WO2019012619A1

WO2019012619A1 - Heat source unit

Info

Publication number: WO2019012619A1
Application number: PCT/JP2017/025382
Authority: WO
Inventors: 洋太前間; 隆宏秋月; 拓也伊藤; 祐二垂水; 靖大越
Original assignee: 三菱電機株式会社
Priority date: 2017-07-12
Filing date: 2017-07-12
Publication date: 2019-01-17
Also published as: JP6824410B2; GB2577431A; JPWO2019012619A1; GB201918060D0; GB2577431B

Abstract

This heat source unit is provided with: a plurality of heat exchangers (1A-1D), each having a plurality of fins and a plurality of flat tubes; and a rectangular machine chamber (4). The heat exchangers (1A-1D) are provided above the machine chamber (4). A pair of heat exchangers (1A, 1B) facing each other among the heat exchangers (1A-1D), said pair of heat exchangers being disposed in the short-side direction of the machine chamber (4), are tilted such that the interval between the end portions thereof on the side far from the machine chamber (4) is larger than the interval between the end portions thereof on the side close to the machine chamber (4).

Description

Heat source unit

The present invention relates to an air conditioner and a heat source unit constituting a heat pump water heater.

An air conditioner and a heat pump water heater include a heat source unit having an air heat exchanger. The air heat exchanger has a plurality of heat transfer tubes and a plurality of fins. Inside the heat transfer tube, a refrigerant that exchanges heat with the air supplied to the heat source unit flows. The fins are configured in combination with the heat transfer tubes to increase the efficiency of heat exchange between the refrigerant and the air. The heat source unit described in Patent Document 1 includes a copper circular tube as a heat transfer tube and an aluminum fin as a fin.

International Publication No. 2016/171177

Since the heat transfer tube of the air heat exchanger described in Patent Document 1 is a circular tube, the contact area with the air supplied to the heat source unit is small. Therefore, many circular tubes are required to achieve high capacity heat exchange performance. Therefore, there are concerns that the number of rows of air heat exchangers mounted on the heat source unit is increased, and the manufacturing cost is increased. In other words, depending on the number of circular tubes mounted, the desired heat exchange performance may not be obtained.

The present invention has been made to solve the problems as described above, and it is an object of the present invention to provide a heat source unit capable of obtaining high heat exchange performance without increasing the number of heat transfer tubes.

The heat source unit according to the present invention is a heat source unit including a plurality of heat exchangers having a plurality of fins and a plurality of flat tubes, and a rectangular parallelepiped machine room, wherein the plurality of heat exchangers are the machine room Among the plurality of heat exchangers, the pair of heat exchangers disposed opposite to each other along the short direction of the machine chamber have end portions on the side far from the machine chamber. The interval is inclined to be larger than the interval between the ends closer to the machine room.

In the heat source unit according to the present invention, since a flat tube is used for the heat transfer tube of the air heat exchanger, the surface area with which the air supplied to the heat source unit is in contact is larger than when a circular tube is used. Therefore, the heat exchange area is secured the same as the heat exchange area when using a circular tube for the heat transfer tube of the air heat exchanger with a smaller number of heat transfer tubes than when the circular tube is used for the heat transfer tube of the air heat exchanger. The cost of manufacturing the heat source unit can be reduced. Further, since the heat exchanger of the heat source unit according to the present invention is inclined, condensation water generated during heating operation does not stay in the flat portion of the flat tube. Therefore, the occurrence of icing in the heat exchanger during the heating operation can be prevented, and the heating operation can be performed while maintaining high heat exchange performance. As described above, according to the present invention, it is possible to obtain a heat source unit having high heat exchange performance while suppressing the increase in the number of heat transfer tubes.

It is a perspective view of a heat source unit concerning Embodiment 1 of the present invention. FIG. 2 is a side view of the heat source unit of the first embodiment. FIG. 2 is a perspective view of a machine room of the heat source unit of the first embodiment. FIG. 5 is a view schematically showing the arrangement of the air heat exchanger in the heat source unit of the first embodiment. FIG. 2 is a view schematically showing a configuration of an air heat exchanger of the heat source unit of the first embodiment. FIG. 6 is a view schematically showing the air heat exchanger according to Embodiment 1 cut along the line BB in FIG. 5 and viewed in the arrow direction. It is a figure for demonstrating the effect at the time of using a flat tube for an air heat exchanger. It is a figure for demonstrating the effect at the time of making an air heat exchanger incline and arrange | positioning. It is a figure which shows typically the modification of arrangement | positioning of an air heat exchanger. It is a figure which shows typically the modification of arrangement | positioning of an air heat exchanger. FIG. 10 is a diagram for explaining the effect of the modification of the first embodiment. It is a figure showing typically a heat source exchanger at the time of seeing a heat source unit concerning Embodiment 2 of the present invention from the top. It is a figure which shows typically the state which injected water from the water spray nozzle to the air heat exchanger of Embodiment 2. FIG. It is a figure which shows typically the state which injected water from the water nozzle to the air heat exchanger of the modification of Embodiment 2. FIG. It is a figure which shows the short side part of an air heat exchanger typically. It is a figure which shows typically the aspect of welding of the corrugated fin in the air heat exchanger of Embodiment 3. FIG. It is a perspective view of the heat-source unit which concerns on Embodiment 7 of this invention. FIG. 21 is a side view of the heat source unit of the seventh embodiment. FIG. 24 schematically shows an arrangement of the air heat exchanger in the heat source unit according to the seventh embodiment. It is a figure which shows typically a heat-source exchanger at the time of seeing the heat-source unit which concerns on Embodiment 8 of this invention from a top.

Hereinafter, an embodiment of a heat source unit in the present invention will be described in detail based on the drawings. The present invention is not limited by the embodiments described below. Moreover, in the following drawings, the size of each component may differ from the actual device.

Embodiment 1
FIG. 1 is a perspective view of a heat source unit according to Embodiment 1 of the present invention. FIG. 2 is a side view of the heat source unit of the first embodiment. FIG. 3 is a perspective view of a machine chamber of the heat source unit according to the first embodiment. FIG. 4: is a figure which shows typically arrangement | positioning of the air heat exchanger in the heat-source unit of Embodiment 1. FIG. FIG. 2 shows the heat source unit from the direction of arrow A in FIG. FIG. 3 shows the machine room from the opposite side of the side shown in FIG. FIG. 4 shows a plurality of air heat exchangers from above the heat source unit. The heat source unit 100 according to the first embodiment is used as a heat source device of a chiller device. In the chiller apparatus, a heat transfer fluid such as water or antifreeze liquid is supplied from a use side unit (not shown) to the heat source unit 100, and the heat transfer fluid is cooled or heated in the heat source unit 100 and supplied to the use side unit. . By circulating the heat transfer fluid in this manner, cold heat or heat is supplied to the use side unit.

The heat source unit 100 includes four air heat exchangers 1A, an air heat exchanger 1B, an air heat exchanger 1C, an air heat exchanger 1D, and a rectangular parallelepiped machine room 4, which constitute a refrigeration cycle on the heat source side. Fan 5A, fan 5B, fan 5C, and fan 5D. The air heat exchanger 1A is a first heat exchanger of the present invention, the air heat exchanger 1B is a second heat exchanger of the present invention, and the air heat exchanger 1C is a third heat exchange of the present invention And the air heat exchanger 1D is the fourth heat exchanger of the present invention.

A ceiling frame 60 is provided above the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D. The sky frame 60 is provided with the above-mentioned fan 5A, fan 5B, fan 5C, and fan 5D. The fan 5A, the fan 5B, the fan 5C, and the fan 5D are each covered with a fan guard (not shown).

The space which the machine room 4 occupies in FIG. 1 is shown by the dotted line. The machine room 4 has an underframe 41, four portals, four intermediate columns, and an upper beam 44. The four portals are a portal 42A, a portal 42B, a portal 42C, and a portal 42D. The four middle columns are a middle column 43A, a middle column 43B, a middle column 43C, and a middle column 43D. The underframe 41 is a plate-like member having a rectangular shape. The portals 42A, the portals 42B, the portals 42C, and the portals 42D are provided to extend in the direction orthogonal to the underframe 41 at the four corners of the underframe 41. The intermediate column 43A and the intermediate column 43B are provided at an interval between the portal column 42A and the portal column 42C in the longitudinal direction of the underframe 41. The intermediate column 43C and the intermediate column 43D are provided at an interval between the portal column 42B and the portal column 42D in the longitudinal direction of the underframe 41. The intermediate column 43A, the intermediate column 43B, the intermediate column 43C, and the intermediate column 43D are provided to extend in the direction orthogonal to the underframe 41. The upper beam 44 is provided on the portals 42A, the portals 42B, the portals 42C, and the portals 42D, and the

intermediate columns

43A, 43B, 43C, and 43D. A plurality of element devices are installed in the machine room 4. The plurality of devices installed in the machine room 4 include the water-side heat exchanger 3, the compressor 31 forming the refrigerant circuit, and the control panel 32. In the following description, the

air heat exchangers

1A, 1B, 1C, and 1D may be collectively referred to as the air heat exchanger 1. In addition, the portals 42A, the portals 42B, the portals 42C, and the portals 42D may be collectively referred to as portals 42. Further, the middle pillar 43A, the middle pillar 43B, the middle pillar 43C, and the middle pillar 43D may be collectively referred to as a middle pillar 43.

Furthermore, as shown in FIG. 2, in the air heat exchanger 1A and the air heat exchanger 1B facing each other in the short direction of the machine room 4, the distance between the end parts far from the machine room 4 is close to the machine room 4. It is inclined to be larger than the distance between the side ends. That is, the air heat exchanger 1A and the air heat exchanger 1B are inclined to form a V when viewed from the side of the heat source unit 100. The air heat exchanger 1C and the air heat exchanger 1D which face each other in the short direction of the machine room 4 are similarly inclined so as to be V-shaped. In the first embodiment, the inclination angle α of the air heat exchanger 1A is 65 degrees to 80 degrees. The inclination angles of the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D are the same.

As shown in FIG. 3, the upper beam 44 of the machine room 4 is provided with a base 10. The base 10 is supported by a portal post 42 and an intermediate post 43. The base 10 is provided with a plurality of rubber sheets 13. The air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D are disposed on the base 10 with the rubber sheet 13 interposed therebetween. And air heat exchanger 1A, air heat exchanger 1B, air heat exchanger 1C, and air heat exchanger 1D are inclined in the above-mentioned mode. A side panel 50 is provided between the air heat exchanger 1A and the air heat exchanger 1C. A side panel 51 is provided between the air heat exchanger 1A and the air heat exchanger 1B. A side panel (not shown) similar to the side panel 50 is provided between the air heat exchanger 1B and the air heat exchanger 1D. Further, a side panel (not shown) similar to the side panel 51 is provided between the air heat exchanger 1C and the air heat exchanger 1D.

FIG. 5 is a diagram schematically showing a configuration of the air heat exchanger of the heat source unit of the first embodiment. FIG. 6 is a view schematically showing the air heat exchanger in the direction of the arrow by cutting the air heat exchanger at the position of line BB in FIG. As shown in FIG. 5, the air heat exchanger 1 is a parallel flow type heat exchanger, and includes a pair of headers 9, a plurality of aluminum flat tubes 7, and a plurality of corrugated fins 8. The plurality of aluminum flat tubes 7 are disposed between the pair of headers 9, and both ends thereof are connected to the headers 9. Between the pair of headers 9, the plurality of aluminum flat tubes 7 are arranged in parallel with an interval, and the respective flat portions face each other. The corrugated fins 8 are provided between opposing flat portions of the plurality of aluminum flat tubes 7.

As shown in FIG. 4, the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D are flat in the aluminum flat tube 7 when viewed from the direction orthogonal to the aluminum flat tube 7. It is bent at an angle of 90 degrees at one position offset from the longitudinal center to one end. That is, when viewed from one end of the header 9, the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D have an L shape. The air heat exchanger 1A and the air heat exchanger 1B face each other along the short direction of the machine room 4, and the air heat exchanger 1C and the air heat exchanger 1D face each other along the short direction of the machine room 4. doing. Further, the air heat exchanger 1A and the air heat exchanger 1C are juxtaposed along the longitudinal direction of the machine chamber 4, and the air heat exchanger 1B and the air heat exchanger 1D are juxtaposed along the longitudinal direction of the machine chamber 4 It is done. Further, the short side 1AS of the air heat exchanger 1A and the short side 1BS of the air heat exchanger 1B face each other along the short direction of the machine chamber 4, and the short side 1CS of the air heat exchanger 1C and the air The short side 1DS of the heat exchanger 1D is opposed along the short direction of the machine room 4. The long side 1AL of the air heat exchanger 1A and the long side 1CL of the air heat exchanger 1C are juxtaposed along the longitudinal direction of the machine chamber 4, and the long side 1BL of the air heat exchanger 1B and the air heat The long side portions 1DL of the exchanger 1D are juxtaposed along the longitudinal direction of the machine room 4. Therefore, the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D constitute a rectangular frame as a whole. The corner 1AE of the air heat exchanger 1A, the corner 1BE of the air heat exchanger 1B, the corner 1CE of the air heat exchanger 1C, and the corner 1DE of the air heat exchanger 1D, which are bent at 90 degrees, Located at the corner of the rectangle.

The heat source unit 100 of the first embodiment is arranged such that the flow direction of the supplied air intersects the long side of the aluminum flat tube 7 of the air heat exchanger 1. Therefore, the supplied air is guided between the opposing flat portions of the plurality of aluminum flat tubes 7 and flows along the width direction orthogonal to the longitudinal direction in the aluminum flat tubes 7.

FIG. 7 is a figure for demonstrating the effect at the time of using a flat tube for an air heat exchanger. In FIG. 7, the flow of air supplied to the heat source unit 100 is indicated by an arrow. As described above, in the first embodiment, the heat transfer tube of the air heat exchanger 1 is the aluminum flat tube 7, and the air supplied to the heat source unit 100 is in the width direction orthogonal to the longitudinal direction in the aluminum flat tube 7. Flow along. As shown in FIG. 7, the surface area of the air supplied to the heat source unit 100 in contact with the aluminum flat tube 7 is larger than that in the case where a heat transfer tube is a circular tube. Therefore, according to the first embodiment, heat is generated when the heat transfer tube of the air heat exchanger is used with a smaller number of heat transfer tubes than when the heat transfer tube of the air heat exchanger is used with a circular tube. The same heat exchange area as the exchange area can be secured. As a result, the manufacturing cost of the heat source unit 100 can be reduced.

FIG. 8 is a figure for demonstrating the effect at the time of making an air heat exchanger incline and arrange | positioning. When a flat tube is used for the heat transfer tube of the air heat exchanger, it is conceivable that dew condensation water generated at the time of heating operation is retained at the flat portion of the flat tube. In the first embodiment, the air heat exchangers 1 opposed in the lateral direction of the machine room 4 are inclined to be V-shaped. Therefore, according to the first embodiment, as shown in FIG. 8, the dew condensation water 16 does not stay in the flat portion of the aluminum flat tube 7 but flows down in the vertical direction. As a result, it is possible to prevent the occurrence of freezing in the air heat exchanger 1 during the heating operation, and it is possible to perform the heating operation while maintaining high heat exchange performance.

FIG. 9 and FIG. 10 are diagrams schematically showing modifications of the arrangement of the air heat exchanger. In the first embodiment, the air heat exchanger 1 is bent in an L shape, and the long side extends in the longitudinal direction of the machine chamber 4 and the short side extends in the short direction of the machine chamber 4. It is not limited to this. As shown in FIG. 9, the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D may be configured. That is, corner 1AF of air heat exchanger 1A, corner 1BF of air heat exchanger 1B, corner 1CF of air heat exchanger 1C, and corner 1DF of air heat exchanger 1D are each greater than 90 degrees. Let it be an angle. The long side 1AL of the air heat exchanger 1A and the long side 1CL of the air heat exchanger 1C are juxtaposed along the longitudinal direction of the machine chamber 4, and the long side 1BL of the air heat exchanger 1B and the air heat exchanger 1D The long side portions 1DL are juxtaposed along the longitudinal direction of the machine room 4. The short sides 1AS, 1BS, 1CS, and 1DS of the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D intersect the short direction of the machine room 4.

Further, as shown in FIG. 10, even when the air heat exchanger 1A is viewed from the direction orthogonal to the aluminum flat tube 7, the corner 1AG may be bent at an obtuse angle at the center in the longitudinal direction of the aluminum flat tube 7. Good. The corner 1BG of the air heat exchanger 1B, the corner 1CG of the air heat exchanger 1C, and the corner 1DG of the air heat exchanger 1D have the same configuration. Then, the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat so that the corner 1AG, the corner 1BG, the corner 1CG, and the corner 1DG face outward of the heat source unit 100. Exchange 1D is arranged.

Although the air heat exchanger 1 of the first embodiment is a parallel flow type heat exchanger, it is not limited thereto. A fin and tube type heat exchanger may be used as an air heat exchanger, in which a plurality of plate-like fins are disposed between a pair of headers 9 and an aluminum flat tube penetrates the plurality of fins. FIG. 11 is a diagram for explaining the effect of the modification of the first embodiment. FIG. 11 shows a cross section of the fin-and-tube type air heat exchanger cut at the same position as the line BB in FIG. The air heat exchanger 110 has a plate-like fin 180 and an aluminum flat tube 170. The aluminum flat tube 170 penetrates the fin 180. As shown in FIG. 11, by arranging the air heat exchanger 110 as described above, the condensed water 16 generated during the heating operation does not stay on the surface of the flat tube of the aluminum flat tube 170, The same effect as described above can be obtained.

Second Embodiment
FIG. 12 is a diagram schematically showing the heat source exchanger when the heat source unit according to Embodiment 2 of the present invention is viewed from above. The same components as the components of the first embodiment are given the same reference numerals as in FIGS. 1 to 11. In the heat source unit 200 according to the second embodiment, the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D are arranged in the same manner as the embodiment shown in FIG. There is. The heat source unit 200 has two water sprinkling pipes 18 and a plurality of water sprinkling nozzles 19. The water sprinkling pipe 18 is made of resin. The water sprinkling pipe 18 and the water sprinkling nozzle 19 face each other between the air heat exchanger 1A and the air heat exchanger 1B facing in the short direction of the machine room 4 and along the short direction of the machine room 4 It is disposed between the air heat exchanger 1C and the air heat exchanger 1D. In other words, inside the rectangular space formed by the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D, the water injection piping 18 and the plurality of water injection nozzles 19 It is arranged. The two water spray pipes 18 are disposed parallel to each other along the longitudinal direction of the machine room 4. The plurality of water spray nozzles 19 are attached to two water spray pipes 18 toward the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D. The water supplied to the water sprinkling pipe 18 is injected to the air heat exchanger 1A, the air heat exchanger 1B, the air heat exchanger 1C, and the air heat exchanger 1D through the water sprinkling nozzle 19.

FIG. 13: is a figure which shows typically the state which injected water from the water spray nozzle to the air heat exchanger. When the chiller device on which the heat source unit 200 is mounted is performing a cooling operation, it is difficult to obtain the cooling performance of the heat source unit 200 in an environment where the outside air temperature exceeds 35 ° C. Ru. When the water sprinkling operation is performed, water is supplied to the water sprinkling pipe 18 and the supplied water is jetted from the water sprinkling nozzle 19 to the air heat exchanger 1. A water droplet 20 hits the end on the side where the is placed. In the second embodiment, as in the first embodiment, the air heat exchanger 1 is disposed to be inclined in a V shape, and the flat aluminum tube 7 is inclined as shown in FIG. Therefore, the water droplet 20 which hits the end on the side where the water spray piping 18 is arranged among the both ends of the aluminum flat tube 7 flows in the flat part of the aluminum flat tube 7 and is vertical from the opposite end Dripping in the direction.

When the air heat exchanger 1 is not inclined, the water droplets 20 that hit the end of the aluminum flat tube 7 on the side where the water spray piping 18 is disposed is the opposite side of the aluminum flat tube 7 It hangs down in the vertical direction without flowing to the end of the. On the other hand, according to the second embodiment, since the water droplets 20 flow through the flat portion of the aluminum flat tube 7, it is possible to obtain a higher water sprinkling effect compared to the case where the air heat exchanger 1 is not inclined. The cooling performance of the unit 200 can be further enhanced.

Although the air heat exchanger 1 of the second embodiment is a parallel flow type heat exchanger, it is not limited to this. The above-described water sprinkling pipe 18 and water sprinkling nozzle 19 may be provided in a heat source unit having a fin-and-tube type air heat exchanger similar to the air heat exchanger of FIG. FIG. 14: is a figure which shows typically the state which injected water from the water spray nozzle to the air heat exchanger of the modification of Embodiment 2. FIG. FIG. 14 shows a cross section cut at the same position as the line BB in FIG. By tilting the air heat exchanger 110 as described above, the water droplets 20 which are jetted from the water spray nozzle 19 and hit the end of the aluminum flat tube 7 on the side where the water spray piping 18 is disposed are It flows through the flat part of the aluminum flat tube 7 and drops from the opposite end in the vertical direction. Therefore, also in this modification, the same effect as described above can be obtained.

Third Embodiment
FIG. 15 is a view schematically showing a short side portion of the air heat exchanger. FIG. 15 shows the short side 1DS of the air heat exchanger 1D of FIG. 4 in the direction of the arrow C. As described above, in the air heat exchanger 1D, the short side 1DS is bent at an angle of 90 degrees with respect to the long side 1DL, and is along the short direction of the machine chamber 4. Therefore, since the inclination direction of the air heat exchanger 1D and the longitudinal direction of the corrugated fins 8 of the short side 1DS of the air heat exchanger 1D coincide with each other, dew condensation water generated during heating operation is corrugated as shown in FIG. It may stay in the valleys of the fins 8. The same applies to the air heat exchanger 1A, the air heat exchanger 1B, and the air heat exchanger 1C.

On the other hand, as shown in FIG. 9 or FIG. 10, when the air heat exchanger 1D is configured, the longitudinal direction of the corrugated fins 8 of the short side portion 1DS of the air heat exchanger 1D is the same as that of the air heat exchanger 1D. It will intersect with the direction of inclination. Therefore, the dew condensation water which flowed in into the valley part of corrugate fin 8 of short side part 1DS falls without staying by falling because air heat exchanger 1D inclines. The same applies to the air heat exchanger 1A, the air heat exchanger 1B, and the air heat exchanger 1C.

Therefore, in the third embodiment, even when the air heat exchanger 1 is bent at an angle of 90 degrees as shown in FIG. 4, the corrugated fins 8 are configured so that condensation water does not stay in the short side portion. FIG. 16 is a view schematically showing a mode of welding of the corrugated fins in the air heat exchanger of the third embodiment. FIG. 16 schematically shows the air heat exchanger 1 of the third embodiment in the direction of the arrows by cutting it at the position of the line DD in FIG. In the third embodiment, the corrugated fins 8 are provided to be inclined with respect to the longitudinal direction of the aluminum flat tube 7. The corrugated fins 8 are welded to the aluminum flat tube 7. When the air heat exchanger 1 configured as described above is bent at an angle of 90 degrees as shown in FIG. 4 and is disposed inclined as shown in FIG. 2, in the short side portion of the air heat exchanger 1, The positions of both ends in the lateral direction of the corrugated fins 8 have a difference in the vertical direction. Accordingly, the condensed water flowing into the valley portion of the corrugated fin 8 at the short side portion of the air heat exchanger 1 flows out of the corrugated fin 8 without staying in the valley portion. According to the third embodiment, dew condensation water generated in the heating operation does not stay in the flat portion of the aluminum flat tube 7 nor in the valley portion of the corrugated fin 8 and the air heat exchanger 1 in the heating operation Can prevent the occurrence of icing more effectively. Therefore, heating operation can be performed while maintaining high heat exchange performance.

Fourth Embodiment
The corrugated fins 8 of the air heat exchanger 1 are configured such that the center in the lateral direction is higher than the ends in the lateral direction. The air heat exchanger configured in this way is bent at an angle of 90 degrees as shown in FIG. 4 and is disposed obliquely as shown in FIG. Then, in the short side portion of the air heat exchanger, the position of the central portion in the lateral direction of the corrugated fin is positioned higher than the positions of the both ends in the lateral direction. As a result, the condensed water flowing into the valleys of the corrugated fins at the short side of the air heat exchanger flows out of the corrugated fins without staying in the valleys. Therefore, the same effect as the third embodiment can be obtained.

Embodiment 5
An opening is formed in the corrugated fin 8 of the air heat exchanger 1 similar to the air heat exchanger 1 described above. The opening is formed in a size that does not affect the heat exchange efficiency of the corrugated fin. The air heat exchanger 1 configured as described above is bent at an angle of 90 degrees as shown in FIG. 4 and is disposed inclined as shown in FIG. In the short side of the air heat exchanger, dew condensation water generated during heating operation falls vertically from the opening of the corrugated fin. Therefore, the same effect as the third embodiment can be obtained.

Sixth Embodiment
The corrugated fins of the air heat exchanger similar to the above-described air heat exchanger 1 are subjected to water repellent finish. The air heat exchanger configured in this way is bent at an angle of 90 degrees as shown in FIG. 4 and is disposed obliquely as shown in FIG. In the short side of the air heat exchanger, condensation water generated during heating operation can be repelled. Therefore, the same effect as the third embodiment can be obtained.

Embodiment 7
FIG. 17 is a perspective view of a heat source unit according to Embodiment 7 of the present invention. FIG. 18 is a side view of the heat source unit of the seventh embodiment. FIG. 19 is a diagram schematically showing the arrangement of the air heat exchanger in the heat source unit of the seventh embodiment. FIG. 18 shows the heat source unit from the direction of arrow C in FIG. FIG. 19 shows a plurality of air heat exchangers from above the heat source unit. In FIGS. 17 to 19, the same components as the components of the first embodiment are denoted by the same reference numerals as those in FIGS. The heat source unit 300 includes four air heat exchangers 301A, an air heat exchanger 301B, an air heat exchanger 301C, an air heat exchanger 301D, and a rectangular parallelepiped machine room 4, which constitute a refrigeration cycle on the heat source side. Fan 5A, fan 5B, fan 5C, and fan 5D. The air heat exchanger 301A is a first heat exchanger of the present invention, the air heat exchanger 301B is a second heat exchanger of the present invention, and the air heat exchanger 301C is a third heat exchange of the present invention And the air heat exchanger 301D is the fourth heat exchanger of the present invention. In the following description, the

air heat exchangers

301A, 301B, 301C, and 301D may be collectively referred to as the air heat exchanger 301.

The air heat exchanger 301 is a parallel flow type heat exchanger, and includes a pair of headers, a plurality of aluminum flat tubes, and a plurality of corrugated fins. The specific configuration is the same as that of the air heat exchanger 1 of the first embodiment described with reference to FIG. That is, the plurality of aluminum flat tubes are disposed between the pair of headers, and both ends thereof are connected to the headers. Between a pair of headers, a plurality of aluminum flat tubes are arranged in parallel at intervals, and respective flat portions face each other. The corrugated fins are provided between the opposing flat portions of the plurality of aluminum flat tubes.

A side panel 310 is provided between the air heat exchanger 301A and the air heat exchanger 301C. A side panel 311 is provided between the air heat exchanger 301A and the air heat exchanger 301B. A side panel (not shown) similar to the side panel 310 is provided between the air heat exchanger 301B and the air heat exchanger 301D. Further, a side panel (not shown) similar to the side panel 311 is provided between the air heat exchanger 301C and the air heat exchanger 301D. A blocking panel 312 is provided between the air heat exchanger 301A and the side panel 311. Similarly, a blocking panel 312 is provided between the air heat exchanger 301 B and the side panel 311. A closing panel (not shown) similar to the closing panel 312 is provided between the air heat exchanger 301C and the side panel between the air heat exchanger 301C and the air heat exchanger 301D. A closing panel (not shown) similar to the closing panel 312 is provided between the air heat exchanger 301D and the side panel between the air heat exchanger 301C and the air heat exchanger 301D. The side panel 311 and the closing panel 312 are omitted in FIG.

As shown in FIG. 18, in the air heat exchanger 301A and the air heat exchanger 301B facing each other in the short direction of the machine room 4, the distance between the end parts far from the machine room 4 is closer to the machine room 4 It is inclined to be larger than the distance between the ends. That is, the air heat exchanger 301A and the air heat exchanger 301B are inclined to form a V when viewed from the side of the heat source unit 300. The air heat exchanger 301C and the air heat exchanger 301D which face each other in the short direction of the machine room 4 are also inclined to be V-shaped similarly. In the seventh embodiment, the inclination angle β of the air heat exchanger 301A is 65 degrees to 80 degrees. The inclination angles of the air heat exchanger 301B, the air heat exchanger 301C, and the air heat exchanger 301D are the same.

As shown in FIG. 19, unlike the air heat exchanger 1 of the above-mentioned Embodiment 1 and Embodiment 2, the air heat exchanger 301 has a flat plate shape and is orthogonal to the aluminum flat tube. It is not bent when viewed from the direction. The air heat exchanger 301A and the air heat exchanger 301B face each other along the short direction of the machine room 4, and the air heat exchanger 301C and the air heat exchanger 301D face each other along the short direction of the machine room 4. doing. The air heat exchanger 301A and the air heat exchanger 301C are juxtaposed along the longitudinal direction of the machine room 4, and the air heat exchanger 301B and the air heat exchanger 301D are juxtaposed along the longitudinal direction of the machine room .

Similar to the heat source unit 100 according to Embodiment 1, the heat source unit 300 according to Embodiment 7 is disposed such that the flow direction of the supplied air intersects the long side of the flat aluminum tube of the air heat exchanger 1. Be done. Therefore, the supplied air is guided between the opposing flat portions of the plurality of aluminum flat tubes, and flows along the width direction orthogonal to the longitudinal direction in the aluminum flat tubes.

According to the seventh embodiment, an aluminum flat tube is used for the air heat exchanger 301. Therefore, the heat exchange area is secured the same as the heat exchange area when using a circular tube for the heat transfer tube of the air heat exchanger with a smaller number of heat transfer tubes than when the circular tube is used for the heat transfer tube of the air heat exchanger. can do. As a result, the manufacturing cost of the heat source unit 300 can be reduced. Further, according to the seventh embodiment, the air heat exchangers 301 opposed in the lateral direction of the machine room 4 are inclined to be V-shaped. Therefore, according to the seventh embodiment, the dew condensation water generated during the heating operation does not stay in the flat portion of the aluminum flat tube, but flows down in the vertical direction. As a result, it is possible to prevent the occurrence of icing in the air heat exchanger 301 during the heating operation, and it is possible to perform the heating operation while maintaining high heat exchange performance.

Furthermore, the air heat exchanger 301 of the seventh embodiment is not bent when viewed from the direction orthogonal to the aluminum flat tube. In other words, no bending process is required in the manufacture of the air heat exchanger 301. Therefore, manufacture of the air heat exchanger 301 is easy.

Eighth Embodiment
FIG. 20 is a view schematically showing a heat source exchanger when the heat source unit according to Embodiment 8 of the present invention is viewed from above. The same components as those of the second embodiment and the seventh embodiment are denoted by the same reference numerals as those in FIGS. 12 and 17-19. In the heat source unit 400 of the eighth embodiment, the air heat exchanger 301A, the air heat exchanger 301B, the air heat exchanger 301C, and the air heat exchanger 301D are arranged in the same manner as the manner shown in FIG. There is. Further, the air heat exchanger 301A, the air heat exchanger 301B, the air heat exchanger 301C, and the air heat exchanger 301D are disposed obliquely as in FIG.

The water sprinkling pipe 18 and the water sprinkling nozzle 19 face each other between the air heat exchanger 301A and the air heat exchanger 301B facing in the short direction of the machine room 4 and along the short direction of the machine room 4 It is disposed between the air heat exchanger 301C and the air heat exchanger 301D. That is, as in the second embodiment, the sprinkle piping 18 and the plurality of sprinkle nozzles 19 are formed of the air heat exchanger 301A, the air heat exchanger 301B, the air heat exchanger 301C, and the air heat exchanger 301D. It is disposed inside the space of shape. The two water spray pipes 18 are disposed parallel to each other along the longitudinal direction of the machine room 4. The plurality of water spray nozzles 19 are attached to two water spray pipes 18 toward the air heat exchanger 301A, the air heat exchanger 301B, the air heat exchanger 301C, and the air heat exchanger 301D. The water supplied to the water sprinkling pipe 18 is injected to the air heat exchanger 301A, the air heat exchanger 301B, the air heat exchanger 301C, and the air heat exchanger 301D through the water sprinkling nozzle 19.

At the time of execution of the water sprinkling operation, when water is supplied to the water sprinkling pipe 18 and the supplied water is jetted from the water sprinkling nozzle 19 to the air heat exchanger 301, the water sprinkling pipe 18 is A drop of water falls on the end of the side where it is placed. In the eighth embodiment, as in the seventh embodiment, the air heat exchanger 301 is disposed to be inclined in a V-shape, and the flat aluminum tube is also inclined. Therefore, the water drop which hit the end on the side where the water distribution piping is arranged among the both ends of the aluminum flat tube flows through the flat part of the aluminum flat tube and drops in the vertical direction from the opposite end. . Therefore, as in the second embodiment, a higher water sprinkling effect can be obtained as compared with the case where the air heat exchanger 1 is not inclined, and the cooling performance of the heat source unit 400 can be further enhanced.

Although the air heat exchangers 301 of the seventh embodiment and the eighth embodiment are parallel flow type heat exchangers, they are not limited to this. A fin and tube type heat exchanger may be used as an air heat exchanger, in which a plurality of plate-like fins are disposed between a pair of headers, and an aluminum flat tube penetrates the plurality of fins.

1 air heat exchanger, 1A air heat exchanger, 1AE corner, 1AF corner, 1AG corner, 1AL long side, 1AS short side, 1B air heat exchanger, 1BE corner, 1BF corner, 1BG corner Part, 1BL long side, 1BS short side, 1C air heat exchanger, 1CE corner, 1CF corner, 1CG corner, 1CL long side, 1CS short side, 1D air heat exchanger, 1DE corner, 1DF corner, 1DG corner, 1DL long side, 1DS short side, 3 water side heat exchanger, 4 machine room, 5A fan, 5B fan, 5C fan, 5D fan, 7 aluminum flat tube, 8 corrugated fin, 9 header, 10 base, 13 rubber sheet, 16 dew condensation water, 18 water sprinkling piping, 19 water sprinkling nozzle, 20 water drops, 31 compressor, 32 control board, 41 frame, 2 portals, 42A portal columns, 42B portal columns, 42C portal columns, 42D portal columns, 43 intermediate columns, 43A intermediate columns, 43B intermediate columns, 43C intermediate columns, 43D intermediate columns, 44 upper beams, 50 side panels, 51 side panels, 60 sky frames , 100 heat source unit, 110 air heat exchanger, 170 aluminum flat tube, 180 fin, 200 heat source unit, 300 heat source unit, 301 air heat exchanger, 301A air heat exchanger, 301B air heat exchanger, 301C air heat exchanger , 301D Air Heat Exchanger, 310 Side Panels, 311 Side Panels, 312 Closed Panels.

Claims

A heat source unit comprising: a plurality of heat exchangers having a plurality of fins and a plurality of flat tubes; and a rectangular parallelepiped machine room,
The plurality of heat exchangers are provided at the top of the machine room,
Among the plurality of heat exchangers, in the pair of heat exchangers disposed opposite to each other along the short direction of the machine chamber, the distance between the end portions far from the machine chamber is the machine chamber A heat source unit which is inclined so as to be larger than the distance between the end portions on the near side.
The plurality of heat exchangers include a first heat exchanger, a second heat exchanger, a third heat exchanger, and a fourth heat exchanger.
The first heat exchanger and the second heat exchanger face each other along the short direction of the machine chamber, and the third heat exchanger and the fourth heat exchanger are the machine chamber. And the first heat exchanger and the third heat exchanger are juxtaposed along the longitudinal direction of the machine chamber, and the second heat exchanger and the fourth heat exchanger are The heat source unit according to claim 1, wherein the heat exchangers of (1) are juxtaposed along the longitudinal direction of the machine chamber.
The heat source unit according to claim 2, wherein the first to fourth heat exchangers are bent at one place in a longitudinal direction when viewed from a direction orthogonal to the flat tube.
The first to fourth heat exchangers are bent at an angle of 90 degrees so as to have a long side portion and a short side portion when viewed in a direction orthogonal to the flat tube,
The short side of the first heat exchanger and the short side of the second heat exchanger face each other along the short direction of the machine chamber,
The short side of the third heat exchanger and the short side of the fourth heat exchanger face each other along the short direction of the machine chamber,
The long side portion of the first heat exchanger and the long side portion of the third heat exchanger are juxtaposed along the longitudinal direction of the machine chamber,
The heat source unit according to claim 3, wherein the long side portion of the second heat exchanger and the long side portion of the fourth heat exchanger are juxtaposed along the longitudinal direction of the machine chamber.
The first to fourth heat exchangers are bent at an angle larger than 90 degrees so as to have a long side portion and a short side portion when viewed in a direction orthogonal to the flat tube,
The long side portion of the first heat exchanger and the long side portion of the third heat exchanger are juxtaposed along the longitudinal direction of the machine chamber,
The heat source unit according to claim 3, wherein the long side portion of the second heat exchanger and the long side portion of the fourth heat exchanger are juxtaposed along the longitudinal direction of the machine chamber.
The first to fourth heat exchangers have corner portions bent at the center in the longitudinal direction when viewed from the direction orthogonal to the flat tube,
The heat source unit according to claim 3, wherein each of the first to fourth heat exchangers is arranged such that the corner portion faces the outside of the heat source unit.
The heat source unit according to claim 2, wherein the first to fourth heat exchangers have a flat plate shape.
Furthermore, it comprises a water spray pipe and a water spray nozzle attached to the water spray pipe,
The heat source unit according to claim 1, wherein the water sprinkling pipe and the water sprinkling nozzle are disposed between the pair of heat exchangers facing each other in the short direction of the machine room.
The plurality of heat exchangers are parallel flow type heat exchangers, the plurality of fins are corrugated fins, and the corrugated fins are provided to be inclined with respect to the longitudinal direction of the flat tube. The heat source unit according to Item 1.
The plurality of heat exchangers are parallel flow type heat exchangers, the plurality of fins are corrugated fins, and the corrugated fins are formed such that the central part in the lateral direction is higher than the both ends in the lateral direction The heat source unit according to claim 1 configured.
The heat source unit according to claim 1, wherein the plurality of heat exchangers are parallel flow type heat exchangers, the plurality of fins are corrugated fins, and an opening is formed in the corrugated fins.
The heat source unit according to claim 1, wherein the plurality of heat exchangers are parallel flow type heat exchangers, the plurality of fins are corrugated fins, and the corrugated fins are subjected to a water repellent finish.