Gas heat pump type air conditioning system and heat exchanger for outdoor unit

Abstract

The invention provides a gas heat pump type air conditioning system which can defrost frost generated on corrugated fins during heating operation. A gas heat pump air conditioning system is provided with an outdoor unit exchanger, a compressor, a drive source for driving the compressor, and a radiator for cooling the drive source. The outdoor unit exchanger is provided with: a plurality of flat perforated pipes which extend in a ventilation direction and a first direction orthogonal to the ventilation direction and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction; and a plurality of corrugated fins which are arranged in parallel in the second direction between the plurality of flat perforated pipes, protrude to the downstream side in the ventilation direction with respect to the plurality of flat perforated pipes, and extend in a wavy shape in the first direction. The radiator is adjacent to the outdoor unit exchanger on the downstream side in the ventilation direction.

Description

Technical Field

[0001] The present disclosure relates to a gas heat pump type air conditioning system and a heat exchanger for an outdoor unit. Background Art

[0002] In Patent Document 1, there is disclosed a parallel flow type outdoor heat exchanger for a heat pump, which is formed by alternately laminating a plurality of flat tubes arranged in parallel and corrugated fins in a ventilation right angle direction. According to Patent Document 1, louvers divided into a plurality of groups are provided only on the downstream side of a certain length along the ventilation direction from the ventilation upstream end of the corrugated fins. Thereby, a parallel flow type outdoor heat exchanger for a heat pump is provided, which prevents blockage caused by frosting on the corrugated fins at the ventilation upstream portion during the heating operation of the air conditioner.

[0003] Prior Art Documents

[0004] Patent Documents

[0005] Patent Document 1: Japanese Patent Laid-Open No. 06-147785

[0006] In the parallel flow type outdoor heat exchanger for a heat pump described in Patent Document 1, although consideration is given to suppressing blockage of the ventilation path caused by frosting, it does not have a structure that takes defrosting into account. Summary of the Invention

[0007] Problems to be Solved by the Invention

[0008] An object of the present invention is to provide a gas heat pump type air conditioning system that can defrost the frost generated on the corrugated fins during the heating operation.

[0009] Means for Solving the Problems

[0010] The present disclosure provides a gas heat pump type air conditioning system, comprising:

[0011] a heat exchanger for an outdoor unit, which includes a plurality of flat porous tubes and a plurality of corrugated fins, the plurality of flat porous tubes extend in a ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged side by side in a second direction orthogonal to the ventilation direction and the first direction, the plurality of corrugated fins are arranged side by side between the plurality of flat porous tubes in the second direction, protrude toward the downstream side in the ventilation direction with respect to the plurality of flat porous tubes, and extend in a wavy shape in the first direction;

[0012] a compressor;

[0013] a drive source for driving the compressor; and

[0014] A radiator, which is adjacent to the outdoor unit heat exchanger on the downstream side in the ventilation direction, is used to cool the drive source.

[0015] In the gas heat pump air conditioning system according to the present disclosure, since the corrugated fins protrude more toward the downstream side in the ventilation direction than the flat porous tubes, and the radiator is adjacent to the outdoor unit exchanger on the downstream side, it is possible to efficiently defrost the frost generated on the corrugated fins using the heat of the radiator. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 is a refrigerant circuit diagram of the gas heat pump air conditioning system of this embodiment.

[0017] Figure 2 is a perspective view of the outdoor unit heat exchanger and the radiator of the first embodiment.

[0018] Figure 3 is a side view of the outdoor unit heat exchanger and the radiator of the first embodiment.

[0019] Figure 4 is a perspective view of the flat porous tube and the corrugated fins of the first embodiment.

[0020] Figure 5 is a top view of the flat porous tube and the corrugated fins of the first embodiment.

[0021] Figure 6 is a perspective view of a part of the flat porous tube and the corrugated fins of the first embodiment removed.

[0022] Figure 7 is along Figure 2 a cross-sectional view of the outdoor unit heat exchanger of the first embodiment taken along line VII-VII.

[0023] Figure 8 is a perspective view of the outdoor unit heat exchanger and the radiator of the second embodiment.

[0024] Figure 9 is a side view of the outdoor unit heat exchanger and the radiator of the second embodiment.

[0025] Figure 10 is Figure 8 a perspective view of the flat porous tube and the corrugated fins of the second embodiment with part V1 enlarged and shown partially.

[0026] Figure 11 is Figure 8 a perspective view of the outdoor unit heat exchanger of the third embodiment with part V2 enlarged and shown partially.

[0027] Figure 12is a perspective view of the heat exchanger for an outdoor unit of the fourth embodiment, which is Figure 11 the same as that shown in

[0028] Figure 13 is a perspective view of the heat exchanger for an outdoor unit of the fifth embodiment, which is Figure 11 the same as that shown in

[0029] Figure 14 Shows the experimental results of the heat exchanger for an outdoor unit of this embodiment.

[0030] Figure 15 Shows the experimental results of the heat exchanger for an outdoor unit of this embodiment.

[0031] Explanation of reference numerals:

[0032] 1: Gas heat pump air conditioning system

[0033] 2: Outdoor unit

[0034] 5: Compressor

[0035] 6, 6a, 6b, 6c, 6d: Heat exchangers for outdoor units

[0036] 61: Core

[0037] 61a: First core

[0038] 61b: Second core

[0039] 62: Flat porous tube

[0040] 63: Corrugated fin

[0041] 63a: First corrugated fin

[0042] 63b: Second corrugated fin

[0043] 631: Downstream protruding part

[0044] 632: Upstream protruding part

[0045] 633: Downstream louver slit part

[0046] 634: Upstream louver slit part

[0047] 635: Central part

[0048] 636: Drain hole

[0049] 637: Main surface

[0050] 64: Header

[0051] 14: Radiator

[0052] d1: Header outer diameter

[0053] w1: Ventilation direction width of the corrugated fin

[0054] w2: Ventilation direction width of the flat porous tube

[0055] H1: First corrugated fin height. Detailed implementation mode

[0056] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings.

[0057] [First Embodiment]

[0058] The gas heat pump type air conditioning system 1 of the present disclosure is a system in which a compressor for circulating a refrigerant in the system is driven by a gas engine as an internal combustion engine in an air conditioning system. Figure 1 The refrigerant circuit diagram of the gas heat pump type air conditioning system of this embodiment is shown.

[0059] The gas heat pump type air conditioning system 1 includes: an outdoor unit 2 provided outdoors, an indoor unit 3 provided indoors, and an air conditioning refrigerant pipe 4 connecting the outdoor unit 2 and the indoor unit 3. The outdoor unit 2 includes: a compressor 5 that compresses the refrigerant into a high-temperature and high-pressure state and circulates the refrigerant in the system, an outdoor unit heat exchanger 6 for exchanging heat between the refrigerant and external gas, an outdoor unit fan 7 that blows external gas to the outdoor unit heat exchanger 6, an expansion valve 8 that decompresses the high-pressure refrigerant, and a four-way valve 9 that switches between cooling and heating by switching the flow direction of the refrigerant.

[0060] The outdoor unit 2 further includes: a drive source 12 of the gas engine that drives the compressor 5, a cooling refrigerant pipe 13 for cooling the drive source 12, and a radiator 14 for cooling the heat of the refrigerant in the cooling refrigerant pipe 13. The air conditioning refrigerant pipe 4 and the cooling refrigerant pipe 13 are independent of each other, and the refrigerant in the air conditioning refrigerant pipe 4 and the refrigerant in the cooling refrigerant pipe 13 do not mix.

[0061] The indoor unit 3 includes: an indoor unit heat exchanger 10 that exchanges heat with the internal gas, and an indoor unit fan 11 that blows the internal gas to the indoor unit heat exchanger 10 and blows the internal gas that has exchanged heat with the indoor unit heat exchanger 10 back into the room again.

[0062] Next, the operation of the gas heat pump type air conditioning system 1 during heating operation will be described. When the gas heat pump type air conditioning system 1 operates, the compressor 5 is driven, and the refrigerant in the air conditioning refrigerant pipe 4 is compressed and flows along Figure 1It circulates in the direction A1. The refrigerant compressed by the compressor 5 to a high-temperature and high-pressure state exchanges heat with the internal air blown by the indoor unit fan 11 in the indoor heat exchanger 10 of the indoor unit 3, thereby providing heat to the internal air. As a result, the internal air is heated. The refrigerant after passing through the indoor unit 3 passes through the expansion valve 8 of the outdoor unit 2, thereby becoming a low-temperature and low-pressure state. The refrigerant in the low-temperature and low-pressure state exchanges heat with the external air blown by the outdoor unit fan 7 in the outdoor heat exchanger 6, thereby receiving heat from the external air. As a result, the external air is cooled. The subsequent refrigerant is compressed by the compressor 5 again and circulates toward the indoor unit 3 in a high-temperature and high-pressure state.

[0063] A drive source 12 is connected to the compressor 5. By driving the compressor 5, the drive source 12 generates heat. A cooling refrigerant pipe 13 is connected to the drive source 12, and the drive source 12 is cooled by the refrigerant in the cooling refrigerant pipe 13. The refrigerant that has received heat by cooling the heat-generating drive source 12 flows toward the radiator 14 connected to the cooling refrigerant pipe 13 ( Figure 1 in the direction B1), exchanges heat with the external air blown by the outdoor unit fan 7 in the radiator 14, thereby providing heat to the external air. The refrigerant that has provided heat to the external air circulates toward the drive source 12 and cools the drive source 12 again.

[0064] It should be noted that during the refrigeration operation, by using the four-way valve 9 to switch the refrigerant circuit, the refrigerant circulates in the Figure 1 direction A2 (the side opposite to A1). At this time, in each of the heat exchangers 6 and 10, a phenomenon opposite to that during the heating operation occurs. That is, in the indoor heat exchanger 10, the refrigerant receives heat from the internal air and the internal air is cooled, and in the outdoor heat exchanger 6, the refrigerant provides heat to the external air and the external air is heated. The operation of the gas heat pump type air conditioning system 1 described above is the same as that of a normal gas heat pump type air conditioning system.

[0065] Next, with reference to Figure 2 and Figure 3 the configuration of the outdoor heat exchanger 6 and the radiator 14 of the first embodiment will be described. Figure 2 is a perspective view of the outdoor heat exchanger 6 and the radiator 14. In Figure 2 , during the operation of the gas heat pump type air conditioning system 1, air flows toward the front side of the paper surface by the outdoor unit fan 7. Here, the direction orthogonal to the air flow direction (ventilation direction) and vertical is called the first direction ( Figure 1 the up-down direction), and the direction orthogonal to the ventilation direction and the first direction is called the second direction ( Figure 1 the horizontal direction).

[0066] The heat exchanger 6 for the outdoor unit has: a core portion 61 having a plurality of flat porous tubes 62 and a plurality of corrugated fins 63 (see Figure 4 ), and extending in a first direction and a second direction; two flat plate-like side plates 65 connected to both ends of the core portion 61 in the second direction and extending in a ventilation direction and the first direction; and two cylindrical headers 64 connected to both ends of the core portion 61 in the first direction and extending in the second direction. The heat exchanger 6 for the outdoor unit is a so-called microchannel heat exchanger. The refrigerant flowing into the heat exchanger 6 for the outdoor unit through the refrigerant pipe 4 for air conditioners enters one of the headers 64 and flows in the first direction within the core portion 61. During the flow in the first direction within the core portion 61, the refrigerant exchanges heat with the external gas. The refrigerant that has passed through the core portion 61 flows within the other header 64 and flows out from the heat exchanger 6 for the outdoor unit. In Figure 2 , the pipes extend from both headers 64 respectively. The pipe extending from the lower header 64 bends toward the front side of the paper surface (downstream side in the ventilation direction) and then bends upward. Usually, the bending direction of the pipe in the paper surface direction coincides with the downstream side of the ventilation direction.

[0067] The radiator 14 is a so-called cross-flow finned tube heat exchanger composed of a plurality of copper pipes and a plurality of fins, and extends in a first direction and a second direction. The radiator is not limited to a cross-flow finned tube heat exchanger, and may also be other forms of heat exchangers such as a microchannel heat exchanger. The radiator 14 is disposed on the downstream side in the ventilation direction and the lower side in the first direction with respect to the heat exchanger 6 for the outdoor unit. The radiator 14 is positioned with respect to the heat exchanger 6 for the outdoor unit by fixing both end portions of the radiator 14 in the second direction to the side plates 65 of the heat exchanger 6 for the outdoor unit using screws or the like.

[0068] Figure 3 is a side view of the heat exchanger 6 for the outdoor unit and the radiator 14 as viewed from the second direction. Several components such as the side plates 65 are omitted. The radiator 14 is adjacent to the heat exchanger 6 for the outdoor unit on the downstream side in the ventilation direction. Here, "adjacent" in this specification means that the distance between the two is 5 mm or more and 15 mm or less. That is, the distance L1 in the ventilation direction between the radiator 14 and the heat exchanger 6 for the outdoor unit is 5 mm or more and 15 mm or less. Specifically, the distance L1 is the distance in the ventilation direction between the radiator 14 and the corrugated fins 63 of the heat exchanger 6 for the outdoor unit (see Figure 4 , 5 ). The radiator 14 is preferably as close as possible to the corrugated fins 63 without contacting the corrugated fins 63.

[0069] Next, with reference to Figures 4 - 7 the structure of the heat exchanger 6 for the outdoor unit of this embodiment will be described. Figure 4A perspective view showing a part of the core 61 of the heat exchanger 6 for an outdoor unit is shown. The heat exchanger 6 for an outdoor unit includes: a plurality of flat porous tubes 62 that extend along the ventilation direction and the first direction and are arranged in parallel in the second direction; and a plurality of corrugated fins 63 that are arranged in parallel in the second direction between the plurality of flat porous tubes 62, project toward the downstream side and the upstream side in the ventilation direction with respect to the plurality of flat porous tubes 62, and extend in a wavy shape in the first direction. In other words, the plurality of corrugated fins 63 are respectively disposed in a plurality of spaces formed between the plurality of flat porous tubes 62 and are wavy in the first direction.

[0070] Figure 5 is Figure 4 a top view. As Figure 4 , Figure 5 shown, a plurality of small holes 621 are arranged in the end face in the first direction of the flat porous tube 62 along the ventilation direction. The small holes 621 penetrate the flat porous tube 62 in the first direction, and a refrigerant flow path in the first direction is formed in the flat porous tube 62. In addition, the respective flat porous tubes 62 are arranged at equal intervals of about 8 mm in the second direction.

[0071] The corrugated fin 63 is formed in a wave shape, for example, by bending a thin film metal having a thickness of 0.1 mm or less with a prescribed fin pitch P1 (refer to Figure 4 ). The peak portions and the valley portions of the waves of the corrugated fin 63 are joined to the end faces in the second direction of the plurality of flat porous tubes 62 connected on both sides by a method such as furnace brazing. The refrigerant flowing in the flat porous tube 62 exchanges heat with the external gas via the corrugated fin 63 joined to the flat porous tube 62. Since the thickness of the corrugated fin 63 is thin, it is a component that is easily deformed due to contact with other components, etc.

[0072] A hydrophilic coating treatment for improving drainage is performed on the corrugated fin 63. As the hydrophilic coating agent, any one can be used. For example, EXCEL PURE manufactured by Central Motor Co., Ltd. can be used.

[0073] As Figure 5As shown, the corrugated fin 63 has: a central portion 635 that is joined to the flat porous tube 62; a downstream protruding portion 631 that protrudes downstream in the ventilation direction with respect to the flat porous tube 62 at the downstream end of the central portion 635 in the ventilation direction; and an upstream protruding portion 632 that protrudes upstream in the ventilation direction with respect to the flat porous tube 62 at the upstream end of the central portion 635 in the ventilation direction. The length of the downstream protruding portion 631 in the ventilation direction is equal to the length of the upstream protruding portion 632 in the ventilation direction. In addition, the downstream protruding portion 631 and the upstream protruding portion 632 do not contact the flat porous tube 62. Therefore, the heat transfer rate of the downstream protruding portion 631 and the upstream protruding portion 632 is less than the heat transfer rate of the central portion 635 that contacts the flat porous tube 62 through which the refrigerant flows. Compared with the case where the corrugated fin of the first embodiment has only either the downstream protruding portion or the upstream protruding portion, the heat transfer rate of the corrugated fin is uniform in the ventilation direction, so it is easy to efficiently exchange heat with the external gas.

[0074] The corrugated fin 63 also has a downstream louver slit portion 633 and an upstream louver slit portion 634 for increasing the heat transfer rate of the corrugated fin 63 on the downstream side and the upstream side, respectively, in the ventilation direction of the central portion 635. Figure 6 is a perspective view of a part of the core 61 where a part of the flat porous tube 62 and the corrugated fin 63 are removed so that each louver slit portion 633, 634 can be seen. The downstream louver slit portion 633 is a slit that slopes upward toward the downstream side in the ventilation direction. The upstream louver slit portion 634 is a slit that slopes upward toward the upstream side in the ventilation direction. The fluid (air or water) around the corrugated fin 63 can move in the first direction through the louver slit portions 633, 634. The louver slit portions 633, 634 of the present embodiment have the same structure as the louver slit portions described in, for example, Japanese Patent Laid-Open No. 06-147785 and are well-known structures.

[0075] In Figure 4 In the outdoor unit heat exchanger 6, a plurality of water flow paths 66 are provided in the second direction. The water flow paths 66 are formed by two upstream protruding portions 632 and the ventilation direction end face of the flat porous tube 62 on the upstream side in the ventilation direction and extend in the first direction. The water flow path 66 is a path for discharging the water defrosted by the corrugated fin 63. The water flow path 66 is also formed by two downstream protruding portions 631 and the ventilation direction end face of the flat porous tube 62 on the downstream side in the ventilation direction and extends in the first direction.

[0076] Figure 7 is along Figure 2A partial cross-sectional view of the outdoor unit heat exchanger 6 taken along line VII-VII, showing the vicinity of the upper end portion of the outdoor unit heat exchanger 6 in the first direction. The flat porous tube 62 is inserted inside the header 64 and joined by methods such as furnace brazing. In Figure 7 this case, the center of the header 64, the center of the width of the flat porous tube 62 in the ventilation direction, and the center of the width of the corrugated fin 63 in the ventilation direction are aligned in the ventilation direction. The width w1 of the corrugated fin 63 in the ventilation direction is equal to or less than the width of the header 64 in the ventilation direction, i.e., the outer diameter d1, and is larger than the width w2 of the flat porous tube 62 in the ventilation direction. That is, the lengths of the downstream protruding portion 631 and the upstream protruding portion 632 of the corrugated fin 63 in the ventilation direction are determined such that the width w1 is equal to or less than the outer diameter d1 and greater than the width w2. By making the width w1 equal to or less than the outer diameter d1, when the outdoor unit heat exchanger 6 is stored with the surface formed by the first direction and the second direction facing downwards, the possibility of the corrugated fin 63 coming into contact with the ground and deforming can be suppressed. In addition, by making the width w1 larger than the width w2, the space in the ventilation direction of the corrugated fin 63 can be effectively utilized.

[0077] Next, the frosting phenomenon that occurs in the outdoor unit heat exchanger 6 during heating operation and the defrosting method in the present embodiment will be described. In the outdoor unit heat exchanger 6, the refrigerant receives heat from the external air, so the temperature of the refrigerant is about 5°C lower than the external air temperature. That is, for example, when the external air temperature is 0°C, the temperature of the refrigerant is about -5°C. The temperature of the corrugated fin 63 depends on the temperature of the refrigerant flowing in the flat porous tube 62, so it is also about -5°C. If the air passing through the corrugated fin 63 in the ventilation direction is cooled to 0°C or lower by the corrugated fin 63, the moisture in the air becomes frost or ice and adheres to the corrugated fin 63. This phenomenon is called frosting.

[0078] If frost continues to accumulate on the corrugated fins 63 due to frosting, the ventilation passages of the corrugated fins 63 are blocked by the frost, the heat transfer performance of the outdoor unit heat exchanger 6 deteriorates, and further, the performance of the air conditioning system may deteriorate. In order to melt the frost that has formed, that is, to defrost, the following defrosting operation is usually performed: by temporarily switching the four-way valve, the high-temperature and high-pressure refrigerant on the indoor unit side circulates to the outdoor unit side to defrost the outdoor unit heat exchanger. In the gas heat pump type air conditioning system 1 of the present embodiment, the radiator 14 is adjacent to the outdoor unit heat exchanger 6 on the downstream side in the ventilation direction, and the corrugated fin 63 has a downstream protrusion 631 on the downstream side in the ventilation direction, that is, on the radiator 14 side. In addition, the temperature of the radiator 14 is as high as about 85°C. Thus, the heat of the radiator 14 is transferred to the downstream protrusion 631 of the corrugated fin 63 through the air between the radiator 14 and the outdoor unit heat exchanger 6, so that the corrugated fin 63 is heated and the frost accumulated on the corrugated fin 63 is defrosted. That is, in the gas heat pump type air conditioning system 1 of the present embodiment, there is no need to perform the operation of switching the four-way valve, and in addition, even an air conditioning system without a four-way valve can perform efficient defrosting. In addition, at this time, it is preferable that the outdoor unit fan 7 does not operate.

[0079] On the other hand, the melted frost becomes water, and flows downward in the first direction under the action of gravity through the louver slit portions 633 and 634 of the respective corrugated fins 63, accumulates in a drain pan (not shown) separately provided in the outdoor unit 2, and is drained to the outside. In addition, when the defrosting amount is large and water overflows from each of the louver slit portions 633 and 634, the water flows in the second direction along the inclination formed by the corrugation of the corrugated fin 63, and accumulates in the drain pan through the water flow path 66 formed by the two upstream protrusions 632 and the flat porous tube 62 (refer to Figure 4 the water flow direction f1). When water flow is formed in the water flow path 66, the water on the corrugated fin 63 around the water flow path 66 is introduced into the flow of the water flow path 66, so the drainage efficiency is further improved. In the case where there is no water flow path formed by the upstream protrusion, this introduction phenomenon does not occur, so the drainage efficiency is not ideal. In addition, based on multiple experimental results obtained by the inventor, it was confirmed that the phenomenon of water overflowing from each of the louver slit portions 633 and 634 is more likely to occur on the upstream side than on the downstream side in the ventilation direction. This is because the air is cooled as it passes through the corrugated fin 63, so the temperature difference between the temperature of the air and the temperature of the corrugated fin 63 is larger on the upstream side in the ventilation direction. Thus, it is considered that the heat exchange amount on the upstream side in the ventilation direction increases, and the amount of moisture adhering to the corrugated fin becomes larger.

[0080] In addition, since the corrugated fin 63 of the first embodiment is subjected to a hydrophilic coating treatment, the water flowing on the corrugated fin 63 can be drained more efficiently.

[0081] The gas heat pump type air conditioning system 1 according to the first embodiment has the following effects.

[0082] (1) The gas heat pump type air conditioning system 1 includes:

[0083] An outdoor unit heat exchanger 6, which includes a plurality of flat porous tubes 62 and a plurality of corrugated fins 63. The plurality of flat porous tubes 62 extend along the ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction. The plurality of corrugated fins 63 are arranged in parallel in the second direction between the plurality of flat porous tubes 62, protrude toward the downstream side in the ventilation direction with respect to the plurality of flat porous tubes, and extend in a wavy shape in the first direction;

[0084] A compressor 5;

[0085] A drive source 12 that drives the compressor 5; and

[0086] A radiator 14, which is adjacent to the outdoor unit heat exchanger 6 on the downstream side in the ventilation direction and is used to cool the drive source 12.

[0087] As a result, the frost accumulated on the corrugated fins 63 during the heating operation is efficiently defrosted by the heat of the radiator 14, so that the deterioration of the heat transfer performance of the outdoor unit heat exchanger 6 can be suppressed.

[0088] (2) The plurality of corrugated fins 63 protrude toward the upstream side in the ventilation direction with respect to the plurality of flat porous tubes 62.

[0089] As a result, compared with the case where the corrugated fins do not protrude toward the upstream side in the ventilation direction, the water generated by defrosting can be efficiently discharged, and the heat transfer rate of the corrugated fins becomes uniform in the ventilation direction, so it is easy to efficiently exchange heat with the external gas.

[0090] (3) The outdoor unit heat exchanger 6 has a columnar header 64, which is connected to both ends of the plurality of flat porous tubes 62 in the first direction and extends along the second direction.

[0091] The width w1 of the corrugated fins 63 in the ventilation direction is less than or equal to the width d1 of the header 64 in the ventilation direction and is larger than the width w2 of the flat porous tubes 62 in the ventilation direction.

[0092] As a result, compared with the case where the width of the corrugated fins in the ventilation direction is greater than the width of the header in the ventilation direction, the possibility of the corrugated fins coming into contact with the ground and deforming can be suppressed. In addition, compared with the case where the width of the corrugated fins in the ventilation direction is less than or equal to the width of the flat porous tubes in the ventilation direction, the space in the ventilation direction of the corrugated fins can be effectively utilized.

[0093] (4) A hydrophilic coating treatment was performed on a plurality of corrugated fins 63.

[0094] As a result, the drainage of water flowing on the corrugated fins 63 is improved, and frosting can be further suppressed.

[0095] [Second Embodiment]

[0096] Next, with reference to Figures 8 - 10 The gas heat pump type air conditioning system and the outdoor unit heat exchanger 6a of the second embodiment will be described. Only the structures different from those of the first embodiment will be described below.

[0097] Figure 8 is the same perspective view of the outdoor unit heat exchanger 6a and the radiator 14 of the second embodiment. In the gas heat pump type air conditioning system of the second embodiment, the components other than the outdoor unit heat exchanger 6a have the same structures as those of the components of the gas heat pump type air conditioning system 1 of the first embodiment. As Figure 2 shown, the core 61 of the outdoor unit heat exchanger 6a has a first core 61a on the lower side in the first direction and a second core 61b on the upper side in the first direction. In the second embodiment, the first core 61a faces the radiator 14 in the ventilation direction, and the second core 61b does not face the radiator 14 in the ventilation direction. That is, in Figure 8 , the boundary between the first core 61a and the second core 61b coincides with the upper edge of the radiator 14. Figure 8

[0098] Figure 9 Figure 3 is the same side view of the outdoor unit heat exchanger 6a and the radiator 14. The radiator 14 is adjacent to the first core 61a of the outdoor unit heat exchanger 6a on the downstream side in the ventilation direction. That is, the distance L1 in the ventilation direction between the radiator 14 and the first core 61a is 5 mm or more and 15 mm or less. More specifically, the distance L1 is the distance in the ventilation direction between the radiator 14 and the first corrugated fin 63a (refer to Figure 10 ) of the first core 61a. That is, the radiator 14 is adjacent to the first corrugated fin 63a on the downstream side in the ventilation direction. The radiator 14 is preferably as close as possible to the first corrugated fin 63a without contacting it. Figure 10 ).

[0099] As Figure 9 shown, the length of the radiator 14 in the first direction is about 2 / 3 of the length of the core 61 in the first direction. In other words, the length of the first core 61a in the first direction is about 2 / 3 of the length of the core 61 in the first direction.

[0100] Next, with reference toFigure 10 The structure of the heat exchanger 6a for an outdoor unit according to the second embodiment will be described. Figure 10 FIG. shows Figure 8 A perspective view of two core parts 61a and 61b which magnify and partially show the V1 part of the heat exchanger 6a for an outdoor unit.

[0101] The corrugated fin 63 has a first corrugated fin 63a on the lower side in the first direction and a second corrugated fin 63b on the upper side in the second direction. The first corrugated fin 63a extends from the lower end of the corrugated fin 63 to the upper edge of the radiator 14 in the first direction. Further, the second corrugated fin 63b extends from the upper edge of the radiator 14 to the upper end of the corrugated fin 63. The first core part 61a is composed of a flat porous tube 62 and the first corrugated fin 63a, and the second core part 61b is composed of the same flat porous tube 62 as the flat porous tube 62 constituting the first core part 61a and the second corrugated fin 63b. In the second embodiment, the first corrugated fin 63a and the second corrugated fin 63b are formed separately. It should be noted that the first corrugated fin 63a and the second corrugated fin 63b are integrally formed.

[0102] The heat exchanger 6a for an outdoor unit according to the second embodiment has the same structure as the heat exchanger 6 for an outdoor unit according to the first embodiment except that the corrugated fin 63 is composed of the first corrugated fin 63a and the second corrugated fin 63b. That is, a plurality of flat porous tubes 62 extend in the ventilation direction and the first direction, and are arranged side by side in the second direction, and a plurality of corrugated fins 63 are arranged side by side in the second direction between the plurality of flat porous tubes 62 and extend in a wavy shape in the first direction.

[0103] Further, the corrugated fin 63 according to the second embodiment is also subjected to a hydrophilic coating treatment for improving drainage, similarly to the first embodiment.

[0104] The first corrugated fin 63a and Figure 5 The corrugated fin 63 according to the first embodiment shown in FIG. has, similarly: a central part 635 joined to the flat porous tube 62, a downstream protruding part 631 protruding toward the downstream side in the ventilation direction with respect to the flat porous tube 62 at the downstream end in the ventilation direction of the central part 635, and an upstream protruding part 632 protruding toward the upstream side in the ventilation direction with respect to the flat porous tube 62 at the upstream end in the ventilation direction of the central part 635. Further, in another aspect, in order to suppress deformation of the corrugated fin to a minimum, the first corrugated fin 63a may not protrude toward the upstream side in the ventilation direction and may only protrude toward the downstream side, and the details are as described below.

[0105] Although detailed illustrations are omitted, the second corrugated fin 63b has the same central portion 635 as the first corrugated fin 63a, but does not have a downstream protruding portion 631 and an upstream protruding portion 632. In other words, the second corrugated fin 63b does not protrude toward the downstream side and the upstream side in the ventilation direction with respect to the flat porous tube 62. That is, both ends of the second corrugated fin 63b in the ventilation direction coincide with both ends of the flat porous tube 62 in the ventilation direction.

[0106] Similar to the corrugated fin 63 of the first embodiment, the first corrugated fin 63a and the second corrugated fin 63b have Figure 6 the louver slit portions 633 and 634 shown.

[0107] Since the radiator 14 is adjacent to the outdoor unit heat exchanger 6a on the downstream side in the ventilation direction, and the first corrugated fin 63a protrudes toward the downstream side in the ventilation direction, the gas heat pump type air conditioning system of the second embodiment can also achieve the same defrosting effect as the gas heat pump type air conditioning system of the first embodiment.

[0108] In addition, the liquid water generated during the frosting process passes through the louver slit portions 633 and 634 and flows downward in the first direction under the action of gravity. Therefore, frosting is likely to occur on the lower corrugated fins. In the second embodiment, the radiator 14 is arranged below the outdoor unit heat exchanger 6a, and the first corrugated fin 63a facing the radiator 14 protrudes toward the downstream side in the ventilation direction. Therefore, defrosting can be performed efficiently.

[0109] On the other hand, such protruding portions 631 and 632 are exposed from the outdoor unit heat exchanger 6a. Therefore, when assembling the outdoor unit heat exchanger 6a or the gas heat pump type air conditioning system, they may be deformed due to contact with other components. When setting up the gas heat pump type air conditioning system, the corrugated fin 63 is exposed. Therefore, the deformation of the corrugated fin 63 is not ideal in appearance.

[0110] In the second embodiment, the upper second corrugated fin 63b does not protrude toward the upstream side and the downstream side in the ventilation direction. Therefore, the possibility of contact with other components can be reduced. Therefore, the deformation of the corrugated fin 63 can be suppressed to a minimum. As a result, the appearance of the outdoor unit heat exchanger 6a is less likely to be damaged. In addition, as described above, frosting is less likely to occur on the upper corrugated fins. Therefore, even if the upper second corrugated fin 63b does not protrude in the ventilation direction, the influence on the deterioration of the heat transfer performance of the outdoor unit heat exchanger 6a is small.

[0111] When the first corrugated fin 63a does not protrude toward the upstream side in the ventilation direction, deformation on the upstream side of the first corrugated fin 63a can be suppressed. Therefore, furthermore, the appearance of the heat exchanger 6a for an outdoor unit is less likely to be damaged. Therefore, from the viewpoint of maintaining the appearance of the heat exchanger 6a for an outdoor unit, it is preferable that the first corrugated fin 63a does not protrude toward the upstream side.

[0112] In addition, since the hydrophilic coating treatment is applied to the corrugated fin 63 of the second embodiment, water flowing on the corrugated fin 63 can be discharged more efficiently.

[0113] The gas heat pump type air conditioning system and the heat exchanger 6a for an outdoor unit according to the second embodiment exhibit the following effects.

[0114] (5) The gas heat pump type air conditioning system includes:

[0115] A heat exchanger 6a for an outdoor unit, which includes a plurality of flat porous tubes 62 and a plurality of corrugated fins 63. The plurality of flat porous tubes 62 extend in the ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction. The plurality of corrugated fins 63 are arranged in parallel in the second direction between the plurality of flat porous tubes 62 and extend in a wavy shape in the first direction. Here, the plurality of corrugated fins 63 include a plurality of first corrugated fins 63a and a plurality of second corrugated fins 63b. The plurality of first corrugated fins 63a are provided on one side in the first direction and protrude toward the downstream side in the ventilation direction with respect to the plurality of flat porous tubes 62. The plurality of second corrugated fins 63b are provided on the other side in the first direction and do not protrude toward the upstream side or the downstream side in the ventilation direction with respect to the plurality of flat porous tubes 62;

[0116] A compressor 5;

[0117] A drive source 12 that drives the compressor 5; and

[0118] A radiator 14 that is adjacent to the plurality of first corrugated fins 63a on the downstream side in the ventilation direction and is used to cool the drive source 12.

[0119] As a result, the frost accumulated on the first corrugated fin 63a during the heating operation is efficiently defrosted by the heat of the radiator 14. Therefore, deterioration of the heat transfer performance of the heat exchanger 6a for an outdoor unit can be suppressed. In addition, since the first corrugated fin 63a protrudes toward the downstream side in the ventilation direction, water generated by defrosting can be discharged efficiently. And since the second corrugated fin 63b does not protrude toward the upstream side or the downstream side in the ventilation direction, deformation of the second corrugated fin 63b caused by contact with other components can be suppressed, and the appearance of the heat exchanger 6a for an outdoor unit can be maintained.

[0120] (6) The plurality of first corrugated fins 63a do not protrude upstream in the ventilation direction relative to the plurality of flat porous tubes 62.

[0121] As a result, compared with the case where the first corrugated fins 63a protrude upstream in the ventilation direction, deformation of the first corrugated fins 63a caused by contact with other components can be suppressed, and the appearance of the heat exchanger 6a for an outdoor unit can be further maintained.

[0122] (7) In a posture where the first direction of the heat exchanger 6 for an outdoor unit is the vertical direction,

[0123] the plurality of first corrugated fins 63a are provided at the lower ends of the corrugated fins 63.

[0124] As a result, since the first corrugated fins 63a are provided below the corrugated fins 63 where frosting is likely to occur, defrosting can be performed efficiently.

[0125] (8) A hydrophilic coating treatment is performed on the plurality of corrugated fins 63.

[0126] As a result, the drainage of water flowing on the corrugated fins 63 is improved, and frosting can be further suppressed.

[0127] (9) A heat exchanger 6a for an outdoor unit includes:

[0128] a plurality of flat porous tubes 62 that extend in the ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction; and

[0129] a plurality of corrugated fins 63 that are arranged in parallel in the second direction between the plurality of flat porous tubes 62 and extend in a wavy shape in the first direction,

[0130] wherein the plurality of corrugated fins 63 include:

[0131] a plurality of first corrugated fins 63a that are provided on one side in the first direction and protrude downstream in the ventilation direction relative to the plurality of flat porous tubes 62; and

[0132] a plurality of second corrugated fins 63b that are provided on the other side in the first direction and do not protrude upstream or downstream in the ventilation direction relative to the plurality of flat porous tubes 62.

[0133] As a result, since the first corrugated fin 63a protrudes toward the downstream side in the ventilation direction, water generated by defrosting can be efficiently discharged. Further, since the second corrugated fin 63b does not protrude toward the upstream side or the downstream side in the ventilation direction, deformation of the second corrugated fin 63b caused by contact with other components can be suppressed, and the appearance of the heat exchanger 6a for an outdoor unit can be maintained.

[0134] [Third Embodiment]

[0135] Figure 11 shows a perspective view of the heat exchanger 6b for an outdoor unit according to the third embodiment in which the V2 portion of Figure 8 is enlarged and partially shown. Note that the side plate 65 is omitted. Hereinafter, only the structures different from the first and second embodiments will be described.

[0136] In Figure 11 , the first corrugated fin 63a extends upward in the first direction from the lower end of the corrugated fin 63 (i.e., the lower end of the first corrugated fin 63a) by a height H1. The height H1 in the second embodiment is 30 mm. In other words, the first corrugated fin 63a in the third embodiment extends in a manner that is bent into about 10 peaks. Therefore, in the third embodiment, the radiator 14 is disposed adjacent to the first corrugated fin 63a and the second corrugated fin 63b on the downstream side in the ventilation direction.

[0137] Therefore, the dimension of the first corrugated fin 63a in the first direction in the third embodiment is shorter than the dimension of the first corrugated fin 63a in the first direction in the second embodiment. As a result, since the ratio of the first corrugated fin 63a to the corrugated fin 63 is reduced, deformation of the corrugated fin 63 caused by contact with other components can be further suppressed.

[0138] [Fourth Embodiment]

[0139] Figure 12 is a perspective view of the heat exchanger 6c for an outdoor unit according to the fourth embodiment that is the same as Figure 11 . Note that, for ease of explanation, the second corrugated fin 63b at the front end on the near side of the paper surface in the second direction is omitted. Hereinafter, only the structures different from the first, second, and third embodiments will be described.

[0140] The main surfaces (i.e., the protruding portions 631, 632, and the central portion 635) of the first corrugated fin 63a in the second and third embodiments that constitute the surface facing the first direction have louver slit portions 633, 634. However, as Figure 12 shown, the main surface 637 of the first corrugated fin 63a in the fourth embodiment is flat and does not have any holes. That is, the main surface 637 does not have the louver slit portions 633, 634.

[0141] As Figure 6 shown, the louver slit portions 633 and 634 of the louver are inclined upward in the first direction. Therefore, there is a case where the flow of the fluid in the ventilation direction of the first corrugated fin 63a is obstructed by the louver slit portions 633 and 634. Therefore, the moisture generated by defrosting stays near the louver slit portions 633 and 634, and it is sometimes difficult to discharge it efficiently.

[0142] The main surface 637 of the first corrugated fin 63a of the fourth embodiment does not have the louver slit portions 633 and 634 and is flat. Therefore, the main cause of obstructing the flow of water on the main surface 637 is eliminated. As a result, the water generated by defrosting can be discharged more efficiently.

[0143] The structure of the fourth embodiment can also be applied to the heat exchanger 6 for an outdoor unit of the first embodiment. That is, the main surfaces of the plurality of corrugated fins 63 of the first embodiment may not have any holes. It is also possible to provide no holes only in the partial main surface on the lower side in the first direction of the plurality of corrugated fins 63 of the first embodiment. For example, in the first embodiment, the region within 30 mm in height from the lower end of the corrugated fin 63, in other words, the main surface of about 10 peaks from the lower end, may be flat and may not have any holes. On the other hand, louver slit portions 633 and 634 may be provided on the main surface in the region where the height from the lower end of the corrugated fin 63 is higher than 30 mm. Even if the structure of the fourth embodiment is applied to the heat exchanger 6 for an outdoor unit of the first embodiment, the same effect can be achieved. As described above, frosting is likely to occur on the lower corrugated fins. Therefore, by providing such a main surface in the lower part of the corrugated fin 63, it is possible to balance efficient defrosting and maintenance of the heat transfer rate of the corrugated fin.

[0144] According to the gas heat pump type air conditioning system of the fourth embodiment,

[0145] The plurality of first corrugated fins 63a have a flat main surface 637 that constitutes the surface facing the first direction,

[0146] and no holes are provided on the main surface 637.

[0147] As a result, the water generated by defrosting can be discharged more efficiently.

[0148] [Fifth Embodiment]

[0149] Figure 13 is for the heat exchanger 6d for an outdoor unit of the fifth embodiment and Figure 11The same three-dimensional view. It should be noted that, for the sake of convenience of explanation, the downstream louver slit portion 633 of the second corrugated fin 63b at the front end near the paper surface in the second direction and the first corrugated fin 63a at the upper end of the front end near the paper surface in the second direction are omitted. Hereinafter, only the structures different from those of the first, second, third, and fourth embodiments will be described.

[0150] As Figure 13 shown, a drain hole 636 is provided on the main surface 637 of the first corrugated fin 63a. Specifically, the drain hole 636 is provided in the downstream protruding portion 631. The shape of the drain hole 636 is a substantially rectangular shape when viewed from the first direction. The dimensions of each side of the drain hole 636 can be set in a range of 2 mm or more so as to efficiently drain the water generated by defrosting. One side of the dimensions of each side of the drain hole 636 in the fourth embodiment is about 7 mm, and the other side is about 7 mm. According to this structure, the water generated by defrosting can be drained more efficiently.

[0151] The structure of the fifth embodiment can also be applied to the heat exchanger 6 for an outdoor unit of the first embodiment. That is, drain holes 636 can also be provided on the main surfaces 637 of the plurality of corrugated fins 63 in the first embodiment. Drain holes 636 can also be provided only on the main surfaces of the lower partial portions of the plurality of corrugated fins 63 in the first embodiment. For example, in the first embodiment, drain holes 636 can also be provided in a region within 30 mm in height from the lower end of the corrugated fin 63, that is, on the main surface of about 10 peaks from the lower end. Even if the structure of the fifth embodiment is applied to the heat exchanger 6 for an outdoor unit of the first embodiment, the same effect can be achieved.

[0152] According to the gas heat pump type air conditioning system of the fifth embodiment,

[0153] the plurality of first corrugated fins 63a have flat main surfaces 637 that form a surface facing the first direction,

[0154] and drain holes 636 are provided on the main surfaces 637.

[0155] As a result, the water generated by defrosting can be drained more efficiently.

[0156] [Example]

[0157] Next, embodiments of the specific outdoor unit heat exchanger of the present disclosure will be described together with comparative examples. As shown in Table 1, Examples 1-7 and Comparative Examples 1-4 were fabricated, and an experiment for evaluating the drainage performance of the corrugated fins was conducted. Specifically, in the posture where the first direction of the outdoor unit heat exchanger is the vertical direction, an experiment was carried out in which water was sprayed onto the entire core of the outdoor unit heat exchanger. When water was continuously sprayed, the water accumulated to a specified height from the lower end of the corrugated fins. When water was further sprayed, the water did not accumulate above this specified height but overflowed from the corrugated fins. This specified height is referred to as the water retention height. That is, a high water retention height means poor drainage performance of the corrugated fins, and a low water retention height means excellent drainage performance of the corrugated fins. In this experiment, the water retention height in each example and comparative example was measured and compared.

[0158] [Table 1]

[0159]

[0160] Next, the structures of each example and comparative example will be described.

[0161] [Examples 1-4]

[0162] The outdoor unit heat exchangers of Examples 1-4 were formed by fixing corrugated fins with a thickness of about 0.1 mm between a plurality of flat porous tubes arranged at intervals of about 8 mm. The length of the corrugated fins of Examples 1-4 in the ventilation direction is 38 mm, protruding 3 mm upstream and downstream of the flat porous tubes in the ventilation direction. In Examples 1-4, the fin pitch of the corrugated fins (refer to Figure 4 ) was changed from 1.2 mm to 1.6 mm. The corrugated fins of Examples 1-4 were not subjected to a hydrophilic coating treatment, nor were drainage holes provided. Upstream and downstream louver slit portions were provided in the corrugated fins of Examples 1-4.

[0163] [Example 5]

[0164] The corrugated fins of Example 5 were obtained by subjecting the corrugated fins of Example 2 to a hydrophilic coating.

[0165] [Example 6]

[0166] The corrugated fins of Example 6 had the same structure as the corrugated fins of Example 2 except that the louver slit portions were not provided. That is, the corrugated fins of Example 6 correspond to the first corrugated fins 63a of the fourth embodiment.

[0167] [Example 7]

[0168] The corrugated fins of Example 7 are formed by providing drain holes in the corrugated fins of Example 2. That is, the corrugated fins of Example 7 correspond to the first corrugated fins 63a of the fifth embodiment.

[0169] [Comparative Examples 1-4]

[0170] The corrugated fins of Comparative Examples 1-4 have the same structure as those of Examples 1-4, except that they do not protrude toward the upstream and downstream sides in the ventilation direction with respect to the flat porous tube. Specifically, the two ends of the corrugated fins of Comparative Examples 1-4 in the ventilation direction coincide with the two ends of the flat porous tube in the ventilation direction. Therefore, the length of the corrugated fins of Comparative Examples 1-4 in the ventilation direction is 32 mm.

[0171] [Experimental Result 1]

[0172] Figure 14 The experimental results of Comparative Examples 1-4 and Examples 1-4 are shown. The horizontal axis is the fin pitch, and the vertical axis is the water retention height. In Figure 14 it, the black dots show the experimental results of Comparative Examples 1-4, and the black squares show the experimental results of Examples 1-4.

[0173] At any fin pitch, the water retention height of Examples 1-4 provided with protrusions is lower than that of Comparative Examples 1-4 not provided with protrusions. In addition, the maximum water retention height within the range confirmed in this experiment is about 30 mm. In other words, the range in which drainage needs to be particularly improved in the corrugated fins is the range from the lower end of the corrugated fins to at least a height of 30 mm.

[0174] [Experimental Result 2]

[0175] Figure 15 The experimental results of Examples 2, 5-7 are shown. The vertical axis is the water retention height.

[0176] The water retention height of Examples 5-7 is lower than that of Example 2. In particular, by applying a hydrophilic coating to the corrugated fins, the water retention height is significantly reduced.

[0177] Based on the above experimental results, the inventors obtained the following insights.

[0178] a. By making the corrugated fins protrude in the ventilation direction with respect to the flat porous tube, water can be efficiently discharged.

[0179] b. By applying a hydrophilic coating to the corrugated fins, water can be discharged more efficiently.

[0180] c. Through the flat and pore-free main surface of the corrugated fins, water can be discharged more efficiently.

[0181] d. By providing drain holes in the corrugated fins, water can be discharged more efficiently.

[0182] e. Water flowing on the corrugated fins accumulates at the lower end of the corrugated fins to a maximum height of 30 mm. Therefore, by applying the technology of the present disclosure to the corrugated fins in the height range from the lower end of the corrugated fins to at least 30 mm, water can be discharged efficiently.

[0183] It should be noted that the gas heat pump type air conditioning system and the heat exchanger for the outdoor unit of the present disclosure are not limited to the structures of the above embodiments, and various modifications can be made.

[0184] In the heat exchanger 6 for the outdoor unit of the present embodiment, the corrugated fins 63 are arranged in a posture extending in the first direction, that is, the vertical direction. However, the corrugated fins 63 can also be arranged in a posture extending in the second direction, that is, the horizontal direction. It should be noted that when the corrugated fins 63 are arranged in a posture extending in the vertical direction, a water flow path for draining water during defrosting is easily formed, so it is preferred.

[0185] The radiator 14 of the present embodiment is adjacent to the heat exchanger 6 for the outdoor unit on the downstream side in the ventilation direction. However, even if it is adjacent to the heat exchanger 6 for the outdoor unit on the upstream side in the ventilation direction, the same effect can be achieved. When the radiator is adjacent to the heat exchanger for the outdoor unit on the downstream side in the ventilation direction, during the cooling operation, the air receives heat from the radiator before receiving heat from the heat exchanger for the outdoor unit, suppressing the phenomenon of a decrease in the heat exchange amount with the heat exchanger for the outdoor unit, so it is preferred.

[0186] The radiator 14 of the present embodiment is arranged on the lower side of the heat exchanger 6 for the outdoor unit in the first direction, but is not limited to this position. It should be noted that water that is not completely discharged during defrosting accumulates on the lower side of the heat exchanger 6 for the outdoor unit under the action of gravity and may freeze again. Therefore, the lower side in the first direction requires more defrosting. Therefore, the radiator 14 is preferably arranged on the lower side in the first direction.

[0187] The corrugated fins 63 of the present embodiment protrude more downstream and upstream in the ventilation direction than the flat porous tubes 62. However, even if they only protrude downstream in the ventilation direction from the flat porous tubes 62, a sufficient defrosting effect can be achieved.

[0188] The header 64 of the present embodiment has a cylindrical shape, but is not limited thereto. For example, it can also be a quadrangular prism shape.

[0189] The hydrophilic coating can be applied only to the first corrugated fins 63a, or can also be applied to the entire core 61.

[0190] The drainage hole 636 may be provided in the central portion 635 of the first corrugated fin 63a and / or the upstream protrusion 632. A plurality of drainage holes 636 may be provided on one main surface 637.

[0191] The upstream and downstream louver slit portions 633 and 634 may not be provided in the corrugated fin 63 of the first embodiment or the first corrugated fin 63a and the second corrugated fin 63b of the fifth embodiment.

[0192] The heat exchanger for an outdoor unit of the present disclosure can also be applied to a heat pump air conditioning system that does not have a radiator, and can advantageously improve drainage performance while maintaining aesthetics.

[0193] The second corrugated fin 63b may be introduced to the inside of the flat multi-hole tube in the ventilation direction. In other words, both ends of the second corrugated fin 63b in the ventilation direction may be located inside of both ends of the flat multi-hole tube in the ventilation direction.

[0194] [Notes]

[0195] The gas heat pump air conditioning system and the outdoor unit heat exchanger disclosed in the present invention provide the following solutions.

[0196] [Solution 1]

[0197] A gas heat pump air conditioning system, wherein:

[0198] The gas heat pump air conditioning system comprises:

[0199] A heat exchanger for an outdoor unit, comprising a plurality of flat multi-hole tubes and a plurality of corrugated fins, wherein the plurality of flat multi-hole tubes extend along a ventilation direction and a first direction orthogonal to the ventilation direction and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction, and the plurality of corrugated fins are arranged in parallel in the second direction between the plurality of flat multi-hole tubes, protrude toward a downstream side of the ventilation direction relative to the plurality of flat multi-hole tubes, and extend in a wave-like manner in the first direction;

[0200] compressor;

[0201] a driving source that drives the compressor; and

[0202] A radiator is adjacent to the outdoor unit heat exchanger on the downstream side in the ventilation direction and is used to cool the driving source.

[0203] [Solution 2]

[0204] According to the gas heat pump air conditioning system of scheme 1,

[0205] A plurality of the corrugated fins protrude toward the upstream side in the ventilation direction with respect to the plurality of flat porous tubes.

[0206] [Solution 3]

[0207] The gas heat pump type air conditioning system according to Solution 1 or 2, wherein

[0208] The heat exchanger for the outdoor unit has a columnar header, and the columnar header is connected to both ends of the plurality of flat porous tubes in the first direction and extends in the second direction.

[0209] The width of the corrugated fin in the ventilation direction is equal to or less than the width of the header in the ventilation direction and is larger than the width of the flat porous tube in the ventilation direction.

[0210] [Solution 4]

[0211] The gas heat pump type air conditioning system according to any one of Solutions 1 to 3, wherein

[0212] A hydrophilic coating treatment is performed on the plurality of corrugated fins.

[0213] [Solution 5]

[0214] The gas heat pump type air conditioning system according to any one of Solutions 1 to 4, wherein

[0215] The plurality of corrugated fins have flat main surfaces that form the surfaces facing the first direction.

[0216] No holes are provided in the main surfaces.

[0217] [Solution 6]

[0218] The gas heat pump type air conditioning system according to any one of Solutions 1 to 4, wherein

[0219] The plurality of corrugated fins have flat main surfaces that form the surfaces facing the first direction.

[0220] Drain holes are provided in the main surfaces.

[0221] [Solution 7]

[0222] This gas heat pump type air conditioning system, wherein

[0223] The gas heat pump type air conditioning system includes:

[0224] The heat exchanger for an outdoor unit includes a plurality of flat porous tubes and a plurality of corrugated fins. The plurality of flat porous tubes extend in a ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction. The plurality of corrugated fins are arranged in parallel in the second direction between the plurality of flat porous tubes and extend in a wavy shape in the first direction. Here, the plurality of corrugated fins include a plurality of first corrugated fins and a plurality of second corrugated fins. The plurality of first corrugated fins are arranged on one side in the first direction and protrude toward the downstream side in the ventilation direction with respect to the plurality of flat porous tubes. The plurality of second corrugated fins are arranged on the other side in the first direction and do not protrude toward the upstream side or the downstream side in the ventilation direction with respect to the plurality of flat porous tubes;

[0225] Compressor;

[0226] A drive source for driving the compressor; and

[0227] A radiator adjacent to the plurality of first corrugated fins on the downstream side in the ventilation direction for cooling the drive source.

[0228] [Solution 8]

[0229] The gas heat pump air conditioning system according to Solution 7, wherein,

[0230] The plurality of first corrugated fins do not protrude toward the upstream side in the ventilation direction with respect to the plurality of flat porous tubes.

[0231] [Solution 9]

[0232] The gas heat pump air conditioning system according to Solution 7 or 8, wherein,

[0233] In a posture where the first direction of the heat exchanger for an outdoor unit is a vertical direction,

[0234] The plurality of first corrugated fins are arranged at the lower ends of the corrugated fins.

[0235] [Solution 10]

[0236] The gas heat pump air conditioning system according to any one of Solutions 7 to 9, wherein,

[0237] A hydrophilic coating treatment is performed on the plurality of corrugated fins.

[0238] [Solution 11]

[0239] The gas heat pump air conditioning system according to any one of Solutions 7 to 10, wherein,

[0240] A plurality of the first corrugated fins have flat main surfaces that form the surfaces facing the first direction.

[0241] No holes are provided in the main surfaces.

[0242] [Solution 12]

[0243] The gas heat pump type air conditioning system according to any one of Solutions 7 to 10, wherein

[0244] A plurality of the first corrugated fins have flat main surfaces that form the surfaces facing the first direction.

[0245] Drain holes are provided in the main surfaces.

[0246] [Solution 13]

[0247] A heat exchanger for an outdoor unit, comprising:

[0248] A plurality of flat porous tubes that extend along the ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction; and

[0249] A plurality of corrugated fins that are arranged in parallel in the second direction between the plurality of flat porous tubes and extend in a wavy shape in the first direction,

[0250] wherein the plurality of corrugated fins include:

[0251] A plurality of first corrugated fins that are provided on one side in the first direction and protrude downstream in the ventilation direction with respect to the plurality of flat porous tubes; and

[0252] A plurality of second corrugated fins that are provided on the other side in the first direction and do not protrude upstream or downstream in the ventilation direction with respect to the plurality of flat porous tubes.

[0253] [Solution 14]

[0254] The heat exchanger for an outdoor unit according to Solution 13, wherein

[0255] The plurality of first corrugated fins do not protrude upstream in the ventilation direction with respect to the plurality of flat porous tubes.

[0256] [Solution 15]

[0257] The heat exchanger for an outdoor unit according to Solution 13 or 14, wherein

[0258] In the posture where the first direction of the heat exchanger for an outdoor unit is the vertical direction,

[0259] A plurality of the first corrugated fins are disposed at the lower end of the corrugated fins.

[0260] [Solution 16]

[0261] The heat exchanger for an outdoor unit according to any one of Solutions 13 to 15, wherein

[0262] A hydrophilic coating treatment is performed on a plurality of the corrugated fins.

[0263] [Solution 17]

[0264] The heat exchanger for an outdoor unit according to any one of Solutions 13 to 16, wherein

[0265] A plurality of the first corrugated fins have a flat main surface that constitutes a surface facing the first direction,

[0266] No holes are provided in the main surface.

[0267] [Solution 18]

[0268] The heat exchanger for an outdoor unit according to any one of Solutions 13 to 16, wherein

[0269] A plurality of the first corrugated fins have a flat main surface that constitutes a surface facing the first direction,

[0270] Drain holes are provided in the main surface.

Claims

1. A gas heat pump air conditioning system, wherein: The gas heat pump air conditioning system comprises: A heat exchanger for an outdoor unit, comprising a plurality of flat multi-hole tubes and a plurality of corrugated fins, wherein the plurality of flat multi-hole tubes extend along a ventilation direction and a first direction orthogonal to the ventilation direction and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction, and the plurality of corrugated fins are arranged in parallel in the second direction between the plurality of flat multi-hole tubes, protrude toward a downstream side of the ventilation direction relative to the plurality of flat multi-hole tubes, and extend in a wave-like manner in the first direction; compressor; a driving source that drives the compressor; as well as A radiator is adjacent to the outdoor unit heat exchanger on the downstream side in the ventilation direction and is used to cool the driving source.

2. The gas heat pump air conditioning system according to claim 1, wherein: The plurality of corrugated fins protrude toward the upstream side in the ventilation direction relative to the plurality of flat multi-hole tubes.

3. The gas heat pump air conditioning system according to claim 1 or 2, wherein: The outdoor unit heat exchanger has a columnar header connected to both ends of the plurality of flat multi-hole tubes in the first direction and extending in the second direction. The width of the corrugated fin in the ventilation direction is less than or equal to the width of the header in the ventilation direction and is larger than the width of the flat multi-hole tube in the ventilation direction.

4. The gas heat pump air conditioning system according to claim 1 or 2, wherein: The plurality of corrugated fins are subjected to a hydrophilic coating treatment.

5. The gas heat pump air conditioning system according to claim 1 or 2, wherein: The plurality of corrugated fins have a flat main surface constituting a surface facing the first direction, No holes are provided in the main surface.

6. The gas heat pump air conditioning system according to claim 1 or 2, wherein: The plurality of corrugated fins have a flat main surface constituting a surface facing the first direction, The main surface is provided with a drainage hole.

7. A gas heat pump air conditioning system, wherein: The gas heat pump air conditioning system comprises: A heat exchanger for an outdoor unit, comprising a plurality of flat multi-hole tubes and a plurality of corrugated fins, wherein the plurality of flat multi-hole tubes extend along a ventilation direction and a first direction orthogonal to the ventilation direction, and are arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction, and the plurality of corrugated fins are arranged in parallel in the second direction between the plurality of flat multi-hole tubes and extend in a wave-like manner in the first direction, wherein the plurality of corrugated fins include a plurality of first corrugated fins and a plurality of second corrugated fins, the plurality of first corrugated fins are arranged on one side of the first direction and protrude toward the downstream side of the ventilation direction relative to the plurality of flat multi-hole tubes, and the plurality of second corrugated fins are arranged on the other side of the first direction and do not protrude toward the upstream side and the downstream side of the ventilation direction relative to the plurality of flat multi-hole tubes; compressor; a driving source that drives the compressor; and A heat sink is adjacent to the plurality of first corrugated fins on a downstream side in the ventilation direction and is used to cool the driving source.

8. The gas heat pump air conditioning system according to claim 7, wherein: The plurality of first corrugated fins do not protrude toward the upstream side in the ventilation direction relative to the plurality of flat multi-hole tubes.

9. The gas heat pump air conditioning system according to claim 8, wherein: In a posture where the first direction of the outdoor unit heat exchanger is a vertical direction, The plurality of first corrugated fins are disposed at the lower end of the corrugated fins.

10. The gas heat pump air conditioning system according to any one of claims 7 to 9, wherein: The plurality of corrugated fins are subjected to a hydrophilic coating treatment.

11. The gas heat pump air conditioning system according to any one of claims 7 to 9, wherein: The plurality of first corrugated fins have a flat main surface constituting a surface facing the first direction, No holes are provided in the main surface.

12. The gas heat pump air conditioning system according to any one of claims 7 to 9, wherein: The plurality of first corrugated fins have a flat main surface constituting a surface facing the first direction, The main surface is provided with a drainage hole.

13. A heat exchanger for an outdoor unit, comprising: a plurality of flat porous tubes extending along a ventilation direction and a first direction orthogonal to the ventilation direction, and arranged in parallel in a second direction orthogonal to the ventilation direction and the first direction; and a plurality of corrugated fins, which are arranged in parallel in the second direction between the plurality of flat porous tubes and extend in a wave shape in the first direction, in, The plurality of corrugated fins have: a plurality of first corrugated fins, which are arranged on one side of the first direction and protrude toward the downstream side of the ventilation direction relative to the plurality of flat porous tubes; as well as A plurality of second corrugated fins are provided on the other side of the first direction and do not protrude toward the upstream side and the downstream side of the ventilation direction relative to the plurality of flat porous tubes.

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