JP2007170308A - Indoor unit of air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem of possibility of significant deterioration in blowing performance or increase in turbulence noise, in a fan blowing system under the conventional design standard when the conventional art has a problem of substantial ventilation resistance. <P>SOLUTION: An indoor unit of an air conditioner comprises: a cross-flow fan sucking indoor air from a suction opening and blowing the air from a supply opening; a first heat exchanger disposed in a flow of the air flowing mainly from a front face side of the suction opening toward the cross-flow fan, and a second heat exchanger disposed in the flow of the air mainly flowing from a back face side of the suction opening toward the cross-flow fan, which are positioned upstream of the cross-flow fan; and a fan duct positioned upstream of the cross-flow fan and provided with a stabilizer part and a rear guide part. A diameter ratio of a blade of the cross-flow fan is 0.720 to 0.800, and a stagger angle of the blade of the cross-flow fan is 22 degrees to 30 degrees. <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 particular, the indoor unit having a wall-hanging type is 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 intended to improve the heat transfer efficiency by increasing the surface area of the heat exchanger 3 while keeping the volume of the indoor unit 1 as compact as possible as much 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, if the conventional design for the cross flow fan and the air flow path is maintained, the air blowing operation is performed at an operating point far from the maximum efficiency point of the fan air blowing system due to the excessive ventilation resistance. Therefore, the energy consumption in the fan blower system is increased unnecessarily, and sometimes the energy consumption increases to the extent that the energy saving effect due to the heat transfer performance of the heat exchanger can be offset. Moreover, the tendency is more remarkable when the above accessories are present. Also, with regard to noise, a large air loss occurs by performing the air blowing operation at an operating point far from the maximum efficiency point of the fan air blowing system, leading to an increase in turbulent noise.

  Therefore, in the indoor unit of an air conditioner having a considerably large ventilation resistance as described above, in order to appropriately perform its function, the fan blower system is considerably improved, and the air volume and noise It was necessary to improve the aerodynamic performance. In addition, it can be expected that the fan blowing system has different air blowing characteristics from the conventional one, and a more suitable heat exchanger configuration that suppresses the negative influence on the blowing performance as much as possible in accordance with the air blowing characteristics. It was necessary to consider.

  The present invention has been made in view of the above circumstances, and optimizes the fan blower system (cross flow fan and blower path) formed in the indoor unit of the air conditioner having a considerable draft resistance to a large extent. The purpose is to provide a design guideline for improving the performance and a method of configuring an appropriate heat exchanger by the fan blower system.

In order to achieve the above object, the present invention provides the following means.
In the indoor unit of the air conditioner according to the present invention, a cross flow fan for sucking room air from the indoor unit suction port and blowing it out from the blower outlet, and located upstream of the crossflow fan, mainly the front surface of the suction port A first heat exchanger disposed in the air flow from the side toward the cross flow fan, and a second heat exchanger disposed in the air flow from the back side of the suction port toward the cross flow fan. An air conditioner indoor unit comprising a heat exchanger and an air duct that is located upstream of the cross flow fan and has a stabilizer part and a rear guide part, and the inner / outer diameter ratio of the blades of the cross flow fan Is set to be 0.720 to 0.800, and the angle difference between the blades of the cross flow fan is set to 22 degrees to 30 degrees.

  According to this configuration, by optimizing the inner / outer diameter ratio of the cross-flow fan and the staggered angle, the air blowing performance of the fan air blowing system itself is improved and the operating point is not greatly deviated from the maximum efficiency point. By keeping the flow loss as low as possible and maintaining an appropriate flow field, it is possible to ensure a considerably large air volume.

  Further, in the indoor unit of the air conditioner, the inner / outer diameter ratio of the blades of the cross flow fan is further set to 0.750 to 0.760.

  According to this configuration, it is possible to optimize the length of the blades of the crossflow fan with respect to the passing air amount and the passing air speed of the fan air blowing system, and it is possible to increase the air amount at the operating point.

  Moreover, in the indoor unit of the air conditioner, the crossing angle of the blades of the crossflow fan is further set to 23 degrees to 26 degrees.

  According to this configuration, it is possible to optimize the angle of attack of the blades with respect to the passing air amount and the passing air speed in the cross flow fan, and the air blowing performance of the fan air blowing system can be improved.

  Further, in the indoor unit of the air conditioner, a line segment La connecting a tip end portion close to the fan of the stabilizer portion and an axis center of the cross flow fan, a bent portion of the rear guide portion, and the cross flow fan The angle formed by the line segment Lb connecting the axis center is 160 to 170 degrees.

  According to this configuration, by optimizing the suction opening angle of the fan blower system, it is possible to optimize the suction side area with respect to the suction air volume in the fan blower system, and to improve the efficiency performance of the fan blower system. Can do.

  Further, in the indoor unit of the air conditioner, a tangent line Lin at the inner peripheral end of the warp line of the blade of the cross flow fan, and a line segment connecting the inner peripheral end of the blade and the axial center of the cross flow fan 4 The angle formed by Li is set to -3.5 degrees to 4.5 degrees.

  According to this configuration, by optimizing the inner peripheral angle of the crossflow fan, the kinetic energy applied to the blown air per unit rotation of the fan is optimized with respect to the passing air amount and the passing air speed in the crossflow fan. And the air blowing performance of the fan air blowing system can be enhanced.

  In the indoor unit of the air conditioner, an installation angle formed between the top side wall surface of the diffuser part and the stabilizer part is set to 54 degrees to 67 degrees.

  According to this configuration, by optimizing the fan fan system stabilizer installation angle, it is possible to optimize the blow-off diversion in the vicinity of the fan stabilizer, which particularly contributes to the fan fan system noise. The noise energy of the system can be suppressed.

  In the indoor unit of the air conditioner, the stabilizer installation angle is optimized, the tangent line Lout at the outer peripheral end of the warp line of the blade of the crossflow fan, the outer peripheral end of the blade and the crossflow fan The angle formed by the line segment Lo connecting the axis centers of the axes is 57 to 61 degrees.

  According to this configuration, by optimizing the outer peripheral angle of the cross flow fan, it is possible to optimize the exit angle of the blade with respect to the blowing air direction defined by the stabilizer installation angle ζ, and at the operating point. The air volume can be increased.

  Moreover, in the indoor unit of the air conditioner, an opening angle of the diffuser formed by the top side wall surface and the bottom side wall surface of the diffuser portion is set to 18 degrees to 23 degrees.

  According to this configuration, by optimizing the diffuser opening angle of the fan blower system, it is possible to optimize the static pressure recovery at the diffuser portion.

  In the indoor unit of the air conditioner, an intersection P between an extension line of the upper end of the first heat exchanger and an extension line of the upper end of the second heat exchanger, and an axial center of the cross flow fan The connecting line segment is Lp, and the angle formed by the line segment La and the line segment Lp is 105 degrees to 135 degrees.

  According to this configuration, by optimizing the suction direction angle of the fan blower system, it is possible to optimize the arrangement of the heat exchanger with respect to the suction direction of the fan blower system, and to reduce the air volume at the operating point. An increase can be aimed at.

  In the indoor unit of the air conditioner, the diameter of the refrigerant pipe of the first heat exchanger is larger than the diameter of the refrigerant pipe of the second heat exchanger.

  According to this configuration, particularly at the lower front side and the upper front side of the heat exchanger, both the heat transfer performance of the heat exchanger and the passing air speed of the heat exchanger are preferably improved, and heat exchange can be performed more effectively than before. Can be done. At the same time, the average passing wind speed at all parts of the heat exchanger can be averaged, and a suction wind speed distribution suitable for the fan blower system can be realized. For this reason, it is possible to suppress a decrease in the air volume as compared with the increase in the airflow resistance of the heat exchanger, and it is possible to realize a generally favorable blowing performance.

  In the indoor unit of the air conditioner, the diameter of the refrigerant pipe of the second heat exchanger is larger than the diameter of the refrigerant pipe of the first heat exchanger.

  According to this configuration, heat transfer performance can be improved overall in all parts of the heat exchanger, and energy saving can be achieved in the entire indoor unit.

  Moreover, in the indoor unit of the air conditioner, an accessory that requires air ventilation is provided on the front side of the first heat exchanger, and one or more means of the above-described configurations are provided.

  According to this configuration, the average passing wind speed in each part of the heat exchanger can be further averaged, and the suction wind speed distribution suitable for the fan blower system can be realized, thereby suppressing the influence of the ventilation resistance due to the accessory as much as possible. It is preferable in the sense that it is possible.

  According to the configuration of the present invention, even in an indoor unit of an air conditioner having a considerably large ventilation resistance, suitable air blowing that has a better maximum efficiency point and does not deviate greatly from the maximum efficiency point. A fan blower system having performance can be easily designed. In addition, by applying the heat exchanger configuration method described in the present invention to the fan blower system, further excellent heat transfer performance is achieved, and the effect of energy saving in the entire indoor unit of the air conditioner is realized. be able to.

  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 reference numerals are assigned to the same parts, and redundant description 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 the indoor unit of 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 horizontal louver 62, a cross flow inside an indoor unit case 2. It has a configuration having a motor (not shown) for driving the 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 front flow lower side 31, the front upper side 32, the rear upper side 33, and the rear lower side 34 so as to surround the cross flow fan, respectively. 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 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 in all of the four parts 31 to 34. Therefore, the ventilation resistance per unit region in each of the parts 31 to 34 is the same.

  Next, characteristic portions of the present invention will be described with reference to FIGS. FIG. 2 is a cross-sectional view showing details of the configuration of the crossflow fan 4 and the air duct 23, and FIG. 3 is a cross-sectional view showing details of the configuration of the crossflow fan 4.

  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 closest to the fan near the upstream end portion. 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.

  Here, the ratio (Db / Da) of the diameter Da of the arc passing through the outer peripheral end of the blade 41 of the crossflow fan 4 and the diameter Db of the arc passing through the inner peripheral end of the blade 41 is defined as an inner / outer diameter ratio α. A line segment connecting the outer peripheral end of the blade 41 of the crossflow fan 4 and the axis center of the crossflow fan 4 is Lo, and a line segment connecting the outer peripheral end and the inner peripheral end of the blade 41 of the crossflow fan 4 is Lw. The angle formed by Lw and Lw is the eating angle β. Further, a line segment connecting the sharp end 26a of the stabilizer 26 and the axial center of the cross flow fan 4 is La, and a line segment connecting the bent portion 27a of the rear guide 27 and the axial center of the cross flow fan 4 is shown. Is Lb, and the angle formed by La and Lb is the suction opening angle θ.

  Further, a tangent at the outer peripheral end of the warp line of the blade 41 of the cross flow fan 4 is Lout, and an angle formed by Lo and Lout is an outer peripheral angle γout. Further, Lin is a tangent line at the inner peripheral end of the warp line of the blade 41 of the cross flow fan 4 and Li is a line segment connecting the inner peripheral end of the blade 41 of the cross flow fan 4 and the axial center of the cross flow fan 4. An angle formed by Li and Lin is defined as an inner peripheral angle γin. 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. Further, the intersection 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 axis center of the cross flow fan 4 Let Lp be the line segment connecting the two, and let the angle formed by La and Lp be the suction direction angle φ.

  In such a fan blower system, in the present embodiment, design guidelines are defined as described below for α, β, θ, γout, γin, ζ, η, and φ.

  The inner / outer diameter ratio α is set to 0.720 to 0.800 (that is, 0.720 ≦ α ≦ 0.800). FIG. 4 shows the relationship between α and the air volume at the operating point of the fan blower system. According to FIG. 4, it can be seen that the air volume is the largest when α is approximately 0.753, and that the air volume decreases in any direction when α is increased or decreased. Accordingly, the range from α at which the air volume at the operating point is the maximum to the 2% air volume is determined to be an appropriate design range of the inner / outer diameter ratio α, and when the range is determined, the above 0.720 ≦ α ≦ 0. .800. By setting the lower limit width of the air volume to 2%, it is possible to ensure the desired air blowing performance.

  More desirably, when the inner / outer diameter ratio α is set to 0.750 to 0.760 (that is, 0.750 ≦ α ≦ 0.760), the air volume at the operating point is 0.5% from the air volume having the largest air volume. It can be specified in the range until it falls. Here, the lower limit width of the air volume is set to 0.5% in view of the fluctuation of the operating point for each experiment and the measurement error of the air volume.

  By defining the inner / outer diameter ratio α as described above, it is possible to optimize the length of the blade 41 with respect to the passing air amount and the passing air speed of the fan air blowing system, and to increase the air amount at the operating point.

  Next, the eating angle β is set to 22 degrees to 30 degrees (that is, 22 degrees ≦ β ≦ 30 degrees). FIG. 5 shows the relationship between β and the air volume at the highest efficiency point of the fan blower system. According to FIG. 5, it can be seen that when β is approximately 24 degrees, the air volume at the highest efficiency point increases most, and when β is increased or decreased, the air volume decreases in any direction. Accordingly, the range from β at which the air volume at the maximum efficiency point is the largest to the 3% air volume is determined to be an appropriate design range for the stagger angle β, and the above range is determined to be 22 degrees ≦ β ≦ 30. It will be a degree. By setting the lower limit width of the air volume to 3%, it is possible to ensure the desired air blowing performance.

  More preferably, if the eating angle β is 23 degrees to 26 degrees (that is, 23 degrees ≦ β ≦ 26 degrees), the fan air blowing system has the highest air volume at the highest efficiency point, and the 1% air volume is from β. The range until it falls can be defined. Here, the reason why the lower limit width of the air volume is set to 1% is in consideration of the calculation error of the maximum efficiency point and the measurement error of the air volume. By defining the eating angle β as described above, it is possible to optimize the angle of attack of the blades with respect to the passing air amount and the passing air speed in the fan 36, and to improve the air blowing performance of the fan air blowing system.

  Next, the suction opening angle θ is set to 160 to 170 degrees (that is, 160 degrees ≦ θ ≦ 170 degrees). FIG. 6 shows the relationship between θ and the efficiency at the highest efficiency point of the fan blower system. According to FIG. 6, it can be seen that when θ is approximately 165 degrees, the efficiency value at the highest efficiency point is the largest, and when θ is increased or decreased, the efficiency value decreases in any direction. Accordingly, when the range from the highest efficiency θ at the maximum efficiency point to the value of the maximum efficiency being reduced by 0.2% is determined as an appropriate design range of the suction opening angle θ, the above range is obtained. That is, degree ≦ θ ≦ 170 degrees. The reason why the lower limit of the maximum efficiency is set to 0.2% is that in consideration of the measurement error of the output and the shaft power that are the data for calculating the efficiency. By defining the suction opening angle θ as described above, it is possible to optimize the suction side area with respect to the suction air volume in the fan air blowing system, and to improve the efficiency performance of the fan air blowing system.

  Next, the inner peripheral angle γin is set to −3.5 degrees to 4.5 degrees (that is, −3.5 degrees ≦ γin ≦ 4.5 degrees). FIG. 7 shows the relationship between γin and the pressure head at the highest efficiency point of the fan blower system. According to FIG. 7, when the value of γin is approximately 1 degree, the value of the pressure head at the highest efficiency point increases, and when the value of γin is increased or decreased, the value of the pressure head at the highest efficiency point decreases in any direction. Is solved. Accordingly, the range from γin having the highest pressure head value at the highest efficiency point to the 5% pressure head being lowered is determined as an appropriate design range of the inner circumferential angle γin, and the range is calculated as described above in -3. It is 5 degrees ≦ γin ≦ 4.5 degrees. Note that the lower limit width of the pressure head at the highest efficiency point is set to 5% in view of the measurement error of the pressure head. By defining the inner circumferential angle γin as described above, it is possible to optimize the kinetic energy imparted to the blown air per unit rotation of the fan with respect to the passing air amount and the passing air speed in the fan 36, and The air blowing performance can be improved.

  Next, the stabilizer installation angle ζ is set to be 54 ° to 67 ° (that is, 54 ° ≦ ζ ≦ 67 °). FIG. 8 shows the relationship between ζ and the noise level of this fan blower system. According to FIG. 8, 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.

  Next, in the appropriate design range (54 degrees ≦ ζ ≦ 67 degrees) of the stabilizer installation angle ζ, the outer peripheral angle γout is set to 57 degrees to 61 degrees (that is, 57 degrees ≦ γout ≦ 61 degrees). FIG. 9 shows the relationship between γout and the air volume at the operating point of the fan blower system. According to FIG. 9, it can be seen that when γout is approximately 59 degrees, the air volume is greatest, and when γout is increased or decreased, the air volume decreases in any direction. Therefore, the range from γout having the largest airflow at the operating point to the 0.5% airflow reduction is determined as an appropriate design range of γout, and when the range is obtained, the above 57 degrees ≦ γout ≦ 61 degrees. It becomes. The reason why the lower limit width of the air volume is set to 0.5% is in consideration of the fluctuation of the operating point for each experiment and the measurement error of the air volume. By defining the outer peripheral angle γout with respect to the appropriate design range of the stabilizer installation angle ζ as described above, it is possible to optimize the exit angle of the blade 41 with respect to the blowing air direction defined by the stabilizer installation angle ζ. The air volume at the operating point can be increased.

  Next, the diffuser opening angle η is set to 18 degrees to 23 degrees (that is, 18 degrees ≦ η ≦ 23 degrees). FIG. 10 shows the relationship between η and the pressure head at the operating point of the fan blower system. According to FIG. 10, it is understood that when η is approximately 21 degrees, the value of the pressure head at the operating point is the largest, and when η is increased or decreased, the value of the pressure head at the operating point decreases in any direction. Karu. Therefore, the range from η having the largest pressure head value at the operating point to the 5% drop of the pressure head is determined as an appropriate design range of the diffuser opening angle η, and when the range is obtained, the above 18 degrees ≦ η ≦ 23 degrees. Note that the lower limit width of the pressure head at the operating point is set to 5% in view of the measurement error of the pressure head. By defining the diffuser opening angle η as described above, it is possible to optimize the static pressure recovery at the diffuser portion 28.

  Next, the suction direction angle φ is set to 105 to 135 degrees (that is, 105 degrees ≦ φ ≦ 135 degrees). FIG. 11 shows the relationship between φ and the air volume at the operating point of the fan blower system. According to FIG. 11, 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. Accordingly, the range from φ with the largest air volume at the operating point to the 0.5% air volume drop is determined as an appropriate design range of φ, and when the range is obtained, the above 105 degrees ≦ φ ≦ 135 degrees It becomes. The reason why the lower limit width of the air volume is set to 0.5% is in consideration of the fluctuation of the operating point for each experiment and the measurement error of the air volume. By defining the suction direction angle φ as described above, it is possible to optimize the arrangement of the heat exchanger with respect to the suction direction of the fan blower system, and to increase the air volume at the operating point.

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

  Here, in FIG. 13, the average passing wind speed at the front lower side 31, front upper side 32, rear upper side 33, and rear lower side 34 of the heat exchanger 3 in each case of the present embodiment is shown by a bar graph. As shown in FIG. 13, since the air volume at the operating point is larger in the present embodiment than in the conventional case, the average passing wind speed is faster in all the parts by pushing, especially the front lower side 31 and the front upper side. It has the characteristic that the increase in the wind speed is large at 32 sites. Therefore, in any region from the lower front side 31 to the upper front side 32 of the heat exchanger 3, the accessory 7 having a relatively high ventilation resistance, such as an electric dust collector, is attached to the front side. That is, the average average passing wind speed can be further averaged, and a suction wind speed distribution suitable for the fan blower system can be realized, so that the influence of the ventilation resistance by the accessory 7 can be suppressed as much as possible. Suitable in terms.

  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. 12 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. 12, in the present embodiment, the front lower heat exchanger 31 and the front upper heat exchanger 32 are thicker than the refrigerant pipe 35 in the first embodiment, and the refrigerant pipe 35 having a diameter of 7 mm is in the thickness direction. In this configuration, two rows are arranged. Since the front lower heat exchanger 31 and the front upper heat exchanger 32 have a large diameter between the refrigerants 35, the surface area between the refrigerants 35 is large, so that the heat transfer coefficient between the air and the refrigerant is increased, but the ventilation resistance is increased. ing.

  Here, in FIG. 13, the front lower side 31, the front upper side 32, the rear upper side 33, and the rear lower side of the heat exchanger 3 in each case of the first embodiment and the second embodiment (this embodiment). The average passing wind speed at 34 is shown by a bar graph. As shown in FIG. 13, in the first embodiment, since the air volume at the operating point is larger than in the conventional case, the average passing wind speed is faster in all parts. The increase in the wind speed is large at the upper 32 portion. And in this 2nd Embodiment, although the ventilation resistance has become large in the site | part of the front lower side 31 and the front upper side 32, although average passing wind speed is smaller than 1st Embodiment, compared with the past. Remain big. Further, the average passing wind speed is slightly higher than that in the first embodiment on the back upper side 33 and the back lower side 34, and therefore the average passing wind speed at each part is averaged compared to the first embodiment. You can see that

  From the above, in the present embodiment, both the heat transfer performance of the heat exchanger 3 and the passing air speed of the heat exchanger 3 are preferably improved particularly in the lower front surface 31 and the upper front surface 32 of the heat exchanger 3. Thus, heat exchange can be performed more effectively than before. At the same time, the average passing wind speed at all parts of the heat exchanger 3 can be averaged, and a suction wind speed distribution suitable for the fan blower system can be realized. Therefore, it is possible to suppress a decrease in the air volume as compared with the increase in the airflow resistance of the heat exchanger 3, and it is possible to realize a favorable air blowing performance as a whole. Therefore, in the indoor unit 1 of the air conditioner in the present embodiment, both heat transfer performance and air blowing performance can be improved and energy saving in the entire indoor unit can be achieved.

  Further, in the present embodiment, in any region from the front lower side 31 to the front upper side 32 of the heat exchanger 3, air ventilation with relatively large ventilation resistance, such as an electric dust collector, is provided on the front side. The attachment of the required accessory 7 is preferable in the sense that the influence of the ventilation resistance due to the accessory 7 can be suppressed as much as possible because the average average passing wind speed can be further averaged.

(Embodiment 3)
The present embodiment has the same form as that of the first embodiment except for the contents of the feature parts described below.

  FIG. 14 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. 14, in the present embodiment, the back lower heat exchanger 34 and the back upper heat exchanger 33 are thicker than the refrigerant pipe 35 in the first embodiment, and the refrigerant pipe 35 having a diameter of 7 mm is in the thickness direction. In this configuration, two rows are arranged. Since the rear lower heat exchanger 34 and the rear upper heat exchanger 33 have a large diameter of the refrigerant pipe 35, the surface area of the refrigerant pipe 35 is large, so that the heat transfer coefficient between air and the refrigerant is increased, but the ventilation resistance is increased. ing.

  Here, FIG. 15 shows the front lower side 31, the front upper side 32, the rear upper side 33, and the lower rear side of the heat exchanger 3 in the respective cases of the first embodiment and the third embodiment (this embodiment). The average passing wind speed at 34 is shown by a bar graph. As shown in FIG. 15, in the first embodiment, since the air volume at the operating point is larger than in the prior art, the average passing wind speed is higher in all the parts by pushing, especially the front lower side 31 and the front upper side. The increase in the wind speed is large at 32 sites. And in this Embodiment, since the ventilation resistance is large in the site | part of the back lower side 34 and the back upper side 33, the average passing wind speed is lower than Embodiment 1, On the other hand, the front upper side 32 The average passing wind speed is larger at the front lower side 31 than in the first embodiment. For this reason, it can be seen that the average passing wind speed at each part is further biased toward the front lower side 31 and the front upper side 32 in comparison with the embodiment.

  From the above, in the present embodiment, heat exchange is performed more effectively than in the prior art by increasing the passing air speed, particularly at the lower front side 31 and the upper front side 32 of the heat exchanger 3. , The refrigerant pipe 35 is thickened at the rear upper side 33 and the lower rear side 34 where the average passing wind speed is relatively small to improve the heat transfer performance of the heat exchanger, so that the entire heat exchanger 3 can transfer heat. Thermal performance can be improved.

  Therefore, in the indoor unit 1 of the air conditioner according to the present invention, the deterioration of the blowing performance due to the thickening of the refrigerant pipe 35 in the back lower heat exchanger 34 and the back upper heat exchanger 33 is transmitted to the extent that it can sufficiently recover. Thermal performance can be improved, and energy saving can be achieved in the entire indoor unit.

  Further, in the present embodiment, in any region from the front lower side 31 to the front upper side 32 of the heat exchanger 3, the front side requires air ventilation such as an ion generator and the like relatively. Attaching the accessory 7 that exhibits suitable performance at a high wind speed contributes favorably to improving the performance of the accessory 7 and also contributes to the ventilation resistance of the accessory 7 in each part 31 to 34 of the heat exchanger. Since it works in the direction of averaging the average passing wind speed and works favorably in the fan blower system, it is preferable in the sense that the influence of the ventilation resistance by the accessory 7 can be suppressed 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 of 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 of Embodiment 1 based on this invention. It is sectional drawing which shows the structure of the principal part regarding the cross flow fan of the indoor unit of Embodiment 1 based on this invention. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between the inner / outer diameter ratio (alpha) and the air volume in the operating point of a fan ventilation system. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between the stagger angle (beta) and the air volume in the highest efficiency point of a fan ventilation system. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between suction opening angle | corner (theta) and the efficiency in the highest efficiency point of a fan ventilation system. It is a figure for demonstrating Embodiment 1 based on this invention, and is a figure which shows the relationship between the internal peripheral angle (gamma) in and the pressure head in the highest efficiency point of a fan ventilation system. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between the stabilizer installation angle (zeta) and the noise level of a fan ventilation system. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between outer peripheral angle (gamma) out and the air volume in the operating point of a fan ventilation system. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between the diffuser opening angle (eta) and the pressure head in the operating point of a fan ventilation system. It is a figure for demonstrating the effect | action of Embodiment 1 based on this invention, and is a figure which shows the relationship between the suction direction angle | corner (phi) and the air volume in the operating point of a fan ventilation system. It is sectional drawing which shows schematic structure of the indoor unit of Embodiment 2 based on this invention. It is the figure which showed the difference of the average passing wind speed in each location of the heat exchanger of Embodiment 2 based on this invention, background art, and Embodiment 1. FIG. It is sectional drawing which shows schematic structure of the indoor unit of Embodiment 3 based on this invention. It is the figure which showed the difference of the average passing wind speed in each location of the heat exchanger of Embodiment 3 based on this invention, background art, and Embodiment 1. FIG. 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, 4 Cross flow fan, 5 Filter for dust collection, 7 Accessories (requires ventilation of air), 21 Exterior surface, 22 Back surface, 23 Air duct, 24 Air inlet, 25 Air outlet, 26 Stabilizer part, 26a Pointer part of stabilizer part, 27 Rear guide part, 27a Bent part of rear guide part, 28 Diffuser part, 28a Top side wall surface of diffuser part, 28b Bottom side wall face of diffuser part, 3 Heat exchanger, 31 Lower part of the front surface of the heat exchanger 3, 32 Upper part of the front surface of the heat exchanger 3, 33 Upper part of the back surface of the heat exchanger 3, 34 Lower part of the back surface of the heat exchanger 3, 35 Refrigerant tube, 36 Fin, 37 Front side heat exchanger group, 38 Back side heat exchanger group, 41 wings, 61 longitudinal louver, 62 lateral louver.

Claims (12)

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, is arranged in the air flow mainly from the front side of the suction port toward the crossflow fan A first heat exchanger, a second heat exchanger disposed mainly in the flow of air from the back side of the suction port toward the cross flow fan, and a position near and downstream of the cross flow fan. An air conditioner indoor unit comprising a stabilizer duct and a fan duct having a rear guide part,
The interior of the air conditioner is characterized in that an inner / outer diameter ratio of the blades of the crossflow fan is 0.720 to 0.800, and an odd angle of the blades of the crossflow fan is 22 degrees to 30 degrees. Machine.   The indoor unit of an air conditioner according to claim 1, wherein the inner / outer diameter ratio of the blades of the cross flow fan is further 0.750 to 0.760.   The indoor unit of an air conditioner according to claim 1, wherein the angle difference between the blades of the crossflow fan is 23 to 26 degrees.   A line segment La connecting the tip of the stabilizer portion close to the fan and the axial center of the cross flow fan, and a line segment Lb connecting the bent portion of the rear guide portion and the axial center of the cross flow fan are formed. The indoor unit of an air conditioner according to any one of claims 1 to 3, wherein the angle is 160 degrees to 170 degrees.   The angle formed by the tangent line Lin at the inner peripheral end of the warp line of the blade of the cross flow fan and the line segment Li connecting the inner peripheral end of the blade and the axial center of the cross flow fan is −3.5 degrees to It is 4.5 degree | times, The indoor unit of the air conditioner in any one of Claim 1 to 4 characterized by the above-mentioned.   The indoor unit of an air conditioner according to any one of claims 1 to 5, wherein an installation angle formed by the top side wall surface of the diffuser part and the stabilizer part is 54 to 67 degrees.   The angle formed between the tangent Lout at the outer peripheral edge of the warp line of the blade of the crossflow fan and the line Lo connecting the outer peripheral edge of the blade and the axial center of the crossflow fan is 57 to 61 degrees. The indoor unit of the air conditioner according to claim 6, wherein   The interior of the air conditioner according to any one of claims 1 to 7, wherein an opening angle of the diffuser formed by a top side wall surface and a bottom side wall surface of the diffuser portion is 18 degrees to 23 degrees. Machine.   A line segment connecting the intersection P of 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 Lp, and the line segment The indoor unit of the air conditioner according to any one of claims 1 to 8, wherein an angle formed by La and the line segment Lp is 105 to 135 degrees.   The air conditioner according to any one of claims 1 to 9, wherein the diameter of the refrigerant pipe of the first heat exchanger is larger than the diameter of the refrigerant pipe of the second heat exchanger. Indoor unit of the machine.   The air conditioner according to any one of claims 1 to 9, wherein the diameter of the refrigerant pipe of the second heat exchanger is larger than the diameter of the refrigerant pipe of the first heat exchanger. Indoor unit of the machine.   The indoor unit of an air conditioner according to any one of claims 1 to 11, wherein an accessory that requires air ventilation is provided on a front side of the first heat exchanger.

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