Outside air processing device

Abstract

To provide an outside air treatment device capable of lowering a blowout temperature of conditioned air introduced into an indoor space while securing operation reliability.SOLUTION: An outside air processing device according to an aspect of the present invention includes an air conditioning flow path through which first outside air flows, a first heat exchanger that cools the first outside air, and a second heat exchanger that exchanges heat between the first outside air that has passed through the first heat exchanger and second outside air that has not passed through the first heat exchanger in the outside air. The first heat exchanger includes a first fin module having a plurality of first fins, and a second fin module having a plurality of second fins and disposed downstream of the first fin module in a flow direction. An interval between the first fins adjacent to each other is narrower than an interval between the second fins adjacent to each other.SELECTED DRAWING: Figure 5

Description

[Technical Field]

[0001] The present invention relates to an outside air treatment device. [Background technology]

[0002] For example, outdoor air treatment devices are sometimes used as air conditioning devices installed in various facilities such as factories and research laboratories. Outdoor air treatment devices are installed in the outdoor spaces of various facilities, and supply outdoor air to indoor spaces after dehumidifying and cooling it (see, for example, Patent Document 1 below). Outdoor air treatment devices can maintain the interior of a facility at a desired temperature and humidity while maintaining a positive pressure state within the facility, and therefore there is a growing need for such devices in terms of hygiene management based on HACCP (Hazard Analysis and Critical Control Point, a hygiene management method that aims to ensure the safety of food, etc.) and infection control measures. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Publication No. 2018-080886 Summary of the Invention [Problem to be solved by the invention]

[0004] Conventional outdoor air treatment devices have room for improvement in terms of lowering the discharge temperature of conditioned air introduced into indoor spaces while ensuring operational reliability. Specifically, lowering the evaporation temperature of the refrigerant in the evaporator to lower the discharge temperature can easily cause frost formation due to moisture condensing on the surface of the evaporator. As a result, the flow of conditioned air may be obstructed between the fins that make up the evaporator. Furthermore, if the flow of conditioned air is obstructed due to frost formation on the evaporator, the heat exchange efficiency between the evaporator and the conditioned air may decrease. As a result, the refrigerant may return to the compressor without vaporizing (so-called liquid backflow).

[0005] The present invention provides an outside air processing device that can lower the blowout temperature of conditioned air introduced into an indoor space while ensuring operational reliability. [Means for solving the problem]

[0006] In order to solve the above problems, the present invention employs the following aspects. An outdoor air treatment device according to one embodiment of the present invention comprises an air conditioning flow path through which first outdoor air flows, which is outdoor air taken in from outdoors; a first heat exchanger provided in the air conditioning flow path and configured to cool the first outdoor air by exchanging heat between the first outdoor air and a heat medium; and a second heat exchanger provided in the air conditioning flow path downstream of the first heat exchanger and configured to exchange heat between the first outdoor air that has passed through the first heat exchanger and second outdoor air that has not passed through the first heat exchanger, wherein the first heat exchanger comprises a first fin module having a plurality of first fins spaced apart from each other in a first direction that intersects the flow direction of the first outdoor air in the air conditioning flow path, and a second fin module having a plurality of second fins spaced apart from each other in the first direction and provided downstream of the first fin module in the flow direction, wherein the spacing between adjacent first fins is narrower than the spacing between adjacent second fins.

[0007] According to this aspect, the first outside air cooled by the first heat exchanger is heat exchanged in the second heat exchanger with the second outside air that has not passed through the first heat exchanger. This increases the temperature of the first outside air passing through the second heat exchanger, and reduces the relative humidity of the first outside air. This makes it possible to suppress condensation around the air outlet for the first outside air.

[0008] Here, in this embodiment, the first heat exchanger is configured such that the spacing (fin pitch) between the first fins that make up the first fin module is narrower than the spacing (fin pitch) between the second fins that make up the second fin module. This configuration increases the heat transfer area in the upstream portion (first fin module) of the first heat exchanger relative to the downstream side. This improves the cooling efficiency in the upstream portion of the first heat exchanger, through which the relatively high-temperature first outside air passes, thereby efficiently cooling the first outside air while suppressing frost formation on the first fin module. Meanwhile, in the first heat exchanger, the fin pitch of the second fin module, through which the relatively low-temperature first outside air flows, is wider than the fin pitch of the first fin module. This allows water to easily drop between the adjacent second fins, even if condensation occurs on the surfaces of the second fins as the first outside air passes between the adjacent second fins. This prevents water from accumulating between the adjacent second fins. Furthermore, even if frost forms on the second fins, the water between the adjacent second fins can prevent the flow of the first outside air from being obstructed between the adjacent second fins. As a result, the temperature of the conditioned air blown into the indoor space can be reduced while ensuring operational reliability.

[0009] In the outside air processing device according to the above aspect, it is preferable that the inner cross-sectional area of ​​the first heat exchanger as viewed from the flow direction is smaller than the inner cross-sectional area of ​​the second heat exchanger as viewed from the flow direction. According to this aspect, the flow velocity (front wind velocity) of the first outside air when passing through the first heat exchanger can be made higher than the flow velocity of the first outside air when passing through the second heat exchanger, thereby improving the cooling efficiency in the first heat exchanger and making it easier to cool the first outside air to a desired temperature.

[0010] In the outdoor air treatment device according to the above aspect, it is preferable that the first heat exchanger has a heat transfer tube that penetrates each of the first fin module and the second fin module in the first direction and is formed in a serpentine shape in the flow direction, and that the heat medium flows through the heat transfer tube so as to pass through the second fin module and then through the first fin module. According to this aspect, the flow direction of the first outside air and the flow direction of the heat medium are set to be opposite (so-called counterflow). This makes it easier to ensure an average temperature difference between the first outside air and the heat medium, and the first outside air can be cooled effectively. In this case, as described above, by widening the fin pitch of the second fin module, it is possible to prevent the flow of the first outside air from being obstructed between adjacent second fins even if frost forms on the second fins.

[0011] In the outside air treatment device according to the above aspect, it is preferable that the first fin module and the second fin module are arranged in series in the flow direction. According to this aspect, since it is possible to suppress temperature changes of the first outside air when it flows between the first fin module and the second fin module, it is easy to control the temperature of the first outside air. Also, it is possible to reduce the size of the equipment in the flow direction in the first heat exchanger.

[0012] In the outside air treatment device according to the above aspect, it is preferable that the dimension of the first fin module in the flow direction is larger than the dimension of the second fin module in the flow direction. According to this aspect, compared to when the dimensions of the first fin module and the second fin module in the flow direction of the first outside air are set equal, the first outside air can be efficiently cooled while suppressing an increase in size of the first heat exchanger in the flow direction of the first outside air. That is, the heat transfer area can be easily secured in the upstream portion of the first heat exchanger (first fin module), where frost is less likely to form on the first outside air, so the first outside air can be effectively cooled. Furthermore, in the downstream portion of the first heat exchanger (second fin module), where frost is likely to form on the first outside air, spacing between adjacent second fins is secured, so even if frost forms on adjacent second fins, it is possible to prevent the frost from bridging between adjacent second fins.

[0013] In the outside air treatment device according to the above aspect, it is preferable that the distance between the adjacent second fins is set to be 1.2 to 2.0 times the distance between the adjacent first fins. According to this aspect, the distance between adjacent second fins is set to be 1.2 times or more the distance between adjacent first fins, thereby ensuring the distance between adjacent second fins in the second fin module. This prevents frost from forming on the surfaces of adjacent second fins, preventing the frost from bridging the gap between adjacent second fins. As a result, the gap between adjacent second fins is prevented from being blocked. By setting the distance between adjacent second fins to 2.0 times or less the distance between adjacent first fins, it is easy to ensure a heat transfer area in the second fin module while preventing the second fin module from becoming too large in the first direction.

[0014] In the outside air treatment device according to the above aspect, the heat medium is preferably an HFO refrigerant. According to this aspect, it is possible to reduce the global warming potential (GWP) and suppress global warming.

[0015] In the outside air treatment device according to the above aspect, it is preferable that the evaporation temperature of the heat medium in the first heat exchanger is set to be in the range of -1°C to 9°C. According to this aspect, by setting the evaporation temperature of the HFO refrigerant to −1° C. or higher, it is possible to suppress frost formation in the first heat exchanger. On the other hand, by setting the evaporation temperature of the HFO refrigerant to 9°C or lower, the blowout temperature of the first outside air can be lowered.

[0016] In the outdoor air treatment device according to the above aspect, the device preferably comprises an air conditioner unit having an air conditioner casing in which the air conditioning flow path is formed and the first heat exchanger and the second heat exchanger housed in the air conditioner casing, a refrigerator unit having a refrigerator casing in which a compressor that compresses a heat medium and a condenser that dissipates heat from the heat medium compressed by the compressor are housed and arranged at a distance from the air conditioner unit, and an expansion device arranged between the air conditioner unit and the refrigerator unit and connecting the condenser and the first heat exchanger, and the air conditioning flow path preferably comprises a first flow path in which the first heat exchanger is provided, and a second flow path that is connected to the downstream side of the first flow path and is folded back so as to overlap with the first flow path when viewed from a second direction and in which the second heat exchanger is provided. According to this aspect, by providing the first flow path and the second flow path at different positions in the second direction, it is possible to provide an outside air treatment device with excellent cooling efficiency while suppressing an increase in the area of ​​the air conditioner unit as seen from the second direction. [Effects of the Invention]

[0017] According to each of the above aspects, it is possible to lower the blowout temperature of the conditioned air introduced into the indoor space while ensuring operational reliability. [Brief explanation of the drawings]

[0018] [Figure 1] 1 is a perspective view of an outside air treatment device according to an embodiment. [Figure 2] FIG. 2 is a view taken along the arrow II in FIG. [Figure 3] 1 is a schematic configuration diagram of an outside air treatment device according to an embodiment. [Figure 4] FIG. 2 is a side view of the air conditioner unit according to the embodiment. [Figure 5] FIG. 2 is a partial perspective view of an evaporator according to the embodiment. [Figure 6] FIG. 2 is a plan view of the evaporator according to the embodiment. [Figure 7] FIG. 2 is a front view of the reheater according to the embodiment. [Figure 8] FIG. 10 is a front view of an air conditioner unit according to a modified example. [Figure 9] FIG. 10 is a plan view of an air conditioner unit according to a modified example. [Figure 10] FIG. 10 is a front view of an air conditioner unit according to a modified example. [Figure 11] FIG. 10 is a plan view of an air conditioner unit according to a modified example. DETAILED DESCRIPTION OF THE INVENTION

[0019] Next, an embodiment of the present invention will be described with reference to the drawings. In the embodiments and modifications described below, corresponding components may be designated by the same reference numerals, and a description thereof may be omitted. In the following description, expressions indicating relative or absolute arrangements, such as "parallel," "orthogonal," "center," and "coaxial," not only strictly refer to such arrangements, but also refer to a state in which there is a relative displacement with an angle or distance to the extent that tolerances or the same function are obtained. In this embodiment, "facing" does not only refer to a case in which the orthogonal directions (normal directions) of two surfaces are aligned with each other, but also includes a case in which the orthogonal directions intersect with each other.

[0020] [Outside air treatment device 1] Fig. 1 is a perspective view of the outside air treatment device 1. Fig. 2 is a view taken along the arrow II in Fig. 1. 1 and 2 is installed in an outdoor space of a factory, facility, etc. The outdoor air processing device 1 cools and dehumidifies the outside air taken in from outdoors and supplies it to the indoor space of the facility.

[0021] FIG. 3 is a schematic diagram of the outside air treatment device 1. As shown in FIG. As shown in FIG. 3, the outside air processing device 1 includes a refrigeration cycle circuit 10 and an air conditioning circuit 11.

[0022] <Refrigeration cycle circuit 10> The refrigeration cycle circuit 10 circulates a refrigerant (heat medium) as a working fluid while changing its phase between gaseous and liquid refrigerants by exchanging heat with outside air. In the refrigeration cycle circuit 10 of this embodiment, an HFO refrigerant is preferably used as the refrigerant. However, an HFC refrigerant or a natural refrigerant may also be used as the refrigerant.

[0023] The refrigeration cycle circuit 10 includes a compressor 21, an oil separator 22, a condenser 23, a receiver 24, an expansion valve (expansion device) 25, and an evaporator (first heat exchanger) 26. The compressor 21, the oil separator 22, the condenser 23, the receiver 24, the expansion valve 25, and the evaporator 26 are arranged in order on a main refrigerant flow path 27 in the direction of refrigerant flow.

[0024] The compressor 21 compresses a low-pressure gas refrigerant introduced into the compressor 21 to produce a high-temperature, high-pressure gas refrigerant. In this embodiment, for example, a reciprocating compressor is used as the compressor 21. However, the compressor 21 is not limited to a reciprocating type, and a scroll type, rotary type, screw type, or the like may also be used. The oil separator 22 is provided downstream of the compressor 21 in the refrigerant main flow path 27. The oil separator 22 separates lubricating oil of the compressor 21 that is discharged from the compressor 21 together with the gaseous refrigerant, from the gaseous refrigerant that has passed through the compressor 21. Note that installation of the oil separator 22 is not an essential component depending on the performance and characteristics of the compressor 21.

[0025] The condenser 23 is provided on the refrigerant main flow path 27, downstream of the oil separator 22. The condenser 23 performs heat exchange between the refrigerant and outside air, thereby releasing heat from the high-temperature, high-pressure gas refrigerant sent from the compressor 21 and converting the high-temperature, high-pressure gas refrigerant into a high-pressure liquid refrigerant. In this embodiment, the condenser 23 is, for example, a microchannel heat exchanger.

[0026] The receiver 24 is provided on the refrigerant main flow path 27 downstream of the condenser 23. The receiver 24 stores the refrigerant condensed in the condenser 23 (high-pressure liquid refrigerant). The expansion valve 25 is provided on the refrigerant main flow path 27, downstream of the receiver 24. The expansion valve 25 reduces the pressure of the high-pressure liquid refrigerant sent from the receiver 24, and converts the high-pressure liquid refrigerant into a low-temperature, low-pressure gas-liquid two-phase refrigerant. The expansion valve 25 is preferably an electronic expansion valve that can adjust the flow rate according to the cooling load.

[0027] The evaporator 26 is provided on the refrigerant main flow path 27 between the expansion valve 25 and the compressor 21. The evaporator 26 vaporizes the low-temperature, low-pressure two-phase gas-liquid refrigerant fed from the expansion valve 25, converting the low-temperature, low-pressure two-phase gas-liquid refrigerant into low-pressure gas refrigerant. When the low-temperature, low-pressure two-phase gas-liquid refrigerant vaporizes, the evaporator 26 removes heat of vaporization from the surroundings, thereby cooling the outside air around the evaporator 26. The low-pressure gas refrigerant that has passed through the evaporator 26 is taken back into the compressor 21. Details of the evaporator 26 will be described later.

[0028] The refrigeration cycle circuit 10 of this embodiment is provided with a refrigerant bypass passage 28. The refrigerant bypass passage 28 connects a portion of the refrigerant main passage 27 that is located between the compressor 21 and the evaporator 26 and a portion that is located between the oil separator 22 and the condenser 23. That is, the refrigerant bypass passage 28 is a passage that, in a situation where the cooling load is small, such as in winter, causes high-temperature, high-pressure gas refrigerant (hot gas) discharged from the compressor 21 to bypass the downstream side of the evaporator 26 without condensing it in the condenser 23. This ensures a sufficient amount of refrigerant circulating in the compressor 21, allowing continuous operation regardless of fluctuations in the cooling load.

[0029] <Air conditioning circuit 11> The air conditioning circuit 11 is a circuit for adjusting the temperature and humidity of outside air to be supplied to an indoor space. The air conditioning circuit 11 includes an air conditioning main flow path 31 and an air conditioning bypass flow path 32. An eliminator 33, a filter 34, and a fan 35 are provided on the air conditioning main flow path 31.

[0030] The eliminator 33 is a so-called gas-liquid separator. The eliminator 33 is provided at the upstream end of the air conditioning main flow path 31. The eliminator 33 captures moisture such as rainwater from the outside air introduced into the air conditioning main flow path 31 as the outside air passes through. The filter 34 is provided on the air conditioning main flow path 31 downstream of the eliminator 33. The filter 34 captures dust and the like from the outside air that has passed through the eliminator 33 as the outside air passes through.

[0031] The fan 35 is provided on the air conditioning main flow path 31, downstream of the filter 34. The fan 35 sends outside air toward the downstream side of the air conditioning main flow path 31. In this embodiment, the fan 35 is, for example, a centrifugal fan.

[0032] In the air conditioning main flow path 31, an evaporator 26 is disposed downstream of the fan 35. When the outside air flowing through the air conditioning main flow path 31 passes through the evaporator 26, heat is exchanged between the outside air and the low-temperature, low-pressure gas-liquid two-phase refrigerant flowing inside the evaporator 26. In the air conditioning main flow path 31, a reheater (second heat exchanger) 37 is arranged downstream of the evaporator 26. The reheater 37 exchanges heat between the outside air that has passed through the evaporator 26 (first outside air) and the outside air that has not passed through the evaporator 26 (second outside air).

[0033] The air conditioning bypass flow path 32 is a flow path for causing a portion of the outside air flowing through the air conditioning main flow path 31 to bypass the evaporator 26. Specifically, the air conditioning bypass flow path 32 includes an inlet flow path 32a and an outlet flow path 32b. The inlet flow path 32 a connects a portion of the air conditioning main flow path 31 that is located between the fan 35 and the evaporator 26 and an inlet portion of the reheater 37 . The outlet flow path 32b connects the outlet portion of the reheater 37 to a portion of the air conditioning main flow path 31 that is located between the filter 34 and the fan 35. In other words, the reheater 37 reheats the outside air that has been cooled by the evaporator 26 by circulating the outside air that bypasses the evaporator 26 and flows on the air conditioning bypass flow path 32. Details of the reheater 37 will be described later.

[0034] In the outside air treatment device 1 of this embodiment, the refrigeration cycle circuit 10 and the air conditioning circuit 11 are housed in a refrigerator casing 50 and an air conditioner casing 51, respectively, to form a refrigerator unit 100 and an air conditioner unit 101.

[0035] <Refrigerator unit 100> 1 and 2, the chiller casing 50 that constitutes the exterior of the chiller unit 100 is installed on the installation surface F of the outside-air processing device 1 via a stand 53. In the following description, the direction perpendicular to the installation surface F is referred to as the up-down direction (arrow UP indicates the up direction), and two directions that are perpendicular to each other when viewed from the up-down direction are referred to as the front-rear direction (arrow FR indicates the forward direction) and the left-right direction (arrow LH indicates the left direction), respectively. In the front-rear direction, the side of the air conditioner casing 51 that faces an inlet 70 (described later) (see FIG. 2) is referred to as the front, and the side opposite the inlet 70 is referred to as the rear.

[0036] The refrigerator casing 50 is formed in a rectangular parallelepiped shape with the longitudinal direction extending in the front-to-rear direction. The interior of the refrigerator casing 50 is divided into an upper space 56 and a lower space 57 by a partition wall 55. The lower space 57 houses the compressor 21, oil separator 22, and receiver 24 (see FIG. 3) of the refrigeration cycle circuit 10.

[0037] The condenser 23 is housed in the upper space 56. Specifically, an opening 58a is formed in a side wall portion 58 facing the left-right direction at the top of the refrigerator casing 50. The upper space 56 is in communication with the outside of the refrigerator unit 100 through the opening 58a. A fan 60 is provided in a top wall portion 59 of the refrigerator casing 50. That is, outside air is taken into the upper space 56 through the opening 58a by operation of the fan 60, passes through the condenser 23, and then is discharged to the outside of the upper space 56 through the fan 60. The refrigerator casing 50 is appropriately provided with an opening / closing door for performing maintenance on the equipment housed in the refrigerator casing 50.

[0038] <Air conditioner unit 101> The air conditioner unit 101 is disposed on one side (right side) in the left-right direction of the refrigerator unit 100 at a distance. An expansion valve 25 is provided in a portion of the main refrigerant flow path 27 located between the air conditioner unit 101 and the refrigerator unit 100 (see FIG. 2).

[0039] FIG. 4 is a side view of the air conditioner unit 101. As shown in FIGS. 2 and 4, the air conditioner casing 51, which constitutes the exterior of the air conditioner unit 101, is installed on an installation surface F via a stand 53. Like the refrigerator casing 50, the air conditioner casing 51 is formed in a rectangular parallelepiped shape with the longitudinal direction extending in the front-to-rear direction. An inlet 70 is formed in the front wall 51a of the air conditioner casing 51. The inlet 70 opens in the front-to-rear direction at the bottom of the front wall 51a. Meanwhile, an air outlet 71 is formed in the right wall 51b of the air conditioner casing 51 (the side wall opposite the refrigerator casing 50). The air outlet 71 opens in the left-to-right direction at the top of the right wall 51b. The air conditioner casing 51 is appropriately equipped with an opening / closing door for performing maintenance on the devices housed in the air conditioner casing 51.

[0040] The air conditioner casing 51 is provided with partition walls (a lower partition wall 73a and an upper partition wall 73b) that separate the interior of the air conditioner casing 51 between the inlet 70 and the outlet 71. The lower partition wall 73a extends rearward from the front wall 51a while being supported between the right side wall 51b and the left side wall 51c (see FIG. 2) of the air conditioner casing 51. The rear end of the lower partition wall 73a is spaced apart from the rear wall 51d of the air conditioner casing 51. On the other hand, the upper partition wall 73b is located above the lower partition wall 73a within the air conditioner casing 51, and extends forward from the rear wall 51d while being supported by the right side wall 51b and the left side wall 51c. The front end of the upper partition wall 73b is spaced apart from the front wall 51a of the air conditioner casing 51. Therefore, inside the air conditioner casing 51, an air conditioning main flow path 31 is formed that extends upward while meandering in the front-rear direction in a side view.

[0041] The air conditioning main flow path 31 includes a lower flow path 31a, a middle flow path 31b, and an upper flow path 31c. The lower flow path 31a, the middle flow path 31b, and the upper flow path 31c are arranged to overlap each other in a plan view. The lower flow path 31a is a space located below the lower partition wall 73a within the air conditioner casing 51. Specifically, the lower flow path 31a extends in the front-to-rear direction in the lower part of the air conditioner casing 51. An upstream end (front end) of the lower flow path 31a communicates with the outside of the air conditioner casing 51 through the inlet 70.

[0042] The middle flow path 31b is a space surrounded by the lower partition wall 73a and the upper partition wall 73b within the air conditioner casing 51. Specifically, the middle flow path 31b extends in the front-to-rear direction in the central portion in the up-down direction of the air conditioner casing 51. The upstream end (rear end) of the middle flow path 31b is connected to the downstream end (rear end) of the lower flow path 31a. The upper flow path 31c is a space located above the upper partition wall 73b within the air conditioner casing 51. Specifically, the upper flow path 31c extends in the front-to-rear direction at the top of the air conditioner casing 51. The upstream end (front end) of the upper flow path 31c is connected to the downstream end (front end) of the middle flow path 31b. The downstream end (rear end) of the upstream flow path 31c communicates with the outside of the air conditioner casing 51 through the air outlet 71.

[0043] As shown in FIG. 4, the lower flow path 31a has the above-mentioned eliminator 33, filter 34, and fan 35 arranged in this order from the upstream side to the downstream side. The evaporator 26 is disposed in the middle flow path 31b. The reheater 37 is disposed in the upper flow path 31c. A refrigerant leakage sensor 75 is disposed in the upper flow path 31c in a portion located between the reheater 37 and the air outlet 71. The refrigerant leakage sensor 75 detects leakage of refrigerant from the main refrigerant flow path 27 to the air conditioning main flow path 31.

[0044] <Evaporator 26> Fig. 5 is a partial perspective view of the evaporator 26. Fig. 6 is a plan view of the evaporator 26. 5 and 6 is provided so as to block the middle flow path 31b (see FIG. 4). The evaporator 26 includes a casing 250, a cooling block 251, and a heat transfer tube 252. The casing 250 is formed in the shape of a rectangular tube that penetrates at least in the front-rear direction (direction of outside air flow). In this embodiment, the casing 250 is flattened in the vertical direction when viewed in the front-rear direction and extends in the front-rear direction. The casing 250 is supported by an air conditioner casing 51 via a frame or the like (not shown). Outside air flows into the evaporator 26 through a rear end opening 250a of the casing 250 and flows out through a front end opening 250b of the casing 250.

[0045] The cooling block 251 is housed in the casing 250. The cooling block 251 includes a first fin module 200 and a second fin module 201.

[0046] The first fin module 200 is disposed on the upstream side (rear side) of the casing 250 in the direction of outside air flow. The first fin module 200 includes a plurality of first fins 210. The first fins 210 are formed in a thin plate shape from a material with excellent thermal conductivity, such as aluminum. The first fins 210 are disposed at intervals in the left-right direction (first direction), for example. That is, the first fins 210 are aligned in a direction perpendicular to the direction of outside air flow in the middle flow path 31b. In the middle flow path 31b, outside air (conditioned air) passes through the gaps between adjacent first fins 210. The first fins 210 have a plurality of through holes 210a (see FIG. 5) formed therein, penetrating the first fin 210 in the thickness direction (left-right direction). The through holes 210a are arranged, for example, in a staggered pattern.

[0047] The second fin module 201 is disposed within the casing 250 downstream (front) of the first fin module 200 in the direction of outside air flow. The second fin module 201 includes a plurality of second fins 211. Like the first fins 210, the second fins 211 are formed in the shape of thin plates made of, for example, aluminum. The second fins 211 are disposed at intervals in the same direction (left-right direction) as the arrangement direction of the first fins 210. In the middle flow path 31b, outside air (conditioned air) that has passed between adjacent first fins 210 passes between adjacent second fins 211. The second fins 211 are formed with a plurality of through holes 211a that penetrate the second fin 211 in the thickness direction (left-right direction). The through holes 211a are arranged, for example, in a staggered pattern.

[0048] In the first fin module 200, the distance between adjacent first fins 210 in the left-right direction is defined as the fin pitch P1, and in the second fin module 201, the distance between adjacent second fins 211 in the left-right direction is defined as the fin pitch P2. In this embodiment, the fin pitch P1 is narrower than the fin pitch P2. Specifically, the fin pitch P2 is preferably set in the range of 1.2 to 2.0 times the fin pitch P1. In this case, the fin pitch P2 is preferably set, for example, in the range of 4 mm to 7 mm.

[0049] The first fin module 200 and the second fin module 201 are assembled together by a casing 250. The first fin module 200 and the second fin module 201 are arranged adjacent to each other in the direction of outside air flow. In this case, the first fin module 200 and the second fin module 201 (the first fins 210 and the second fins 211) may be in contact with each other in the direction of outside air flow, or may be arranged with a gap therebetween that prevents them from contacting each other due to processing.

[0050] The first fin module 200 and the second fin module 201 have the same external shape when viewed from the direction of outside air flow. In this case, the entire second fin module 201 overlaps the entire first fin module 200 when viewed from the direction of outside air flow.

[0051] 6, the dimension T1 of the first fin module 200 in the outside air flow direction is larger than the dimension T2 of the second fin module 201 in the outside air flow direction. That is, the dimension of each first fin 210 in the outside air flow direction is larger than the dimension of each second fin 211 in the outside air flow direction. In this embodiment, the dimension T1 of the first fin module 200 is preferably two to three times the dimension T2 of the second fin module 201.

[0052] 5, heat transfer tube 252 constitutes part of refrigerant main flow path 27. That is, refrigerant that has passed through expansion valve 25 flows through heat transfer tube 252. Heat transfer tube 252 is assembled to first fin module 200 and second fin module 201 in a serpentine state from the downstream side to the upstream side in the outside air flow direction. That is, the refrigerant flow direction is set to be opposite (counterflow) to the outside air flow direction.

[0053] The heat transfer tubes 252 are arranged to pass through the second fin module 201 and then through the first fin module 200. Specifically, the portions of the heat transfer tubes 252 that pass through the second fin module 201 penetrate through the through holes 211a that face each other in the left-right direction in adjacent second fins 211, and extend upstream in the outside air flow direction while meandering in the left-right direction by being folded back outside the second fin module 201. The portions of the heat transfer tubes 252 that pass through the first fin module 200 penetrate through the through holes 210a that face each other in the left-right direction in adjacent first fins 210, and extend upstream in the outside air flow direction while meandering in the left-right direction by being folded back outside the first fin module 200.

[0054] <Reheater 37> FIG. 7 is a front view of the reheater 37. 7 is provided in the upper flow path 31c so as to block the upper flow path 31c (see FIG. 4). The reheater 37 includes a plurality of fins 220 and a heat transfer tube 221. The fins 220 are arranged at intervals in the left-right direction, similar to the fins 210, 211 of the evaporator 26. That is, in the upper flow path 31c, outside air passes through the gaps between adjacent fins 220. The fins 220 are housed in a casing (not shown) that penetrates in the front-rear direction, constituting a fin module 222.

[0055] A plurality of through-holes 220a are formed in each fin 220, penetrating the fin 220 in the thickness direction (left-right direction). The through-holes 220a are arranged, for example, in a staggered pattern.

[0056] The heat transfer tube 221 constitutes a part of the air conditioning bypass flow path 32. That is, the heat transfer tube 221 connects the inlet flow path 32a and the outlet flow path 32b, and outside air that has bypassed the evaporator 26 flows through the heat transfer tube 221. As shown in FIG. 4, the upstream end of the inlet flow path 32a opens into the middle flow path 31b through the upper partition wall 73b. The downstream end of the inlet flow path 32a is connected to the upstream end of the heat transfer tube 221 (see FIG. 7). On the other hand, the upstream end of the outlet flow path 32b is connected to the downstream end of the heat transfer tube 221. The downstream end of the outlet flow path 32b opens into a portion of the lower flow path 31a that is located between the filter 34 and the fan 35. That is, in this embodiment, at least a part of the outside air that has passed through the heat transfer tube 221 is configured to circulate within the air conditioner casing 51.

[0057] The heat transfer tubes 221 are attached to the respective fins 220 so as to pass through the through holes 220a of the adjacent fins 220 that face each other in the left-right direction.

[0058] Here, the internal cross-sectional area of ​​the evaporator 26 as viewed from the direction of outside air flow is smaller than the internal cross-sectional area of ​​the reheater 37. The internal cross-sectional area refers to the area inside the casing as viewed from the direction of outside air flow. In this case, the internal cross-sectional area of ​​the evaporator 26 is equal to the external shape of the cooling block 251 (the first fin module 200 and the second fin module 201). Furthermore, the internal cross-sectional area of ​​the reheater 37 is equal to the external shape of the fin module 222.

[0059] On the other hand, the dimension of the evaporator 26 in the direction of outside air flow is larger than the dimension of the reheater 37 in the direction of outside air flow. In this case, the heat transfer area of ​​the evaporator 26 (the surface area of ​​the fin modules 200, 201) is set to be larger than the heat transfer area of ​​the reheater 37. Therefore, the evaporator 26 is set to have a higher flow rate than the outside air passing through the reheater 37 while ensuring a larger heat transfer area than the reheater 37. However, the dimensions of the evaporator 26 and the reheater 37 can be changed as appropriate.

[0060] [Outside air processing method] Next, a description will be given of an outside air processing method using the above-described outside air processing device 1. The following mainly describes the operation of the air conditioner unit 101 in a state where the refrigeration cycle circuit 10 is operating normally. In the air conditioner unit 101, by operating the fan 35, outside air at, for example, 32°C is introduced into the air conditioner casing 51 through the inlet 70 (see arrow F1). The outside air introduced into the air conditioner casing 51 has moisture, dust, and the like captured as it passes through the eliminator 33 and filter 34 in the lower flow path 31a, and then flows into the middle flow path 31b (see arrow F2).

[0061] The outside air flowing through middle flow path 31b is branched upstream of evaporator 26 into conditioned air (first outside air: see arrow F3) that passes through evaporator 26 and bypass air (second outside air: see arrow Q1) that bypasses evaporator 26. As the conditioned air passes through evaporator 26, it exchanges heat with a low-temperature, low-pressure refrigerant in a gas-liquid mixture state that flows through heat transfer tube 252 via fins 210 and 211. This cools the conditioned air. As the conditioned air cools, the absolute humidity of the conditioned air decreases, and the conditioned air is dehumidified. That is, as the conditioned air cools, the amount of saturated water vapor decreases, and moisture contained in the conditioned air condenses (dews) within middle flow path 31b.

[0062] Here, in the evaporator 26, the conditioned air is gradually cooled as it passes through the first fin module 200 (between adjacent first fins 210) and the second fin module 201 (between adjacent second fins 211) in sequence. Specifically, as the conditioned air passes through the first fin module 200 having the narrow fin pitch P1, it is cooled to a temperature (e.g., 6°C) at which moisture present in the middle flow path 31b does not solidify (frost). Thereafter, the conditioned air is further cooled to, for example, 0°C as it passes through the second fin module 201 having the wide fin pitch P2. That is, in this embodiment, the conditioned air is dehumidified in the first fin module 200 having the narrow fin pitch P1, and then supplied to the second fin module 201 having the wide fin pitch P2. Note that in this embodiment, the evaporation temperature of the refrigerant in the evaporator 26 is set to be in the range of -1°C to 9°C.

[0063] The flow velocity (front wind velocity) of the conditioned air as it passes through evaporator 26 is preferably set to 1.0 m / s or more and 4.0 m / s or less. This makes it easy to cool the conditioned air to the desired temperature even when the evaporation temperature of the refrigerant in evaporator 26 is set to -1°C or more and 9°C or less. The flow velocity of the conditioned air can be set by adjusting the internal cross-sectional area of ​​evaporator 26, for example, depending on the rated torque of fan 35.

[0064] The conditioned air that has passed through the evaporator 26 flows into the upper flow path 31c (see arrow F4). When the conditioned air that has flowed into the upper flow path 31c passes through the reheater 37 (between adjacent fins 220), it exchanges heat with the bypass air via the fins 220. This heats the conditioned air. As the conditioned air is heated, the relative humidity of the conditioned air decreases. The bypass air that has passed through the heat transfer tubes 221 of the reheater 37 is returned to the lower flow path 31a via the outlet flow path 32b (arrow Q2 in FIG. 4). Thereafter, the fan 35 returns the air to the lower flow path 31a and sends it back into the middle flow path 31b.

[0065] The conditioned air that has passed through the reheater 37 is blown out from the air conditioner unit 101 through the air outlet 71. The conditioned air blown out from the air conditioner unit 101 is supplied to an indoor space through an appropriate duct or the like.

[0066] As described above, the outdoor air treatment device 1 of this embodiment is configured to include an evaporator (first heat exchanger) 26 that is provided in the main air conditioning flow path 31 and cools the conditioned air by exchanging heat between the conditioned air and the refrigerant, and a reheater (second heat exchanger) 37 that exchanges heat between the conditioned air that has passed through the evaporator 26 and bypass air that is part of the outdoor air and has not passed through the evaporator 26. According to this configuration, in the reheater 37, heat exchange occurs between the conditioned air (first outside air) that has passed through the evaporator 26 and the bypass air (second outside air) that has not passed through the evaporator 26, thereby increasing the temperature of the conditioned air and decreasing the relative humidity of the conditioned air. As a result, condensation around the air outlet 71 for the conditioned air can be suppressed.

[0067] Furthermore, in the outdoor air treatment device 1 of this embodiment, the evaporator 26 comprises a first fin module 200 having a plurality of first fins 210, and a second fin module 201 having a plurality of second fins 211 and arranged downstream of the first fin module 200 in the outdoor air flow direction, and the fin pitch P1 between adjacent first fins 210 is narrower than the fin pitch P2 between adjacent second fins 211. This configuration increases the heat transfer area per unit length in the direction of outside air flow in the upstream portion (first fin module 200) of evaporator 26 compared to the downstream portion (second fin module 201). This improves the cooling efficiency in the upstream portion of evaporator 26, through which relatively high-temperature conditioned air passes, thereby efficiently cooling the conditioned air while suppressing frost formation on the first fin module 200. Meanwhile, in evaporator 26, the fin pitch P2 of second fin module 201, through which relatively low-temperature conditioned air passes, is wider than the fin pitch P1 of first fin module 200. This allows water to easily drop between adjacent second fins 211, even if conditioned air condenses on the surfaces of the second fins 211. This prevents water from accumulating between adjacent second fins 211. Furthermore, even if frost forms on the second fins 211 due to water between the adjacent second fins 211, the flow of conditioned air between the adjacent second fins 211 can be prevented from being obstructed. As a result, the temperature of the conditioned air blown into the indoor space can be reduced while ensuring operational reliability.

[0068] In the outside air processing device 1 of this embodiment, the internal cross-sectional area of ​​the evaporator 26 as viewed from the outside air flow direction is smaller than the internal cross-sectional area of ​​the reheater 37 as viewed from the outside air flow direction. According to this configuration, the flow velocity (front wind velocity) of the conditioned air when passing through the evaporator 26 can be easily increased compared to the flow velocity of the conditioned air when passing through the reheater 37. This improves the cooling efficiency of the evaporator 26, making it easier to cool the conditioned air to a desired temperature.

[0069] In the outdoor air treatment device 1 of this embodiment, the evaporator 26 is provided with a heat transfer tube 252 that penetrates the first fin module 200 and the second fin module 201 in the left-right direction and is formed in a serpentine shape in the outdoor air flow direction, and the refrigerant flows through the heat transfer tube 252 so that it passes through the second fin module 201 and then through the first fin module 200. According to this configuration, the flow direction of the conditioned air (outside air flow direction) and the flow direction of the refrigerant are set to be opposite (so-called counterflow). This makes it easier to ensure an average temperature difference between the conditioned air and the refrigerant, and the conditioned air can be cooled effectively. In this case, as described above, by widening the fin pitch P2 of the second fin module 201, it is possible to prevent the flow of conditioned air from being obstructed between adjacent second fins 211 even if frost forms on the second fins 211.

[0070] In the outside air treatment device 1 of this embodiment, the first fin module 200 and the second fin module 201 are arranged in series in the direction of outside air flow. This configuration makes it easier to control the temperature of the conditioned air because it is possible to suppress temperature changes of the conditioned air when it flows between the first fin module 200 and the second fin module 201. It is also possible to reduce the size of the evaporator 26 in the direction of outside air flow.

[0071] In the outside air treatment device 1 of this embodiment, the dimension T1 of the first fin module 200 in the outside air flow direction is larger than the dimension T2 of the second fin module 201 in the outside air flow direction. This configuration can efficiently cool the conditioned outdoor air while minimizing the increase in size of the evaporator 26 in the outdoor air flow direction compared to when the first fin module 200 and the second fin module 201 are set to the same dimensions in the outdoor air flow direction. Specifically, the heat transfer area can be easily secured in the upstream portion of the evaporator 26 (first fin module 200), where frost formation on the conditioned air is unlikely, thereby effectively cooling the conditioned air. Furthermore, in the downstream portion of the evaporator 26 (second fin module 201), where frost formation on the conditioned air is likely, spacing between adjacent second fins 211 is secured. Therefore, even if frost does form on adjacent second fins 211, the frost formed on the adjacent second fins 211 can be prevented from crossing over each other. In this case, by setting the dimension T1 of the first fin module 200 to be at least twice the dimension T2 of the second fin module 201, the heat transfer area can be easily secured in the upstream portion of the evaporator 26, where frost formation is unlikely. On the other hand, by setting the dimension T1 of the first fin module 200 to be three times or less the dimension T2 of the second fin module 201, the increase in pressure loss when passing through the first fin module 200 can be suppressed, and an increase in running costs can be suppressed.

[0072] In the outside air treatment device 1 of this embodiment, the fin pitch P2 of the second fin module 201 is set to be 1.2 times or more and 2.0 times or less the fin pitch P1 of the first fin module 200. According to this configuration, the fin pitch P2 is set to be 1.2 times or more the fin pitch P1, thereby ensuring a sufficient distance between adjacent second fins 211 in the second fin module 201. This makes it possible to prevent the frost formed on the adjacent second fins 211 from bridging each other even if frost forms on the surfaces of the adjacent second fins 211. As a result, it is possible to prevent the gap between the adjacent second fins 211 from being blocked. By setting the fin pitch P2 to 2.0 times or less the fin pitch P1, it is possible to prevent the second fin module 201 from becoming too large in the left-right direction, while making it easier to ensure a heat transfer area in the second fin module 201.

[0073] The outside air treatment device 1 of this embodiment is configured to use an HFO refrigerant as the refrigerant. This configuration reduces the global warming potential (GWP) and can suppress global warming.

[0074] In the outside air treatment device 1 of this embodiment, the evaporation temperature of the refrigerant in the evaporator 26 is set to be in the range of -1°C to 9°C. According to this configuration, by setting the evaporation temperature of the refrigerant to −1° C. or higher, it is possible to suppress frost formation on the surfaces of the evaporator fins 210, 211. On the other hand, by setting the evaporation temperature of the refrigerant to 9°C or less, the blowout temperature of the conditioned air can be lowered.

[0075] The outside air processing device 1 of this embodiment includes an air conditioner unit 101 having an air conditioner casing 51 in which a main air conditioning flow path 31 is formed, and an evaporator 26 and a reheater 37 housed in the air conditioner casing 51, a refrigerator unit 100 having a refrigerator casing 50 housing a compressor 21 that compresses a refrigerant and a condenser 23 that dissipates heat from the refrigerant compressed by the compressor 21 and disposed apart from the air conditioner unit 101, and an expansion valve (expansion device) 25 disposed between the air conditioner unit 101 and the refrigerator unit 100 and connecting the condenser 23 and the evaporator 26. The main air conditioning flow path 31 includes a middle flow path (first flow path) 31b in which the evaporator 26 is provided, and an upper flow path 31c connected to the downstream side of the middle flow path 31b, folded back so as to overlap with the middle flow path 31b when viewed from the up-down direction (second direction), and in which the reheater 37 is provided. According to this configuration, the middle flow path 31b and the upper flow path 31c are provided at different positions in the vertical direction, thereby making it possible to provide an outdoor air treatment device 1 with excellent cooling efficiency while suppressing an increase in the area (installation area) of the air conditioner unit 101 as viewed from the vertical direction.

[0076] (First Modification) In the above-described embodiment, the air conditioner casing 51 has a configuration in which the interior thereof is formed in three serpentine stages in the vertical direction, but the configuration is not limited to this. For example, as in the air conditioner casing 51 shown in Figures 8 and 9, the upper stage flow path of the air conditioning main flow path 31 may be configured so as to be folded back so as to overlap when viewed from the left and right. Specifically, the air conditioning main flow path 31 shown in Figures 8 and 9 includes a lower stage flow path 300 located at the bottom of the air conditioner casing 51, and an upper stage flow path 301 located at the top of the air conditioner casing 51 and folded back so as to overlap with the lower stage flow path 300 when viewed from the top and bottom.

[0077] The upper flow path 301 includes an upstream flow path 301a and a downstream flow path 301b that is connected to the downstream end of the upstream flow path 301a and that is bent back in the front-rear direction relative to the upstream flow path 301a. The upstream flow path 301a and the downstream flow path 301b overlap each other when viewed from the left-right direction (second direction). In this case, the evaporator 26 is disposed in the upstream flow path 301a, and the reheater 37 is disposed in the downstream flow path 301b.

[0078] (Second Modification) As shown in Figures 10 and 11, the lower flow path 300 of the air conditioning main flow path 31 may be configured to be folded back as viewed from the left-right direction. Specifically, the lower flow path 300 includes an upstream flow path 300a and a downstream flow path 300b that is connected to the downstream end of the upstream flow path 300a and is folded back in the front-rear direction relative to the upstream flow path 300a. The upstream flow path 300a and the downstream flow path 300b overlap as viewed from the left-right direction. In this case, the evaporator 26 is disposed in the downstream flow path 300b, and the reheater 37 is disposed in the upper flow path 301. The upper flow path 301 and the downstream flow path 300b are folded back so as to overlap as viewed from the top-bottom direction (second direction).

[0079] (Other variations) Although the preferred embodiments of the present invention have been described above, the present invention is not limited to these embodiments. Addition, omission, substitution, and other modifications of the configuration are possible without departing from the spirit of the present invention. The present invention is not limited by the above description, but is limited only by the appended claims. In the above-described embodiment, the refrigerator casing 50 and the air conditioner casing 51 are arranged apart from each other, but the present invention is not limited to this configuration. The refrigeration cycle circuit 10 and the air conditioning circuit 11 may be housed together in a single casing. In the above-described embodiment, the evaporation temperature of the refrigerant in the evaporator 26 is set to a value between −1° C. and 9° C., but the invention is not limited to this. The evaporation temperature of the refrigerant in the evaporator 26 can be changed as appropriate. In the above-described embodiment, the refrigeration cycle circuit 10 is of a direct expansion type (a type in which the evaporator 26 is in direct contact with the outside air), but the present invention is not limited to this configuration. The refrigeration cycle circuit 10 may be of an indirect expansion type (a type in which a heat medium is interposed between the evaporator 26 and the outside air), for example.

[0080] In the above-described embodiment, a configuration has been described in which part of the outside air flowing through the air conditioning main flow path 31 is supplied to the reheater 37 by bypassing the evaporator 26, but the present invention is not limited to this configuration. The outside air supplied to the reheater 37 may be supplied via a circuit separate from the air conditioning main flow path 31. In other words, any configuration may be used as long as the outside air supplied to the reheater 37 does not pass through the evaporator 26. In the above-described embodiment, the arrangement direction of the fins 210, 211 of the evaporator 26 and the arrangement direction of the fins 220 of the reheater 37 are the same, but this is not limiting. The arrangement direction of the fins 210, 211 of the evaporator 26 and the arrangement direction of the fins 220 of the reheater 37 may intersect with the flow direction of outside air passing through them.

[0081] In the above-described embodiment, a configuration has been described in which the dimension T1 of the first fin module 200 is larger than the dimension T2 of the second fin module 201, but this configuration is not limiting. The dimension T1 of the first fin module 200 may be equal to or smaller than the dimension T2 of the second fin module 201. In the above-described embodiment, the configuration in which the internal cross-sectional area of ​​the evaporator 26 is smaller than the internal cross-sectional area of ​​the reheater 37 has been described, but this configuration is not limiting. The internal cross-sectional area of ​​the evaporator 26 may be equal to or larger than the internal cross-sectional area of ​​the reheater 37.

[0082] In the above-described embodiment, a configuration in which the outside air and the refrigerant flow in opposite directions in the evaporator 26 has been described, but the present invention is not limited to this configuration. The outside air and the refrigerant may flow in the same direction (parallel flow). Also, the first fin module 200 and the second fin module 201 may be provided with heat transfer tubes of different systems. In the above-described embodiment, the evaporator 26 and the reheater 37 are separately disposed in flow paths that are folded back from each other, but the present invention is not limited to this configuration. The evaporator 26 and the reheater 37 may be disposed in flow paths that extend linearly. In the above-described embodiment, the evaporator 26 is configured to include two stages of fin modules (the first fin module 200 and the second fin module 201), but the configuration is not limited to this. The evaporator 26 may also include three or more stages of fin modules.

[0083] In addition, within the scope of the spirit of the present invention, it is possible to replace the components in the above-described embodiments with well-known components as appropriate, and the above-described modified examples may be combined as appropriate. [Explanation of symbols]

[0084] 1: Outdoor air treatment device 21: Compressor 23: Condenser 25: Expansion valve (expansion device) 26: Evaporator (first heat exchanger) 31: Main air conditioning channel (air conditioning channel) 31b: Middle flow path (first flow path) 31c: Upper flow path (second flow path) 37: Reheater (second heat exchanger) 50: Refrigerator casing 51: Air conditioner casing 100: Refrigeration unit 101: Air conditioner unit 200: First fin module 201: Second fin module 210: First Fin 211: Second Fin 252: Heat transfer tube 300b: downstream flow path (first flow path) 301: Upper flow path (second flow path) 301a: upstream flow path (first flow path) 301b: downstream flow path (second flow path) T1: Dimensions T2: Dimensions

Claims

1. an air conditioning flow path through which first outside air flows out of the outside air taken in from outdoors; a first heat exchanger provided in the air conditioning flow path and configured to cool the first outside air by exchanging heat between the first outside air and a heat medium; a second heat exchanger that is provided in the air conditioning flow path downstream of the first heat exchanger and that performs heat exchange between the first outside air that has passed through the first heat exchanger and second outside air that has not passed through the first heat exchanger, The first heat exchanger is a first fin module including a plurality of first fins arranged at intervals in a first direction intersecting a flow direction of the first outside air in the air conditioning flow path; a second fin module having a plurality of second fins spaced apart from one another in the first direction and disposed downstream of the first fin module in the flow direction; The outside air processing device, wherein the distance between adjacent first fins is narrower than the distance between adjacent second fins.

2. The outside air processing device according to claim 1 , wherein an inner cross-sectional area of ​​the first heat exchanger as viewed from the flow direction is smaller than an inner cross-sectional area of ​​the second heat exchanger as viewed from the flow direction.

3. the first heat exchanger includes a heat transfer tube that penetrates the first fin module and the second fin module in the first direction and is formed in a serpentine shape in the flow direction, The outside air treatment device according to claim 1 or 2, wherein the heat medium flows through the heat transfer tube so as to pass through the second fin module and then the first fin module.

4. The outside air treatment device of claim 1 or 2, wherein the first fin module and the second fin module are arranged in series in the flow direction.

5. 3. The outside air treatment device according to claim 1, wherein a dimension of the first fin module in the flow direction is larger than a dimension of the second fin module in the flow direction.

6. 3. The outside air treatment device according to claim 1, wherein the distance between the adjacent second fins is set to be 1.2 to 2.0 times the distance between the adjacent first fins.

7. The outside air treatment device according to claim 1 or 2, wherein the heat medium is an HFO refrigerant.

8. The outside air treatment device according to claim 7, wherein the evaporation temperature of the heat medium in the first heat exchanger is set to be in the range of -1°C to 9°C.

9. an air conditioner unit including an air conditioner casing in which the air conditioning flow path is formed, and the first heat exchanger and the second heat exchanger housed in the air conditioner casing; a refrigerator unit having a refrigerator casing that houses a compressor that compresses a heat medium and a condenser that dissipates heat from the heat medium compressed by the compressor, the refrigerator unit being disposed apart from the air conditioner unit; an expansion device disposed between the air conditioner unit and the refrigerator unit, connecting the condenser and the first heat exchanger; The air conditioning flow path is a first flow path provided with the first heat exchanger; 3. The outdoor air treatment device according to claim 1, further comprising: a second flow path that is connected to the downstream side of the first flow path, is folded back so as to overlap the first flow path when viewed from a second direction, and has the second heat exchanger provided therein.

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