JP2015132425A - air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem that, in a conventional air conditioner, the seal performance of blown air at a drain pan portion of a lower stage of an indoor heat exchanger is not taken into consideration, air which is not heat-exchanged is liable to pass through a clearance between a drain pan and the heat exchanger, and thereby there arises a possibility that a heat exchange capacity of the heat exchanger becomes insufficient, and drain water is blown out and spilled by air blowing.SOLUTION: In an indoor heat exchanger 7, a lower part of an indoor heat exchanger 7a in a partial row is formed shorter than an indoor heat exchanger 7b in the other row so that the number of upper rows becomes larger than the number of lower rows, and a vertical dimension between a lower end 7h of a fin 7d contacting with a drain pan 11 and the piping 7f of the lowest stage of the indoor heat exchanger 7b in the other row is set at 1 mm or longer and not larger than a half of a clearance between the vertically-adjoining piping 7f.

Description

  The present invention relates to an air conditioner, and more particularly to a configuration of a heat exchanger and a drain pan of an indoor unit.

  Air conditioner indoor units use a turbofan that blows air sucked in from the suction port formed below the center to the outside in the radial direction, and heat exchange is performed to surround the outside in the radial direction. A drain pan is disposed so as to cover the lower part of the heat exchanger. (For example, refer to Patent Document 1).

Japanese Patent Laying-Open No. 2004-232952 (paragraph 0009, FIG. 2)

  However, in the conventional air conditioner, the width of the heat exchanger in the flow direction of the air blown by the turbo fan (blower) of the indoor unit is the same across the top and bottom, so the lower stage of the heat exchanger with a slow wind speed The heat exchange capacity may be insufficient in the heat exchanger, and the sealing performance of the air blown in the drain pan part at the lower part of the heat exchanger is not considered, so heat is exchanged between the drain pan and the heat exchanger. However, there is a problem that the air that has not been passed easily passes through and the heat exchange capacity of the heat exchanger is insufficient, or condensate water (drain water) may be blown out and blown out.

  The present invention has been made to solve such a problem, and can improve the sealing performance against air blowing at the drain pan portion of the lower stage of the heat exchanger, and can prevent the heat exchanger from having insufficient heat exchange capability. An object of the present invention is to obtain an air conditioner that can prevent condensed water (drain water) from being blown out by blowing air and spilling.

  An air conditioner according to the present invention includes a turbo fan that blows indoor air sucked from a lower suction port to a blow-out port provided around the suction port, and fins arranged in a plurality of stages of pipes arranged vertically. A plurality of rows of indoor heat exchangers formed so as to surround the turbofan and a drain pan provided so as to cover a lower portion of the indoor heat exchanger, The heat exchanger is formed such that the lower part of the indoor heat exchangers in some rows is shorter than the indoor heat exchangers in the other rows so that the number of upper rows is greater than the number of lower rows, The vertical dimension from the lowermost pipe of the exchanger to the lower end of the fin in contact with the drain pan is formed from 1 mm or more to ½ or less of the gap dimension of the pipe adjacent vertically.

  An air conditioner according to the present invention includes a turbo fan that blows indoor air sucked from a lower suction port to a blower outlet provided around the suction port, and a plurality of pipes arranged vertically. A plurality of rows of indoor heat exchangers that are formed by laminating fins and are provided so as to surround the periphery of the turbofan, and a drain pan that is provided so as to cover a lower portion of the indoor heat exchanger, The indoor heat exchanger is formed such that the lower part of the indoor heat exchanger in some rows is shorter than the indoor heat exchangers in other rows so that the number of upper rows is greater than the lower row number, The vertical dimension from the lowermost pipe of the indoor heat exchanger to the lower end of the fin contacting the drain pan is formed to be 1 mm or more and 3 mm or less.

  An air conditioner according to the present invention includes a turbo fan that blows indoor air sucked from a lower suction port to a blow-out port provided around the suction port, and fins in a plurality of stages of pipes arranged above and below. A plurality of rows of indoor heat exchangers formed so as to surround the turbofan and a drain pan provided to cover a lower portion of the indoor heat exchanger, the indoor heat The exchanger is formed such that the lower part of the indoor heat exchanger in some rows is shorter than the indoor heat exchanger in the other rows so that the number of upper rows is larger than the number of lower rows, and the indoor heat exchange in the other rows. Since the vertical dimension from the lowermost pipe of the vessel to the lower end of the fin in contact with the drain pan is formed from 1 mm or more to 1/2 or less of the gap dimension of the pipe adjacent to the upper and lower sides, Indoor heat exchanger with low flow rate Heat exchange is also promoted in the lower part, and deformation of the portion of the indoor heat exchanger that comes into contact with the drain pan is prevented, making it difficult to form a gap between the lower end of the indoor heat exchanger and the drain pan, and improving the sealing performance against blowing. Furthermore, it is possible to prevent a shortage of heat exchange capacity of the indoor heat exchanger. Moreover, it has the effect that it can prevent that drain water blows off from a drain pan by ventilation, and spills.

  Further, the air conditioner of the present invention includes a turbo fan that blows indoor air sucked from a lower suction port to a blower outlet provided around the suction port, and a plurality of pipes arranged vertically. A plurality of rows of indoor heat exchangers formed by laminating fins so as to surround the turbofan, and a drain pan provided so as to cover a lower portion of the indoor heat exchanger, The indoor heat exchanger is formed such that the lower part of the indoor heat exchangers in some rows is shorter than the indoor heat exchangers in other rows so that the number of upper rows is larger than the lower row number, Since the vertical dimension from the lowermost pipe of the heat exchanger to the lower end of the fin contacting the drain pan is 1 mm or more and 3 mm or less, the lower part of the indoor heat exchanger where the flow rate of the turbofan is slow is also heated. Exchange is promoted and The deformation of the portion of the indoor heat exchanger that comes into contact with the drain pan is prevented, making it difficult to form a gap between the lower end of the indoor heat exchanger and the drain pan, improving the sealing performance against air blowing, and further exchanging the heat of the indoor heat exchanger Insufficient capacity can be prevented. Moreover, it has the effect that it can prevent that drain water blows off from a drain pan by ventilation, and spills.

It is a perspective view which shows the whole general view of the indoor unit of the air conditioner by Embodiment 1 of this invention. It is a longitudinal cross-sectional view of the indoor unit which abbreviate | omits and shows the decorative panel of the air conditioner by Embodiment 1 of this invention. It is a longitudinal cross-sectional view which expands and shows the right half surface of FIG. 2 of the air conditioner by Embodiment 1 of this invention. It is a longitudinal cross-sectional view explaining the dimensional relationship of the indoor heat exchanger of FIG. 3 of the air conditioner by Embodiment 1 of this invention. It is a top view of the indoor heat exchanger seen from the up-and-down direction explaining the schematic structure of the whole heat exchanger of the air conditioner by Embodiment 1 of this invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a plan view of a part of an indoor heat exchanger as viewed from the top and bottom directions for explaining the interval dimensions of fins stacked along the piping of an indoor heat exchanger of an air conditioner according to Embodiment 1 of the present invention. . The room seen from the up-and-down direction explaining the space | interval dimension of the lamination | stacking of the fin laminated | stacked along the piping of the indoor heat exchanger of the air conditioner equivalent to FIG. 6 which shows the other example by Embodiment 1 of this invention It is a top view of a part of heat exchanger. It is a longitudinal cross-sectional view equivalent to FIG. 3 which shows another example by Embodiment 1 of this invention.

Embodiment 1.
Embodiment 1 of the present invention will be described below with reference to FIGS. FIG. 1 is a perspective view showing the overall appearance of an indoor unit of an air conditioner according to Embodiment 1 of the present invention. FIG. 2 is a longitudinal sectional view of the indoor unit of the air conditioner according to the first embodiment. FIG. 3 is an enlarged longitudinal sectional view of the right half surface of FIG. 2 of the air conditioner according to the first embodiment. 4 is a longitudinal sectional view for explaining the dimensional relationship of the indoor heat exchanger of FIG. 3 of the air conditioner according to the first embodiment. FIG. 5 is a plan view of the indoor heat exchanger as viewed from above and below, explaining the schematic configuration of the entire indoor heat exchanger of the air conditioner according to Embodiment 1. FIG. 6 is a plan view of a part of the indoor heat exchanger as viewed from above and below, explaining the dimensional relationship of the pitch of the fins stacked along the piping of the indoor heat exchanger of the air conditioner according to Embodiment 1. .

  As shown in the perspective view of FIG. 1, the air conditioner is composed of an indoor unit 1 and an outdoor unit (not shown). The outdoor unit is installed outdoors, and the indoor unit 1 is installed indoors. It performs air conditioning such as heating and cooling. This indoor unit 1 is formed by attaching an indoor unit main body 2 having an open bottom surface and a rectangular decorative panel 3 to the lower surface of the indoor unit main body 2 in this embodiment, and is installed on the ceiling of the room. And the indoor unit main body 2 is arrange | positioned on the back side of a ceiling surface, the decorative panel 3 is arrange | positioned on the ceiling surface, and it is installed beautifully so that only the decorative panel 3 can be seen on the ceiling.

  A suction port 4 for sucking air into the indoor unit 1 is provided in the vicinity of the center of the decorative panel 3, and a blower that blows out heat-exchanged air around each side (four sides) of the decorative panel 3 around the suction port 4. An outlet 5 is provided. Inside the indoor unit main body 2 is provided a turbo fan 6 that blows air sucked from a suction port 4 formed in the central portion of the indoor unit main body 2 radially outward with respect to the rotation axis. An indoor heat exchanger 7 (hereinafter referred to as a heat exchanger) is disposed so as to surround the outside in the radial direction. Further, the turbo fan 6 is rotated by a fan motor 6a disposed at the upper center of the indoor unit body 2, and the air sucked from the suction port 4 by the bell mouth 8 provided at the lower part of the indoor unit body 2 is shown in FIG. 3, as indicated by arrows 9 a to 9 d in FIG. 3, the air is sucked from below the turbo fan 6, blown out around the turbo fan 6 by the rotation of the blades of the turbo fan 6, and passes through the heat exchanger 7. Then, the air is exchanged and passes through the air passage 10 formed around the interior of the indoor unit body 2 so that the air is again blown out into the room from the outlets 5 on the four sides.

  Further, a drain pan 11 is disposed so as to cover the lower part of the heat exchanger 7, and moisture (drain water) of air cooled and dehumidified by the heat exchanger 7 during cooling or dehumidifying operation is discharged from the heat exchanger 7. The drain water is temporarily accumulated in the drain pan 11 and discharged to the outside by a drain pump or the like (not shown) so that the drain water does not leak into the room.

  Next, a detailed configuration of the indoor heat exchanger 7 will be described. In this embodiment, the heat exchanger 7 is used as the indoor heat exchanger in the first row on the upstream side, which is the windward side indicated by the air flow 9b along the air blowing direction of the turbo fan 6 that is the indoor heat exchanger in some rows. A second row of indoor heat exchangers 7b (hereinafter, referred to as the first row heat exchanger) and the downstream second row of indoor heat exchangers 7b (hereinafter referred to as the air flow 9c) that are the indoor heat exchangers of the other rows. The two rows (referred to as the second row heat exchanger) are laminated. The heat exchanger 7 has a thickness of, for example, about 0.05 mm to 0.15 mm so that the heat exchanger 7a in the first row and the heat exchanger 7b in the second row are made of a material such as aluminum and have good heat exchange efficiency. Flat plate-like fins 7c and 7d that are long in the upper and lower dimensions are formed by laminating in a plane direction that is a lateral direction with a slight gap so that air can pass along the pipes 7e and 7f provided in a plurality of upper and lower stages. Then, the indoor air passes through the gap between the fins 7c and 7d, so that heat is exchanged with the refrigerant flowing in the pipes 7e and 7f, thereby performing indoor cooling, dehumidification, and heating. If an example of the thickness dimension of the fins 7c and 7d is further shown, the long fins 7c and 7d having a thickness dimension of about 0.1 mm may be used.

  And when explaining the dimensional relationship of the heat exchanger 7 of this embodiment, the vertical height of the heat exchanger 7a in the first row on the windward side is made shorter than the height of the heat exchanger 7b in the second row, The heat exchanger 7 composed of a plurality of rows has an upper heat exchanger row number (two rows) larger than a lower heat exchanger row number (one row). That is, in the indoor heat exchanger 7 (heat exchanger), the lower part of the indoor heat exchanger 7a (first row heat exchanger) in some rows is placed in the other row so that the number of upper rows is larger than the lower row number. It is formed shorter than the row of indoor heat exchangers 7b (second row heat exchanger). This is because the air 9a sucked from the lower suction port 4 is blown in the peripheral direction 9b and 9c as indicated by arrows 9b and 9c in FIGS. Centrifugal force is generated, and the flow rate blown out by this centrifugal force is faster on the upper side than on the lower side. For this reason, the number of rows of the heat exchangers 7 on the upper side is increased from below so that the heat exchanger 7 on the upper side can sufficiently exchange heat.

  Further, the pipe 7e of the first row heat exchanger 7a and the pipe 7f of the second row heat exchanger 7b are made of copper material circular pipes in this embodiment, as shown in dimension A of FIG. As an example of the pipe diameter, an article having a diameter of about 5 mm to about 9 mm is often used. For example, a pipe having a diameter of about 7 mm may be used. When the upper and lower sizes of the heat exchanger 7 are described, the number of pipes arranged side by side above and below the pipes 7e and 7f is referred to as the number of stages. As shown in FIG. 4, the distance B between the centers of the pipes 7e, which is the interval between the steps, is referred to as a step pitch. In this example, the upper and lower stage pitch B dimensions of the respective pipes 7e and 7f are set to the same pitch dimension, for example, in both the first row heat exchanger 7a and the second row heat exchanger 7b. For example, the step pitch B dimension may be about 15 mm to 25 mm, and may be about 20 mm, for example.

  In addition, the pipes 7e and 7f having the same stage pitch (dimension B) of the heat exchanger 7a in the first row and the heat exchanger 7b in the second row are placed between the upper and lower stages of the pipe 7f of the heat exchanger 7b in the second row. The heat exchanger 7a and the pipe 7f are arranged so that the pipes 7e and 7f are alternately arranged in a staggered manner so that the pipes 7e and 7f do not overlap in the vertical direction. The air passing through the heat exchanger 7 is smoothly exchanged from the heat exchanger 7a in the first row to the heat exchanger 7b in the second row so as to be efficiently exchanged with the heat exchanger 7.

  Further, the width dimension of the heat exchanger 7a in the first row and the heat exchanger 7b in the second row are also set to the same width dimension in this embodiment as shown in the width dimension C. For example, when the diameters of the pipes 7e and 7f are about 7 mm, for example, the width C may be about 10 mm to 20 mm. As described above, in this embodiment, the heat exchanger 7a in the first row and the heat exchanger 7b in the second row have different upper and lower dimensions, but the same material has the same pipe diameter A size, step pitch B size, and width C size. Because it is sized, when manufacturing the first row of heat exchangers 7a and the second row of heat exchangers 7b, there are many parts that can share the same production equipment, and the heat exchanger 7 can be manufactured with good quality and at low cost. There is also an effect.

  In addition, compared to the case where the first row heat exchanger 7a and the second heat exchanger 7b are integrally formed, the equipment can be easily made, and even when a heat exchanger that requires a three row width is manufactured, It is only necessary to increase the number of rows to be stacked, and the equipment is simple and heat exchangers of various widths can be easily produced. Further, in the indoor unit 1 housed in the ceiling, as shown in the schematic overall configuration of the heat exchanger in FIG. 5, a case that is bent many times so as to surround the turbofan 6 (in this example, it is bent three times). There is also an effect that it is easy to perform bending work because it is divided into one row and divided like the first row heat exchanger 7a and the second row heat exchanger 7b.

  The stacking pitch in the plane direction of the heat exchanger 7a in the first row and the heat exchanger 7b in the second row is the same as shown in dimension J in FIG. An example of the stacking dimensions is an interval of about 1 mm to 2 mm. The stacking pitch (J dimension) between the fins 7c of the first row heat exchanger 7a and the fins 7d of the second row heat exchanger 7b is the same. Therefore, there is an effect that it is easier to make the heat exchanger 7.

  Next, the arrangement configuration of the fins 7d and the pipes 7f in the lower part of the second row heat exchanger 7b will be described. Inside the dish-shaped drain pan 11 provided to cover the lower part of the entire circumference of the heat exchanger 7 so as to receive all of the drain water dripped from the heat exchanger 7 is the lower part of the heat exchanger 7b in the second row. A bank portion 11a protruding upward is formed so as to contact the lower end 7h of the fin 7d. The height of the bank portion 11a is formed to be lower than the depth at which the drain water of the drain pan 11 can be accumulated, so that the drain water falling through the heat exchanger 7b in the second row is surely collected in the drain pan 11. In addition, the air blown out from the turbofan 6 so that there is no gap between the second row heat exchanger 7b and the drain pan 11 is not exchanged in the second row heat exchanger 7b. Passing (bypassing) between the lower end 7h and the drain pan 11 and passing without heat exchange with the second row heat exchanger 7b causes insufficient heat exchange capacity, or the second row heat exchanger 7b. The drain water in the drain pan 11 is wound up by the flow of wind passing between the lower part of the drain pan 11 and the drain pan 11, and the drain water is blown from the drain pan 6 or dropped from the second heat exchanger 7 b to the drain pan 11. To being blown up so that there is no such thing as drain water is blown out from the air outlet 5.

  However, as described above, the fins 7c and 7d of the heat exchanger 7 are parts made of a material that is easily deformed because they are formed of very thin aluminum or the like, and in particular, the heat exchanger that is in contact with the bank portion 11a. The lower end 7h of the heat exchanger 7b in the second row, which is the lower end of 7 is the cut end portion of the fin 7d and is easily deformable. When bent and deformed, the lower end 7h of the heat exchanger 7 There is a problem that there is a gap between the upper and lower sides of the drain pan 11 and air that is not heat-exchanged as described above may pass or the drain water may be blown from the drain pan 11 by blowing.

  For this reason, in this embodiment, in the lower end 7h portion of the second row heat exchanger 7b, which is the lower end of the heat exchanger 7, as shown in FIG. 4, the lowermost row of the second row heat exchanger 7b. The distance between the outer diameters of the pipes 7f adjacent to each other up and down is the D dimension from the lower end of the lowermost pipe 7f of the second row heat exchanger 7b to the lower end 7h of the fin 7d. The gap dimension E is shorter than half of the dimension E.

  That is, it is made smaller than the dimension obtained by subtracting the radius of the pipe 7f from the half of the step pitch B dimension. In this way, by shortening the D dimension from the lowermost line 7f of the heat exchanger 7b in the second row to the lower end 7h of the fin 7d, the lower end 7h part of the fin 7d is supported by the lowermost line 7f and deformed. It is difficult to prevent the lower end 7h of the fin 7d from deforming in the laminating direction of the fin 7d to form a gap between the lower end 7h of the heat exchanger 7 and the top and bottom of the drain pan 11, and heat is not exchanged as described above. There is an effect that it is possible to prevent the air from passing through or the drain water from being blown from the drain pan 11 due to the passing air.

  The D dimension from the lowermost pipe 7f of the heat exchanger 7b in the second row to the lower end 7h of the fin 7d is preferably as short as possible. That is, when the dimension is shorter than 1 mm, the portion where the fin 7d is connected is too small and the connected portion is weakened, and the fin 7d may be deformed when connected to the lowermost pipe 7f. It is preferable that the length is 1 mm or more and shorter than a half of the upper and lower clearance E between the pipes 7f.

In addition, when the D dimension from the lowermost pipe 7f of the heat exchanger 7b in the second row to the lower end 7h of the fin 7d is in the range of 1 mm to 3 mm, the lower end 7h of the fin 7d is effectively the fin 7d. It was possible to prevent deformation in the stacking direction, and to prevent a gap from being formed between the lower end 7 h of the heat exchanger 7 and the top and bottom of the drain pan 11. That is, the dimension D from the lowermost pipe 7f of the heat exchanger 7b in the second row to the lower end 7h of the fin 7d is weaker because there are too few connected portions if the dimension is shorter than 1 mm as described above. The fins 7d may be deformed when they are connected to each other, and if it is up to about 3 mm, even if the fins 7d have a very thin thickness, the lower end 7h of the fins 7d is simply the length of the pipe 7f. It was strong enough not to be deformed in the laminating direction of 7d.

  Further, the F dimension up to the uppermost pipe 7f of the second row heat exchanger 7b and the upper end 7k of the fin 7d will be described with reference to FIG. The F dimension between the uppermost pipe 7f of the second row heat exchanger 7b and the upper end 7k of the fin 7d is preferably formed long enough to exchange heat with the air from the turbofan 6, and the F dimension is two rows. The dimension may be longer than the dimension D from the bottom pipe 7f of the eye heat exchanger 7b to the lower end 7h of the fin 7d. That is, the upper end 7j of the first row heat exchanger 7a and the upper end 7k of the second row heat exchanger 7b are formed at the same height so that there is no gap in the upper portion of the heat exchanger 7. Since the upper row 7k of the second row heat exchanger 7b is slightly deformed, the first row heat exchanger 7a allows the air that is not heat exchanged to flow above the heat exchanger 7 even if the upper end 7k of the second row heat exchanger 7b is slightly deformed. The F dimension from the uppermost pipe 7f of the heat exchanger 7b in the second row to the upper end 7k of the fin 7d is 1 of the gap dimension E between the pipes 7f. It is good to set it as the dimension of the range longer than / 2, and the clearance gap dimension E dimension between the pipes 7f.

  Further, in the case of the heat exchanger 7a in the first row, the upper pipe 7e is arranged in the upper and lower height ranges of the F dimension to the uppermost pipe 7f and the upper end 7k of the fin 7d in the second row heat exchanger 7b. Thus, the dimension from the uppermost line 7e of the heat exchanger 7a of the first row to the upper end 7j of the fin 7c is changed from the pipe 7f of the lower end 7h of the heat exchanger 7b to the lower end 7h of the fin 7d. Similarly to the D dimension, if the G dimension is 1 mm or more and shorter than half the E dimension between the pipes 7f, the upper end 7j of the fin 7c can be prevented from being deformed, and the upper ends 7j and 7k of the heat exchanger 7 can be prevented. In addition, it is possible to further prevent air that is not heat-exchanged at the upper part of the heat exchanger 7 from being blown to the outlet 5 side. In particular, the G dimension is set to 1 mm or more and 3 mm or less like the D dimension. If the upper end 7j portion of the fin 7c is efficiently prevented Can heat exchanger 7 the upper end 7j of the effect of obtained it can hardly a gap between the 7k and indoor unit upper part of the main body 2.

  In addition, the dimension H1 for shortening the lower portion of the heat exchanger 7a in the first row so that the number of rows in the flow direction of the air flow at the upper portion of the heat exchanger 7 is larger than the lower portion will be described. As shown in FIG. 3 to FIG. 4, for example, the dimension H1 indicates that the height of the lower end 7g portion of the first row heat exchanger 7a is higher than the height of the lower end 7h portion of the second row heat exchanger 7b. The height of the step pitch B may be about 2 to 5 steps (2 to 5 times the step pitch B size of the pipe 7f). In this embodiment, the height is about 4 steps. An example of the height is shown. The vertical dimension of the heat exchanger 7a in the first row is the vertical dimension (H3 dimension) of the turbo fan sending section 6b in which the turbo fan 6 blows air around the side as shown by the dimensions H2 and H3 in FIG. ), The heat can be exchanged efficiently. In other words, as shown in the dimension H2, the position of the lower end 7g of the fin 7c is preferably formed so as to be shorter than the position of the lower end 6c of the blower portion of the turbofan 6 above and below the heat exchanger 7b in the second row. .

  Thus, the turbo fan which is provided in the indoor unit main body 2 and blows out indoor air sucked from the lower central suction port 4 to the side and blows it to the blower outlet 5 provided around the suction port 4. And a heat exchanger 7 formed so as to surround the periphery of the turbofan 6 by pipes 7e and 7f provided in a plurality of upper and lower stages and fins 7c and 7d stacked on the pipes 7e and 7f, and indoor heat exchange An air conditioner 1 having a drain pan 11 provided so as to cover the lower part of the heat exchanger 7, wherein the number of upper rows in the blowing direction of the heat exchanger 7 is larger than the number of lower rows. The heat exchanger 7b in the second row of the heat exchanger 7 is arranged so as to be in contact with the drain pan 11, and the distance from the lowermost pipe 7f of the heat exchanger 7b in the second row in contact with the drain pan 11 to the lower end 7h of the fin 7d Up and down between 1mm and pipe 7f Since the gap dimension E is ½ or less of the dimension E, the lower end 7h of the fin 7d is supported by the lowermost pipe 7f and is difficult to deform, and the lower end 7h of the fin 7d is deformed in the laminating direction of the fin 7d. Thus, it is possible to prevent a gap from being formed between the lower end 7 h of the heat exchanger 7 and the drain pan 11, and it is possible to prevent air that has not been heat exchanged from passing through or the drain water from being blown from the drain pan 11 due to the passing air. There is an effect.

FIG. 7 shows another example according to the first embodiment of the present invention. Up and down directions for explaining the interval dimensions of the fins laminated along the piping of the heat exchanger of the air conditioner equivalent to FIG. It is a top view of a part of heat exchanger seen from. In the above embodiment, the stacking pitch J dimension between the fins 7c of the first row heat exchanger 7a and the stacking pitch J dimension of the second row heat exchanger 7b and between the fins 7d are the same. As shown in FIG. 7, the stacking pitch J dimension between the fins 7c of the first row heat exchanger 7a may be different from the stacking pitch J1 dimension of the second row heat exchanger 7b and between the fins 7d. The lamination pitch J1 dimension of the fins 7d on the side of the heat exchanger 7b in the second row, which is in contact with the drain pan 11, is made smaller than the lamination pitch J dimension of the fins 7c in the heat exchanger 7a in the first row. In this way, by narrowing the stacking pitch of the fins 7d of the second row heat exchanger 7b, the fins 7d of the second row heat exchanger 7b have a strong structure, which prevents deformation and prevents the second row heat. There is an effect that it is possible to further reduce the amount of bypass through which air that is not heat-exchanged below the exchanger 7b passes and to improve heat exchange.

  FIG. 8 is a longitudinal sectional view corresponding to FIG. 3 and showing another example according to Embodiment 1 of the present invention. In this example, the drain pan 11 arranged so as to cover the lower portion of the heat exchanger 7 is at least K on the outer bank portion 11a on the downstream side of the air blowing contacting the fins 7d in the lower portion of the second row heat exchanger 7b. As shown in the dimensions, a protrusion 11b having a height equal to or higher than the center of the lowermost pipe 7f is provided. By this protrusion 11b, air that has not been heat-exchanged is blocked from passing through the lower part of the heat exchanger 7b in the second row (prevention of bypass), and drain water can be prevented from being blown out. Also, by providing this protrusion 11b, it is possible to make the D dimension wide, and even if the D dimension and the F dimension, which are the upper and lower dimensions of the heat exchanger 7b in the second row, are reversed, the second row Between the lower part of the heat exchanger 7b and the drain pan 11, air that has not been heat-exchanged is blocked from passing through the lower part of the second-row heat exchanger 7b (bypass prevention), and the drain water is also blown out. Can be prevented.

  Moreover, in the said embodiment, the heat exchanger 7a of the 1st line with short vertical dimension is inside the heat exchanger 7b of the 2nd line which contact | connects the drain pan 11 (upstream side of the ventilation by the turbo fan 6 shown by the air flow 9b). Even if the drain water drops from the lower end 7g of the short first row heat exchanger 7a and is blown off by the blow of the turbofan 6, the drain water is received by the second row heat exchanger 7b and enters the drain pan 11. Although an easy example has been described, the first row of heat exchangers that are short in the vertical direction may be arranged outside the second row of heat exchangers (downstream of the air blown by the turbofan 6 indicated by the air flow 9c). Good. Moreover, in the said embodiment, although the heat exchanger comprised by 2 rows of the heat exchanger 7a of the 1st row and the heat exchanger 7b of the 2nd row was shown, even if it is a heat exchanger of a 3 rows structure, Good.

  According to this embodiment, the turbo fan 6 that blows indoor air sucked from the lower suction port 4 to the blower outlet 5 provided around the suction port 4, and a plurality of pipes arranged vertically 7e and 7f are laminated with fins 7c and 7d, and are formed of a plurality of rows of heat exchangers 7 provided so as to surround the periphery of the turbofan 6, and a drain pan provided so as to cover the lower part of the heat exchanger 7 11, and the heat exchanger 7 is configured so that the lower part of the heat exchanger in one row (the first heat exchanger 7 a) is connected to the heat in the other row so that the upper row number is larger than the lower row number. The vertical dimension (D dimension) from the lowermost pipe 7f of the heat exchanger 7b in the other row to the lower end 7h of the fin 7d that contacts the drain pan 11 is formed shorter than the exchanger (second row heat exchanger 7b). The clearance dimension (E dimension) between the pipes 7f vertically adjacent to each other from 1 mm or more ), The lower part of the heat exchanger 7b where the air flow rate of the turbo fan 6 is slow has little resistance to ventilation and heat exchange is promoted, and the part that contacts the drain pan 11 of the heat exchanger 7 Is prevented from forming a gap between the lower end 7h of the heat exchanger 7 and the drain pan 11, improving the sealing performance against the air blowing, and further preventing the heat exchanger 7 from being insufficient in heat exchange capacity. 11 has an effect that drain water can be prevented from being blown out by air blowing and spilling.

  In addition, a turbofan 6 that blows indoor air sucked in from the lower suction port 4 to a blowout port 5 provided around the suction port 4, and heat radiation fins in a plurality of upper and lower pipes 7 e and 7 f A heat exchanger 7 composed of a plurality of rows formed so as to surround the turbo fan 6 and a drain pan 11 provided so as to cover the lower portion of the heat exchanger 7. In the heat exchanger 7, the lower part of the heat exchanger in one row (the first heat exchanger 7a) is connected to the heat exchanger in the other row (two rows) so that the upper row number is larger than the lower row number. The vertical dimension from the lowermost pipe 7f of the heat exchanger in the other row (second row heat exchanger 7b) to the lower end 7h of the fin 7d in contact with the drain pan 11 is formed shorter than the heat exchanger 7b). (D dimension) is 1mm or more and 3mm or less, so turbo fan Heat exchange is also promoted at the lower part of the heat exchanger 7 where the flow rate of the air is slow, and deformation of the portion of the heat exchanger 7 that contacts the drain pan 11 is prevented, so that the space between the lower end 7h of the heat exchanger 7 and the drain pan 11 It is difficult to form a gap in the air, and it is possible to improve the sealing performance against the air blowing, to further prevent the heat exchanger 7 from being insufficient in heat exchanging ability, and to prevent the drain water from being blown out from the drain pan 11 by the air blowing. is there.

  Further, the pitch dimension (J, j1) for laminating the fins 7c and 7d is such that the indoor heat exchangers in the other rows coming into contact with the drain pan 11 from the indoor heat exchangers in the first row (the first heat exchanger 7a). Since the (second-row heat exchanger 7b) is narrowly formed, it is difficult to form a gap between the lower portion of the heat exchanger 7 and the drain pan 11, and the heat exchanger 7 is improved in sealing performance against blowing. Insufficient heat exchange capability can be prevented, and drain water can be prevented from being blown out from the drain pan 11 by blowing air and spilling.

  In addition, since the vertical dimension (G dimension) from the uppermost pipe 7e to the upper end of the fin 7c of the indoor heat exchanger of some rows (the first row heat exchanger 7a) is 1 mm or more and 3 mm or less, There exists an effect that the sealing performance with respect to the ventilation of the heat exchanger 7 upper part can be improved.

  Further, the vertical dimension (F dimension) from the uppermost pipe 7f to the upper end 7k of the fin 7d of the indoor heat exchanger in the other row (second row heat exchanger 7b) is changed from the lowermost pipe 7f to the fin 7d. Since it was formed longer than the vertical dimension (D dimension) up to the lower end 7h, there is an effect that the heat exchange efficiency of the upper part of the heat exchanger 7 can be improved.

  In addition, the indoor heat exchangers in some rows (first row heat exchangers 7a), which are shorter than the indoor heat exchangers in the other rows (second row heat exchanger 7b), are connected to the other rows. Since it arrange | positions in the upstream of the ventilation of the turbo fan 6 rather than the indoor heat exchanger (2nd row heat exchanger 7b), there exists an effect that it is easy to collect the drain water from the heat exchanger 7. FIG.

  Also, a dimension (H1 dimension) in which the lower part of the indoor heat exchangers in some rows (first row heat exchanger 7a) is formed shorter than the other row indoor heat exchangers (second row heat exchanger 7b). Is in the range of 2 to 5 times the step pitch (B dimension) of the pipes 7e, 7f, and therefore has the effect of improving the heat exchange efficiency of the heat exchanger 7.

  In addition, the pipes 7e and 7f are made of copper pipes having a diameter of 5 mm or more and 9 mm or less, and the fins 7c and 7d are made of aluminum material having a thickness of 0.05 mm or more and 0.15 mm or less. There is an effect that heat exchange efficiency can be improved.

  In addition, since the drain pan 11 is provided with a projection 11b that contacts the lower downstream side of the air blown by the turbo fan 6 of the indoor heat exchanger in the other row (second row heat exchanger 7b), the heat exchanger 7 It is difficult to form a gap between the lower part and the drain pan 11, the sealing performance against the air blowing can be improved, and the heat exchange capacity of the heat exchanger 7 can be prevented from being insufficient, and the drain water is blown out from the drain pan 11 by the air blowing. There is an effect that can be prevented.

  DESCRIPTION OF SYMBOLS 1 Indoor unit, 2 Indoor unit main body, 3 Cosmetic panel, 4 Suction inlet, 5 Air outlet, 6 Turbo fan, 6a Fan motor, 6b Turbo fan ventilation part, 6c Lower end of ventilation part, 7 Indoor heat exchanger (Heat exchange ), 7a Indoor heat exchanger in the first row (some of the indoor heat exchangers), 7b Indoor heat exchanger in the second row (inner heat exchangers in the other rows), 7c fins, 7d fins, 7e Piping, 7f Piping, 7g lower end, 7h lower end, 7j upper end, 7k upper end, 8 bell mouth, 9a to 9d Air flow, 10 air passage, 11 drain pan, 11a bank portion, 11b protrusion.

Claims (9)

  A turbo fan that blows indoor air sucked from a lower suction port to a blower outlet provided around the suction port, and the turbofan formed by laminating fins on a plurality of upper and lower pipes. A plurality of rows of indoor heat exchangers provided so as to surround the periphery of the indoor heat exchanger, and a drain pan provided so as to cover a lower portion of the indoor heat exchanger, the indoor heat exchanger having an upper row number The lower part of the indoor heat exchanger of some rows is formed shorter than the indoor heat exchangers of other rows so as to be larger than the number of lower rows, and the lowermost piping of the indoor heat exchangers of the other rows The air conditioner characterized in that the vertical dimension to the lower end of the fin in contact with the drain pan is formed from 1 mm or more to ½ or less of the gap dimension of the pipe adjacent vertically.   A turbo fan that blows indoor air sucked from a lower suction port to a blower outlet provided around the suction port, and the turbofan formed by laminating fins on a plurality of upper and lower pipes. A plurality of rows of indoor heat exchangers provided so as to surround the periphery of the indoor heat exchanger, and a drain pan provided so as to cover a lower portion of the indoor heat exchanger, the indoor heat exchanger having an upper row number The lower part of the indoor heat exchanger of some rows is formed shorter than the indoor heat exchangers of other rows so as to be larger than the number of lower rows, and the lowermost piping of the indoor heat exchangers of the other rows The air conditioner characterized in that the vertical dimension to the lower end of the fin that contacts the drain pan is 1 mm or more and 3 mm or less.   The pitch dimension for laminating the fins is characterized in that the indoor heat exchanger of the other row contacting the drain pan is formed narrower than the indoor heat exchanger of the partial row. Air conditioner as described in.   4. The vertical dimension from the uppermost pipe of the partial row of indoor heat exchangers to the upper end of the fin is formed to be 1 mm or more and 3 mm or less. 5. The air conditioner described in the paragraph.   The vertical dimension from the uppermost line of the indoor heat exchanger in the other row to the upper end of the fin is longer than the vertical dimension from the lowermost line to the lower end of the fin. The air conditioner according to any one of claims 1 to 4.   The indoor heat exchangers of the partial rows, which are formed shorter than the indoor heat exchangers of the other rows, are arranged on the upstream side of the blower of the turbofan from the indoor heat exchangers of the other rows. The air conditioner according to any one of claims 1 to 5, wherein:   The dimension of forming the lower part of the indoor heat exchanger of the partial row shorter than the indoor heat exchanger of the other row is in a range of 2 to 5 times the step pitch of the pipe. The air conditioner according to any one of claims 1 to 6.   8. The copper pipe having a diameter of 5 mm or more and 9 mm or less is used for the pipe, and an aluminum material having a thickness of 0.05 mm or more and 0.15 mm or less is used for the fin. The air conditioner of any one of Claims.   9. The projection according to claim 1, wherein the drain pan is provided with a protrusion that contacts a lower downstream side of the air blown by the turbofan of the indoor heat exchanger of the other row. Air conditioner.

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