JP6545277B2 - Outdoor unit of air conditioner - Google Patents

Description

The present invention relates to an outdoor unit of an air conditioner with improved energy efficiency.

  In a conventional air conditioner, liquid refrigerant condensed by a heat exchanger functioning as a condenser mounted in an indoor unit is decompressed by an expansion valve, and a gas-liquid two-phase state in which a gas refrigerant and a liquid refrigerant are mixed It flows into the heat exchanger which functions as an evaporator mounted on the outdoor unit. When the refrigerant flows into the heat exchanger functioning as an evaporator in the gas-liquid two-phase state, the distribution performance of the refrigerant to the heat exchanger is deteriorated. Therefore, in order to improve the distribution performance of the refrigerant, a header is used as a distributor of the heat exchanger mounted on the outdoor unit, and the branch pipe protrusion amount into the header, the partition plate in the header, installation of the ejection holes, etc. There is a way to adjust the structure in the header.

  However, even when the structure in the header is adjusted as described above, the distribution of the gas-liquid two-phase refrigerant in the header is greatly influenced by the mass velocity of the refrigerant. For example, when operating at high output, more refrigerant is distributed at the top of the header than at the bottom of the header, and when operating at low output, more refrigerant is distributed at the bottom of the header than at the top of the header It will be done. Then, the heat exchange performance of the heat exchanger is deteriorated due to the deterioration of the distribution performance of the refrigerant, so there is a problem that the energy efficiency of the air conditioner is lowered. In addition, in the outdoor unit of the air conditioner, the wind flows more toward the portion closer to the fan. Therefore, if more refrigerant is distributed in the lower part of the header than in the upper part of the header than in the upper part of the header, the distribution performance of the refrigerant and the heat exchange performance of the heat exchanger are further deteriorated. There was a problem of causing a decline.

  In order to improve the energy efficiency of the air conditioner, it is necessary to equalize the distribution of the gas-liquid two-phase refrigerant. As a method therefor, conventionally, a method of providing a turbulence promoter for agitating the refrigerant in the header is used. (See Patent Document 1). In Patent Document 1, the gas-liquid two-phase refrigerant in the header is agitated by the turbulent flow promoting body to make the distribution of the gas-liquid two-phase refrigerant uniform.

JP-A-5-203286

  In the conventional method as disclosed in Patent Document 1, the distribution performance of the refrigerant is improved by providing a structure for agitating the refrigerant in the header, but the structure in the header becomes complicated, thereby increasing the cost. There was a problem that it was invited.

The present invention was made in order to solve the problems as described above, and it is an object of the present invention to provide an outdoor unit of an air conditioner having improved energy efficiency while suppressing an increase in cost.

The outdoor unit of the air conditioner according to the present invention has a suction port and a blowout port, and is provided in a casing forming an outer shell and in the casing, sucks outside air from the suction port, and discharges outside air from the blowout port. And a heat exchanger provided in the casing, the heat exchanger exchanging heat between the outside air and the refrigerant absorbed by the fan, the heat exchanger including a plurality of fins juxtaposed at intervals. A first heat exchanger main body configured by a plurality of flat tubes which pass through the fins in a direction parallel to each other and the refrigerant flows inside; a plurality of fins juxtaposed spaced apart; and the fins And a plurality of circular pipes through which the refrigerant flows, and a second heat exchanger main body including the plurality of circular pipes, and the first heat exchanger main body is the second heat exchanger main body. It is arranged closer to the fan than at the time of heating operation Upstream of kicking the first heat exchanger body, header is connected, on the upstream side of the second heat exchanger body during the heating operation, in which the distributor through the capillary tube is connected .

  According to the outdoor unit of the air conditioner pertaining to the present invention, the first heat exchanger main body in which the flat tube with high heat exchange performance is a heat transfer pipe is disposed near the fan with high contribution rate to heat exchange performance. The second heat exchanger main body, in which the heat transfer performance is low but the refrigerant distribution performance is high and the production cost is low, is a heat transfer tube far from the fan with a low contribution rate to the heat exchange performance. . Therefore, energy efficiency can be improved while suppressing an increase in cost.

It is a perspective view of the outdoor unit of the air conditioner concerning Embodiment 1 of this invention. It is the heat exchanger which concerns on Embodiment 1 of this invention, and the side surface schematic diagram of the periphery. It is AA sectional drawing of FIG. It is a figure which shows another example of AA sectional drawing of FIG. It is a BB sectional view of FIG. It is a schematic diagram of the distributor which concerns on Embodiment 1 of this invention. It is a schematic diagram which shows a distributor different from the distributor which concerns on Embodiment 1 of this invention. It is a figure which shows the air volume with respect to the height direction of the heat exchanger which concerns on Embodiment 1 of this invention. It is the heat exchanger which concerns on Embodiment 2 of this invention, and the side surface schematic diagram of the periphery. It is a side schematic diagram which shows another example of the heat exchanger which concerns on Embodiment 2 of this invention, and its periphery. It is a side schematic diagram which shows another example of the heat exchanger which concerns on Embodiment 2 of this invention, and its periphery. It is the heat exchanger which concerns on Embodiment 3 of this invention, and the side surface schematic diagram of the periphery. It is a perspective view of the outdoor unit of the air conditioner concerning Embodiment 4 of this invention. It is a side schematic diagram of the heat exchanger which concerns on Embodiment 4 of this invention. It is a schematic diagram which shows a part of structure at the time of using an internal heat exchanger as a dryness adjustment apparatus of the outdoor unit of an air conditioner. It is a 1st figure which shows another example of FIG. It is a 2nd figure which shows another example of FIG. It is the 3rd figure which shows another example of FIG. It is the heat exchanger which concerns on Embodiment 5 of this invention, and the side surface schematic diagram of the periphery. It is the heat exchanger which concerns on Embodiment 6 of this invention, and the side surface schematic diagram of the periphery. It is the heat exchanger which concerns on Embodiment 7 of this invention, and the side surface schematic diagram of the periphery. It is the heat exchanger which concerns on Embodiment 8 of this invention, and the side surface schematic diagram of the periphery. It is a 1st schematic diagram which shows the indoor unit of the air conditioner which mounts the turbo fan which concerns on Embodiment 9 of this invention. It is a 2nd schematic diagram which shows the indoor unit of the air conditioner which mounts the turbo fan which concerns on Embodiment 9 of this invention.

  Hereinafter, embodiments of the present invention will be described based on the drawings. The present invention is not limited by the embodiments described below. Moreover, in the following drawings, the relationship of the magnitude | size of each structural member may differ from an actual thing.

Embodiment 1
FIG. 1 is a perspective view of an outdoor unit 100a of an air conditioner according to Embodiment 1 of the present invention, and FIG. 2 is a schematic side view of a heat exchanger 10a according to Embodiment 1 of the present invention and the periphery thereof. 3 is a cross-sectional view taken along the line AA of FIG. 2, FIG. 4 is a view showing another example of the cross-sectional view taken along the line AA of FIG. 2, and FIG. 5 is a view taken along the line B-B of FIG. FIG. In addition, the arrow in FIG. 1 has shown the flow of the wind, and the arrow in FIG. 2 has shown the flow of the refrigerant | coolant at the time of heating operation, or the flow of the wind.

  In the following description, terms that indicate direction (for example, "upper", "lower", "right", "left", "front", "rear", etc.) are used as appropriate to facilitate understanding. For the purpose of explanation, these terms are not intended to limit the present invention. Further, in the first embodiment, “upper”, “lower”, “right”, “left”, “front”, and “rear” are used in a state where the outdoor unit 100 a is viewed from the front. The same applies to second to fourth embodiments described later.

The outdoor unit 100a of the air conditioner according to Embodiment 1 is equipped with a heat exchanger 10a shown in FIG.
The outdoor unit 100a of the air conditioner is of a top flow type, and forms a refrigeration cycle by circulating a refrigerant with an indoor unit (not shown). The outdoor unit 100a is used, for example, as a multi-unit outdoor unit for a building, and is installed on the roof of a building or the like.

  As shown in FIG. 1, the outdoor unit 100 a is disposed in the casing 1 along the box-shaped casing 1, the suction port 2 formed by the opening of the side surface of the casing 1, and the suction port 2. The heat exchanger 10a, the blowout port 3 formed by the opening of the upper surface of the casing 1, the fan guard 4 ventilated so as to cover the blowout port 3, and the inside of the fan guard 4 It has a fan 5 for sucking in the outside air from the port 2 and discharging the outside air from the outlet 3.

  The heat exchanger 10a mounted on the outdoor unit 100a of the air conditioner exchanges heat between the outside air sucked from the suction port 2 by the fan 5 and the refrigerant. As shown in FIG. 2, the heat exchanger 10 a is disposed below the fan 5 and includes an upper heat exchanger 11 and a lower heat exchanger 12. The upper heat exchanger 11 and the lower heat exchanger 12 are disposed in the vertical direction in front view or in side view. Specifically, the upper heat exchanger 11 is disposed on the upper side close to the fan 5, and the lower heat exchanger 12 is disposed on the lower side distant from the fan 5.

  The upper heat exchanger 11 is composed of a plurality of fins 21 juxtaposed spaced apart, and a plurality of heat transfer tubes which pass through the fins 21 in the direction in which the fins 21 are arranged and through which the refrigerant flows. An upper heat exchanger body 20, an upper first header 23 connected to one end of the plurality of heat transfer tubes, and an upper second header 24 connected to the other end of the plurality of heat transfer tubes are provided. Note that the upper first header 23 is connected to the upstream side of the upper heat exchanger main body 20 during heating operation, and the upper second header 24 is connected to the downstream side of the upper heat exchanger main body 20 during heating operation. There is. Hereinafter, a distributor connected to the upstream side of the upper heat exchanger main body 20 or the lower heat exchanger main body 30 in the heating operation will be referred to as an upstream distributor.

  On the other hand, the lower heat exchanger 12 is composed of a plurality of fins 31 juxtaposed spaced apart, and a plurality of heat transfer pipes passing through the fins 31 in the direction in which the fins 31 are juxtaposed and the refrigerant flowing inside A lower heat exchanger body 30, a distributor 34, a capillary tube 33 connecting one end of the plurality of heat transfer tubes to the distributor 34, and a lower header 35 connected to the other end of the plurality of heat transfer tubes There is. The distributor 34 is connected to the upstream side of the lower heat exchanger main body 30 during the heating operation via the capillary tube 33, and the lower header 35 is connected to the downstream side of the lower heat exchanger main body 30 during the heating operation. ing.

Further, the upper first header 23 of the upper heat exchanger 11 is connected to the first branch pipe 41 branched from the first pipe 40 through which the gas-liquid two-phase refrigerant in which the gas refrigerant and the liquid refrigerant are mixed passes during heating operation. ing. Further, the upper second header 24 of the upper heat exchanger 11 is connected to the first branch pipe 51 branched from the second pipe 50 through which the gas refrigerant passes during the heating operation.
On the other hand, the distributor 34 of the lower heat exchanger 12 is connected to the second branch pipe 42 branched from the first pipe 40. The lower header 35 of the lower heat exchanger 12 is connected to a second branch pipe 52 branched from the second pipe 50.

  The heat transfer tube of the upper heat exchanger 11 according to the first embodiment is a flat tube 22 having a flat cross section shown in FIG. 3, but the cross section shown in FIG. It is good also as flat porous pipe 22a in which is formed. Moreover, although the flat tube 22 shown in FIG. 3 and the flat porous tube 22a shown in FIG. 4 are both smooth surfaces, they may be grooved surfaces to increase the heat transfer area by cutting the grooves. Further, the heat transfer pipe of the lower heat exchanger 12 according to the first embodiment is a circular pipe 32 having a circular cross section shown in FIG.

16 is a first view showing another example of FIG. 2, and FIG. 17 is a second view showing another example of FIG.
In the first embodiment, as shown in FIG. 2, a gap is present between the upper heat exchanger 11 and the lower heat exchanger 12, but in practice the water droplets on the fin surface of the upper heat exchanger 11 In order to drain water, the upper heat exchanger 11 and the lower heat exchanger 12 may be brought into close contact as shown in FIG. Further, as shown in FIG. 17, the fins may have no break between the upper heat exchanger 11 and the lower heat exchanger 12 and may share an integral fin.

  The flat tube 22 shown in FIG. 3 and the flat porous tube 22a shown in FIG. 4 have high heat exchange performance because the heat transfer area per unit volume of refrigerant is large compared to the circular tube 32 shown in FIG. However, since the cross-sectional area is small, the flow resistance is large and the pressure loss is large. Therefore, it is necessary to increase the number of paths of the heat transfer tube and to suppress the increase in pressure loss. At that time, there is a problem of technology for optimally distributing the refrigerant to a large number of heat transfer tubes. On the other hand, the circular tube 32 shown in FIG. 5 has lower heat exchanger performance but lower manufacturing cost than the flat tube 22 shown in FIG. 3 and the flat porous tube 22a shown in FIG. However, since the cross-sectional area is large, the flow resistance is small and the pressure loss is small, so that the number of heat transfer pipe paths can be reduced, and there is an advantage that the distribution can be easily optimized.

Next, the flow of the refrigerant at the time of heating operation of the outdoor unit 100a of the air conditioner according to Embodiment 1 will be described using FIG.
During the heating operation, the gas-liquid two-phase refrigerant passes through the first pipe 40 and is branched into the first branch pipe 41 and the second branch pipe 42. The gas-liquid two-phase refrigerant that has flowed to the second branch pipe 42 flows to the distributor 34 and is homogenized there, and then flows into the lower heat exchanger body 30 through the capillary tube 33. The gas-liquid two-phase refrigerant flowing into the lower heat exchanger main body 30 is gasified by heat exchange with the outside air sucked from the suction port 2 there and flows out to the lower header 35.

  On the other hand, the gas-liquid two-phase refrigerant that has flowed to the first branch pipe 41 flows to the upper first header 23 where it is distributed to the flat pipes 22 and flows from the flat pipes 22 to the upper heat exchanger body 20. The gas-liquid two-phase refrigerant flowing into the upper heat exchanger main body 20 is gasified by heat exchange with the outside air sucked from the suction port 2 there and flows out to the upper second header 24.

FIG. 6 is a schematic view of the distributor 34 according to the first embodiment of the present invention.
The distributor 34 shown in FIG. 6 includes a main dis- ing pipe portion 61, a dis- ity expanding portion 62, and a diversion member 63. The distorting main pipe portion 61 is provided with a rapidly reducing area 64. Further, one end of a capillary tube 33 is connected to the distributor 34.

  A gas-liquid two-phase refrigerant flows into the distributor 34 and is squeezed by the area rapid reduction section 64 of the distribution main pipe section 61, and the gas refrigerant and the liquid refrigerant are agitated and homogenized in the distribution expansion section 62. The homogenized gas refrigerant and the liquid refrigerant are distributed to the respective capillary tubes 33 by the distributor members 63. The other end of the capillary tube 33 is connected to the circular tubes 32 of the lower heat exchanger 12, and the flow rate of the refrigerant flowing in each circular tube 32 can be controlled by adjusting the length of the capillary tube 33.

FIG. 7 is a schematic view showing a distributor different from the distributor 34 according to Embodiment 1 of the present invention. In addition, the arrow in FIG. 7 has shown the gravity direction.
The distributor connected to the upstream side of the lower heat exchanger main body 30 during the heating operation is the distributor 34 shown in FIG. 6, but may be a header 70 shown in FIG.
A header 70 shown in FIG. 7 has a structure in which a gas-liquid two-phase refrigerant flowing into the header 70 is distributed to circular pipes 32 which are a plurality of heat transfer pipes arranged in parallel in the direction of gravity. The gas-liquid two-phase refrigerant flows upward in the header 70 in a vertical upward direction, and is diverted to the plurality of circular tubes 32 at an angle perpendicular to the flow in the header 70.

  Generally, the distributor 34 has a higher refrigerant distribution performance than the header. However, when the flat tube 22 is used for a heat exchanger which is a heat transfer tube, the number of paths increases, so it is necessary to increase the number of branches of the distributor 34 or to use a plurality of distributors 34. There is a disadvantage that the management of the

  On the other hand, the header is easy to manage piping, is easy to apply automation such as automatic brazing, and can be manufactured at low cost. However, since gravity acts on the gas-liquid two-phase refrigerant, for example, when the flow rate of the refrigerant is small, there is a problem that the liquid refrigerant having a large density flows more toward the lower portion of the heat transfer tube. The distribution performance has the disadvantage of being lower than the distributor 34.

  Also, compared with the distributor 34, the header does not have the area abrupt reduction portion 64 or the like like the distributor 34, and the capillary tube 33 is also not connected, so the pressure loss is small. Therefore, in the heat exchanger main body in which the flat tubes 22 are heat transfer tubes in the upstream side distributor, the number of paths is large, and therefore, a header with small pressure loss and easy piping management is more suitable. On the other hand, for the heat exchanger main body in which the circular pipe 32 is a heat transfer pipe, the distributor 34 having a high refrigerant distribution performance is more suitable because the number of paths is small and the piping management is not complicated. Thus, the heat exchanger main body in which the flat pipe 22 is a heat transfer pipe and the upstream side distributor of the heat exchanger main body in which the circular pipe 32 is a heat transfer pipe are respectively suitable.

FIG. 8 is a diagram showing the air volume in the height direction of the heat exchanger 10a according to the first embodiment of the present invention.
The heat exchanger 10a according to the first embodiment is mounted on the top-flow outdoor unit 100a, so the fan 5 is disposed above the heat exchanger 10a, and the fan 5 exchanges the wind with the heat exchanger It passes through the gap of 10a and thereby exchanges heat with the air. And since the fan 5 is arrange | positioned above the upper heat exchanger 11, as for the air volume distribution which flows through the outdoor unit 100a, the upper side of the heat exchanger 10a near the fan 5 is lower than lower side, as shown in FIG. Will also increase. That is, in the upper heat exchanger 11 disposed above the lower heat exchanger 12 disposed on the lower side, the flow of wind is greater. Therefore, assuming that the front heat transfer areas of upper heat exchanger 11 and lower heat exchanger 12 are the same, upper heat exchanger 11 has a higher contribution rate to the heat exchange performance of outdoor unit 100a than lower heat exchanger 12. Become.

  Therefore, the upper heat exchanger 11 having high heat exchange performance, in which the flat tube 22 is a heat transfer tube, is disposed on the upper side of the outdoor unit 100a where there is a lot of wind flow, that is, close to the fan 5, On the lower side of the small outdoor unit 100a, that is, at a position far from the fan 5, the lower heat exchanger 12 in which the circular pipe 32 is a heat transfer pipe having low heat exchange performance but high refrigerant distribution performance is disposed. By doing so, the heat exchange performance can be efficiently improved. As a result, the energy efficiency of the outdoor unit 100a of the air conditioner can be improved.

  Further, the heat exchange performance is enhanced by flowing a large amount of refrigerant to the upper heat exchanger 11 disposed at a position where the flow of wind is large. Therefore, optimal ones are used as the upstream side distributors of the heat exchanger whose flat tube 22 is a heat transfer tube and the heat exchanger whose circular tube 32 is a heat transfer tube. A heat exchanger in which the flat tube 22 is a heat transfer tube, that is, a header is used as a distributor for the upper heat exchanger 11, and a heat exchanger in which the circular tube 32 is a heat transfer tube, that is, is distributed to the lower heat exchanger 12. The distributor 34 is used as a container.

  Since the flow resistance of the distributor is larger in the distributor 34 than in the header, more refrigerant can flow in the upper heat exchanger 11 by using the distributor as described above. Therefore, the distribution characteristics of the refrigerant can be improved, and the heat exchange performance of the heat exchanger 10a can be improved. In addition, by changing the length of the capillary tube 33 connected to the distributor 34, the flow rate of the refrigerant flowing in the header can be adjusted, which is more preferable.

FIG. 18 is a third diagram showing another example of FIG.
In the first embodiment, the distributor 34 is connected to the circular pipe 32 and the header is connected to the flat pipe 22 as shown in FIG. 2, but this is merely an example. For example, as shown in FIG. The same distributor may be attached to either the flat tube 22 or the flat tube 22, or a distributor 34 may be connected to the flat tube 22 and a header may be connected to the circular tube 32.

  Moreover, since the flat tube 22 is generally higher in manufacturing cost than the circular tube 32, the flat tube 22 with high heat exchange performance is a heat transfer tube near the fan 5 with a high contribution rate to the heat exchange performance of the outdoor unit 100a. By arranging a certain upper heat exchanger 11, it is possible to provide a cost-effective heat exchanger 10a.

  From the above, according to the outdoor unit 100a of the air conditioner according to the first embodiment, an upper portion heat in which the flat tube 22 having a high heat exchange performance is a heat transfer pipe near the fan 5 having a high contribution rate to the heat exchange performance. The lower heat exchanger having the exchanger 11 and the heat transfer performance is low but the refrigerant distribution performance is high and the production cost is low, the circular pipe 32 being a heat transfer pipe, far from the fan 5 having a low contribution rate to the heat exchange performance. By arranging 12, the energy efficiency can be improved while suppressing the increase in cost.

Second Embodiment
Hereinafter, the second embodiment of the present invention will be described, but the description of (parts) that is the same as the first embodiment is omitted, and the same or corresponding portions as the first embodiment are denoted by the same reference numerals. Attached.
FIG. 9 is a side schematic view of a heat exchanger 10 b according to Embodiment 2 of the present invention and the periphery thereof. The arrows in FIG. 9 indicate the flow of the refrigerant or the flow of the wind during the heating operation.
The outdoor unit 100b of the air conditioner according to Embodiment 2 includes a gas-liquid separator 80 upstream of the heat exchanger 10b. The gas-liquid separator 80 is used to adjust the dryness of the refrigerant, and a third pipe 82 through which the gas-liquid two-phase refrigerant flows, a fourth pipe 83 through which the gas refrigerant separated by the gas-liquid separator 80 flows, The liquid refrigerant separated by the gas-liquid separator 80 is connected to the first pipe 40 through which the liquid refrigerant flows. The fourth pipe 83 is connected to the bypass flow valve 85, the bypass flow valve 85 is connected to the fifth pipe 84, and the fifth pipe 84 is connected to the second pipe 50. In addition, the second pipe 50 is connected to the compressor 81.

FIG. 15: is a schematic diagram which shows a part of structure at the time of using the internal heat exchanger 110 as a dryness adjustment apparatus of the outdoor unit of an air conditioner.
In addition, although the gas-liquid separator 80 is corresponded to the "dryness adjustment apparatus" of this invention, it is an example of the apparatus which adjusts a dryness to the last, and it is not limited to this. As another dryness adjustment device, a heat exchanger which exchanges heat with an internal heat exchanger 110 as shown in FIG. 15 or another low temperature heat source may be used.

  As shown in FIG. 15, the refrigerant passes through the pipe 111 and flows into the internal heat exchanger 110. The refrigerant that has flowed into the internal heat exchanger 110 is self-cooled by a part of the refrigerant bypassed to the pipe 116 at the outlet of the heat exchanger 117, passes through the pipe 112 in a state of reduced dryness, and flows to the heat exchanger 117 . On the other hand, the bypassed refrigerant passes through the pipe 115, and the bypass flow rate is adjusted by the valve 114 installed on the pipe 113. The valve 114 installed on the pipe 113 is not limited to the valve, and may be a flow resistor such as a capillary tube, a capillary, or a float valve.

Next, the flow of the refrigerant during the heating operation of the outdoor unit 100b of the air conditioner according to Embodiment 2 will be described with reference to FIG.
During the heating operation, the gas-liquid two-phase refrigerant passes through the third pipe 82 and flows into the gas-liquid separator 80. The gas-liquid two-phase refrigerant flowing into the gas-liquid separator 80 is separated into the gas refrigerant and the liquid refrigerant there. The gas refrigerant separated by the gas-liquid separator 80 passes through the fourth pipe 83, the bypass flow valve 85, the fifth pipe 84, and the second pipe 50, and flows into the compressor 81. On the other hand, the liquid refrigerant separated by the gas-liquid separator 80 passes through the first pipe 40 and is divided into the first branch pipe 41 and the second branch pipe 42.

  The liquid refrigerant that has flowed to the second branch pipe 42 flows to the distributor 34 where it is homogenized and then flows into the lower heat exchanger body 30 through the capillary tube 33. The liquid refrigerant that has flowed into the lower heat exchanger main body 30 is gasified by heat exchange with the outside air sucked from the suction port 2 there and flows out to the lower header 35. On the other hand, the liquid refrigerant that has flowed to the first branch pipe 41 flows to the upper first header 23, is distributed to the flat pipes 22 there, and flows from the flat pipes 22 to the upper heat exchanger main body 20. The gas-liquid two-phase refrigerant flowing into the upper heat exchanger main body 20 is gasified by heat exchange with the outside air sucked from the suction port 2 there and flows out to the upper second header 24.

  The flow ratio of the refrigerant flowing to the first branch pipe 41 and the second branch pipe 42 is determined by comparing the first branch pipe 41, the upper first header 23, the flat pipe 22, the upper second header 24, and the first branch pipe 51. The total flow resistance is determined by the total flow resistance of the second branch pipe 42, the distributor 34, the capillary tube 33, the circular pipe 32, the lower header 35, and the second branch pipe 52. In particular, by adjusting the length of the capillary tube 33, the flow ratio of the refrigerant flowing to the first branch pipe 41 and the second branch pipe 42 can be optimally adjusted.

  Here, when a large amount of gas is mixed with the refrigerant flowing through the first branch pipe 41, that is, when the gas refrigerant flow rate / total refrigerant flow rate (hereinafter, referred to as dryness) is large, the gas is the upper first header 23 The liquid refrigerant tends to flow unevenly in the flat tubes 22. Therefore, by reducing the gas refrigerant flowing to the upper first header 23 using the gas-liquid separator 80, the distribution performance of the refrigerant flowing to the upper first header 23 is improved, and the heat exchange performance is improved.

  In the second embodiment, although the gas-liquid two-phase refrigerant is separated into the gas refrigerant and the liquid refrigerant by the gas-liquid separator 80, the gas flowing to the upper first header 23 can not be completely separated. It is only necessary to reduce the amount of refrigerant. Further, by using the gas-liquid separator 80, the pressure loss when passing through the distributor and the heat transfer tube can be reduced as a whole, and the adjustment of the flow rate ratio by the capillary tube 33 becomes easy.

FIG. 10 is a schematic side view showing another example of the heat exchanger 10 b according to Embodiment 2 of the present invention and the periphery thereof, and FIG. 11 is a heat exchanger 10 b according to Embodiment 2 of the present invention and It is a side schematic diagram which shows another example of the periphery. Arrows in FIGS. 10 and 11 indicate the flow of the refrigerant or the flow of the wind during the heating operation.
The arrangement of the gas-liquid separator 80 is not limited to the position shown in FIG. 9, and the gas-liquid separator 80 may be arranged in the first branch pipe 41 as shown in FIG. As shown, the gas-liquid separator 80 may be disposed in the second branch pipe 42. In addition, when a plurality of gas-liquid separators 80 are disposed, the control range of the flow rate of the refrigerant flowing to the first branch pipe 41 and the second branch pipe 42 is further expanded, which is more preferable.

Third Embodiment
The third embodiment of the present invention will be described below, but (partial) description of parts overlapping with the first embodiment is omitted, and the same or corresponding parts as the first embodiment are denoted by the same reference numerals. Attached.
FIG. 12 is a schematic side view of a heat exchanger 10 c according to Embodiment 3 of the present invention and the periphery thereof. The arrows in FIG. 12 indicate the flow of the refrigerant or the flow of the air during the cooling operation.
In a heat exchanger 10c according to the third embodiment, at least two types of heat transfer tubes, a flat tube 22 and a circular tube 32, are connected in series via an intermediate header 26.
The heat exchanger 10 c is disposed below the fan 5 and includes an upper heat exchanger body 20, a lower heat exchanger body 30, a header 25, an intermediate header 26, a distributor 34, and a capillary tube 33. Is equipped.

  The upper heat exchanger main body 20 is composed of a plurality of fins 21 juxtaposed spaced apart, and a plurality of flat tubes 22 which pass through the fins 21 in the direction in which the fins 21 are arranged and through which the refrigerant flows It is done. The lower heat exchanger main body 30 includes a plurality of fins 31 arranged in parallel at intervals, and a plurality of circular tubes 32 which pass through the fins 31 in the direction in which the fins 31 are arranged and through which the refrigerant flows. It consists of The upper heat exchanger main body 20 and the lower heat exchanger main body 30 are vertically disposed in a front view or a side view, and the upper heat exchanger main body 20 is on the upper side closer to the fan 5. The lower heat exchanger main body 30 is disposed on the lower side far from the fan 5.

That is, the plurality of flat tubes 22 of the upper heat exchanger body 20 and the plurality of circular tubes 32 of the lower heat exchanger body 30 are juxtaposed in the direction of gravity.
One end of the plurality of flat tubes 22 of the upper heat exchanger body 20 is connected to the header 25, and one end of the plurality of circular tubes 32 of the lower heat exchanger body 30 is connected to the distributor 34 via the capillary tube 33. It is done. Further, the other ends of the plurality of flat tubes 22 of the upper heat exchanger body 20 and the other ends of the plurality of circular tubes 32 of the lower heat exchanger body 30 are connected to the intermediate header 26. The distributor connected to the upstream side of the upper heat exchanger main body 20 in the cooling operation is the header 25 and the distributor connected to the upstream side of the lower heat exchanger main body 30 in the cooling operation is the header 25. , Is a distributor 34.

  The header 25 is connected to a first pipe 91 through which the gas refrigerant passes during the cooling operation, and the distributor 34 is connected to a second pipe 92 through which the liquid refrigerant passes during the cooling operation.

Next, the flow of the refrigerant during the cooling operation of the outdoor unit 100c of the air conditioner according to Embodiment 3 will be described using FIG.
During the cooling operation, the high temperature and high pressure gas refrigerant passes through the first pipe 91 and flows to the header 25, where it is distributed to the flat tubes 22 and flows from the flat tubes 22 to the upper heat exchanger body 20. The gas refrigerant that has flowed into the upper heat exchanger main body 20 exchanges heat with the outside air sucked from the suction port 2 there and radiates heat to become a gas-liquid two-phase state, and flows to the intermediate header 26. In the middle header 26, the gas-liquid two-phase refrigerant flows into the circular pipe 32 of the lower heat exchanger main body 30, where it further exchanges heat with the surrounding air and becomes liquid single phase.

  At this time, if the flat tube 22 is used as a heat exchanger in which a gas-liquid two-phase refrigerant having a large ratio of liquid refrigerant flows like the lower heat exchanger 12 in which the circular tube 32 is a heat transfer tube, the heat exchanger height In the case of the flat tube 22, the decrease in the heat transfer coefficient in the liquid single phase is more significant than in the case of the circular tube 32. For this reason, by using the flat tube 22 in the heat exchanger in which the refrigerant having a large proportion of liquid refrigerant flows and the flat tube 22 in the heat exchanger in which the gas single phase to gas-liquid two phase state flows, the flat in the liquid single phase portion It is possible to compensate for the disadvantages of the tube 22 and provide a cost effective heat exchanger.

Fourth Embodiment
The fourth embodiment of the present invention will be described below, but the description of (partially) the same parts as in the first embodiment is omitted, and the same or corresponding parts as in the first embodiment have the same reference numerals. Attached.
FIG. 13 is a perspective view of the outdoor unit 100d of the air conditioner according to Embodiment 4 of the present invention, and FIG. 14 is a schematic side view of a heat exchanger 10d according to Embodiment 4 of the present invention. Arrows in FIG. 14 indicate the flow of wind.

The outdoor unit 100d of the air conditioner according to Embodiment 4 is equipped with a heat exchanger 10d shown in FIG.
The outdoor unit 100d of the air conditioner is a side flow type, and constitutes a refrigeration cycle by circulating a refrigerant with an indoor unit (not shown). The outdoor unit 100d is used, for example, as a multi-unit outdoor unit for a building, and is installed on the roof of a building or the like.

  As shown in FIG. 13, the outdoor unit 100 d is disposed on the back side of the casing 101, a suction port (not shown) formed by an opening on the back side of the casing 101, and a casing 101 formed in a box shape. The heat exchanger 10d, the outlet 103 formed by the opening of the front surface of the casing 101, the fan guard 104 ventilated so as to cover the outlet 103, and the fan guard 104 A fan 105 for sucking in the outside air from the mouth and discharging the outside air from the outlet 103 is provided.

  The heat exchanger 10d mounted on the outdoor unit 100d of the air conditioner exchanges heat between the ambient air sucked from the suction port by the fan 105 and the refrigerant, and the heat exchanger 10d has a back surface more than the fan 105. It is arranged on the side.

  The heat exchanger 10 d includes a front heat exchanger main body 120 composed of the fins 21 and the flat tubes 22, and a rear heat exchanger body 130 composed of the fins 31 and the circular tubes 32. The front heat exchanger main body 120 and the rear heat exchanger main body 130 are disposed in the front-rear direction in a front view. Specifically, the front heat exchanger body 120 is disposed on the front side of the outdoor unit 100 d near the fan 105, and the rear heat exchanger body 130 is disposed on the rear side of the outdoor unit 100 d far from the fan 105.

  As in the fourth embodiment, the front heat exchanger main body 120 in which the flat tubes 22 having high heat exchange performance are heat transfer tubes is disposed in the front row close to the fan 105 and the rear surface heat heat transfer tubes are heat transfer tubes in the rear row. By arranging the exchanger body 130, it is possible to improve the heat exchange performance with good cost performance in the front row where the temperature difference between the refrigerant and the outside air is large.

  The upper heat exchanger main body 20 and the front heat exchanger main body 120 correspond to the “first heat exchanger main body” of the present invention, and the lower heat exchanger main body 30 and the rear heat exchanger main body 130 It corresponds to "the second heat exchanger body". Further, the front surface of the casing 101 corresponds to the “side surface of the casing” in the present invention.

Embodiment 5
The fifth embodiment of the present invention will be described below, but the description of (part of) the same parts as in the first embodiment is omitted, and the same or corresponding parts as in the first embodiment have the same reference numerals. Attached.
FIG. 19 is a schematic side view of a heat exchanger 10 e according to Embodiment 5 of the present invention and the periphery thereof. The arrows in FIG. 19 indicate the flow of refrigerant or the flow of wind during heating operation.

  The heat exchanger 10e according to the fifth embodiment is disposed upstream of the upper heat exchanger body 20 with respect to the refrigerant flow, and upstream of the upper first header 23 and the lower heat exchanger body 30 with respect to the refrigerant flow. Is connected, the flow control valve 150 is provided on the upstream side of the lower first header 140, and the flow rate of refrigerant flowing to the upper heat exchanger body 20 and the lower heat exchanger body 30 is adjusted by the valve opening degree .

  In addition, although the expansion valve is mentioned as an example of a mechanism which adjusts a refrigerant | coolant flow volume here, it is an example to the last, and a capillary tube, a float, etc. should just change flow resistance and adjust a refrigerant | coolant flow. Further, the distributor connected to the upper heat exchanger main body 20 or the lower heat exchanger main body 30 is connected to the header as an example of the fifth embodiment to the last, but the present invention is not limited to this. A header and a distributor may be used together.

  According to the fifth embodiment, during the heating operation, the flow rate of the refrigerant flowing to the lower heat exchanger main body 30 formed of the circular pipe 32 is controlled by the flow rate adjustment valve 150 to achieve distribution adjustment and the lower heat exchanger main body It is possible to change the heat exchange contribution rate of 30. For example, a large amount of refrigerant can be supplied stably to the upper heat exchanger main body 20 having a high heat exchange contribution rate even at low load operation, and the cost performance is excellent. A heat exchanger can be provided.

Sixth Embodiment
The sixth embodiment of the present invention will be described below, but the description of (part of) the same parts as in the first embodiment is omitted, and the same or corresponding parts as in the first embodiment have the same reference numerals. Attached.
FIG. 20 is a schematic side view of a heat exchanger 10 f according to Embodiment 6 of the present invention and the periphery thereof. Arrows in FIG. 20 indicate the flow of refrigerant or the flow of wind during heating operation.

The heat exchanger 10f according to the sixth embodiment is connected to the upstream side of the upper heat exchanger body 20 formed of the lower heat exchanger body 30 formed of the circular pipe 32 and the flat pipe 22 during heating operation. The header being processed and the header connected downstream are a single upstream header 160 and a downstream header 170 without being divided up and down respectively. That is, one upstream header 160 and one downstream header 170 are connected across the upper heat exchanger body 20 and the lower heat exchanger body 30.
In this manner, by dividing the header into upper and lower parts, it is possible to reduce piping, or to improve cost performance without the need to attach multiple headers.

  In the sixth embodiment, the header connected to the upstream side of the upper heat exchanger body 20 and the lower heat exchanger body 30 during the heating operation and the header connected to the downstream side are respectively Although it is comprised by one, it is not limited to it. For example, although the upstream side is connected to one header, the downstream side may be a plurality of headers divided up and down, and the upstream side is connected to a distributor other than a header such as one distributor The downstream side may be a plurality of headers divided up and down. Further, the upstream side may be a plurality of headers or distributors divided up and down, and the downstream side may be connected to one header.

Embodiment 7
Seventh Embodiment A seventh embodiment of the present invention will be described below, but the description of (parts of) duplicates with the first embodiment is omitted, and the same or corresponding parts as in the first embodiment are denoted by the same reference numerals. Attached.
FIG. 21 is a schematic side view of a heat exchanger 10g according to Embodiment 7 of the present invention and the periphery thereof. The arrows in FIG. 21 indicate the flow of refrigerant or the flow of wind during heating operation.

  The heat exchanger 10g according to the seventh embodiment is such that an anticorrosion sheet 180 is inserted between the upper heat exchanger body 20 and the lower heat exchanger body 30. This is because, for example, when the flat tube 22 is aluminum, the circular tube 32 is a copper tube, etc., and different metals are present at the top and bottom, the progress of corrosion of the lower heat exchanger body 30 is reduced by drainage or the like. is there. In addition, it is also effective to comprise the upper heat exchanger main body 20 and the lower heat exchanger main body 30 with the same material instead of the anti-corrosion sheet | seat 180. FIG.

Eighth Embodiment
Hereinafter, the eighth embodiment of the present invention will be described, however, the description of (partially) the same parts as in the first embodiment will be omitted, and the same or corresponding parts as in the first embodiment will be denoted by the same reference numerals. Attached.
FIG. 22 is a schematic side view of a heat exchanger 10 h according to Embodiment 8 of the present invention and the periphery thereof. The arrows in FIG. 22 indicate the flow of the refrigerant during the heating operation or the flow of the wind.

  In the heat exchanger 10 h according to the eighth embodiment, the lower heat exchanger main body 30 formed of the circular pipe 32 is farther from the fan 5 than the upper heat exchanger main body 20 formed of the flat pipe 22 during heating operation. The heat transfer tubes of the heat exchanger are disposed substantially vertically, that is, vertically oriented, at least one of the upper heat exchanger main body 20 and the lower heat exchanger main body 30 being disposed at a position. Accordingly, the refrigerant flowing in the header connected to the upper heat exchanger body 20 or the lower heat exchanger body 30 is less affected by the head difference of the header, and distribution can be improved.

  In addition, the flat tube 22 with relatively high heat transfer performance is used at a position close to the fan 5, and the heat transfer performance is relatively low at a position far from the fan 5, but a circular tube 32 with good cost performance. By arranging, a heat exchanger excellent in cost performance can be provided. Further, in FIG. 22, the header position into which the refrigerant flows is the lower portion of the heat exchanger main body, but this is merely an example, for example, the refrigerant inflow position is the upper portion of the heat exchanger main body, or the upper heat exchanger main body The lower part of 20 and the upper part of the lower heat exchanger main body 30 may be used.

Embodiment 9
The ninth embodiment of the present invention will be described below.
FIG. 23 is a first schematic diagram showing an indoor unit 100e of an air conditioner equipped with a turbofan 250 according to Embodiment 9 of the present invention, and FIG. 24 is a turbo according to Embodiment 9 of the present invention. It is a 2nd schematic diagram which shows the indoor unit 100e of the air conditioner which mounts the fan 250. As shown in FIG. Arrows in FIGS. 23 and 24 indicate the flow of wind.

  The indoor unit 100e of the air conditioner according to Embodiment 9 is equipped with a turbo fan 250 shown in FIG. 23 and FIG. Further, the first heat exchanger 200 and the second heat exchanger 210 are mounted around the turbofan 250, and the first heat exchanger 200 is located above the indoor unit 100e than the second heat exchanger 210, That is, they are disposed near the tip of the turbo fan 250.

  The turbo fan 250 is rotated by the motor 230, and as the turbo fan 250 rotates, the wind flows along the bell mouth 240 and is blown out centrifugally by the turbo fan 250. The blown-out wind exchanges heat by passing through the first heat exchanger 200 and the second heat exchanger 210 arranged around the turbo fan 250, and is blown along the air path formed by the ceiling material 190. It is detected. Moreover, the drain pan 220 is arrange | positioned in the lower part of the 2nd heat exchanger 210, and it has a structure which hold | stores the condensed water which generate | occur | produces with a heat exchanger.

  The air volume distribution of the indoor unit 100e according to the ninth embodiment is as shown in FIG. 24, and the heat exchange performance is relative to the first heat exchanger 200 near the tip of the turbo fan 250 and having a large wind flow rate. The second heat exchanger 210 which has a relatively high flat tube 22 and is far from the tip of the turbo fan 250 and uses a circular tube 32 having a relatively low heat exchange performance but a high cost performance for the second heat exchanger 210 having a low wind velocity.

The refrigerant circuits of the first heat exchanger 200 and the second heat exchanger 210 may be connected in parallel or may be connected in series, and the second heat exchanger 210 may be in a liquid single phase during the cooling operation. It is better to use as a heat exchanger for Also, although a gap is depicted between the first heat exchanger 200 and the second heat exchanger 210 in FIGS. 23 and 24, the first heat exchanger 200 and the second heat exchanger 210 By contacting, the drainage path of the fins may be secured.
The configuration of the indoor unit 100e according to the ninth embodiment can also be applied to an outdoor unit.

  Reference Signs List 1 casing, 2 suction port, 3 outlet, 4 fan guard, 5 fan, 10a heat exchanger, 10b heat exchanger, 10c heat exchanger, 10d heat exchanger, 10e heat exchanger, 10f heat exchanger, 10g heat Exchanger, 10f heat exchanger, 11 upper heat exchanger, 12 lower heat exchanger, 20 upper heat exchanger body, 21 fins, 22 flat tubes, 22a flat porous tubes, 23 upper first headers, 24 upper second headers , 25 headers, 26 middle headers, 30 lower heat exchanger bodies, 31 fins, 32 circular tubes, 33 capillary tubes, 34 distributors, 35 lower headers, 40 first pipes, 41 first branch pipes, 42 second branch pipes, 50 second piping, 51 first branch pipe, 52 second branch pipe, 61 distribution main pipe, 62 distribution expansion, 63 DISTRIBUTION CURRENT DISTRIBUTION MEMBER, 64 AREA DIFFUSION PART, 70 HEADER, 80 GAS LIQUID SEPARATOR, 81 COMPRESSOR, 82 THIRD TERMINAL, 83 THIRD PIPING, 84 FOURTH PIPE, 85 FIFTH PITCH, 85 BYPASS FLOW VALVE, 91 FIRST PIPE, 92 THIRD Two piping, 100a outdoor unit, 100b outdoor unit, 100c outdoor unit, 100d indoor unit, 100e indoor unit, 101 casing, 103 casing, 103 air outlet, 104 fan guard, 105 fan, 110 internal heat exchanger, 111 piping, 112 piping, 113 Piping, 114 valve, 115 piping, 116 piping, 117 heat exchanger, 120 front heat exchanger body, 130 back heat exchanger body, 140 lower first header, 150 flow control valve, 160 upstream header, 170 downstream header, 180 Anticorrosion sheet, 190 ceiling material, 200 first heat exchanger, 210 first Heat exchanger, 220 drain pan, 230 motor, 240 bellmouth, 250 turbofan.

Claims (13)

A casing having an inlet and an outlet and constituting an outer shell;
A fan which is provided in the casing and sucks outside air from the suction port and discharges the outside air from the blowout port;
And a heat exchanger provided in the casing and performing heat exchange between the refrigerant and the ambient air sucked by the fan.
The heat exchanger is
A first heat exchanger main body including a plurality of fins juxtaposed spaced apart, and a plurality of flat tubes which pass through the fins in the juxtaposed direction and through which the refrigerant flows inside;
A second heat exchanger main body including a plurality of fins juxtaposed spaced apart and a plurality of circular pipes penetrating the fins in the juxtaposed direction and having the refrigerant flowing therein;
The first heat exchanger body is disposed closer to the fan than the second heat exchanger body,
A header is connected to the upstream side of the first heat exchanger body during heating operation,
An outdoor unit of an air conditioner, wherein a distributor is connected to the upstream side of the second heat exchanger main body during heating operation via a capillary tube. The outdoor unit of the air conditioner according to claim 1, wherein a dryness adjusting device for adjusting the dryness of the refrigerant is provided upstream of the heat exchanger during heating operation. The first heat exchanger main body and the second heat exchanger main body are vertically disposed in a front view, and the first heat exchanger main body is disposed above the second heat exchanger main body. The outdoor unit of the air conditioner according to claim 1 or 2, wherein the first heat exchanger main body and the second heat exchanger main body are connected in series by an intermediate header. The outdoor unit of an air conditioner according to claim 3, wherein the air outlet is a top flow type having the air outlet on the upper surface of the casing. The outdoor unit of the air conditioner according to claim 1 or 2, wherein the first heat exchanger main body and the second heat exchanger main body are disposed in the front-rear direction in a front view. The outdoor unit of an air conditioner according to claim 5, wherein the air outlet is a side flow type having a side surface of the casing. At least one of the first heat exchanger body and the second heat exchanger body has a mechanism for adjusting the flow rate of refrigerant flowing to the first heat exchanger body and the second heat exchanger body during heating operation The outdoor unit of the air conditioner as described in any one of Claims 1-6. The first heat exchanger body and the second heat exchanger body in at least one of the upstream side and the downstream side of the first heat exchanger body and the second heat exchanger body during heating operation The outdoor unit of the air conditioner according to any one of claims 1 to 7, wherein one distributor is connected across the two. The outdoor unit of the air conditioner according to any one of claims 1 to 8, wherein an anticorrosion sheet is inserted between the first heat exchanger main body and the second heat exchanger main body. The outdoor unit of the air conditioner according to any one of claims 1 to 9, wherein the first heat exchanger main body and the second heat exchanger main body are made of the same material. The air conditioning according to any one of claims 1 to 5, 7 to 10, wherein the heat transfer tubes of at least one of the first heat exchanger body and the second heat exchanger body are vertically oriented. Unit outdoor unit. A casing having an inlet and an outlet and constituting an outer shell;
A fan which is provided in the casing and sucks outside air from the suction port and discharges the outside air from the blowout port;
And a heat exchanger provided in the casing and performing heat exchange between the refrigerant and the ambient air sucked by the fan.
The heat exchanger is
A first heat exchanger main body including a plurality of fins juxtaposed spaced apart, and a plurality of flat tubes which pass through the fins in the juxtaposed direction and through which the refrigerant flows inside;
A second heat exchanger main body including a plurality of fins juxtaposed spaced apart and a plurality of circular pipes penetrating the fins in the juxtaposed direction and having the refrigerant flowing therein;
The first heat exchanger body is disposed closer to the fan than the second heat exchanger body,
An outdoor unit of an air conditioner, wherein the first heat exchanger main body and the second heat exchanger main body are disposed in the front-rear direction in a front view. The outdoor unit of an air conditioner according to claim 12 , wherein the air outlet is a side flow type having the air outlet on a side surface of the casing.

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