JP2005337571A - High-place installed air-conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a high-place installed air-conditioner in a two-way blow structure with heat exchangers each having an increased area for improved heat exchanging performance without increasing the outer size of an air-conditioner body. <P>SOLUTION: In the high-place installed air-conditioner in the two-way blow structure using two-series cross flow fans, the heat exchangers each have an increased surface area without increasing the outer size of the air-conditioner body. Each of two sets of heat exchangers arranged in a truncated shevron shape has such a bent structure that its lower part is bent into a dogleg shape at a preset angle to enlarge a gap between a drain pan bottom portion and itself, or it has a sub air inlet formed corresponding to two sets of sub heat exchangers continuously provided at the lower ends of the two sets of heat exchangers in the truncated shevron shape. Thus, the area of the heat exchanger is increased without increasing the outer size of the air-conditioner body, resulting in an increased amount of suction air with low pressure drop. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a configuration of an air conditioner of a high installation type with a two-way blowing structure.

  In a high-altitude air conditioner such as a ceiling-embedded air conditioner with a two-way blowing structure using two crossflow fans, the first and second linear heat exchangers are The shaft object is inclined and arranged in a C shape (see, for example, Patent Document 1).

  If it does in this way, compared with the thing of the vertical arrangement | positioning until then, the surface area of a heat exchanger can be increased by the part which can lengthen the length of the heat exchanger. An example is shown in FIG.

  That is, the thing of FIG. 6 comprises the two-way blowing ceiling embedded type air conditioner 1 using the 1st, 2nd two sets of fan rotor 30A, 30B of the same capacity, The code | symbol 2 is It is a cassette-type main body casing of the ceiling-embedded air conditioner 1. The main casing 2 is embedded in the ceiling such that the decorative panel 4 portion on the lower surface side thereof is substantially flush with the ceiling of the room.

  The decorative panel 4 of the main body casing 2 is provided with an elongated air suction port 5 that is located at the center in the left-right direction in the figure and extends to both ends in the front-rear direction in the figure. First and second air passages 10a and 10b that are divided in two directions are connected via two fan rotors 30A and 30B. Also, on the left and right sides of the air suction port 5 of the decorative panel 4 of the main body casing 2, first and second air having a predetermined width extending in the same direction in both the front and rear sides for blowing out the air after temperature adjustment. Air outlets 9a and 9b are provided.

  On the other hand, the first and second air passages 10a and 10b are divided into the air outlets 9a and 9b in the direction from the first and second air suction ports 5 through the upper portion thereof and smoothly make a U-turn. The parabolic scroll portions are integrated with each other, and are formed between the scroll portions and the tongue portions facing each other, in the left and right directions upstream of the first and second air passages 10a and 10b. The upper and lower fan rotors 30A and 30B are positioned in a bifurcated region (above the air suction port 5), with the upper ends approaching each other and the lower ends separated from each other. Corresponding first and second heat exchangers 12A and 12B are installed.

  The upper end sides close to each other of the first and second heat exchangers 12A and 12B are connected by a predetermined connecting plate, while the lower end sides separated from each other are on the decorative panel 4 The first and second drain pans 29A, 29B are fixedly supported on the bottom b between the inner partition wall a and the tongue side vertical wall c.

  The length of the heat exchanger is increased according to the degree of inclination, and the heat exchange surface area is increased to some extent without increasing the outer dimension of the main casing 2 itself.

JP 2001-12790 A (page 1-13 of the specification, FIG. 1)

  However, in the case of the above conventional configuration, it has been difficult to further improve the heat exchange performance as described above without enlarging the outer size of the air conditioner 1 main body at all.

  Further, in the case of the same configuration, the first and second heat exchangers 12A and 12B and the first and second fan rotors 30A and 30B are inclined by being inclined in a C shape as described above. The gaps D and D are too small, and there is a problem that interference sound is likely to occur between them.

  Furthermore, when it is simply inclined in the shape of a letter C as described above, the lower side thereof is positioned below the tongue portions 32a and 32b, as is apparent from the configuration of FIG. In addition, the air circulation is inherently poor because the inner partition walls a, a of the drain pans 29A, 29B are obstructed, and do not necessarily contribute effectively to heat exchange.

  In other words, the air suction area is narrow for the heat exchanger surface area. In addition, the pressure loss increases.

  The present invention has been made in order to solve such a problem, and the lower part of the two sets of heat exchangers arranged in a substantially C shape has a predetermined width so as to expand the gap between the drain pan bottom. A bent structure such as bending outward at an angle is adopted, or a secondary heat exchanger is combined with the lower end of two heat exchangers of the same C-shape, and a secondary air is correspondingly Uses two cross flow fans that can effectively expand the area of the heat exchanger and increase the intake air volume without increasing the external dimensions of the air conditioner body by forming a suction port. It is an object of the present invention to provide an altitude installation type air conditioner having a two-way blowing structure.

  In order to achieve the above object, the present invention is configured with the following problem solving means.

(1) 1st subject solution means The 1st subject solution means of this invention is the main body casing 2 installed in a high place, the air suction inlet 5 provided in the lower surface side center part of this main body casing 2, The air blowout ports 9a and 9b provided on both sides of the air suction port 5 are provided between the scroll portions 31a and 31b and the tongue portions 32a and 32b, and the air sucked from the air suction port 5 is converted into the air blowout ports. First and second air passages 10a and 10b for branching and blowing air in the 9a and 9b directions, and first and second fan rotors 30A and 30B provided in the first and second air passages 10a and 10b. And the first and second fan rotors 30A and 30B, the first and second fan rotors 30A and 30B are provided in a substantially C shape with the upper end sides approaching each other and the lower end sides spaced apart from each other. The second heat exchangers 12A and 12B and the first and first heat exchangers In the high-place installation type air conditioner comprising first and second drain pans provided below the heat exchangers 12A and 12B, the lower part S of the first and second heat exchangers 12A and 12B. , S are bent outward and air suction passages are formed between the bottoms b, b of the first and second drain pans 29A, 29B.

  According to the above configuration, the first and second drain pans are formed by bending the lower portions S and S of the first and second heat exchangers 12A and 12B, which are arranged in a substantially C shape as a whole, outward. By forming the air suction passage between the bottom portions b and b of 29A and 29B, the surface areas of the heat exchangers 12A and 12B can be increased while the air suction area is expanded.

  Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

  Moreover, the length of the C-shaped main body portions M and M of the first and second heat exchangers 12A and 12B is shortened by the bending, and the first and second heat exchangers 12A and 12B are shortened. The space W between the main body portions M and M can be reduced. As a result, the gaps D and D between the first and second fan rotors 30A and 30B and the main body portions M and M of the first and second heat exchangers 12A and 12B are enlarged, and interference sound between them is generated. It is suppressed.

  Further, as described above, the first and second fan rotors 30A and 30B are first bent with respect to the first and second fan rotors 30A and 30B by bending the lower portions S and S of the first and second heat exchangers 12A and 12B outward and upward. , The second heat exchangers 12A and 12B can correspond to each other at a relatively uniform distance, and the wind speed distribution is uniform throughout the first and second heat exchangers 12A and 12B.

(2) Second Problem Solving Means The second problem solving means of the present invention is the lower part S of the bent first and second heat exchangers 12A and 12B in the configuration of the first problem solving means. , S is characterized in that its tip is in a low position below the bent portion.

  In the case of such a configuration, since the bending angle is small, manufacturing is easy.

(3) Third Problem Solving Means A third problem solving means of the present invention is the lower part S of the bent first and second heat exchangers 12A and 12B in the configuration of the first problem solving means. , S is characterized in that its tip is located higher than the bent portion.

  As described above, when the lower portions S, S of the first and second heat exchangers 12A, 12B are bent outward and their tips are positioned higher than the bent portion, the first, second, The entire first and second heat exchangers 12A and 12B correspond to the fan rotors 30A and 30B at a more uniform distance, and pass through the entire first and second heat exchangers 12A and 12B. The wind speed distribution is uniform.

  In the case of the above configuration, the lower S and S portions of the first and second heat exchangers 12A and 12B are close to the vicinity of the fan rotors 30A and 30B and the tongue portions 32a and 32b. As a result, the suction air volume increases. Therefore, also from this point, the heat exchange performance is improved.

(4) Fourth Problem Solving Means The fourth problem solving means of the present invention is the lower part S of the bent first and second heat exchangers 12A and 12B in the configuration of the third problem solving means. , S are supported by the first and second drain pans 29A, 29B in the vicinity of the tongue portions 32a, 32b.

  As described above, when the lower portions S, S of the first and second heat exchangers 12A, 12B are bent outward and supported by the drain pans 29A, 29B at positions near the tongue portions 32a, 32b that are higher than the horizontal position, The entire first and second heat exchangers 12A and 12B correspond to the first and second fan rotors 30A and 30B at a more uniform distance, so that the first and second heat exchanges are performed. The wind speed distribution becomes more uniform throughout the devices 12A and 12B.

  In the case of the above configuration, the aerodynamic performance is improved more effectively because the lower portions S and S of the first and second heat exchangers 12A and 12B approach the fan rotors 30A and 30B and the tongue portions 32a and 32b. Further, the suction air volume increases. Therefore, also from this point, the heat exchange performance is effectively improved.

(5) Fifth Problem Solving Means According to a fifth problem solving means of the present invention, the first, second, and second problems solved in the first, second, third, or fourth problem solving means are configured. The lower portions S and S of the heat exchangers 12A and 12B are characterized in that they are structured separately from the upper-side main body portions M and M.

  As the turning angle increases, it is difficult to bend the integral heat exchanger.

  Therefore, the lower portions S and S of the first and second heat exchangers 12A and 12B are divided into separate structures from the upper-side main body portions M and M, so that the heat transfer tubes are connected to each other. Be able to cope with the angle of formation.

  In addition, such a configuration is convenient for adjusting the air inflow pressure loss by reducing the number of rows of heat transfer tubes in the lower S and S portions or by reducing the number of fins.

(6) Sixth Problem Solving Means The sixth problem solving means of the present invention is the lower part S of the bent first and second heat exchangers 12A and 12B in the configuration of the fifth problem solving means. , S has a multi-row structure similar to that of the upper body portions M, M.

  According to the configuration of each means described above, by bending the lower portions S and S of the first and second heat exchangers 12A and 12B arranged in a substantially C shape as a whole upward and outward, The gaps between the drain pans 29A and 29B and the bottom portions b and b can be increased, and the surface areas of the heat exchangers 12A and 12B can be effectively increased while the air suction area is expanded.

  Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

  Therefore, the bent lower S and S portions of the first and second heat exchangers 12A and 12B ensure the necessary intake air volume even in the case of a multi-row structure similar to the upper body M and M portions. can do.

(7) Seventh Problem Solving Means The seventh problem solving means of the present invention is the lower part S of the bent first and second heat exchangers 12A and 12B in the configuration of the fifth problem solving means. , S is characterized in that it has a structure in which the number of rows of heat transfer tubes is smaller than that of the upper body portions M, M.

  According to the configuration of each means described above, by bending the lower portions S and S of the first and second heat exchangers 12A and 12B arranged in a substantially C shape as a whole upward and outward, The gap between the bottoms b and b of the drain pans 29A and 29B can be increased, and the surface areas of the heat exchangers 12A and 12B can be increased while expanding the air suction region.

  Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

  However, the bent lower S and S portions have a bad wind speed distribution due to the influence of the inner walls of the drain pans 29A and 29B.

  Therefore, by dividing the heat exchangers in the lower S and S portions into a plurality of rows and reducing the number of rows, the inflow pressure loss of air to the heat exchanger portion is reduced and the amount of inflow air is increased, thereby totaling To improve the heat exchange performance.

(8) Eighth Problem Solving Means The eighth problem solving means of the present invention is the lower part S of the bent first and second heat exchangers 12A and 12B in the configuration of the sixth problem solving means. , S has a structure in which the number of fins on the front row side is smaller than that on the rear row side.

  According to the configuration of each means described above, by bending the lower portions S and S of the first and second heat exchangers 12A and 12B arranged in a substantially C shape as a whole upward and outward, The gap between the bottoms b and b of the drain pans 29A and 29B can be increased, and the surface areas of the heat exchangers 12A and 12B can be increased while expanding the air suction region.

  Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

  However, the bent lower S and S portions have a bad wind speed distribution due to the influence of the inner walls of the drain pans 29A and 29B.

  Therefore, for the heat exchangers in the lower S and S parts, by reducing the number of fins, the inflow pressure loss of the air to the heat exchanger part is reduced and the inflow air volume is increased, thereby the total heat exchange performance. To improve.

(9) Ninth Problem Solving Means The ninth problem solving means of the present invention includes a main body casing 2 installed at a high place, and a main air suction port 5 provided in the lower surface side central portion of the main body casing 2. The air outlets 9a and 9b provided on both sides of the main air inlet 5 and the scrolls 31a and 31b and the tongues 32a and 32b are provided between the air inlets 5 and the air. First and second air passages 10a and 10b that branch and blow in the direction of the air outlets 9a and 9b, and first and second fan rotors 30A provided in the first and second air passages 10a and 10b. , 30B and the first and second fan rotors 30A, 30B, the first fan rotors 30A, 30B being provided in a substantially C shape with the upper end sides approaching each other while the lower end sides are spaced apart from each other. , Second heat exchangers 12A, 12B, In the high-place installation type air conditioner comprising first and second drain pans 29A and 29B provided below the second heat exchangers 12A and 12B, the first and second heat exchangers 12A and 12B Sub-heat exchangers 12C and 12D extending from the lower end of 12B to the vicinity of tongues 32a and 32b are provided, and sub-air suction is provided between the air outlets 9a and 9b and the first and second drain pans 29A and 29B. The ports 5a and 5b are provided, and the air sucked from the auxiliary air intake ports 5a and 5b is supplied to the first and second fan rotors 30A and 30B via the auxiliary heat exchangers 12C and 12D. It is characterized by.

  According to the configuration as described above, the auxiliary heat exchangers 12C and 12D extending from the lower ends of the first and second heat exchangers 12A and 12B, which are arranged in a substantially C shape as a whole, to the vicinity of the tongue portions 32a and 32b. The total surface area of the heat exchanger can be increased while the air suction area is expanded by the sub air suction ports 5a and 5b provided corresponding to the presence and the sub heat exchangers 12C and 12D.

  Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

  In the case of the same configuration, the interval between the first and second auxiliary heat exchangers 12C and 12D and the tongue portions 32a and 32b of the first and second fan rotors 30A and 30B may be increased. it can. As a result, interference noise between the first and second fan rotors 30A and 30B and the first and second auxiliary heat exchangers 12C and 12D is suppressed.

(10) Tenth Problem Solving Means According to a tenth problem solving means of the present invention, in the configuration of the ninth problem solving means, the number of rows of heat transfer tubes of the first and second auxiliary heat exchangers 12C and 12D is provided. Is characterized in that the number of rows is smaller than that of the first and second heat exchangers 12A and 12B.

  According to the configuration of the ninth problem solving means described above, the sub heat exchangers 12C and 12D are provided separately from the first and second heat exchangers 12A and 12B, which are arranged in a substantially C shape as a whole. By providing the corresponding auxiliary air suction ports 5a and 5b, the surface area of the heat exchanger is expanded as a whole without increasing the pressure loss while expanding the air suction region.

  Therefore, the heat exchange performance can be effectively increased without increasing the outer size of the air conditioner body casing 2.

However, although the sub air inlets 5a and 5b are provided, the installation portion of the sub heat exchangers 12C and 12D has a wind speed distribution due to the partition wall C ₁ that is originally on the outer side of the drain pans 29A and 29B. bad.

  Therefore, for example, by dividing the first and second sub heat exchangers 12C and 12D into a plurality of rows and reducing the number of rows, the air to the first and second sub heat exchangers 12C and 12D portions is reduced. The inflow pressure loss is reduced to increase the inflow air volume, thereby improving the total heat exchange performance of the heat exchanger.

(11) Eleventh problem solving means The eleventh problem solving means of the present invention is the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth or tenth. In the configuration of the problem solving means, the upper end sides of the first and second heat exchangers 12A and 12B are abutting and integrated with each other.

  As described above, when the upper end sides of the first and second heat exchangers 12A and 12B that are inclinedly arranged in a substantially C shape are brought into contact with each other, the inclination angle becomes larger, and the first and second Since the distances D and D between the fan rotors 30A and 30B are increased, the mutual interference noise is suppressed, and the length itself can be increased, so that the surface area of the heat exchanger can be further increased. become.

  Further, a special connecting member as in the case of being separated is not necessary, and the cost can be reduced accordingly.

(12) Twelfth problem solving means The twelfth problem solving means of the present invention is the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth. Alternatively, in the configuration of the eleventh problem solving means, the air conditioner is a ceiling-embedded air conditioner.

  According to the first, second, third, fourth, fifth, sixth, seventh, eighth, ninth, tenth or eleventh problem solving means, the two sets arranged in a C shape The lower part of each heat exchanger is bent outward at a predetermined angle so as to widen the gap between the bottom of the drain pan, and with respect to the lower ends of the two heat exchangers in the C-shape By combining the sub heat exchangers and forming the sub air suction ports correspondingly, the heat exchanger area can be expanded without increasing the outer dimensions of the air conditioner body, and the suction air volume can be increased. it can.

  Therefore, it is effective for a ceiling-embedded air conditioner that is installed in the ceiling and is particularly required to be thin and compact.

  As a result, according to the present invention, the heat exchange performance is improved, and the in-machine pressure loss can be reduced as much as possible under the same air volume. Therefore, the rotation speed, blowing sound, and shaft power of the blower fan can be reduced as much as possible.

<First Embodiment>
First, FIG. 1 shows a configuration of an altitude installation type air conditioner according to the best embodiment 1 of the present invention.

  In this embodiment, as an example of an altitude installation type air conditioner, for example, a two-way blow type ceiling embedded type air conditioner using two cross flow fans is adopted. The surface area of the heat exchangers 12A and 12B can be increased without enlarging the outer dimensions of the air conditioner main body, and the entire surface corresponding to each of the two fan rotors 30A and 30B. As shown, the lower portions S and S of the heat exchangers 12A and 12B installed in a substantially C shape are bent outwardly at a predetermined angle into a U shape, and the tip portions thereof are formed as tongue portions 32a and 32b. While fixing the drain pans 29A and 29B being formed below the horizontal position of the outer vertical wall C, the total length of the heat exchangers 12A and 12B is lengthened to increase the heat exchange area. , Heat exchanger 12 , 12B and the bottoms b, b of the drain pans 29A, 29B are widened to widen the suction area, and the folded main body portions of the heat exchangers 12A, 12B by the above-described bending. By shortening the lengths of the M and M portions and reducing the interval W between the heat exchanger main body portions M and M, the fan rotors 30A and 30B and the heat exchangers 12A and 12B can be reduced. The gaps D and D between the main body portions M and M are enlarged so that the interference sound between them can be suppressed.

  That is, in this embodiment, the two-way blown ceiling-embedded air conditioner 1 is configured by using the first and second two sets of fan rotors 30A and 30B having the same capacity. These are the cassette-type main body casings of the ceiling-embedded air conditioner 1. The main casing 2 is embedded in the ceiling such that the decorative panel 4 portion on the lower surface side thereof is substantially flush with the ceiling of the room.

  The decorative panel 4 of the main body casing 2 is provided with an elongated air suction port 5 that is located at the center in the left-right direction in the figure and extends to both the front and rear ends in the figure. First and second air conditioning passages 10a and 10b that are divided in two directions are connected via the first and second fan rotors 30A and 30B. Further, first and second air blowers having predetermined widths extending in the front and rear both end directions for blowing out air for temperature control are provided on the left and right sides of the air suction port 5 of the decorative panel 4 of the main body casing 2. Outlets 9a and 9b are provided.

  On the other hand, the first and second air passages 10a and 10b are parabolic scrolls that are smoothly U-turned from the air suction port 5 through the upper portion thereof in the direction of the air outlets 9a and 9b. The parts 31a and 31b are integrated with each other, and formed between the scroll parts 31a and 31b and the tongue parts 32a and 32b facing each other, and the upstream of the first and second air passages 10a and 10b. Each of the first and second crossflows is located in a bifurcated region in both the left and right directions (the upper portion of the air inlet 5), with the upper ends approaching each other and the lower ends separated from each other. The first and second heat exchangers 12A and 12B in the present embodiment corresponding to the fans 30A and 30B are installed.

  The upper ends of the first and second heat exchangers 12A and 12B that are close to each other are connected by a predetermined connecting plate, while the lower portions S and S that are separated from each other are described below. Thus, it supports by fixing with respect to the lower taper surface of the tongue part 32a, 32b side vertical wall part C of the drain pans 29A and 29B on the said decorative panel 4. FIG.

  In other words, in the case of this embodiment, the heat exchangers 12A and 12B having a substantially C shape as a whole have their lower portions S and S as gaps between the bottom portions b and b of the drain pans 29A and 29B. It is bent in a dogleg shape outward and upward at a predetermined angle θ so as to expand sufficiently wide.

And the vertical wall part which expands the heat exchange surface area effectively without enlarging the outer dimension of main body casing 2 itself, and forms the said tongue parts 32a and 32b and the air blower outlets 9a and 9b by it While being supported by the lower tapered surface of C, the lower S portion is constituted by two sets of heat exchangers S ₁ and S _{2 in} two rows in the front and rear.

  As a result, as shown in the drawing, the gaps (air suction passages) between the lower portions S, S of the first and second heat exchangers 12A, 12B and the bottom portions b, b of the drain pans 29A, 29B are widened, The inflow pressure loss is reduced, and the amount of ventilation to the lower portions S and S is sufficiently increased (see the phantom line in FIG. 1). Further, the distance D between the fan rotors 30A and 30B is also increased, and interference noise is suppressed.

  Therefore, in the case of this configuration, for example, in the cooling or heating operation, when the first and second cross flow fans 30A and 30B as the air blowing means are driven, the heat exchange area is large and the air suction area is Temperature-controlled air (cold air or warm air) that is uniformly and effectively heat-exchanged with low-pressure loss through the wide first and second heat exchangers 12A and 12B is horizontally directed from both the front and rear air outlets 9a and 9b. A comfortable cooling or heating air-conditioning environment for the user is realized by being blown down and gradually descending downward by convection.

  According to the above configuration, the lower portions S and S of each of the first and second sets of heat exchangers 12A and 12B arranged in a substantially C shape as a whole are formed in a U shape on the outer side. The gap between the drain pans 29A and 29B and the bottom portions b and b of the drain pans 29A and 29B can be increased, and the first and second heat exchangers 12A and 12B can be effectively expanded while expanding the air suction area. The surface area can be enlarged. Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

In addition, the lower S and S portions bent in a dogleg shape have a bad wind speed distribution due to the influence of the inner walls a and a of the drain pans 29A and 29B. Therefore, the lower S, or dividing the heat exchanger of the S portion in a plurality of rows (two rows of S _1, S _2), reducing the number of fin heat exchanger S ₁ portion of the front row side (upstream side) Alternatively, as a finless portion, the inflow pressure loss of air to the heat exchanger portion is reduced to increase the inflow air volume, thereby improving the total heat exchange performance.

  In addition, as described above, the lower portions S and S of the first and second sets of heat exchangers 12A and 12B, which are arranged in a substantially C shape as a whole, are formed in a dogleg shape on the outer side. When bent, as shown in the figure, the distances D and D between the main body portions M and M in the upper part of the heat exchanger corresponding to the conventional linear portion and the first and second fan rotors 30A and 30B are enlarged. The generation of interference sound as in the conventional case can be reduced as much as possible.

  Further, by bending the first and second heat exchangers 12A and 12B in a U-shape, the first and second heat exchangers 12A and 12B are bent with respect to the first and second fan rotors 30A and 30B. The whole of 12B respond | corresponds by a comparatively uniform distance, and a wind speed distribution becomes uniform throughout the 1st, 2nd heat exchanger 12A, 12B. In the case of the above configuration, the lower portions S and S of the first and second heat exchangers 12A and 12B are particularly close to the vicinity of the first and second fan rotors 30A and 30B and the tongue portions 32a and 32b by the bending. As a result, the aerodynamic performance is improved, and the intake air volume is increased. Therefore, also from this point, the heat exchange performance is improved.

  As a result, according to the above configuration, the heat exchange performance is improved, and the in-machine pressure loss can be reduced as much as possible under the same air volume. Therefore, the rotation speed, blowing sound, and shaft power of the blower fan can be reduced as much as possible.

  In the above case, for example, the lower sides of the first and second heat exchangers 12A and 12B arranged in a C shape are left as they are, and only the upper side is placed outward so as to be in a vertical state. It is also possible to fold it to the side to form a square shape.

  However, in such a configuration, the entirety of the first and second heat exchangers 12A and 12B approaches the first and second fan rotors 30A and 30B at a relatively uniform distance. Even if there is a merit in the point that the wind speed distribution of the entire heat exchanger is uniform, improvement of the air flow performance on the lower side of the first and second heat exchangers 12A and 12B described as the problem of the conventional example, It does not contribute to the improvement of heat exchange performance.

(Modification)
In the case of this embodiment, a partition plate 7 is further inserted between the left and right first and second heat exchangers 12A and 12B, for example, as shown in FIG. The air passages up to 9a and 9b can be formed as independent intake air passages corresponding to the respective cross flow fans.

  According to such a configuration, the air drawn into the space between the heat exchangers 12A and 12B is evenly distributed in the left and right directions by the partition plate 7 provided between the heat exchangers 12A and 12B. Therefore, the flow of air flowing into the heat exchangers 12A and 12B becomes smooth.

  As a result, the first and second heat exchangers 12A and 12B each formed in a U-shape as a whole are on the concave space surface side and correspond to the heat exchange surface of the heat exchanger as uniformly as possible. Since the inflow wind speed of the intake air sucked into the first and second fan rotors 30A and 30B is made as uniform as possible, and the wind speed distribution of the entire first and second heat exchangers 12A and 12B is also made uniform. Furthermore, the heat exchange efficiency is improved.

<Best Embodiment 2>
Next, FIG. 3 shows a configuration of an altitude installation type air conditioner according to the second preferred embodiment of the present invention.

  In this embodiment, in the two-side blow type ceiling-embedded air conditioner 1 using two fan rotors similar to those in the first embodiment, the outer size of the air conditioner main body is enlarged. The heat exchange surface area of the first and second heat exchangers 12A and 12B can be increased, and corresponds to the two first and second fan rotors 30A and 30B. The lower portions S and S of the first and second heat exchangers 12A and 12B, which are installed in a generally square shape as a whole, are outwardly moved at an angle θ that is equal to or larger than a predetermined angle in the first embodiment. The drain pans 29A and 29B are bent by being bent in a larger U-shape on the side and facing the tongues 32a and 32b near the upper end of the vertical wall C higher than the horizontal position. Clearance between bottom b, b (air suction passage 1 and the second fan rotor by enlarging the distance W much larger than in the case of the first embodiment and reducing the distance W between the first and second heat exchangers 12A and 12B in the same manner. The gaps D and D between the main bodies M and M of 30A and 30B and the first and second heat exchangers 12A and 12B are also enlarged.

  The configuration of the other parts is exactly the same as that of the first embodiment described above, and has the same effect.

  According to such a configuration, the substantially C-shaped first and second heat exchangers 12A and 12B are close to a substantially W shape as a whole, and the heat exchanger surface area is reduced without reducing the suction area as a whole. Can be increased.

  In addition, in the same configuration, the lower portions S and S of the first and second heat exchangers 12A and 12B are bent farther outward than the first embodiment, and the cross flow fan is The drain pans 29A and 29B are supported on the outer side vertical wall portions (tongue portions and air blower outlet forming walls) C of the drain pans 29A and 29B in a state of being close to the vicinity of the tongue portions 32a and 32b (directly below).

  Accordingly, the gaps (air suction passages) between the lower portions S and S of the first and second heat exchangers 12A and 12B and the bottom portions b and b of the drain pans 29A and 29B are the same as those in the first embodiment. The air flow pressure loss to the lower portions S and S of the first and second heat exchangers 12A and 12B is greatly reduced, and the intake air volume is effectively increased.

Further, the lower S and S portions bent in the same letter shape have a bad wind speed distribution due to the influence of the inner partition portions a of the drain pans 29A and 29B as described above. Therefore, the heat exchangers in the lower S and S portions are divided into a plurality of rows (two rows S ₁ and S ₂ ), and the number of fins in the heat exchanger S ₁ portion on the foremost row side (the most upstream side) is reduced. In addition, by reducing the inflow pressure loss of air to the heat exchangers S ₁ and S _{2 as} finless parts, the intake air volume is increased, thereby further improving the total heat exchange performance. ing.

  In this case, the number of rows of heat exchangers in the lower portions S and S may be made smaller than the number of rows on the main body M and M side, and the inflow pressure loss of air may be further reduced.

  In each of these cases, if the lower portions S and S are provided facing the tongue portions 32a and 32b as described above, the aerodynamic performance is improved, and the first and second fan rotors 30A and 30B. Since the suction force acts more effectively, the air volume is further increased.

  Further, as described above, when the lower portions S and S of the first and second heat exchangers 12A and 12B arranged in a substantially C shape as a whole are bent into a dogleg shape, as shown in the figure, The distance W between the heat exchanger main body (upper portion) M, M corresponding to the straight portion can be reduced, and the distance D, between the main body M, M and the fan rotors 30A, 30B can be reduced. Since D can be enlarged on the contrary, the generation of interference sound as in the prior art can be reduced as much as possible.

(Modification)
In the case of this embodiment, as in the case of the first embodiment, a partition plate is provided between the first and second left and right heat exchangers 12A and 12B, for example, as shown in FIG. 7 and the air passage from the air inlet 5 to the air outlets 9a, 9b can be formed as an independent intake air passage corresponding to each cross flow fan.

  According to such a configuration, the air sucked into the space between the heat exchangers 12A and 12B is left and right by the partition plate 7 provided in the middle between the heat exchangers 12A and 12B as described above. Therefore, the flow of air flowing into the heat exchangers 12A and 12B becomes smoother.

  As a result, the first and second heat exchangers 12A and 12B formed in the shape of a dogleg as a whole are located on the concave space surface side and correspond to the heat exchange surfaces of the heat exchanger as uniformly as possible. Since the inflow wind speed of the suction air sucked into the second fan rotors 30A and 30B is made as uniform as possible, and the wind speed distribution of the entire first and second heat exchangers 12A and 12B is made uniform. Exchange efficiency is improved.

<Third Embodiment>
Next, FIG. 5 shows a configuration of an altitude installation type air conditioner according to the third preferred embodiment of the present invention.

  In this embodiment, the outer size of the main body of the air conditioner is enlarged in the two-way blowing type ceiling-embedded air conditioner 1 using two fan rotors similar to those in the first and second embodiments. The surface areas of the first and second heat exchangers 12A and 12B can be increased without the need for the two fan rotors 30A and 30B. The upper ends of the first and second heat exchangers 12A and 12B installed in a letter shape are closed in an inverted V shape by bringing them into contact with each other, and the first and second fans are tilted more inwardly. The heat exchange area is expanded by separating the rotors 30A and 30B from each other as much as possible, and the auxiliary heat exchangers 12C and 12D are added to the outer sides of the lower ends of the heat exchange areas. Tongue 32a, 32b By approaching and fixing in the vicinity, a W-shaped heat exchanger is formed as a whole, and each of the sub-heat exchangers 12C and 12D is provided separately from the central main air intake 5 to the sub-air intakes 5a and 5b. By increasing the heat exchanger surface area, the air suction area is increased correspondingly and the pressure loss in the machine is reduced as much as possible.

  That is, in this embodiment, as an example, a two-way blown ceiling-embedded air conditioner 1 is configured by using two sets of first and second left and right cross flow fans (fan rotors 30A and 30B) having the same capacity. Reference numeral 2 denotes a cassette-type main body casing of the ceiling-embedded air conditioner 1. The main casing 2 is embedded in the ceiling such that the decorative panel 4 portion on the lower surface side thereof is substantially flush with the ceiling of the room.

  The decorative panel 4 of the main body casing 2 has an elongated main air suction port (and main air suction port) that is located at the center in the illustrated left-right direction (left-right direction on the paper) and extends to both ends in the front-rear direction (the vertical direction on the paper). The first and second air passages are provided in the upper direction on the inner side and are divided in two directions via the fan rotors 30A and 30B of the first and second cross flow fans. 10a and 10b are continuously provided. Further, first and second air having a predetermined width extending to both ends in the front-rear direction for blowing out temperature-adjusting air on the left and right sides of the main air inlet 5 of the decorative panel 4 of the main casing 2. Air outlets (and air outlet passages) 9a and 9b are provided.

  In the case of this embodiment, the air suction port (and the air suction passage) to the first and second fan rotors 30A and 30B are the first and second fan rotors 30A and 30A at the center of the decorative panel 4, respectively. 30B between the main air inlet (and main air inlet passage) 5 and the air outlets (and air outlet passages) 9a, 9b on both the left and right sides of the main air inlet (and main air inlet passage) 5 The auxiliary air inlets (and auxiliary air inlet passages) 5a and 5b are provided in two sets.

The main air suction port (and main air suction passage) 5 is provided between the partition walls a and a inside the first and second drain pans 29A and 29B on the decorative panel 4 and also the sub air suction port (and the sub air). suction path) 5a, 5b, the tongue and the vertical wall portion C ₂ and the first air outlet passage or the like formed, a second drain pan 29A, the tongue 32a be in between the outer side partition wall C ₁ of the 29B , 32b is gently curved in the direction of the air inlet.

On the other hand, the first, second air passage 10a, 10b is the main air inlet through the grill portion G and a filter unit F (and the main air intake passage) from 5, also the grill portion G ₁ and the filter unit F ₁ from the auxiliary air inlets (and auxiliary air inlet passages) 5a and 5b via ₁ through the upper space portions, respectively, in the direction of the air outlets (and air outlet passages) 9a and 9b, and is smoothly divided into Y shapes. The parabolic scroll portions 31a and 31b that are turned are integrated with each other, and formed between the scroll portions 31a and 31b and the tongue portions 32a and 32b facing each other.

  The upper and lower airflow passages 10a and 10b are located in the right and left bifurcated regions upstream of the first and second air passages 10a and 10b. The first and second fan rotors 30 </ b> A and 30 </ b> B of the first and second cross-flow fans are in the shape of a square with a large inclination angle separated outward (inverted V-shape). 1 and 2nd heat exchanger 12A, 12B is installed.

  Each of the first and second heat exchangers 12A and 12B is bent at a predetermined angle θ into a V shape further outwardly from the lower end of the C-shaped heat exchanger body. Sub-heat exchangers 12C and 12D, which are added in a state of being attached and extend in the vicinity of the tongue portions 32a and 32b, are continuously provided. The sub heat exchangers 12C and 12D are divided, for example, independently from the first and second heat exchangers 12A and 12B, and the number of heat transfer tube rows is reduced to ½, thereby forming an air Inflow pressure loss is greatly reduced.

The lower ends of the first and second heat exchangers 12A and 12B and the auxiliary heat exchangers 12C and 12D connected to each other are connected to the first and second drain pans 29A and 29B on the decorative panel 4, respectively. The drain pan bottom (between the outer partition wall C ₁ and the main air suction port (and main air suction passage) 5 side partition wall a forming the sub air outlets (and sub air suction passages) 5a and 5b ( It is supported on the groove part b.

The tips of the auxiliary heat exchangers 12C and 12D are connected to the tongue portions 32a and 32b and the air inlet (and the auxiliary air suction passage) through the downstream area of the auxiliary air outlets (and the auxiliary air suction passages) 5a and 5b. 5a, the tongue 32a of the air inlet side of the vertical wall portion C ₁ forming the 5b, abuts against fixed to 32b near (just below), auxiliary air inlet (and auxiliary air intake passage) 5a, 5b By efficiently sucking the air sucked through the air into the first and second fan rotors 30A and 30B with low pressure loss, heat exchange is efficiently performed.

  Therefore, in the case of this configuration, for example, when the first and second fan rotors 30A and 30B of the first and second cross flow fans serving as the air blowing means are driven during cooling or heating operation, Temperature-controlled air (cold air or warm air) that is effectively heat-exchanged via the first and second heat exchangers 12A and 12B and the first and second auxiliary heat exchangers 12C and 12D having a large heat exchange area. ) Is blown out horizontally from both the left and right air outlets 9a, 9b, and gradually descends downward to realize a comfortable cooling or heating air-conditioning environment for the user.

  According to the configuration as described above, the auxiliary heat exchangers 12C and 12D extending from the lower ends of the first and second heat exchangers 12A and 12B, which are arranged in a substantially C shape as a whole, to the vicinity of the tongue portions 32a and 32b. The total surface area of the heat exchanger can be increased while the air suction area is expanded by the sub air suction ports 5a and 5b provided corresponding to the presence and the sub heat exchangers 12C and 12D.

  Therefore, the heat exchange performance can be increased without increasing the outer size of the air conditioner body casing 2.

  In the case of the same configuration, the distance (opposite angle) between the first and second auxiliary heat exchangers 12C and 12D and the tongue portions 32a and 32b of the first and second fan rotors 30A and 30B is set. Can be bigger. As a result, interference noise between the first and second fan rotors 30A and 30B and the first and second auxiliary heat exchangers 12C and 12D is suppressed.

(Modification)
In the case of this embodiment as well, in the same manner as in the first and second embodiments, the partition plate 7 is inserted between the first and second left and right heat exchangers 12A and 12B, and the air The air passages from the suction port 5 to the air outlets 9a and 9b can be formed as independent intake air passages corresponding to the respective cross flow fans.

  According to such a configuration, the air sucked into the space between the heat exchangers 12A and 12B is left and right by the partition plate 7 provided in the middle between the heat exchangers 12A and 12B as described above. Therefore, the flow of air flowing into the heat exchangers 12A and 12B becomes smoother.

  As a result, the inflow air velocity of the suction air sucked into the first and second fan rotors 30A and 30B becomes as uniform as possible, and the first and second heat exchangers 12A and 12B and the first and second heat exchangers 30A and 30B become as uniform as possible. Since the sub-heat exchangers 12C and 12D have a uniform wind speed distribution, the heat exchange efficiency is further improved.

(Other best embodiments)
In addition, if the upper end sides of the first and second heat exchangers 12A and 12B that are inclinedly arranged in a letter C shape are brought into contact with each other and integrated as in the configuration of the third embodiment, the inclination is further increased. Since the angle is increased, the distances D and D between the first and second fan rotors 30A and 30B are enlarged, the mutual interference sound is suppressed, and the length itself can be increased, so that It becomes possible to increase the surface area of the exchanger.

  Further, a special connecting member as in the case of being separated is not necessary, and the cost of the product can be reduced accordingly.

  Therefore, even if this configuration is applied to, for example, those of the best embodiments 1 and 2, the same effect can be obtained.

  Further, in each of the above embodiments, a ceiling-embedded type is adopted as an example of an altitude installation type air conditioner in any case, but this is a ceiling-suspended type, for example. Needless to say, it may be.

It is sectional drawing which shows the structure of the high place installation type air conditioner which concerns on the best Embodiment 1 of this invention. It is sectional drawing which shows the structure of the high place installation type air conditioner which concerns on the modification of best Embodiment 1 of this invention. It is sectional drawing which shows the structure of the high place installation type air conditioner which concerns on best Embodiment 2 of this invention. It is sectional drawing which shows the structure of the high place installation type air conditioner which concerns on the modification of best Embodiment 2 of this invention. It is sectional drawing which shows the structure of the high place installation type air conditioner which concerns on best Embodiment 3 of this invention. It is sectional drawing which shows the structure of the high place installation type air conditioner which concerns on a prior art example.

Explanation of symbols

  1 is a ceiling-embedded air conditioner, 2 is a main body casing, 3 is a ceiling, 4 is a decorative panel, 5 is an air inlet (main air inlet), 5a and 5b are sub-air inlets, 7 is a partition plate, 10a and 10b are first and second air passages, 9a and 9b are air outlets, 12A and 12B are first and second heat exchangers, 30A and 30B are first and second fan rotors, and M is The heat exchanger body, S is the lower part of the heat exchanger.

Claims (12)

  A main body casing (2) installed at a high place, an air suction port (5) provided at the center of the lower surface side of the main body casing (2), and air provided on both sides of the air suction port (5) Air provided between the air outlets (9a) and (9b), the scroll portions (31a) and (31b) and the tongue portions (32a) and (32b), and the air sucked from the air inlet port (5) The first and second air passages (10a) and (10b) for branching and blowing air in the direction of the air outlets (9a) and (9b) and the first and second air passages (10a) and (10b) The first and second fan rotors (30A) and (30B) provided and the upstream sides of the first and second fan rotors (30A) and (30B) are brought close to each other. On the other hand, the first and second heat exchangers (substantially C-shaped with the lower end sides separated from each other) 2A), (12B), and a first place and second drain pan provided below the first and second heat exchangers (12A), (12B). The lower portions (S), (S) of the first and second heat exchangers (12A), (12B) are bent outward, and the first, second drain pans (29A), ( 29B) An air conditioner installed at a high place, characterized in that an air suction passage is formed between the bottom (b) and (b).   The lower ends (S), (S) of the bent first and second heat exchangers (12A), (12B) have their tips at a low position below the bent portion. The height-installed air conditioner according to 1.   The lower ends (S), (S) of the bent first and second heat exchangers (12A), (12B) have their tips positioned higher than the bent portion. The height-installed air conditioner according to 1.   The lower portions (S) and (S) of the bent first and second heat exchangers (12A) and (12B) are positioned in the vicinity of the tongue portions (32a) and (32b), respectively. The air conditioner installed at high place according to claim 3, wherein the air pan is supported by the drain pans (29A) and (29B).   The lower parts (S), (S) of the bent first and second heat exchangers (12A), (12B) are separated from the upper body parts (M), (M). The altitude installation type air conditioner according to claim 1, 2, 3, or 4, characterized in that:   The lower portions (S) and (S) of the bent first and second heat exchangers (12A) and (12B) have a multi-row structure similar to the upper side main body portions (M) and (M). The altitude installation type air conditioner according to claim 5, wherein:   The lower part (S), (S) of the bent first and second heat exchangers (12A), (12B) has more heat transfer tubes than the upper body parts (M), (M). 6. The height-installed air conditioner according to claim 5, wherein the air conditioner has a small structure.   The number of fins on the front row side of the lower portions (S) and (S) of the bent first and second heat exchangers (12A) and (12B) is less than that on the rear row side. The altitude installation type air conditioner according to claim 6.   A main body casing (2) installed at a high place, a main air inlet (5) provided in the lower surface side central portion of the main body casing (2), and provided on both sides of the main air inlet (5) Provided between the air outlets (9a), (9b), the scroll portions (31a), (31b) and the tongue portions (32a), (32b), and the air sucked from the air inlet port (5) First and second air passages (10a) and (10b) for branching and blowing air in the air outlets (9a) and (9b), and the first and second air passages (10a) and (10b) ) Provided on the upstream side of the first and second fan rotors (30A), (30B) and the first and second fan rotors (30A), (30B) First and second heat exchangers provided in a substantially C shape with the lower end sides being spaced apart from each other 12A), (12B), and first and second drain pans (29A), (29B) provided below the first and second heat exchangers (12A), (12B). In the high-place installation type air conditioner, the auxiliary heat exchangers 12C and 12D extending from the lower ends of the first and second heat exchangers (12A) and (12B) to the vicinity of the tongues (32a) and (32b) are provided. On the other hand, auxiliary air inlets (5a) and (5b) are provided between the air outlets (9a) and (9b) and the first and second drain pans (29A) and (29B), Air sucked from the air inlets (5a) and (5b) is supplied to the first and second fan rotors (30A) and (30B) via the auxiliary heat exchangers (12C) and (12D). An altitude installation type air conditioner characterized by   The number of rows of heat transfer tubes of the first and second sub heat exchangers (12C) and (12D) is smaller than that of the first and second heat exchangers (12A) and (12B). The altitude installation type air conditioner according to claim 9, wherein   The upper ends of the first and second heat exchangers (12A) and (12B) are in contact with each other to be integrated. 7. A height-installed air conditioner according to 7, 8, 9 or 10.   The air conditioner according to claim 1, 2, 3, 4, 5, 6, 7, 8, 9, 10 or 11, wherein the air conditioner is a ceiling-embedded air conditioner. Machine.

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