JP2007170757A - Indoor unit of air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a guideline for designing a constitution of an indoor unit capable of achieving a more desired suction flow place and proper heat transferring and air distributing performances in a case when a suction opening angle of a fan air distribution system is narrower than a heat exchanger surrounding angle to a respectable degree. <P>SOLUTION: A suction direction angle ϕ between a line segment Lc and a line segment Lp is determined to be 100-140 degrees, when Lc is the line segment connecting an apex portion 26a of a stabilizer portion 26 and an axial center of a cross flow fan 4, and Lp is the line segment connecting an intersecting point P of an extended line of an upper end of a front side upper heat exchanger 32 and an extended line of an upper end of a back side upper heat exchanger 33, and the axial center of the cross flow fan 4. Further an angle between the segment line Lp and a bisector Lm of an opening angle between a top face side wall face 28a and a bottom face side wall face 28b of a diffuser portion 28, is a blowout direction angle ω. The blowout direction angle ω is 130 degrees or less. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an indoor unit of an air conditioner, and more particularly to a technique for ensuring a suitable blowing performance against the presence of a relatively large ventilation resistance in an air blowing system of an indoor unit employing a cross flow fan.

  In general, a so-called separate air conditioner composed of two units of an indoor unit and an outdoor unit, in which the indoor unit is a wall-mounted type, as shown in FIG. A suction port 24 is provided in the range from the front surface to the top surface, a blowout port 25 is provided in the range from the front surface to the bottom surface of the indoor unit case 2, and the cross flow fan 4 is provided in the indoor unit case 2. The heat exchanger 3 is provided between the flow fan 4 and the suction port 24, and the air duct 23 that communicates the downstream portion of the cross flow fan 4 and the air outlet is provided.

In the indoor unit 1 of the air conditioner having such a configuration, for example, as shown in Patent Document 1 (Japanese Utility Model Publication No. 4-68721), the heat exchanger 3 is composed of a plurality of parts, and the front side heat exchanger The group 37 and the heat exchanger group 38 on the back side are arranged so as to form a substantially inverted V shape, and the heat exchanger groups 37 and 38 on the front side and the back side are plural parts so as to surround the cross flow fan 4. The heat exchangers are each arranged at a predetermined angle. This is to increase the surface area of the heat exchanger 3 and improve the heat transfer efficiency while keeping the volume of the indoor unit 1 as compact as possible in view of the demand for energy saving in the operation of the air conditioner. is there.
Japanese Utility Model Publication No. 4-69921

  In the above background art, there is a problem that the ventilation resistance is greatly increased as the surface area of the heat exchanger is increased by installing the heat exchanger so as to surround the cross flow fan. In particular, in order to obtain more heat transfer performance, for example, the number of rows of refrigerant tubes is 3 or more and the thickness of the heat exchanger is considerably increased, or the diameter of the refrigerant tubes is 7 mm or more, for example. Is considerably thicker, a ventilation resistance that greatly exceeds the assumption of the fan blowing system (cross flow fan and blowing path) in the conventional design standard is generated. Furthermore, if an accessory that requires air ventilation and has a considerable degree of ventilation resistance, such as an electrostatic precipitator or an ion generator, is installed in the ventilation path in the indoor unit, the ventilation resistance will increase even further. Will occur.

  In this case, as one of means for improving the performance of the fan blower system, a means for extending the rear guide portion to the upstream side is taken. This increases the length of the scroll curve formed by the rear guide part and increases the blowing air volume, and also optimizes the balance between the air volume and the static pressure by optimizing the suction side area of the fan blowing system. Expecting.

  However, when the above-mentioned method is adopted, along with the extension of the rear guide part, the suction opening angle of the fan blower system particularly when viewed from the cross section of the indoor unit (the upstream end of the stabilizer part with the crossflow fan as the axis center) The opening angle from the upper part to the upstream end of the rear guide part) is more significant than the surrounding angle of the heat exchanger (the surrounding angle from the lower end on the front side of the heat exchanger to the lower end on the back side with the crossflow fan as the axis) Becomes narrower. For this reason, in the suction side portion of the fan blower system, an event has occurred in which the suction is not performed evenly from the entire surrounding angle range of the heat exchanger as in the prior art, but is biased with a certain degree of directivity.

  Therefore, when suction with directivity is performed in the suction side portion of the fan blower system in this way, in order to draw out the performance more suitably without deteriorating the performance related to heat transfer and blower, the direction and heat It was necessary to set the positional relationship and shape of the fan blower system, which is appropriate for the surroundings of the exchanger.

  The present invention has been made in view of the above circumstances, and in the case where the suction opening angle of the fan blower system is considerably narrower than the surrounding angle of the heat exchanger, a more preferable suction flow field is realized and more preferable. It aims at providing the design guideline of the structure of an indoor unit which can implement | achieve heat transfer and ventilation performance.

In order to achieve the above object, the present invention provides the following means.
In the indoor unit of the air conditioner based on the present invention, a crossflow fan for sucking room air from the suction port and blowing it out from the blowout port, and located upstream of the crossflow fan, mainly the front surface of the suction port A first heat exchanger disposed in a flow of air from the side toward the cross flow fan, and a second heat exchanger disposed in a flow of air mainly from the back side of the suction port toward the cross flow fan. A heat exchanger and a blower duct having a stabilizer part and a rear guide part, located near and downstream of the cross flow fan, the suction opening angle being smaller than the heat exchanger surrounding angle, A line segment connecting the tip of the stabilizer close to the fan and the axial center of the crossflow fan is Lc, and the extension line at the upper end of the first heat exchanger and the second heat The line segment connecting the intersection P with the extension line at the upper end of the converter and the axial center of the cross flow fan is Lp, and the angle formed by the line segment Lc and the line segment Lp is 100 degrees to 140 degrees, and The bisector of the opening angle formed by the top side wall surface and the bottom side wall surface of the diffuser part is Lm, and the angle formed by the line segment Lp and the bisector Lm is 130 degrees or less. It is a feature.

  By adopting this configuration, when the suction opening angle of the fan blower system shown in the subject of the present invention is considerably narrower than the surrounding angle of the heat exchanger, the fan blower system can exhibit appropriate blowing performance. A more suitable suction flow field can be realized.

  In the indoor unit of the air conditioner, an angle formed by the line segment Lc and the line segment Lp is 115 degrees to 130 degrees. With this configuration, it is possible to realize a suitable blowing performance even in a configuration in which the fan blowing system is biased in the suction direction with respect to the arrangement of the heat exchanger, and further, the front side of the heat exchanger having a relatively large amount of passing air It is possible to minimize the difference in the passing air volume from the back side where the passing air volume is relatively small.

  In the indoor unit of the air conditioner, an angle formed by the line segment Lp and the bisector Lm is 100 degrees to 120 degrees. With this configuration, it is possible to realize a more favorable blowing performance in the configuration in which the rear guide portion is extended to the upstream side, and furthermore, in the heat exchanger, the front side with a relatively large amount of passing air and the back side with a relatively small amount of passing air The difference in the passing air volume can be minimized.

  In the indoor unit of the air conditioner, a line segment connecting the upstream end of the stabilizer unit and the axial center of the crossflow fan is La, and an angle formed by the line segment La and the line segment Lc. Is 0 to 10 degrees. With this configuration, the flow at the stabilizer upstream end is rectified, and a noise reduction effect of about 1 to 2 dB (A) can be obtained.

  Moreover, in the indoor unit of the air conditioner, an installation angle formed by the top side wall surface of the diffuser part and the stabilizer part is 54 to 67 degrees. With this configuration, it is possible to optimize the blow-off diversion in the vicinity of the fan stabilizer, which contributes to the noise of the fan blower system, and to suppress the noise energy of the fan blower system.

  Further, in the indoor unit of the air conditioner, the top surface side wall surface of the diffuser portion has a bent portion, and the bent portion is located on the front side of the downstream end portion of the bottom side wall surface of the diffuser portion. In addition, the top side wall surface on the downstream side of the bent portion has a larger opening angle than the top side wall surface on the upstream side. With this configuration, the flow resistance can be suppressed at the downstream end of the bottom side wall surface, and the effect of the diffuser can be further continued.

  Further, in the indoor unit of the air conditioner, the angle formed by the downstream side wall surface of the top surface side wall surface with the horizontal plane is larger than the angle formed by the upstream side wall surface of the top surface side wall surface with the horizontal surface. And With this configuration, the amount of momentum in the horizontal or top direction can be applied to the cold air by the diffuser effect after the bent portion, especially during the cooling air blowing during the cooling operation, and the dripping of the cold air after the blowing is reduced as much as possible. can do.

  According to the configuration of the present invention, an indoor unit of an air conditioner that can realize a good suction flow field is easily designed even when the suction opening angle of the fan blower system is considerably narrower than the surrounding angle of the heat exchanger. can do. And the effect of energy saving in the whole indoor unit of an air conditioner can be implement | achieved by implement | achieving better heat transfer and ventilation performance.

  Hereinafter, an indoor unit of an air conditioner according to an embodiment of the present invention will be described with reference to the drawings. In each embodiment, the same parts are denoted by the same reference numerals, and the description thereof will not be repeated.

(Embodiment 1)
The indoor unit of the air conditioner in Embodiment 1 based on this invention is demonstrated with reference to drawings. FIG. 1 is a cross-sectional view showing a schematic configuration of an indoor unit in the present embodiment. As shown in FIG. 1, an indoor unit 1 includes a heat exchanger 3, a cross flow fan 4, a dust collecting filter 5, a wind direction control vertical louver 61, and a wind direction control horizontal louver inside an indoor unit case 2. 62, a motor having a motor (not shown) for driving the cross flow fan 4 and a control unit (not shown) for controlling the operation of the fan motor and the cooling / heating cycle.

  The indoor unit case 2 is mainly used as a fan casing for the cross flow fan 4 mainly in the exterior surface 21 that forms the exterior of the indoor unit 1, the back surface 22 that is preferably installed on the wall surface, and the internal ventilation path of the indoor unit 1. The air duct 23 has the following purpose. Of the exterior surface 21, a suction port 24 is formed mainly on the top surface side, and an air outlet 25 is formed mainly on the bottom surface side. The air inlet 24 and the air outlet 25 are in communication with the internal air flow path of the indoor unit 1, and in particular, the air outlet 25 is in communication with the air outlet side of the cross flow fan 4 via the air duct 23.

  The air duct 23 includes a stabilizer portion 26, a rear guide portion 27, and a diffuser portion 28 in order to suitably blow the cross flow fan 4. The stabilizer portion 26 is located on the front side of the cross flow fan 4 and is connected to the top surface side 28 a of the diffuser portion 28. The rear guide portion 27 is located on the back side of the cross flow fan 4 and is connected to the bottom surface side 28b of the diffuser portion 28 while forming a so-called scroll shape.

  The heat exchanger 3 is located in a path from the suction port 24 to the blowout side of the cross flow fan 4 in the internal air blowing path, and heat exchange is performed so that most of the air passing through this path passes through the heat exchanger 3. Both ends of the vessel 3 are installed in contact with the internal air flow path. Here, the heat exchanger 3 is configured by a combination of four plate fin tube type heat exchangers, and surrounds the crossflow fan, respectively, the front lower side 31, the front upper side 32, the rear upper side 33, and the rear lower side 34. The front upper heat exchanger 32 and the rear upper heat exchanger 33 are arranged so as to form a substantially inverted V shape. The lower end of the lower front portion 31 and the lower end of the lower lower portion 34 are the ends of the heat exchanger 3 and are in contact with the internal air flow path.

  The other end portions of the plate fin tube type heat exchangers 31 to 34 are in direct or indirect contact with each other, and are arranged at a predetermined angle. In the plate fin tube type heat exchangers 31 to 34, three rows of refrigerant tubes 35 having a diameter of 5 mm arranged at equal intervals are arranged in the thickness direction, and the thickness is about 0.00 mm so that the refrigerant tubes are skewered. The configuration is such that the 3 mm fins 36 are arranged in the depth direction at intervals of about 2 mm. The interval and thickness of the refrigerant pipes are the same as those of the four plate fin tube heat exchangers 31 to 34. Therefore, the ventilation resistance per unit area in each of the plate fin tube heat exchangers 31 to 34 is all. The same.

  Next, characteristic parts of the present embodiment will be described with reference to FIG. FIG. 2 is a cross-sectional view showing details of the arrangement of the cross flow fan 4, the air duct 23, and the heat exchanger 3. As described above, the air duct 23 includes the stabilizer portion 26, the rear guide portion 27, and the diffuser portion 28. The diffuser portion 28 is an enlarged flow path having a downstream opening as an outlet 25, and is a flow path section sandwiched between a substantially planar top side wall surface 28a and a bottom side wall surface 28b. A stabilizer portion 26 is arranged in communication with the upstream side of the top side wall surface 28 a of the diffuser portion 28. In addition, the rear guide portion 27 communicates with the upstream side of the bottom side wall surface 28 b of the diffuser portion 28. The rear guide portion 27 has a so-called scroll shape in which the opening gradually increases toward the downstream side, and has a bent portion 27a that forms a point closest to the fan near the upstream end portion. is doing. The stabilizer portion 26 is located on the front side of the cross flow fan 4 and is connected to the top surface side 28a of the diffuser portion 28 on the downstream side. Further, in the vicinity of the upstream end portion, there is a tip end portion 26a that forms a pointed end closest to the fan.

  The cross flow fan 4 is disposed in the vicinity of the upstream end portion of the air duct 23 so as to be sandwiched between the stabilizer portion 26 and the rear guide portion 27. The cross flow fan 4 is provided with a plurality of (35 in the present embodiment) blades 41 on the peripheral edge of the cylinder.

  The lower end F of the front lower side 31 of the heat exchanger 3 is located in a recess formed by the front side of the stabilizer part 26 and the top side of the top side wall face 28a of the diffuser part 28. The lower end R of the rear lower side 34 of the device 3 is located in a recess formed on the rear side of the rear guide portion 27.

  Here, a line segment connecting the sharp end portion 26a of the stabilizer portion 26 and the axial center of the cross flow fan 4 is Lc, and a line connecting the bent portion 27a of the rear guide portion 27 and the axial center of the cross flow fan 4 is used. Let the minute be Ld, and the angle formed by the line segment Lc and the line segment Ld be the suction opening angle θ.

  Further, a line segment connecting the lower end F of the lower front surface 31 of the heat exchanger 3 and the axial center of the cross flow fan 4 is Lf, and the lower end R of the lower rear surface 34 of the heat exchanger 3 is connected to the cross flow fan. A line segment connecting the four axis centers is Lr, and an angle formed by the line segment Lf and the line segment Lr is a heat exchanger surrounding angle ψ.

  Further, the intersection point P (substantially inverted V-shaped root portion) of the upper end extension line of the front side upper heat exchanger 32 and the upper end extension line of the rear side upper heat exchanger 33 and the axial center of the cross flow fan 4 Is defined as Lp, and an angle formed by the line segment Lc and the line segment Lp is defined as a suction direction angle φ.

  Further, a line segment connecting the upstream end of the stabilizer section 26 and the axial center of the crossflow fan 4 is La, and an angle formed by the line segment La and the line segment Lc is a stabilizer running angle ν.

  Further, the bisector of the opening angle formed by the top side wall surface 28a and the bottom side wall surface 28b of the diffuser portion 28 is Lm, and the angle formed by the line segment Lp and the bisector Lm is the blowing direction angle ω. To do.

  Further, an installation angle formed by the top side wall surface 28a of the diffuser portion 28 and the stabilizer portion 26 is ζ. Further, an opening angle of the diffuser formed by the top side wall surface 28a and the bottom side wall surface 28b of the diffuser portion 28 is η.

  In the present embodiment, for example, in the configuration shown in FIG. 2, the suction opening angle θ is about 150 degrees, and the heat exchanger surrounding angle ψ is about 220 degrees, that is, θ <ψ. This is due to the fact that the rear guide 27 is extended upstream in order to overcome the ventilation resistance of the heat exchanger 3 in order to improve the blowing performance of the fan blowing system.

  In such a fan blower system, in the present embodiment, design guidelines are defined as described below for φ, ω, and η.

  The suction direction angle φ is set to 100 degrees to 140 degrees (that is, 100 degrees ≦ φ ≦ 140 degrees). FIG. 3 shows the relationship between φ and the air volume at the operating point of the fan blower system. According to FIG. 3, it can be seen that the air volume is the largest when φ is approximately 120 degrees, and the air volume decreases in any direction when φ is increased or decreased. Therefore, the range from φ with the largest air volume at the operating point to the 2% air volume drop is judged as the appropriate design range of φ, and when the range is obtained, the above 100 degrees ≦ φ ≦ 140 degrees. is there. By setting the lower limit width of the air volume to 2%, it is possible to ensure the desired air blowing performance.

  More preferably, the suction direction angle φ is set to 115 degrees to 130 degrees (that is, 115 degrees ≦ φ ≦ 130 degrees). FIG. 4 shows the relationship between φ and the amount of passing air on the rear sides 33 and 34 of the heat exchanger at the operating point of the fan blower system. According to FIG. 4, it can be seen that the passing air volume is the largest when φ is approximately 124 degrees, and that the passing air volume decreases in any direction when φ is increased or decreased. Accordingly, the range from φ having the largest passing air volume on the heat exchanger back side 33, 34 to the 2% passing air volume falling is determined as an appropriate design range of φ, and the above range is 115 degrees. ≦ φ ≦ 130 degrees. The reason why the lower limit width of the passing air volume is set to 2% is in consideration of the measurement error of the passing air volume.

  By defining the suction direction angle φ as described above, it is possible to achieve a suitable blowing performance even in a configuration in which the suction direction of the fan blowing system is biased with respect to the arrangement of the heat exchanger 3 as in this embodiment. Furthermore, in the heat exchanger 3, the difference in the amount of passing air between the front sides 31, 32 with a relatively large amount of passing air and the back surfaces 33, 34 with a relatively small amount of passing air can be minimized.

  Further, when the stabilizer run-up angle ν is provided here and 0 degrees to 10 degrees (that is, 0 degrees ≦ ν ≦ 10 degrees), the flow at the stabilizer upstream end is rectified, and is about 1 to 2 dB (A). Noise reduction effect can be obtained.

  Next, the blowing direction angle ω is set to 130 degrees or less (that is, ω ≦ 130 degrees). FIG. 5 shows the relationship between ω and the air volume at the operating point of the fan blower system. According to FIG. 5, it can be seen that the air volume is greatest when ω is approximately 110 degrees. Therefore, if the range from φ with the largest air volume at the operating point to the 2% air volume drop is determined as an appropriate design range of φ and the range is obtained, the above-mentioned ω ≦ 130 degrees. By setting the lower limit width of the air volume to 2%, it is possible to ensure the desired air blowing performance.

  More preferably, the blowing direction angle ω is set to 100 degrees to 120 degrees (that is, 100 degrees ≦ ω ≦ 120 degrees). FIG. 6 shows the relationship between ω and the amount of passing air on the rear sides 33 and 34 of the heat exchanger at the operating point of the fan blowing system. According to FIG. 6, it can be seen that the passing air volume is the largest when ω is approximately 110 degrees, and that the passing air volume decreases in any direction when φ is increased or decreased. Therefore, the range from ω where the passing air volume at the heat exchanger back side 33, 34 is the largest to the 2% passing air volume is determined to be an appropriate design range of ω, and the above range is 100 degrees. ≦ ω ≦ 120 degrees. The reason why the lower limit width of the passing air volume is set to 2% is in consideration of the measurement error of the passing air volume.

  By defining the blowing direction angle ω as described above, it is possible to achieve a more favorable blowing performance in the configuration in which the rear guide portion 27 is extended to the upstream side as in the present embodiment, and furthermore, in the heat exchanger 3 The difference in the passing air volume between the front sides 31 and 32 having a relatively large passing air volume and the back surfaces 33 and 34 having a relatively small passing air volume can be minimized.

  Next, the stabilizer installation angle ζ is set to be 54 ° to 67 ° (that is, 54 ° ≦ ζ ≦ 67 °). FIG. 7 shows the relationship between ζ and the noise level of the fan blower system. According to FIG. 7, it can be seen that the value of the noise level is the smallest when ζ is approximately 61 degrees, and the value of the noise level increases in any direction when ζ is increased or decreased. Therefore, the range from the lowest noise level ζ up to the noise level rising by 0.5 dB (A) is determined as an appropriate design range of the stabilizer installation angle ζ, and the above range is determined to be 54 degrees ≦ γin ≦ 67 degrees. Note that the noise level increase upper limit is set to 0.5 dB (A) in view of the measurement error of the noise level. By defining the stabilizer installation angle ζ as described above, it is possible to optimize the blow-off diversion in the vicinity of the stabilizer portion 26 of the fan 36 that contributes particularly to the noise of the fan blower system, and to reduce the noise energy of the fan blower system. Can be suppressed.

  The above-described improvement effect can be obtained by optimizing the fan blower system with the above-mentioned definition.

  The heat exchanger in the present embodiment is not limited to the plate fin tube type heat exchanger in which three rows of the refrigerant tubes having a diameter of 5 mm are arranged in the thickness direction, and for example, a refrigerant having a diameter of 7 mm having a slightly higher resistance. It may be a plate fin tube type heat exchanger in which tubes are arranged in two rows in the thickness direction. Furthermore, if it is a heat exchanger having a ventilation resistance such that up to six rows of refrigerant tubes having a diameter of 5 mm are arranged in the thickness direction, the effect of optimizing the fan blower system according to the above-described provision can be obtained. For example, a plate fin tube type heat exchanger in which three rows of refrigerant tubes having a diameter of 5 mm are arranged in the thickness direction and a plate fin tube type heat exchanger in which one row of refrigerant tubes having a diameter of 7 mm are arranged in the thickness direction are secondary. Even in the case where the heat exchangers are used in an overlapping manner, the ventilation resistance is within the range of optimization of the fan blower system according to the above-mentioned regulations.

(Embodiment 2)
The present embodiment has the same form as that of the first embodiment except for the contents of the feature parts described below. FIG. 8 is a cross-sectional view illustrating a schematic configuration of the indoor unit 1 of the air conditioner according to the present embodiment. As shown in FIG. 8, in the present embodiment, the top side wall surface 28 a of the diffuser portion 28 has a bent portion 29 in the vicinity of the outlet (near the installation position of the horizontal louver). The bent portion 29 is located on the front side of the downstream end Q of the bottom side wall surface 28b of the diffuser portion 28. The upstream side wall surface of the top surface side wall surface 28a located on the upstream side of the bent portion 29 forms a diffuser flow path having a constant opening angle η with the bottom surface side wall surface 28b. The downstream side wall surface 29a of the top surface side wall surface 28a located on the downstream side of the bent portion 29 is inclined to the front surface (toward the top surface) by an angle κ with respect to the upstream side wall surface 28b. On the other hand, it has a larger opening angle (η + κ) than the upstream side. Further, when the angle formed between the upstream side wall surface and the horizontal plane is λ1, and the angle formed between the downstream side wall surface 29a and the horizontal plane is λ2, the relationship of λ1 <λ2 is established.

  In the indoor unit of an air conditioner having the above-described configuration, the following advantages can be obtained. Conventionally, when the top side wall surface 28a is extended further downstream than the downstream side end portion Q of the bottom side wall surface 28b of the diffuser portion 28, the flow along the bottom side wall surface up to the upstream in the extension portion is obtained. Since the flow is biased toward the top surface and the flow width is reduced, the effect of the diffuser up to the upstream side is impaired and the flow resistance is also caused. Therefore, by providing the bent portion 29 as described above, the flow along the top surface side wall surface 28a can be given a function as a channel further expanding downstream from the bent portion 29. The effect of the diffuser can be further continued, and the flow path resistance as described above can be suppressed. Note that the angle κ is preferably about 15 to 25 degrees so that it does not cause separation of the flow at the bent portion 29 and works as a diffuser.

  In addition, when λ1 <λ2 as described above, it is possible to add momentum in the horizontal or top direction to the cool air by the diffuser effect after the bent portion, particularly when the cool air is blown during the cooling operation. The sag of the cool air afterwards can be alleviated as much as possible.

  In addition, the said embodiment disclosed this time is an illustration in all the points, Comprising: It does not become the basis of limited interpretation. Therefore, the technical scope of the present invention is not interpreted only by the above-described embodiments, but is defined based on the description of the claims. Further, all modifications within the meaning and scope equivalent to the scope of the claims are included.

It is sectional drawing which shows the schematic structure of the indoor unit in Embodiment 1 based on this invention. It is sectional drawing which shows the structure of the principal part regarding the fan ventilation system of the indoor unit in Embodiment 1 based on this invention. It is a figure for demonstrating the effect | action of the indoor unit in Embodiment 1 based on this invention, and is a figure which shows the relationship between a suction direction angle and the air volume in the operating point of a fan ventilation system. It is a figure for demonstrating the effect | action of the indoor unit in Embodiment 1 based on this invention, and is a figure which shows the relationship between a suction direction angle | corner and the passing air volume in the back side of the heat exchanger in the operating point of a fan ventilation system. It is. It is a figure for demonstrating the effect | action of the indoor unit in Embodiment 1 based on this invention, and is a figure which shows the relationship between a blowing direction angle and the air volume in the operating point of a fan ventilation system. It is a figure for demonstrating the effect | action of the indoor unit in Embodiment 1 based on this invention, and is a figure which shows the relationship between a blowing direction angle | corner and the passing air volume in the back side of the heat exchanger in the operating point of a fan ventilation system. It is. It is a figure for demonstrating the effect | action of the indoor unit in Embodiment 1 based on this invention, and is a figure which shows the relationship between a stabilizer installation angle and the noise level of a fan ventilation system. It is sectional drawing which shows the structure of the principal part regarding the blower outlet periphery of the indoor unit in Embodiment 2 based on this invention. It is sectional drawing which shows schematic structure of the indoor unit of the air conditioner in background art.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Indoor unit, 2 Indoor unit case, 3 Heat exchanger, 4 Cross flow fan, 5 Dust collection filter, 21 Exterior surface, 22 Back surface, 23 Air duct, 24 Air inlet, 25 Air outlet, 26 Stabilizer part, 26a Stabilizer 28a diffuser part, 28a diffuser part top side wall surface, 28b diffuser part bottom side wall surface, 29 diffuser part top side wall surface bent part, 29a Downstream side wall surface of the bent portion, 31 Lower front portion of the heat exchanger, 32 Upper front portion of the heat exchanger, 33 Upper upper portion of the heat exchanger, 34 Lower lower portion of the heat exchanger, 35 Refrigerant pipe, 36 fins, 37 front side heat exchanger group, 38 back side heat exchanger group, 41 wing, 61 longitudinal louver, 62 lateral louver.

Claims (7)

A crossflow fan for sucking room air from the suction port and blowing it out from the blowout port, and located in the upstream side of the crossflow fan, mainly disposed in the flow of air from the front side of the suction port toward the crossflow fan The first heat exchanger, the second heat exchanger disposed in the flow of air mainly from the back side of the suction port toward the cross flow fan, and the vicinity and the downstream side of the cross flow fan And an air conditioner indoor unit having a ventilation duct having a stabilizer part and a rear guide part, the suction opening angle being smaller than the heat exchanger surrounding angle,
Lc is a line segment connecting the tip of the stabilizer portion close to the fan and the axial center of the crossflow fan,
A line segment connecting an intersection point P between the extension line at the upper end of the first heat exchanger and the extension line at the upper end of the second heat exchanger and the axial center of the cross flow fan is defined as Lp, and the line segment Lc. And the line segment Lp is 100 degrees to 140 degrees, and the bisector of the opening angle formed between the top side wall surface and the bottom side wall surface of the diffuser part is Lm, and the line segment Lp An indoor unit of an air conditioner, wherein an angle formed with the bisector Lm is 130 degrees or less.   The indoor unit of the air conditioner according to claim 1, wherein an angle formed by the line segment Lc and the line segment Lp is 115 degrees to 130 degrees.   The indoor unit of the air conditioner according to claim 1, wherein an angle formed by the line segment Lp and the bisector Lm is 100 degrees to 120 degrees.   A line segment connecting the upstream end of the stabilizer section and the axial center of the crossflow fan is La, and an angle formed by the line La and the line segment Lc is 0 degree to 10 degrees. The indoor unit of the air conditioner according to any one of claims 1 to 3.   The indoor unit of an air conditioner according to any one of claims 1 to 4, wherein an installation angle formed by a top side wall surface of the diffuser part and the stabilizer part is 54 to 67 degrees. . Having a bent part on the top side wall surface of the diffuser part;
The bent portion is located on the front side of the downstream side end portion of the bottom side wall surface of the diffuser portion, and the top side wall surface downstream of the bent portion has a larger opening angle than the upstream top side wall surface. The indoor unit for an air conditioner according to any one of claims 1 to 5, wherein the indoor unit is an air conditioner.   The air conditioner according to claim 6, wherein an angle formed by a downstream side wall surface of the top surface side wall surface with a horizontal plane is larger than an angle formed by an upstream side wall surface of the top surface side wall surface with a horizontal surface. Indoor unit.

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