the turbulence of the airflow due to the generation of backflow, resulting in a decrease in the performance of the fan or an increase in noise. In addition, if suck back occurs during cooling operation, the high-humidity indoor air that has been drawn into the indoor unit due to suck back will come into contact with the low-temperature wall surface inside the indoor unit to condense, and the dew condensation will scatter as water droplets. to indoors (this phenomenon is called dew scattering). In addition, an unsteady phenomenon in which blowing and suction are repeated may occur, and noise may increase.

In particular, if the ventilation resistance increases due to, for example, accumulation of dust at the suction port, it becomes difficult to supply sufficient energy to the air from the fan, and suckback tends to occur.

As a structure to realize the improvement of the flow rate performance at both ends of the rotation axis direction of the fan, which is a part where the above-mentioned back sucking is likely to occur, there is a method of gradually reducing the size of the fan in the air passage of the blowing part of the frame from the blowing part of the fan. An example in which the shape of the side wall is changed by the form of the ventilation passage in the direction of the rotation axis (for example, refer to Patent Document 1). In addition, there are cases in which backflow prevention plates are provided at both ends of the fan in the direction of the rotation axis to cover the blowout portion near the suction portion, and further formed into a chamfered shape to reduce ventilation resistance (for example, refer to Patent Document 2).

[Patent Document 1] Japanese Patent Laying-Open No. 8-121395 (columns 0013 to 0023, FIG. 1 )

[Patent Document 2] Japanese Unexamined Patent Publication No. 2001-201078 (columns 0030-0035, Figure 2)

In the case where the shape of the side wall is changed so as to gradually narrow the blowing air path in the direction of the rotation axis of the fan in the blowing air path of the blowing portion of the frame from the blowing portion of the fan, the reduction of the blowing air path prevents conspicuous stalling , and then prevent significant peeling from the side wall, forming a smooth flow site. However, in order to eliminate the rotational friction between the fan end and the side wall, the gap between the rotating fan and the side wall of the indoor unit main body of the air conditioner, which is the fixed part, cannot be made zero. Therefore, there is a problem that it is difficult to prevent indoor air from being sucked back into the interior of the indoor unit through the air outlet and the narrowed air outlet. In addition, no consideration is given to the part where the pressure is the lowest due to the vortex, that is, the side of the outlet connected to the stabilizer.

In addition, in a structure in which backflow prevention plates are provided at both ends of the fan in the direction of the rotation axis so as to cover the blowing portion near the suction portion, and further formed into a chamfered shape to reduce the ventilation resistance, the vortex becomes a low pressure. The stabilizer side is also provided with a chamfered portion. Therefore, there is a problem that room air is easily sucked into the interior of the indoor unit from the air outlet by widening the gap between the backflow prevention plate and the fan by the amount of the chamfer.

Utility model content

This utility model is completed in order to solve the above-mentioned problems, and its purpose is to obtain a blower that can prevent collapse at both ends of the length direction of the blower outlet, especially at the stabilizer side of the blower outlet where the pressure is the lowest due to eddy currents. The air conditioner which sucks, and can realize low power and low noise.

The air conditioner involved in the utility model has:

an indoor unit main body having a suction port through which air is sucked in and an outlet through which air is blown out, and the outlet is formed to be long in a left-right direction;

A cross-flow fan provided in the indoor unit main body so that the left-right direction of the indoor unit main body coincides with the rotation axis, and has left and right end portions extending outward from the longitudinal end portions of the air outlet. fan extension;

A stabilizer and a rear guide part, the stabilizer and the rear guide part are disposed opposite to each other with the cross-flow fan interposed therebetween, and form a blowing air passage for guiding indoor air blown out from the cross-flow fan toward the blowing outlet; and

a wall structure provided in the indoor unit main body on the outer sides of the left and right end portions of the air outlet respectively, and has a wall structure substantially along the fan extension so as to face the air flow blown out from the fan extension. A part of the outer peripheral part is provided on the opposite surface,

When the distance between the opposing surface and the outer peripheral portion of the fan extension in the radial direction of the fan extension in the cross-section perpendicular to the rotation axis of the fan extension is set When is the distance M,

The above-mentioned distance M, that is, the distance Ma at the point a on the side of the stabilizer with respect to the above-mentioned opposing surface is configured such that at least a part of the area of the above-mentioned opposing surface on the side of the rear guide part with respect to the above-mentioned point a is The above-mentioned distance M is longer than the above-mentioned distance Ma.

According to the present invention, the stagnation pressure can be made higher than the atmospheric pressure at both ends of the outlet in the longitudinal direction, especially on the stabilizer side of the outlet where the pressure becomes the lowest due to the vortex. Therefore, suck-back can be prevented, and increase in energy loss due to collision with the wall can be suppressed, and power reduction and noise reduction can be achieved.

Description of drawings

1 is an external perspective view showing an indoor unit of an air conditioner equipped with a cross-flow fan according to Embodiment 1 of the present invention.

FIG. 2 relates to Embodiment 1 and is a longitudinal sectional view taken along line Q-Q in FIG. 1 .

3 is a schematic diagram showing a cross-flow fan according to Embodiment 1, FIG. 3( a ) is a side view of the cross-flow fan, and FIG. 3( b ) is a U-U line of FIG. 3( a ). sectional view at.

FIG. 4 relates to Embodiment 1, and is an enlarged perspective view ((a) of FIG. 4 ) showing a fan in which five impeller units (connections) are fixed in the direction of the rotation axis, and an explanatory view showing a support plate ( (b) of Figure 4).

Fig. 5 is a perspective view of the indoor unit of the air conditioner according to Embodiment 1 viewed obliquely from below.

FIG. 6 is a perspective view showing a collision wall according to Embodiment 1. FIG.

FIG. 7 relates to Embodiment 1 and is a cross-sectional view taken along line W-W in FIG. 5 .

Fig. 8 relates to Embodiment 1 and is a schematic diagram showing a simplified internal structure of the indoor unit.

FIG. 9 relates to Embodiment 1, and is an explanatory diagram showing enlarged the vicinity of the collision wall at the right end portion in FIG. 8 viewed from the front.

Fig. 10 relates to Embodiment 1, and is an explanatory diagram showing the air flow in the indoor unit main body generated by the cross-flow fan.

11 is a graph showing the static pressure Ps with respect to the position in the depth direction AY when no collision wall is provided on the blowing side of the cross-flow fan according to Embodiment 1. FIG.

12 relates to Embodiment 1, and is a diagram showing the distance M between the opposing surface of the collision wall and the outer peripheral portion of the fan. FIG. 12(a) is an explanatory diagram showing a cross section perpendicular to the rotation axis. (b) is a graph in which the horizontal axis represents the position in the depth direction AY of the opposing surface of the collision wall, and the vertical axis represents the distance M between the opposing surface and the outer peripheral portion of the fan.

Fig. 13 relates to Embodiment 1 and is an explanatory diagram showing the function of the collision wall at the stabilizer-side end.

Fig. 14 relates to Embodiment 1, and is an explanatory diagram showing the function of the collision wall at the rear guide portion side end.

15 relates to Embodiment 1, and is a graph showing collision pressure Pv ( FIG. 15( a )) and stagnation pressure Pst ( FIG. 15( a )) at positions in the depth direction AY of the opposing surface.

FIG. 16 relates to another configuration example of Embodiment 1, and is a graph showing positions in the depth direction AY on the horizontal axis and stagnation pressure Pst on the vertical axis.

17 relates to another configuration example of Embodiment 1, and is a graph showing the position of the opposing surface of the collision wall in the depth direction AY on the horizontal axis and the distance M between the opposing surface and the outer peripheral portion of the fan on the vertical axis.

Fig. 18 is a perspective view showing a collision wall according to Embodiment 2 of the present invention.

Fig. 19 relates to Embodiment 2 and is a diagram showing the distance M between the opposing surface of the collision wall and the outer peripheral portion of the fan. Fig. 19(a) is a longitudinal sectional view perpendicular to the rotation axis, and Fig. 19(b) is A graph in which the horizontal axis represents the position in the depth direction AY, and the vertical axis represents the distance M between the facing surface and the outer peripheral portion of the fan.

20 is a graph showing the static pressure Ps with respect to the position in the depth direction AY when no collision wall is provided on the blowing side of the cross-flow fan according to Embodiment 2. FIG.

Fig. 21 relates to Embodiment 3 of the present invention, and is a cross-sectional view showing the vicinity of end portions when the collision wall is cut on a plane including the rotation axis.

22 relates to Embodiment 3 and is a diagram showing the distance M between the opposing surface of the collision wall in the direction of the rotation axis AX and the outer peripheral portion of the fan. A graph of the distance M between the mounting surface and the outer periphery of the fan.

Fig. 23 relates to Embodiment 3 and is an explanatory diagram illustrating an enlarged collision wall.

24 relates to another configuration example of Embodiment 3, and is a diagram showing the distance M between the opposing surface of the collision wall in the rotation axis direction AX and the outer peripheral portion of the fan, where the horizontal axis represents the position in the rotation axis direction AX, The vertical axis represents a graph of the distance M between the facing surface and the outer peripheral portion of the fan.

FIG. 25 relates to Embodiment 3, and is an explanatory diagram showing the shape of opposing surfaces of another configuration example.

Detailed ways

Implementation mode 1.

Hereinafter, Embodiment 1 of this invention is demonstrated based on drawing. 1 is an external perspective view showing an indoor unit 1 of an air conditioner equipped with a cross-flow fan 8 according to Embodiment 1, and FIG. 2 is a longitudinal sectional view taken along line Q-Q in FIG. 1 . The gas flow is indicated by blank arrows in FIG. 1 , and the gas flow is indicated by dotted arrows in FIG. 2 . The air conditioner actually uses the indoor unit and the outdoor unit to form a refrigeration cycle, but the utility model relates to the structure of the indoor unit, and the description of the outdoor unit is omitted. As shown in FIGS. 1 and 2 , an indoor unit (hereinafter referred to as an indoor unit) 1 of an air conditioner is formed in an elongated substantially rectangular parallelepiped shape extending in the left-right direction, and is installed on a wall surface of a room. The upper part 1a of the main body of the indoor unit 1 is provided with a suction grille 2 which becomes a suction port for sucking in indoor air, an electric dust collector 5 which collects dust contained in the sucked indoor air by static electricity, and similarly A mesh-shaped filter 6 for dust removal. In addition, the heat exchanger 7 having a structure in which a plurality of parallel aluminum fins 7a penetrate the pipe 7b is disposed on the front side and the upper side of the cross-flow fan 8 so as to surround the cross-flow fan 8, and the heat exchanger 7 is connected to the air from the suction side. The grill 2 performs heat exchange with the room air sucked in. In addition, the front surface of the main body of the indoor unit 1 is covered by the front panel 1b, and the lower part of the main body of the indoor unit 1 is provided with an air outlet 3 through which indoor air after heat exchange in the heat exchanger 7 is blown out into the room. The air outlet 3 is constituted by an opening extending elongatedly with the left-right direction of the main body of the indoor unit 1 as the longitudinal direction. That is, the air outlet 3 is provided so that the longitudinal direction of the air outlet 3 coincides with the left-right direction of the main body of the indoor unit 1 .

A cross-flow fan 8 as a blower is installed between the heat exchanger 7 and the air outlet 3 so that the left-right direction (longitudinal direction) of the main body of the indoor unit 1 is the direction in which the rotation axis extends (referred to as the direction of the rotation axis), and is Motor 16 (see FIG. 3 ) is rotationally driven to blow room air from suction grill 2 to blower outlet 3 . Inside the main body of the indoor unit 1 are a stabilizer 9 and a rear guide 10 that separate the suction area E1 and the blowing area E2 from the cross-flow fan 8 . The stabilizer 9 constitutes the front side of the outlet air passage 11 that guides indoor air blown out from the cross-flow fan 8 to the outlet 3 , and the rear guide 10 is formed in a spiral shape, for example, and constitutes the rear side of the outlet air passage 11 . The rear guide part 10 is formed as a gentler curved surface than the stabilizer 9 on the front side of the blowing air passage 11 , and the blowing air passage 11 is formed in a shape gradually widening toward the air outlet 3 . Up and down wind direction guide pieces 4a and left and right wind direction guide pieces 4b are rotatably installed on the outlet 3, and the air blowing direction toward the room is changed by the up and down wind direction guide pieces 4a and left and right wind direction guide pieces 4b. In the figure, O represents the rotation center of the cross-flow fan 8 , E1 represents the suction area of the cross-flow fan 8 , and E2 represents the blowing area on the opposite side of the suction area E1 with respect to the rotation center O. The suction area E1 and the blowing area E2 of the cross-flow fan 8 are separated by the tongue portion 9 a of the stabilizer 9 and the upstream end portion 10 a of the airflow of the rear guide portion 10 . In addition, RO represents the rotation direction of the cross-flow fan 8, and AY represents the depth direction of the indoor unit 1. In the depth direction AY of the main body of the indoor unit 1, the side where the air outlet 3 is located is referred to as the front side, and the rear guide portion is referred to as the front side. The side on which 10 is located is called the rear side.

When the air conditioner is operated, the cross-flow fan 8 rotates in the RO direction, and indoor air is sucked in from the suction grill 2 provided on the upper part 1a of the main body of the indoor unit 1 . Air from which dust and the like have been removed by the filter 6 and the electrostatic precipitator 5 passes between the fins 7 a of the heat exchanger 7 . Here, the refrigerant circulating in the refrigerating cycle flows through the pipe 7b, and the air exchanges heat with the refrigerant to be heated in the heating operation and cooled in the cooling operation to be conditioned. Thereafter, the air is sucked into the cross-flow fan 8 from the suction area E1 , passes through the inside of the cross-flow fan 8 , and is blown out from the air outlet 3 into the room through the blow-out area E2 .

FIG. 3 is a schematic diagram showing cross-flow fan 8 according to Embodiment 1, FIG. 3( a ) is a side view of the cross-flow fan, and FIG. 3( b ) is U-U of FIG. 3( a ). Sectional view at the line. The lower half of (b) of FIG. 3 shows a state where a plurality of fins on the facing side are seen, and the upper half shows one fin 13 . 4( a ) is an enlarged perspective view showing a cross-flow fan 8 in which five impeller units 14 according to Embodiment 1 are fixed in the rotation axis direction AX, and FIG. 4( b ) is a perspective view showing An explanatory diagram of the support plate 12 is shown. In FIG. 4 , the motor 16 and the motor shaft 16 a are omitted, and the part of the impeller is shown as the cross-flow fan 8 . The number of individual impellers 14 constituting the cross-flow fan 8 and the number of vanes 13 constituting one impeller individual 14 may be arbitrary.

As shown in FIGS. 3 and 4 , the cross-flow fan 8 has a plurality of, for example, five impeller units 14 in the rotation axis direction AX (longitudinal direction). An annular support plate 12 is disposed at one end of the impeller unit body 14 , and a plurality of fins 13 extending in the rotation axis direction AX are disposed along the outer periphery of the support plate 12 . For example, a plurality of impeller units 14 formed of thermoplastic resin such as AS resin and ABS resin are provided in the rotation axis direction AX, and the side ends of the blades 13 are fixed to the supporting plates of the adjacently arranged impeller units 14 by ultrasonic welding or the like. 12. Connect the impeller units 14 to each other. Furthermore, the disc-shaped fan end plate 12b is fixed to the vane 13 of the impeller unit 14 connected to the endmost portion, thereby constituting the impeller of the cross-flow fan 8 shown in FIG. 4( a ). A fan shaft 15a is provided at the center of a support plate 12a (hereinafter referred to as a fan end plate) at one end in the rotation axis direction AX, and a fan bushing 15b is provided at the center of the fan end plate 12b at the other end. Furthermore, the fan boss 15b and the motor shaft 16a of the motor 16 are fixed with screws or the like. That is, the cross-flow fan 8 has fan end plates 12a and 12b at both ends in the rotation axis direction AX formed in a disk shape, and a fan shaft 15a and a fan bushing 15b are formed at the center portion where the rotation axis 17 is located. The central portion of the support plate 12 other than the support plates at both ends, where the rotation axis 17 as the rotation center is located, is formed in a ring shape of space, having an inner diameter K1 and an outer diameter K2 as shown in FIG. 4( b ). Here, in Fig. 3 (b) and Fig. 4 (b), the dotted line connects the motor shaft 16a and the fan shaft 15a, and is a virtual rotation axis representing the rotation center O, which is referred to as the rotation axis 17 here, and the rotation The direction of extension of the axis 17 is the axis of rotation direction AX. In addition, one single impeller is called a link 14, and the links 14 located at both ends of the cross-flow fan 8 in the rotation axis direction AX are called end links 14a, respectively.

Fig. 5 is a perspective view of the main body of the indoor unit 1 of the air conditioner according to the embodiment viewed obliquely from below. In this figure, for easy understanding of the description, the vertical air direction guide piece 4 a and the left and right air direction guide piece 4 b are removed, and a part of the cross-flow fan 8 can be seen through the air outlet 3 . The length L2 of the rotation axis direction AX of the cross-flow fan 8 is longer than the length L1 of the longitudinal direction of the air outlet 3 (L2>L1). The air outlet 3 opens so that its longitudinal direction coincides with the left-right direction of the main body of the indoor unit 1 . Furthermore, a part of the end portion 14a of the cross-flow fan 8 is extended from both ends in the longitudinal direction of the air outlet 3 in the direction in which the rotation axis 17 extends, and the extended portion is called a fan extension portion 8a. That is, the fan extension portion 8a is a part of each end portion 14a located at both ends of the cross-flow fan 8, and is a portion that protrudes from the left and right ends of the air outlet 3 toward the outside in the longitudinal direction and does not face the air outlet 3. . In addition, at positions separated by a predetermined distance from the fan end plates 12a, 12b of the cross-flow fan 8 in the rotation axis direction AX, side walls are provided so as to extend substantially parallel to the outwardly facing surfaces of the fan end plates 12a, 12b. 30. The side walls 30 constitute the left and right side surfaces of the air passage from the suction grille 2 to the air outlet 3 inside the indoor unit 1 .

In the part of the rotation axis direction AX of the cross-flow fan 8 except the fan extension parts 8a at both ends, that is, the central part of the rotation axis direction AX of the cross-flow fan 8, as shown in FIG. The side is constituted by the rear guide portion 10 until the air outlet 3, and a swirl shape is formed from the upstream side end portion 10a of the rear guide portion 10 to the air outlet 3, and the distance from the outer periphery of the impeller of the cross-flow fan 8 to the rear guide portion 10 is formed. A structure that gradually becomes longer as it approaches the outlet 3. The front side of the outlet air passage 11 is constituted by a stabilizer 9 . By the rotation of the cross-flow fan 8, the airflow accelerated toward the front side of the cross-flow fan 8 and blown out flows in a curved line in the blowing air passage 11 as indicated by a dotted arrow, and is blown out toward the front side from the outlet 3. .

Here, the collision wall 18 facing the fan extension part 8a is provided in both ends inside the main body of the indoor unit 1. As shown in FIG. The airflow blown out from the fan extension 8 a collides with the collision wall 18 . 6 is a perspective view showing the respective collision walls 18 provided at both ends in the left-right direction inside the main body of the indoor unit 1 according to Embodiment 1. The collision wall 18 at the end. The collision wall 18 disposed at the left end portion of the air outlet 3 viewed from the front is also formed in the same shape, and the collision wall 18 on the right side may be reversed left and right. 7 is a cross-sectional view along line WW in FIG. 5 , showing a longitudinal section perpendicular to the rotation axis 17 of the indoor unit 1 of a portion including the collision wall 18 in the vicinity of the fan end plate 12b. In FIG. 7 , in the cross section at the fan extension 8a, the rear guide 10, the stabilizer 9, and the collision wall 18 form walls for the airflow blown from the fan extension 8a, and are indicated by oblique lines.

As shown in Figure 6, at both ends of the interior of the main body of the indoor unit 1, the opposite surface 18a as one side of the collision wall 18 is the surface facing the fan extension 8a, and the airflow blown from the fan extension 8a is opposite to this. Faces 18a collide. BIGNQIE, as shown in the cross section of FIG. 7, the back side of the blowing air duct 11 facing the fan extension 8a is constituted by the upstream side of the rear guide part 10 halfway, but from the midway rear guide part side end 19b It is constituted by the opposing surface 18 a of the collision wall 18 , and is continuous with the stabilizer 9 without being connected to an opening such as the outlet 3 . In the opposing surface 18a of the collision wall 18, one end connected to the stabilizer 9 is set as a stabilizer-side end 19a, and the other end connected to the rear guide 10 is set as a rear guide-side end. 19b. That is, the collision wall 18 surrounds the outer periphery of the fan extension 8 a so as to connect the stabilizer-side end 19 a disposed on the stabilizer 9 side and the rear guide-side end 19 b disposed on the rear guide 10 side.

Here, in a cross section perpendicular to the rotation axis 17, when the cross-flow fan 8 rotates around the rotation center O, the locus drawn by the vane portion located on the outermost peripheral side with respect to the rotation center O (with the rotation center O as The position of the circle at the center) is set as the outer peripheral part, and here it is set as the fan outer peripheral part 8b. Furthermore, in the cross section shown in FIG. 7 , each position where a straight line connecting each position in the depth direction AY of the opposing surface 18a and the rotation center O of the cross-flow fan 8 intersects the fan outer peripheral portion 8b, The length of a straight line to each position of the facing surface 18a is set as the distance M. That is, the distance M is the distance between the fan outer peripheral portion 8b and the facing surface 18a in the radial direction of the cross-flow fan 8 . For example, when the distance in the radial direction (the distance between the position 20a and the position 19a) between the fan outer peripheral portion 8b at the stabilizer side end portion 19a and the opposing surface 18a is set to Ma, the rear guide portion When the distance in the radial direction (the distance between the position 20b and the position 19b) between the fan outer peripheral portion 8b at the side end portion 19b and the opposing surface 18a is set to Mb, in this embodiment, it is characterized in that The distance Mb is longer than the distance Ma (Ma<Mb).

In addition, a collision region where the air flow blown out from the fan extension 8 a collides with the collision wall 18 is represented by a region E3 . That is, a region where the airflow blown from the fan extension 8a collides with the collision wall 18 in the blowout region E2 (see FIG. 2 ) representing the region where the airflow is blown from the cross-flow fan 8 is set as the collision region E3. This collision area E3 becomes a part of the blowing area E2.

In addition, since the rear guide part side end part 19b of the collision wall 18 is smoothly connected with the rear guide part 10, the height which the collision wall 18 rises from the rear guide part 10 at the most end part is zero actually. Here, for easy understanding of the description, the rear guide portion side end portion 19b is located near the end portion where the collision wall 18 is connected to the rear guide portion 10, and is located on the opposing surface 18a from the adjacent end when viewed along the rotation axis direction AX. The position where the surface of the rear guide part 10 protrudes with a slight step difference.

Also, the distance M is the same at any position of the collision wall 18 in the rotation axis direction AX. That is, the opposing surface 18 a of the collision wall 18 is configured to be parallel to the rotation axis 17 in the rotation axis direction AX.

8 is a schematic diagram showing a simplified internal structure of the indoor unit 1 according to Embodiment 1, and schematically shows the suction grill 2, the heat exchanger 7, the cross-flow fan 8, and the air outlet 3 according to the airflow direction (blank arrows). Relationship. In the rotation axis direction AX, the end parts 14a arranged at both ends of the cross-flow fan 8 respectively have fan extensions 8a, and the fan extensions 8a face the opposing surface 18a of the collision wall 18 in the collision area E3. On the other hand, in the rotational axis direction AX of the cross-flow fan 8 , a portion other than the fan extension 8 a , that is, a central portion of the cross-flow fan 8 in the rotational axis direction AX faces the air outlet 3 .

The collision walls 18 provided at both left and right end portions are integrally formed with, for example, the left and right side walls 30 , so they are connected to the side walls 30 and extend inwardly in the left and right direction with the side walls 30 as one end. In addition, due to the relationship between the structure, there are cases where the side wall 30 is formed with unevenness in the direction of the axis of rotation AX. Therefore, the length Na of the direction of the axis of rotation AX of the facing surface 18a is substantially parallel to the axis of rotation 17 and faces the fan extension 8a. The length of the opposing surface 18a from the fan end plates 12a, 12b. Here, the positions of the two fan end plates 12a, 12b in the rotation axis direction AX are the positions of the outward surfaces of the fan end plates 12a, 12b facing the outside of the main body of the indoor unit 1 .

An example of each length of the cross-flow fan 8 used in this embodiment is shown below.

The outer diameter K2 (see FIG. 4 ) of the ring-shaped support plate 12 fixed to the blade 13 at the end of the impeller unit 14 is set to Φ110 mm, and the inner diameter K1 (see FIG. 4 ) is set to Φ60 mm. For example 35 fins 13 are fixed on the circumference of the support plate 12 . In addition, in the rotation axis direction AX, the longitudinal length L1 of the air outlet 3 = 610 mm, and the total length L2 of the cross-flow fan 8 in the rotation axis direction AX = 640 mm. The length Na of the rotation axis direction AX of the opposing surface 18a of the collision wall 18 was 15 mm. In addition, a region denoted by S in FIG. 8 represents a space formed between the fan end plates 12 a , 12 b at both ends of the cross-flow fan 8 and the side wall 30 . The length of the space S in the rotation axis direction AX is, for example, 10 mm. In addition, the length of the rotation axis direction AX of the end link 14a is 25 mm at the end link 14a at one end (left side in FIG. 8 ), and 70 mm at the end link 14a at the other end (right side in FIG. 8 ). ), and the length of the rotation axis direction AX of the other chains 14 other than the two end chains 14a is set to approximately 80mm. And, at the end portion 19a on the stabilizer side and the increase start position 19c, the distance Ma=Mc=5mm between the fan outer peripheral portion 8b and the facing surface 18a, and at the rear guide portion side end portion 19b, the distance between the fan outer peripheral portion 8b and the facing surface 18a The distance Mb between the opposing surfaces 18 a is 25 mm.

FIG. 9 is an explanatory diagram showing enlarged the vicinity of the collision wall 18 at the right end portion of FIG. 8 viewed from the front. The airflow inside the indoor unit 1 and the actions of the collision walls 18 at both ends in the longitudinal direction of the indoor unit 1 will be described based on FIGS. 8 and 9 .

The air conditioner is operated, and the cross-flow fan 8 is rotated in the RO direction by the motor 16 . As the cross-flow fan 8 rotates, the indoor air sucked in from the suction grill 2 is heat-exchanged in the heat exchanger 7 . Furthermore, the heat-exchanged room air becomes the airflow A, blown by the cross-flow fan 8, and blown out from the outlet 3 into the room through the blowing area E2. Here, the indoor air sucked in from the suction grill 2 generates frictional resistance (pressure loss) when passing through the heat exchanger 7, and therefore, as shown in FIG. Becomes Pe, becomes lower than atmospheric pressure P0. The static pressure Ps representing the air pressure inside the indoor unit 1 takes on various values at various places in the indoor unit 1 due to the influence of ventilation resistance. The space S near the outward surface of the end plate 12b is a space continuous with the suction area E1, and has the same pressure atmosphere, and therefore exhibits the same static pressure Ps as the suction area E1, which is Pe (<atmospheric pressure P0). And, if focusing on the blowing side of the fan extension part 8a, the airflow Aa blown toward the place facing the collision wall 18 collides with the opposite surface 18a of the collision wall 18, and the energy of the wind speed is converted into pressure energy, adding Static pressure Ps in the collision area E3, thereby generating stagnation pressure Pst in the collision area E3. In this collision area E3, when the static pressure is called Ps and the pressure converted from the energy of the wind speed is called collision pressure Pv, stagnation pressure Pst=static pressure Ps+collision pressure Pv. As the rotation of the cross-flow fan 8 becomes faster, the wind velocity Va of the airflow Aa becomes larger, which is converted into greater pressure energy, the collision pressure Pv becomes higher, and the stagnation pressure Pst becomes higher. If the wind speed Va is equal to or greater than a predetermined value, the value of the stagnation pressure Pst becomes higher than the atmospheric pressure P0. The wind speed Va at which the stagnation pressure Pst becomes higher than the atmospheric pressure P0 differs depending on the pressure loss of a mounted heat exchanger or the like.

The space S located outside the both ends of the cross-flow fan 8 is an area where the air blowing by the cross-flow fan 8 does not function. The static pressure Ps of the space S is Pe, which is lower than the atmospheric pressure P0, and there is almost no pressure increase due to blowing air, so sucking back caused by indoor air flowing into the space S through the outlet 3 is likely to occur. On the other hand, in the collision area E3 between the space S and the blowing air passage 11 communicating with the blowing port 3, a wall of a stagnation pressure Pst higher than the atmospheric pressure P0 is formed, whereby the indoor air can be cut off from the indoor unit 1. The suction G that flows in from the outside of the machine through the outlet 3.

However, the collision flow toward the collision wall 18 does not become a blowing airflow toward the outside of the indoor unit 1 , and therefore, it is a loss if the stagnation pressure Pst becomes too much higher than the atmospheric pressure P0 for the purpose of blowing air. That is, providing the collision wall 18 forming the same collision pressure Pv from the stabilizer-side end portion 19a to the rear guide portion-side end portion 19b in the depth direction AY and causing the blown airflow to collide with the collision wall 18 increases the ventilation resistance. . Increasing the ventilation resistance increases the load on the cross-flow fan 8, leading to energy loss and increased noise. In the indoor unit 1 shown in this embodiment, when the stagnation pressure Pst higher than the atmospheric pressure P0 is formed on the entire surface of the opposing surface 18a of the collision wall 18, the balance between suckback prevention and air blowing is considered. Specifically, by configuring the collision wall 18 so that the collision pressure Pvb near the rear guide portion side end 19b is lower than the collision pressure Pva near the stabilizer side end 19a, the energy loss due to the collision can be minimized. Case.

Next, the static pressure Ps inside the indoor unit 1 in the depth direction AY will be described. FIG. 10 is an explanatory diagram showing the airflow in the main body of the indoor unit 1 by the cross-flow fan 8 according to the first embodiment. Inside the cross-flow fan 8 and in the vicinity of the stabilizer 9 , a vortex (circulation vortex) F1 accompanying the passage of the air flow is generated. The area E4 around the vortex F1 has the lowest static pressure Ps in the indoor unit 1 and exhibits the lowest value Pmin, and the difference from the atmospheric pressure P0 is also the largest. Therefore, in the outlet 3, the stabilizer side (Ga) to which the airflow J1 passing around the vortex F1 is blown out is quieter than the rear guide part side (Gb) to which the airflow J2 passing through the part separated from the vortex F1 is blown out. The pressure Ps is low and the difference from the atmospheric pressure P0 is large.

11 is a graph showing the static pressure Ps when no collision wall 18 is provided on the blowing side of the cross-flow fan 8 at both ends in the left-right direction of the indoor unit 1 according to Embodiment 1, and the horizontal axis indicates the static pressure Ps. The position in the depth direction AY represents the static pressure Ps on the vertical axis. Pe represents the static pressure Ps of the suction area E1 which is the suction side of the cross-flow fan 8 inside the indoor unit 1 . In addition, Ha indicates that the airflow J1 passes through the cross-flow fan 8 in the vicinity of the stabilizer tongue 9a of the stabilizer 9. 8 resulting in a reduction in pressure. In addition, in the depth direction AY, Psa represents the static pressure Ps near the stabilizer-side end portion 19a, and Psb represents the static pressure Ps near the rear guide portion-side end portion 19b.

Due to the ventilation resistance caused by the indoor air passing through the heat exchanger 7, the pressure in the indoor unit 1 is lower than the atmospheric pressure P0, and the static pressure Ps becomes Pe (lower than the atmospheric pressure P0) in the suction area E1 of the cross-flow fan 8 . Furthermore, due to the vortex F1 generated inside the cross-flow fan 8 when the indoor air flows across the cross-flow fan 8, the pressure drop Ha at the stabilizer-side end 19a is large, and the static pressure Ps at the stabilizer-side end 19a Psa shows the lowest value Pmin in the indoor unit 1 . On the other hand, the pressure drop Hb at the rear guide side end 19b is smaller than the pressure drop Ha because the air flow passes through the part where the vortex F1 leaves, and the static pressure Ps at the rear guide side end 19b becomes lower than Psa. High Psb. Therefore, in order to form the stagnation pressure Pst equal to or higher than the atmospheric pressure P0 in the collision area E3, the collision pressure Pv higher in the stabilizer side end portion 19a than the rear guide portion side end portion 19b is required. In other words, the stagnation pressure Pst higher than the atmospheric pressure P0 can be formed at the rear guide portion side end portion 19 b with a collision pressure Pv lower than that of the stabilizer side end portion 19 a. Therefore, at the end 19b on the side of the rear guide part, the airflow capable of obtaining at least the required collision pressure Pv collides with the opposing surface 18a, and the airflow other than the airflow required for the collision pressure Pv is sent to the blower port 3. wind.

FIG. 12 is a diagram showing the distance M between the facing surface 18a of the collision wall 18 and the fan outer peripheral portion 8b according to the first embodiment. 12( a ) is an explanatory diagram showing a cross section perpendicular to the rotation axis 17 (refer to FIG. 9 ) at both ends in the longitudinal direction of the indoor unit 1 , and FIG. 12( b ) shows the collision wall 18 on the horizontal axis. The position in the depth direction AY of , and the distance M between the opposing surface 18a of the collision wall 18 and the fan outer peripheral portion 8b are shown on the vertical axis. At the rear guide portion side end 19b of the collision wall 18, the distance Mb in the radial direction between the facing surface 18a and the fan outer peripheral portion 8b, which faces the cross-flow fan 8, is formed to be larger than that at the stabilizer side end 19a. The distance is Ma long. In this embodiment, as shown by the straight line ln1 in FIG. The distance (Ma) is the shortest, the distance (Mb) at the rear guide side end 19b is the longest, and the distance M from the stabilizer side end 19a to the increase start position 19c is set as Ma=Mc. Furthermore, the region from the increase start position 19c to the rear guide side end 19b on the facing surface 18a is configured such that the distance M increases smoothly from the increase start position 19c to the rear guide side end 19b.

Here, the start of increase means the start of increase of the distance M in the radial direction between the facing surface 18a and the fan outer peripheral portion 8b. The increase start position 19c is provided midway between the stabilizer-side end 19a and the rear guide-side end 19b on the facing surface 18a, and is a place where the distance M between the facing surface 18a and the fan outer peripheral portion 8b is increased. Starting position on the 9 side of the stabilizer. For example, in the depth direction AY of the opposing surface 18a, the increase start position 19c is set at a position about 10% away from the entire length from the stabilizer side end 19a toward the rear guide side end 19b.

The function of the collision wall 18 at the stabilizer-side end portion 19 a is the same as the general description of the function of the collision wall 18 in FIG. 9 . FIG. 13 is an explanatory diagram illustrating the function of the collision wall 18 at the stabilizer-side end portion 19 a according to the first embodiment. As described above, at both end portions of the indoor unit 1 in the longitudinal direction, at the stabilizer-side end portion 19a located on the front side in the depth direction AY, the static pressure Ps appears in the room due to the vortex F1 generated in the cross-flow fan 8 . Machine 1 has the lowest value Pmin in the machine. Furthermore, the airflow blown out from the fan extension part 8a collides with the opposing surface 18a of the collision wall 18 separated by the distance Ma from the fan outer peripheral part 8b. By colliding with the opposing surface 18a, the collision pressure Pva converted from the energy of the wind speed is added, and stagnation pressure Psta=Psa (exhibits the lowest value Pmin)+Pva is formed in the collision area E3. At this time, the distance Ma is the same as the distance between the tongue portion 9a of the stabilizer 9 disposed closest to the cross-flow fan 8 and the fan outer peripheral portion 8b, and is relatively short. Therefore, the airflow blown from the fan outer peripheral portion 8b flows toward the opposing surface 18a as it is, and by colliding with the opposing surface 18a, the collision pressure Pva is added to form stagnation pressure Psta in the collision area E3 of the stabilizer side end portion 19a. At this time, almost all of the airflow blown out from the fan outer peripheral portion 8b collides with the facing surface 18a to form stagnation pressure Psta, therefore, a sufficiently higher stagnation pressure than the atmospheric pressure P0 is formed to the extent that suckback does not occur. Psta.

Next, the action of the collision wall 18 at the rear guide portion side end portion 19b will be described based on FIG. 14 . FIG. 14 is an explanatory diagram showing the action of the collision wall 18 at the end portion 19b on the rear guide portion side according to Embodiment 1, and shows the airflow not just when the cross-flow fan 8 starts operating, but after the operation. Airflow at steady state after a moment. Since the distance Mb is longer than the distance Ma at the stabilizer-side end portion 19a, the airflow blown from the fan extension portion 8a tends to spread around before reaching the opposing surface 18a of the cross-flow fan 8 . When looking at the expansion of the rotation axis direction AX, when the cross-flow fan 8 just starts to operate, the end of the rotation axis direction AX of the indoor unit 1, that is, the side wall 30 side (right side when facing the figure), and the indoor The central side of the machine 1, that is, the side of the blowing air passage 11 communicating with the blowing outlet 3 (the left side when facing the figure) expands. The air flow toward the side wall 30 collides with the side wall 30 to add pressure, and stagnation pressure is generated in the side wall 30 . This creates a pressure gradient that is higher on the side wall 30 and lower on the side of the blowing air passage 11 . As a result, in the steady state, the air flow tending to expand toward the blowing air passage 11 side due to the generated pressure gradient increases compared to the time immediately after the operation starts. That is, as shown in FIG. 14 , the airflow blown from the fan outer peripheral portion 8 b facing the opposing surface 18 a flows toward the opposing surface 18 a as it is, and flows toward the outlet air passage 11 on the central side of the indoor unit 1 . airflow.

The air flow flowing toward the opposing surface 18a as it is collides with the opposing surface 18a, and the collision pressure Pvb is added to the static pressure Psb of the opposing surface 18a, and stagnation pressure Pstb=Psb is formed in the collision area E3 of the rear guide side end 19b. +Pvb.

FIG. 15 is a graph ((a) of FIG. 15 ) showing the collision pressure Pv at the position in the depth direction AY of the facing surface 18 a according to Embodiment 1 and the stagnation pressure Pst at the position in the depth direction AY. Graph ((b) of Fig. 15). When the collision pressure Pva at the stabilizer side end 19a is compared with the collision pressure Pvb at the rear guide side end 19b, the ratio of the air flow colliding with the collision wall 18 at the rear guide side end 19b is greater than that of the stabilizer. There are few side end portions 19a, and as shown in (a) of FIG. 15 , the collision pressure Pv becomes Pva>Pvb. Further, the collision pressure Pv has substantially the same value as Pva from the stabilizer side end 19a to the increase start position 19c, and gradually decreases relative to Pva from the increase start position 19c to the rear guide side end 19b. In (b) of FIG. 15 , the static pressure Ps explained in FIG. 11 is shown by adding the collision pressure Pva shown in (a) of FIG. At the end 19b is the stagnation pressure Pst after the collision pressure Pvb.

Here, the difference (Pva−Pvb) of the collision pressure Pv between the stabilizer-side end portion 19a and the rear guide portion-side end portion 19b in FIG. The reduced difference (Ha-Hb) is the same degree. That is, if the distance M is adjusted to obtain such a collision pressure Pv, the difference in static pressure Ps (Psa-Psb) is canceled, and the stagnation pressure Pst formed in the collision area E3 of the opposing surface 18a is shown in (b) of FIG. ) is higher than the atmospheric pressure P0 throughout the entire depth direction AY from the stabilizer-side end portion 19a to the rear guide portion-side end portion 19b, and is almost constant.

On the other hand, the airflow flowing toward the outlet air passage 11 on the central side of the indoor unit 1 is blown out to the outside of the indoor unit 1 through the outlet air passage 11 and the air outlet 3 . The air flow flowing in the blowing air passage 11 acts on the blowing air.

In this way, by configuring the distance M between the fan outer peripheral portion 8b and the opposing surface 18a of the collision wall 18 at the rear guide portion side end portion 19b to be longer than that at the stabilizer side end portion 19a (Mb>Ma), it is possible to The region E3 forms a stagnation pressure Pst capable of preventing suck back and ensuring a blown air flow. Therefore, compared with the configuration in which the distance in the radial direction between the fan outer peripheral portion 8b and the opposing surface 18a is the same from the stabilizer-side end portion 19a to the rear guide portion-side end portion 19b, the impact caused by the collision with the wall 18 can be reduced. The increase of the ventilation resistance can be suppressed to be small, and the power consumption required to generate the required air volume can be suppressed to be small. In addition, it is also possible to reduce an increase in noise due to a collision.

In addition, the number of rotations of the cross-flow fan 8 mounted in the indoor unit 1 of the air conditioner is set according to an operation mode such as weak cooling or forced cooling, for example. As a method of dimensioning the collision wall 18, a stagnation pressure Psta higher than the atmospheric pressure P0 can be obtained at the stabilizer side end 19a at the wind speed when the cross-flow fan 8 rotates at the lowest rotational speed in the operation mode, The radial distance Ma between the collision wall 18 at the stabilizer-side end portion 19 a and the outer peripheral portion 8 b of the cross-flow fan 8 , and the length Na in the rotation axis direction AX are determined. For example, the distance Ma is set to the extent of the distance between the fan outer peripheral portion 8b and the stabilizer 9 (here, 5 mm), and a stagnation pressure Psta higher than the atmospheric pressure P0 can be obtained through experiments or simulations. Na (set to 15mm here. In addition, by imagining the change of the static pressure Ps in the depth direction AY near the facing surface 18a in the indoor unit 1, that is, each position in the depth direction AY of the facing surface 18a The static pressure Ps of the static pressure Ps can be set to form the necessary minimum collision pressure Pv for forming a stagnation pressure Pst higher than the atmospheric pressure P0 at each position. Furthermore, as long as the set collision pressure Pv can be obtained and then guided The distance Mb between the collision wall 18 at the side end 19b of the cross-flow fan 8 and the outer peripheral portion 8b of the cross-flow fan 8, and the distance Mb at each position in the depth direction AY from the stabilizer side end 19a to the rear guide side end 19b. The distance M is enough. In general, the expansion of the jet flow width of the jet fluid (in the above, the expansion of the rotation axis direction AX) and the distance in the direction of fluid advancement (here, from the fan outer peripheral portion 8b to the collision wall 18 The distance M) is proportional to the distance M, so it is only necessary to consider this point and set the distance M. If the collision wall 18 is provided to have such a determined size, during the operation of the indoor unit 1, that is, when the cross-flow fan 8 rotates Therefore, the collision area E3 can be formed as a space of a substantially constant stagnation pressure Pst higher than the atmospheric pressure P0 by the airflow blown out from the fan extension 8a.

In the above, as shown by the straight line Pst1 in FIG. 15(b), the same level of stagnation pressure Pst is formed in the collision area E3 on the entire surface from the stabilizer-side end portion 19a to the rear guide portion-side end portion 19b. The distance between the fan outer peripheral portion 8b and the facing surface 18a is set in such a manner. On the other hand, the collision wall 18 may be configured so that the stagnation pressure Pst is not uniform but varies in the collision region E3 of the entire surface from the stabilizer-side end 19a to the rear guide-side end 19b.

16 relates to another configuration example of the first embodiment, and is a graph showing the stagnation pressure Pst formed in the collision area E3 with respect to the position in the depth direction AY. The horizontal axis represents the position in the depth direction AY, and the vertical axis represents stagnation. Pressure Pst. Even the stagnation pressure Pst indicated by the straight line Pst2 in FIG. 16 shows a stagnation pressure Pst higher than the atmospheric pressure P0 over the entire surface from the stabilizer side end 19a to the rear guide side end 19b in the depth direction AY. Therefore, suck back can be prevented. The rear guide portion side end portion 19b is farther away from the circulating vortex F1 and the outlet 3 than the stabilizer side end portion 19a, so stagnation pressure Pst required for preventing suck back can also be made lower than the stabilizer side end portion 19a. In this configuration example, the stagnation pressure Pst having a large difference from the atmospheric pressure P0 is formed at the end portion 19a on the stabilizer side where suckback is likely to occur, thereby reliably preventing suckback. In addition, at the rear guide portion side end portion 19b that is less likely to cause suck back, the distance Mb from the fan outer peripheral portion 8b to the collision wall 18 is increased compared with the straight line Pst1 shown in FIG. The guide portion side end portion 19b forms a stagnation pressure Pst that is about the same as the atmospheric pressure P0 or slightly higher than the atmospheric pressure P0, and the ratio of the blowing air flow is increased compared to the straight line Pst1. The collision pressure Pvb on the straight line Pst2 is smaller than the collision pressure Pvb on the straight line Pst1 compared to the case where the stagnation pressure Pst indicated by the straight line Pst1 in FIG. 15( b ) is formed. By reducing the collision pressure Pvb at the rear guide portion side end portion 19b as compared with the straight line Pst1 as in this structure, it is possible to further reduce the increase in ventilation resistance and noise due to the collision with the wall 18 .

In this way, it does not need to be configured so that the same stagnation pressure Pst can be obtained from the stabilizer-side end portion 19a to the rear guide portion-side end portion 19b. In addition, in the depth direction AY of the collision wall 18, the change of the stagnation pressure Pst formed from the stabilizer side end 19a to the rear guide side end 19b is represented by the straight lines Pst1 and Pst2, but the present invention is not limited thereto. For example, the stagnation pressure Pst formed from the stabilizer-side end portion 19 a to the rear guide portion-side end portion 19 b may change in a curve shape or may change in a step shape.

As long as stagnation pressure Pst necessary to prevent suck back from occurring at each position in the depth direction AY from the stabilizer-side end 19a to the rear guide-side end 19b is formed, the fan outer peripheral portion 8b is considered. The distance M in the radial direction from the opposing surface 18 a may constitute the collision wall 18 .

In addition, as for the distance M between the fan outer peripheral portion 8b and the opposing surface 18a of the collision wall 18 on a cross section perpendicular to the rotation axis 17, the distance from the stabilizer-side end portion 19a to the increase start position 19c is constant as Ma =Mc. Therefore, it is possible to reliably prevent the occurrence of suction on the side of the stabilizer 9 where the suction is likely to occur.

In addition, the increase start position 19c is set to a position at which the distance from the stabilizer-side end portion 19a is approximately 10% of the length of the collision wall 18 in the depth direction, but the present invention is not limited thereto. However, as shown in FIG. 10 , it is preferable that the increase start position 19c is located at the intersection of the opposing surface 18a of the collision wall 18 with the straight line Z connecting the rotation center O of the cross-flow fan 8 and the rear guide portion 10 side of the air outlet 3 , that is, Gb. The position (indicated by the increase start position 19c in FIG. 10) is close to the position of the rear guide side end 19b. The reason for this is that the area from the stabilizer side end 19a to the intersection point where the straight line Z intersects the opposing surface 18a is close to the area E4 of low pressure due to the vortex F1, and suckback is likely to occur.

As described above, in the cross section perpendicular to the rotation axis 17, the collision wall 18 has the distance M between the fan outer peripheral portion 8b and the facing surface 18a in the middle between the stabilizer side end portion 19a and the rear guide portion side end portion 19b. The start position on the side of the stabilizer 9 when it is longer than the distance Ma is the increase start position 19c. Furthermore, as for the distance M in the radial direction between the fan outer peripheral portion 8b and the facing surface 18a, by making the distance M of the area from the stabilizer side end portion 19a to the increase start position 19c the same as the distance Ma, it is easy to cause a collapse. From the stabilizer side end 19a of the suction to the increase start position 19c, the stagnation pressure Pst sufficiently higher than the atmospheric pressure P0 is stably formed, thereby having the effect of reliably preventing suckback.

In addition, 1n2 to 1n5 of FIG. 17 show other configuration examples of the distance M relative to the position of the facing surface 18 a in the depth direction AY in a cross section perpendicular to the rotation axis 17 according to the present embodiment. 17 relates to another configuration example of Embodiment 1, and the horizontal axis represents the position in the depth direction AY of the facing surface 18a of the collision wall 18, and the vertical axis represents the radial direction between the facing surface 18a and the fan outer peripheral portion 8b. Graph of distance M. It may also be configured by changing any one of the distances of ln2 to ln5 shown here. The straight line ln2 is not provided with the increase starting position 19c, the shortest distance Ma is set at the stabilizer side end 19a, the longest distance Mb is set at the rear guide side end 19b, and the shortest distance Ma and An example in which the longest distance Mb changes linearly. The curve ln3 is an example of setting the shortest distance Ma at the stabilizer-side end 19a, and increasing the distance M at a portion where the distance from the rear guide-side end 19b is approximately 2/3 of the whole, and is applied to the rear guide. The indoor unit 1 has a structure that substantially does not cause suck back in the vicinity of the side end 19b.

And, conversely, in the case of the indoor unit 1 having a structure that easily causes sucking back near the rear guide side end 19b, as in the curves ln4 and ln5, even in the vicinity of the rear guide side end 19b The distance M is also shortened in order to obtain a high collision pressure Pv and thus a stagnation pressure Pst. In either case, since the distance Ma is shortened at least at the stabilizer-side end portion 19a, stagnation pressure Psta sufficiently higher than the atmospheric pressure P0 can be formed at the stabilizer-side end portion 19a. Furthermore, since the distance Mb is the longest at the rear guide portion side end 19b, the collision pressure Pvb is lower than the collision pressure Pva, but a stagnation pressure Pstb higher than the atmospheric pressure P0 can be obtained, and the stagnation pressure Pstb can be used. Suckback is prevented, and the air flow that contributes to blowing air can be obtained by spreading the air flow toward the center side in the rotation axis direction AX. In particular, the distance M between the stabilizer-side end portion 19a and the rear guide portion-side end portion 19b can be optimally configured by considering the state of the static pressure Ps inside the indoor unit 1 as shown in FIG. 11 . Shaped collision wall 18 .

As described above, in this embodiment, the air conditioner is characterized by including: the suction grill 2 provided on the main body of the indoor unit 1 to suck in indoor air; The heat exchanger 7; is installed in the lower part of the main body of the indoor unit 1 in such a way that the longitudinal direction extends along the left and right direction of the main body of the indoor unit 1, and the indoor air after the heat exchange in the above-mentioned heat exchanger 7 is directed toward the indoor The outlet 3 for blowing out is provided between the heat exchanger 7 and the outlet 3 so that the left-right direction of the main body of the indoor unit 1 coincides with the direction AX in which the rotation axis 17 extends, and has The cross-flow fan 8 of the fan extension part 8a extending outward compared with the end of the longitudinal direction of the air outlet 3; the blowing air passage 11 that guides indoor air toward the air outlet 3 is formed on the downstream side of the above-mentioned cross-flow fan 8 The stabilizer 9 on the front side; the rear guide part 10 on the back side constituting the above-mentioned blowing air passage 11; The collision wall 18 having an opposing surface 18a provided approximately along a part of the outer periphery of the fan extension 8a so as to face the indoor air blown out from the fan extension 8a is configured as follows: When the distance in the radial direction between the opposing surface 18a and the outer peripheral portion 8b of the fan extension 8a in a cross section perpendicular to the rotation axis 17 is set as the distance M, compared to the distance between the opposing surface 18a and the above The distance Ma at the stabilizer-side end 19a connected to the stabilizer 9 is longer than the distance Mb at the rear guide-side end 19b connected to the rear guide 10 of the opposing surface 18a.

By configuring in this way, in the vicinity of both ends in the longitudinal direction of the air outlet 3, near the stabilizer 9 where the vortex is generated and the static pressure Ps is lowered, the blown airflow from the fan extension 8a of the cross-flow fan 8 is matched with the When the collision wall 18 collides, a high collision pressure Pv is obtained, and a stagnation pressure Pst (static pressure Ps+collision pressure Pv) higher than the atmospheric pressure P0 is formed on the opposing surface 18 a of the collision wall 18 . By forming this high-pressure field, it is possible to prevent indoor air from being sucked back into the interior of the indoor unit 1 through the air outlet 3 from the outside of the indoor unit 1 . Further, on the side of the rear guide portion 10 away from the vortex F1 where suckback is less likely to occur, the radial distance M between the fan outer peripheral portion 8b and the facing surface 18a is formed longer than the distance Ma at the stabilizer-side end portion 19a. Here, part of the airflow from the fan extension 8a is used as the blowing airflow, and the airflow blown out from the fan extension 8a and colliding with the collision wall 18 is smaller than that on the side of the stabilizer 9 . Thereby, although it is lower than the collision pressure Pv of the airflow in the vicinity of the vortex F1, a stagnation pressure Pst higher than the atmospheric pressure P0 is formed near the rear guide part 10 to the extent that suckback can be prevented, thereby suppressing the air flow from the fan. All of the airflow blown out from the extension portion 8a collides with the collision wall 18 to increase energy loss and increase noise, thereby enabling reduction in power consumption and noise reduction.

Implementation mode 2.

Hereinafter, Embodiment 2 of this invention is demonstrated based on drawing. 18 and 19 are explanatory diagrams showing the indoor unit of the air conditioner according to this embodiment. FIG. 18 relates to this embodiment and is a perspective view showing the collision wall 18 located on the right side when viewed from the indoor unit 1 . 19 is a diagram showing the distance M between the opposing surface 18a of the collision wall 18 and the fan outer peripheral portion 8b according to Embodiment 2, and (a) of FIG. 19 is a longitudinal sectional view perpendicular to the rotation axis 17 of the indoor unit 1. 19( b ) is a graph showing the position in the depth direction AY of the collision wall 18 on the horizontal axis and the distance M between the fan outer peripheral portion 8 b and the opposing surface 18 a of the collision wall 18 on the vertical axis. In this embodiment, as shown in FIG. 18 , it is characterized in that, compared with the position of Embodiment 1 shown in FIG. The vicinity of the upstream side end 10a of the In each figure, the same code|symbol as Embodiment 1 represents the same or corresponding part.

FIG. 10 shows the relationship between the fan outer peripheral portion 8 b and the blowing air duct 11 at the center portion in the left-right direction of the indoor unit 1 , that is, the center portion where the collision wall 18 is not formed. In the structure when the cross-flow fan 8 is mounted, the vicinity of the upstream end 10a of the air flow of the rear guide 10 and the tongue 9a of the stabilizer 9 have the function of separating the suction area E1 and the blowing area E2. Therefore, the upstream side end portion 10a and the front end portion of the tongue portion 9a of the stabilizer 9 are arranged closer to the fan outer peripheral portion 8b than the other components. In Embodiment 1, the distance between the opposing surface 18a and the fan outer peripheral portion 8b is configured such that the distance Mb at the rear guide portion side end portion 19b is longer than the distance Ma at the stabilizer side end portion 19a. On the other hand, in this embodiment, the distances Ma and Mb at the stabilizer-side end portion 19a and the rear guide portion-side end portion 19b are formed to be shorter than the distance M at the opposing surface 18a therebetween. For example, the distance Md at the position 19d of the central part in the depth direction AY is made the longest.

With respect to the distance M of the position in the depth direction AY of the opposing surface 18a, from the front side to the back side, as shown by the curve ln6 in FIG. So far as short (Ma, Mc). Furthermore, it increases from the increase start position 19c, is the longest (Md) at the central position 19d, and remains longer for a predetermined section from the central position 19d toward the rear guide side end 19b. Then, it becomes shorter gradually toward the rear guide part side end part 19b, and becomes distance Mb at the rear guide part side end part 19b. Here, the distance Mb is longer than the distance Ma and shorter than the distance Md.

Depending on the internal structure of the indoor unit 1 of the air conditioner, the ventilation resistance varies, and a vortex F2 as shown in FIG. When the eddy currents F1 and F2 are generated in this way, the static pressure Ps inside the indoor unit 1 decreases due to the influence of the eddy currents F1 and F2. As an example, the static pressure Ps with respect to the position in the depth direction AY is shown in FIG. 20 . At the end 19a on the stabilizer side, the air pressure decreases by Ha due to the influence of the vortex F1, and the static pressure Ps becomes Psa. And since the air pressure decreases by Hd (<Ha, Hb) at the position 19d of the center part in the depth direction AY, static pressure Ps becomes Psd (>Psa, Psb). On the other hand, the collision wall 18 having the shape shown in (b) of FIG. Since the distances between the fan outer peripheral portions 8b are approximately the same, most of the airflow blown out from the cross-flow fan 8 collides with the collision wall 18, and a high collision pressure Pv can be obtained. On the other hand, near the central position 19d, the distance Md is longer than the distances Ma and Mb, so part of the airflow blown from the cross-flow fan 8 spreads toward the central side in the rotation axis direction AX before reaching the collision wall 18 . Therefore, a part of the airflow blown out from the cross-flow fan 8 flows toward the blowing air passage 11 reaching the air outlet 3 to become a blowing airflow. At the center position 19d, the collision pressure Pv is lower than that of the stabilizer-side end portion 19a and the rear guide portion-side end portion 19b, but since the static pressure Ps is high, a stagnation pressure higher than the atmospheric pressure P0 is formed. Pst. That is, at the position 19d in the center, when stagnation pressure Pst is set to Pstd, static pressure Ps is set to Psd, and collision pressure Pv is set to Pvd, stagnation pressure Pstd=static pressure Psd+collision pressure Pvd, Similar to the stagnation pressure Psta at the stabilizer-side end portion 19a and the stagnation pressure Pstb at the rear guide portion-side end portion 19b, a stagnation pressure Pstd higher than the atmospheric pressure P0 can be formed.

Thus, in the longitudinal section perpendicular to the rotation axis 17 of the indoor unit 1, the distance M between the fan outer peripheral portion 8b and the collision wall 18 is not the same from the stabilizer side end portion 19a to the rear guide portion side end portion 19b, A high collision pressure Pv is obtained by shortening the distance M at the position where the static pressure Ps becomes lower, and a lower specific static pressure Ps is obtained by increasing the distance M at the position where the static pressure Ps becomes higher than the position where the static pressure Ps becomes lower The distance M is changed in accordance with the static pressure Ps in such a manner that the collision pressure Pv at the position is lower than the collision pressure Pv. Thus, from the stabilizer side end 19a of the opposing surface 18a of the collision wall 18 to the rear guide side end 19b, a stagnation pressure above the atmospheric pressure P0 can be formed to prevent suck back, and to obtain the desired The way the collision pressure Pv makes the airflow collide. Furthermore, the airflow that does not contribute to the collision pressure spreads toward the center side in the rotation axis direction AX while flowing from the fan outer peripheral portion 8b to the opposing surface 18a, flows toward the blowing air passage 11, and can function as a blowing airflow. Therefore, suck-back can be prevented by forming the collision wall 18 , and pressure loss and increase in noise due to the formation of the collision wall 18 can be reduced.

As described above, in this embodiment, the air conditioner is characterized by including: the suction grill 2 provided on the main body of the indoor unit 1 to suck in indoor air; The heat exchanger 7 is arranged at the lower part of the main body of the above-mentioned indoor unit 1 so that the longitudinal direction extends along the left-right direction of the main body of the air conditioner 1, and the indoor air after heat exchange in the above-mentioned heat exchanger 7 is blown out into the room. The air outlet 3 is provided between the heat exchanger 7 and the air outlet 3 so that the left-right direction of the main body of the indoor unit 1 coincides with the direction in which the rotation axis 17 extends, and there are relatively The cross-flow fan 8 of the fan extension part 8a extending outward from the longitudinal end of the air outlet 3; the blowing air that guides the indoor air toward the air outlet 3 is formed at a position on the downstream side of the cross-flow fan 8. The stabilizer 9 on the front side of the passage 11; the rear guide part 10 constituting the back side of the above-mentioned blowing air passage 11; 10, and has a collision wall 18 with an opposing surface 18a provided approximately along a part of the outer peripheral portion of the fan extension 8a so as to face the indoor air blown out from the fan extension 8a, and is configured as : When the distance in the radial direction between the above-mentioned opposing surface 18a and the outer peripheral portion 8b of the above-mentioned fan extension 8a in the cross section perpendicular to the above-mentioned rotation axis 17 is set as the distance M, the same as the above-mentioned opposing surface 18a and Compared with the above-mentioned distance M at the stabilizer-side end 19a connected to the above-mentioned stabilizer 9, that is, the distance Ma, from the above-mentioned stabilizer-side end 19a to the rear guide part side connected to the above-mentioned rear guide part 10 of the above-mentioned opposing surface 18a At least a part of the above-mentioned distance M in the section of the end portion 19b is longer than the above-mentioned distance Ma, thereby, sucking back can be prevented, and an increase in energy loss and an increase in noise caused by the blown airflow colliding with the collision wall 18 can be suppressed, and Low power consumption and low noise can be achieved.

In addition, in this embodiment, the change of the distance M with respect to the position of the depth direction AY is not limited to ln6 shown in FIG.19(b). Here, the distance M between the opposing surface 18a and the fan outer peripheral portion 8b is made constant from the stabilizer-side end portion 19a to the increase start position 19c, but the present invention is not limited thereto. For example, when a sufficient stagnation pressure Pst capable of preventing suckback can be obtained at the stabilizer-side end 19a, and the decrease in the static pressure Ps near the increase start position 19c is not as large as that of the stabilizer-side end 19a, The increase start position 19c may not be provided, and the distance M between the fan extension 8a and the opposing surface 18a may be increased from the stabilizer side end 19a toward the central position 19d. By increasing the distance M, it is possible to increase the ratio of the air flow blown out from the fan extension 8a to the air blowing action, and thus further reduce power consumption and noise reduction. In addition, the change shown in ln6 is not limited, and the distance M from the stabilizer-side end portion 19a to the rear guide portion-side end portion 19b may be configured to change in a stepwise, curved, or linear manner. Make it change in other shapes. If it is configured to make at least a part of the distance M from the stabilizer-side end 19a to any one of the rear guide-side ends 19b longer than the distance Ma at the stabilizer-side end 19a, and the entire distance on the opposing surface 18a Both are formed so that the electric power and the noise can be reduced compared with the configuration in which the distance Ma is the same.

And the rear guide part side end part 19b is as follows.

As shown in FIG. 10, in a section perpendicular to the rotation axis 17, the front side of the collision wall 18 is connected to the stabilizer 9, but the back side is connected to the rear guide part Gb from the upstream side end 10a to the outlet 3. Any rear guide 10 is connected. According to the internal structure of the main body of the indoor unit 1, the air flow and ventilation resistance flowing inside are different. Therefore, only the air flow and the static pressure Ps inside the main body of the indoor unit 1 should be considered, and the rear of the collision wall 18 can be determined according to whether or not the collision pressure is required. The position of the guide part side end part 19b is sufficient. In addition, the distance M between the fan outer peripheral portion 8b and the facing surface 18a can be determined in consideration of how much collision pressure is required.

Implementation mode 3.

An air conditioner according to Embodiment 3 of the present invention will be described below. 21 relates to this embodiment, and is a cross-sectional view showing the vicinity of the end portion 14a inside the indoor unit 1, and shows a cross-section when the collision wall 18 is cut on a plane including the rotation axis 17. As shown in FIG. Here, too, the right end portion in the left-right direction of the cross-flow fan 8 is shown, and the left end portion is formed in a left-right reversed configuration. In the drawings, the same reference numerals as those in Embodiment 1 denote the same or corresponding parts. In Embodiment 1 and Embodiment 2, in the opposing surface 18a of the collision wall 18, the distance M between the fan outer peripheral portion 8b and the opposing surface 18a is made the same in the rotation axis direction AX. On the other hand, in this embodiment, the distance M is configured to be different in the rotation axis direction AX. In FIG. 21 , when the opposing surface 18a is viewed in the direction of the axis of rotation AX, the end portion located on the end plate 12b side of the cross-flow fan 8 is set as the side wall-side end portion 21e, and the central side of the cross-flow fan 8, That is, the edge part adjacent to the blowing air path 11 is set as the blowing air path side edge part 21f. Furthermore, the distance M between the fan outer peripheral portion 8b and the opposing surface 18a is set such that the distance Me at the side wall side end portion 21e<the distance Mf at the blowing air passage side end portion 21f. However, at any position in the rotation axis direction AX of the fan extension portion 8a, the depth of the opposing surface 18a is satisfied as described in Embodiment 1 or Embodiment 2 on a cross section perpendicular to the rotation axis 17. The relationship between the distance M at each position in the direction AY.

As shown in FIG. 21 , in the opposing surface 18 a, distance Me<distance Mf, and the distance M between the side wall side end 21 e and the blowing air path side end 21 f is linearly changed. For example, the distance Me=20 mm of the side wall side edge part 21e is set, and the distance Mf=25 mm of the blowing air path side edge part 21f is set. 22 is a diagram showing the distance M between the opposing surface of the collision wall in the rotation axis direction AX and the outer peripheral portion of the fan according to Embodiment 3, where the horizontal axis represents the position in the rotation axis direction AX and the vertical axis represents A graph showing the distance M between the facing surface and the outer periphery of the fan. In FIG. 22, the change of the distance M shown in FIG. 21 is represented by a straight line ln11. FIG. 23 is an explanatory view showing the air flow at the facing surface 18a configured in this way. The side wall side end 21e of the opposing surface 18a is adjacent to the space S where the static pressure Ps is low and the blown airflow does not flow directly, and the ventilation resistance ratio is lower due to the existence of the end plate 12b and the like at the side wall side end 21e. The side end 21f of the blowing air path is still high and the static pressure Ps is low, etc., which easily causes indoor air to be sucked back into the machine through the blowing port 3 . Therefore, it is comprised so that the distance Me with respect to the fan outer peripheral part 8b in the side wall side end part 21e may be made shorter than the distance Mf in the outlet air path side end part 21f. At the side wall-side end portion 21e with a short distance M, the airflow blown from the fan outer peripheral portion 8b spreads in the rotation axis direction AX before reaching the opposing surface 18a compared with the blowing air passage-side end portion 21f with a long distance M. The air flow is small, and the collision pressure Pve higher than the collision pressure Pvf of the blowing air path side edge part 21f can be obtained.

For example, the static pressure Ps near the side wall side end 21e is set as Pse, and the static pressure Ps of the blowing air path side end 21f is set as Psf. When Pse and Psf are the same, the collision pressures Pve and Pvf are added, The stagnation pressure Pst formed at the side wall side end portion 21e of the facing surface 18a is Pste, which is higher than the stagnation pressure Pst formed at the outlet air path side end portion 21f, that is, Pstf (Pste>Pstf>P0). In addition, the collision wall 18 is formed so that both of the stagnation pressures Pste and Pstf are higher than the atmospheric pressure P0. By forming a stagnation pressure Pste higher than the atmospheric pressure P0 at the side wall side end 21e, a pressure field that prevents indoor air from entering the machine through the outlet 3 can be created, and sucking back of indoor air into the space S can be prevented.

In addition, as described above, when the static pressure Ps or Psf of the end portion 21f on the side wall side is higher than the static pressure Ps or Pse of the end portion 21e on the side wall side, compared with the case where the static pressure Ps is the same, It is possible to further increase the distance Mf at the end portion 21f on the blowing air path side. Even if the distance Mf at the blowing air path side end 21f is further increased in this way, the stagnation pressure Pstf of the blowing air path side end 21f can be made to be about the same as the stagnation pressure Pstf of the side wall side end 21e. By configuring to increase the distance Mf, the airflow flowing toward the blowing air passage 11 reaching the blowing outlet 3 without reaching the collision wall 18 increases, and the blowing effect can be further obtained to suppress energy loss and increase in noise.

That is, in the vicinity of the side wall side end portion 21e, the distance Me is set so as to obtain the collision pressure Pve required to form the stagnation pressure Pste of a magnitude for reliably preventing suckback. On the other hand, near the end portion 21f of the blowing air path, the distance Mf is set so as to obtain the collision pressure Pvf required to form the stagnation pressure Pstf (≥P0) equivalent to the atmospheric pressure P0. The distance Mf is longer than the distance Me, and the end portion 21f on the side of the blowing air path of the facing surface 18a is farther from the outer peripheral portion 8b of the fan than the end portion 21e on the side wall side, so a part of the air flow is directed toward the blowing air path reaching the air outlet 3. 11 flows, thereby contributing to the supply air.

It also has the following effects. According to Embodiment 3, the airflow does not collide with the opposing surface 18a perpendicularly but collides with the inclined surface of the opposing surface 18a. Therefore, as shown in FIG. The airflow Xb that the supply air contributes to. With the airflow component Xb that contributes to the air blowing and the pressure difference caused by the stagnation pressure Pst in the direction of the rotation axis AX, a flow from the side wall side end 21e toward the blowing air path side end is generated on the opposing surface 18a. The airflow Xc of the part 21f. Therefore, the airflow Xc collides with the sucked back airflow, and the sucked back can be further prevented.

As described above, the distance Mf between the end portion 21f on the blowing air passage side of the opposing surface 18a and the outer peripheral portion 8b of the cross-flow fan 8 is smaller than that on the side of the opposing surface 18a located on the end portion side of the cross-flow fan 8 . The distance Me between the wall-side end portion 21e and the above-mentioned fan outer peripheral portion 8b is also long. That is, when viewed in the direction of the rotation axis 17, the end portion of the facing surface 18a near the center of the cross-flow fan 8, that is, the end portion 21f on the outlet air passage side, and the end portion near the end of the cross-flow fan 8, that is, the side The wall-side end portion 21e is relatively farther from the outer peripheral portion 8b of the fan extension portion 8a. Thereby, there is an effect that stagnant pressure is formed on the facing surface 18a and the air flow for blowing is increased, sucking back can be prevented, and the reduction of the blowing volume and the increase of the collision noise due to the formation of the collision wall can be suppressed. Large, the power consumption relative to the required air blowing volume can be suppressed to be small, and an air conditioner that achieves low power consumption and low noise can be obtained.

In addition, although the example in which the shape of the opposing surface 18a in the rotation axis direction AX was changed linearly like the straight line ln11 (refer FIG. 22) was described above, it is not limited to this. For example, as shown in FIG. 24 , the distance M may be changed like a straight line ln12 in accordance with the position in the rotation axis direction AX. (a) of FIG. 25 shows the shape of the facing surface 18a configured so that the distance M indicated by the curve ln12 in FIG. 24 can be obtained. As shown in (a) of FIG. 25 , it can also be changed in the following manner: at the position close to the side wall side end 21e, as shown by the curve ln12 in FIG. 24 , from the side wall side end 21e to the position 21g The plane facing the fan outer peripheral portion 8b is formed so that the distance M is substantially constant, and the distance M from the position 21g to the end portion 21f on the side wall side becomes longer than the distance at the position 21g and the end portion 21e on the side wall side. Ways change. In this case, the pressure field of the stagnation pressure formed at the side wall side end portion 21e can be formed broadly in the rotation axis direction AX from the side wall side end portion 21e to the position 21g, and suckback can be reliably prevented.

25( b ) shows the facing surface 18 a when the distance M is changed corresponding to the position in the rotation axis direction AX as shown by the curve ln13 of FIG. 24 . As shown in (b) of FIG. 25, when the distance M is changed as shown in the curve ln13 of FIG. The opposite surface 18a. In this case, the flow of the airflow flowing on the opposing surface 18a becomes smooth, especially the airflow which flows smoothly toward the blowing air path 11 can be obtained, and ventilation resistance can be reduced.

The shape of the facing surface 18a is not limited to a shape capable of obtaining changes in the distance M such as ln11, ln12, and ln13, and the shape of the facing surface 18a may be changed arbitrarily in the rotation axis direction AX. The shape of the opposing surface 18a viewed from the rotation axis direction AX may change smoothly in a straight line from the end portion 21e on the side wall side to the end portion 21f on the side of the blowing air passage, and may also change in a stepped shape or in a curved shape. Variety.

However, at any position in the direction of the rotation axis AX, the distance M on the side closer to the end 21 f on the side of the side wall side than that on the side closer to the side wall side end 21 e at that position is preferably longer or equal to the distance M. The shape of the opposing surface 18a is changed in a manner. That is, it is preferable to form the opposing surface 18a so that the distance M from the fan outer peripheral part 8b does not decrease from the side wall side end part 21e toward the blowing air path side end part 21f. If it is configured to obtain a higher collision pressure at the side wall side end 21e of the opposing surface 18a than the blowing air path side end 21f in the rotation axis direction AX, in the air flow blown out from the fan extension 8a, The airflow that does not collide with the collision wall 18 smoothly flows toward the blowing air passage 11 .

In addition, if the end portion 21f on the side of the blowing air path has a rounded shape instead of a corner, the air flow will not be disturbed by the corner to form a vortex, so the air flow will flow smoothly toward the downstream of the blowing air path 11. , can prevent the increase of ventilation resistance.

Furthermore, the shape of the opposing surface 18a in the rotation axis direction AX may be different at each position in the depth direction AY. For example, in the vicinity of the stabilizer-side end portion 19a, in the rotation axis direction AX, it may be formed in a shape in which a relatively high collision pressure Pv is broadly formed in the rotation axis direction AX as shown in the curve ln12 shown in FIG. The vicinity of the rear guide portion side end portion 19b is formed in a shape capable of obtaining a large amount of air flow toward the blowing air passage 11, like a straight line ln11 shown in FIG. 22 and a curved line ln13 shown in FIG. 24 .

In addition, the collision wall 18 may be formed integrally with the housing of the indoor unit 1, or may be formed separately and fixed to the inner side of the side wall 30 by, for example, adhesion, claw fixing, or screw fixing. Furthermore, the shape may be configured so as to convert the energy of the wind speed into pressure energy by colliding with the airflow blown from both ends in the left-right direction of the cross-flow fan 8 .

In addition, in the first to third embodiments described above, it is shown that the end region of the stabilizer 9 facing the fan extension 8a, the end region of the rear guide 10, and the collision wall 18 connecting the above regions are used to form a An example of the wall structure of the facing surface 18a provided substantially along the outer peripheral portion of the fan extension portion 8a so as to face the airflow blown out from the fan extension portion 8a. However, such a wall structure may be constituted by an integral member other than the stabilizer 9 and the rear guide 10 . Specifically, for example, the left and right widths of the stabilizer 9 and the rear guide part 10 are made the same as the left and right widths of the air outlet 3, and the structure is equivalent to the fan extension part 8a provided corresponding to the fan extension part 8a in Embodiments 1 to 3 by an integral member. The structure of the above-mentioned wall structure is adopted, and it is arranged inside the side wall 30 of the indoor unit 1 . In this way, the same effects as those of the configurations shown in Embodiments 1 to 3 can also be obtained.

Label description:

1: Indoor unit (air conditioner); 2: Suction grille; 3: Air outlet; 4: Wind direction guide; 5: Electric dust collector; 6: Filter; 7: Heat exchanger; 8: Cross-flow fan ( impeller); 8a: fan extension; 8b: fan peripheral; 9: stabilizer; 10: rear guide; 10a: upstream end; 11: blowing air path; 12: support plate; 12a, 12b: fan end plate; 13: vane; 14: connection (impeller unit); 14a: end connection; 15: fan bushing; 16: motor; 17: rotation axis; 18: collision wall; 18a: opposite surface; 19a: Stabilizer side end; 19b: rear guide side end; 19c: increasing start position; 20: outer peripheral position; 21e: side wall side end; 21f: air outlet side end; 30: side wall.

Claims (7)

1. an air conditioner, is characterized in that,

Described air conditioner possesses:

Indoor set main body, this indoor set main body has the suction port of air amount and the blow-off outlet of blow out air, and it is long that blow-off outlet forms left and right directions;

Axial-flow fan, this axial-flow fan is arranged in described indoor set main body in the left and right directions of the described indoor set main body mode consistent with spin axis, has the fan extending portion also extending towards outside than the end of the length direction of described blow-off outlet at two end part, left and right;

Stabilizer and rear guide portion, described stabilizer and described rear guide portion, across described axial-flow fan arranged opposite, form the wind path that blows out towards described blow-off outlet guiding by the indoor air being blown from described axial-flow fan; And

Wall structure, this wall is configured in the outside that is arranged at respectively the two end part, left and right of described blow-off outlet in described indoor set main body, and there is the opposed faces roughly arranging along the part of the peripheral part of described fan extending portion in the opposed mode of air-flow with being blown from described fan extending portion

When the distance on the radial direction of described fan extending portion in the cross section vertical with described spin axis of described opposed faces and described fan extending portion, between described opposed faces and the peripheral part of described fan extending portion is set as apart from M,

Be configured to: with respect to described opposed faces by the some a place of described stabilizer side described apart from M apart from Ma, at least a portion place described also longer apart from Ma than described apart from M of leaning on the region of described rear guide portion side with respect to described some a in described opposed faces.

2. air conditioner according to claim 1, is characterized in that,

By the end regions of the end regions of the described stabilizer on left and right directions, described rear guide portion on left and right directions and to connect, the end regions of described stabilizer of arranged opposite and the mode of the end regions of described rear guide portion arrange described wall structure and the impact walls with described opposed faces forms.

3. air conditioner according to claim 2, is characterized in that,

Point on the end being connected with described stabilizer that described some a is described opposed faces,

Be configured to: the some b place on the end being connected with described rear guide portion of described opposed faces described also long apart from Ma than described apart from Mb apart from M.

4. according to the air conditioner described in any one in claims 1 to 3, it is characterized in that,

When by described opposed faces, from described stabilizer side observe described apart from M become than described apart from Ma also long set positions when increasing initial position,

Region from described some a to described increase initial position described apart from M with described identical apart from Ma.

5. air conditioner according to claim 3, is characterized in that,

Be configured to: described apart from Ma and described apart from Mb described also short apart from M than the location between described some a of described opposed faces and described some b.

6. according to the air conditioner described in any one in claim 1 to 5, it is characterized in that,

From the direction of described spin axis, observe, the peripheral part away from described fan extending portion is also compared in the end of the center side by described axial-flow fan of described opposed faces with the end of the tip side by described axial-flow fan.

7. according to the air conditioner described in any one in claim 1 to 6, it is characterized in that,

In the inside of described indoor set main body, possesses the heat exchanger that carries out heat exchange with the indoor air being inhaled into from described suction port.