GB2579476A

GB2579476A - Heat exchange unit and refrigeration cycle device

Info

Publication number: GB2579476A
Application number: GB2001225.8A
Authority: GB
Inventors: Kibe Atsushi; Sato Hiroki; Ishikawa Tomotaka
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2017-08-29
Filing date: 2017-08-29
Publication date: 2020-06-24
Anticipated expiration: 2037-08-29
Also published as: JP6888102B2; WO2019043771A1; JPWO2019043771A1; GB202001225D0; CN111065868A; CN111065868B; GB2579476B

Abstract

This heat exchange unit comprises: a heat exchanger having a first heat exchange part that exchanges heat with a refrigerant, and a second heat exchange part that exchanges heat with the refrigerant that has undergone heat exchange in the first heat exchange part; a blower for forming an airflow that causes air to pass through the heat exchanger; and an electrical component box in which electrical components are accommodated. The electrical component box is provided nearer to the second heat exchange part than the first heat exchange part.

Description

DESCRIPTION

TITLE OF INVENTION

Heat Exchanger Unit and Refrigeration Cycle Device

TECHNICAL FIELD

[0001] The present invention relates to a heat exchanger unit including an electrical component box.

BACKGROUND ART

[0002] Conventionally, heat exchanger units each including an electrical component box have been known (see, for example, PTL 1). In PTL 1, a heat sink attached to an electrical component box is exposed to a heat exchange chamber, and the heat sink is cooled by air flowing within the heat exchange chamber.

CITATION LIST

PATENT LITERATURE

[0003] PTL 1: Japanese Patent Laying-Open No. 2016-166734

SUMMARY OF INVENTION

TECHNICAL PROBLEM

[0004] However, in PTL 1, heat dissipation of the electrical component box may be insufficient depending on the positional relation between the heat sink and a heat exchanger. When heat dissipation of the electrical component box is insufficient, an electrical component accommodated in the electrical component box may be deteriorated or damaged.

[0005] The present invention has been made in view of the aforementioned problem, and an object thereof is to obtain a heat exchanger unit capable of efficiently performing heat dissipation of an electrical component box.

SOLUTION TO PROBLEM

[0006] A heat exchanger unit in accordance with the present invention includes: a heat exchanger having a first heat exchange part to perform heat exchange on refrigerant and a second heat exchange part to perform heat exchange on the refrigerant subjected to heat exchange in the first heat exchange part; a blower to form an air flow that causes air to pass through the heat exchanger; and an electrical component box to accommodate an electrical component, the electrical component box being provided closer to the second heat exchange part than to the first heat exchange part.

ADVANTAGEOUS EFFECTS OF INVENTION

[0007] According to the present invention, a heat exchanger unit capable of efficiently performing heat dissipation of an electrical component box can be obtained.

BRIEF DESCRIPTION OF DRAWINGS

[0008] Fig. 1 is a view of a heat exchanger unit in accordance with a first embodiment of the present invention, viewed from the front.

Fig. 2 is a view showing an example of the inside of the heat exchanger unit shown in Fig. 1 Fig. 3 is a view showing an example of a heat exchanger shown in Fig. 2. Fig. 4 is a view showing an example of a refrigeration cycle device in accordance with the first embodiment of the present invention.

Fig. 5 is a view of a heat exchange chamber shown in Fig. 2, viewed from above.

Fig. 6 is a view showing an example of a configuration of a control device shown in Fig. 1.

Fig. 7 is a view showing an example of an operation of the control device shown in Fig. 6.

Fig. 8 is a view showing a first variation of Fig. 5.

Fig. 9 is a view of a heat exchanger, an air path formation part, and a heat dissipation promotion part in Fig. 8, viewed from a side.

Fig. 10 is a view showing a second variation of Fig. 8.

Fig. 11 is a view of a heat exchanger, an air path formation part, and a heat dissipation promotion part in Fig. 10, viewed from a side.

Fig. 12 is a view showing an example of a refrigeration cycle device in accordance with a second embodiment of the present invention.

DESCRIPTION OF EMBODIMENTS

[0009] Hereinafter, embodiments of the present invention will be described with reference to the drawings. It should be noted that identical or corresponding parts in the drawings will be designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, and the like of each component shown in the drawings can be changed as appropriate within the scope of the present invention.

[0010] First Embodiment Fig. 1 is a view of a heat exchanger unit in accordance with a first embodiment of the present invention, viewed from the front. Fig. 2 is a view showing an example of the inside of the heat exchanger unit shown in Fig. 1. Fig. 3 is a view showing an example of a heat exchanger shown in Fig. 2. Fig. 4 is a view showing an example of a refrigeration cycle device in accordance with the first embodiment of the present invention. Fig. 5 is a view of a heat exchange chamber shown in Fig. 2, viewed from above. A heat exchanger unit 100 shown in Fig. 1 is an outdoor unit provided outdoors on the outside of a room. The present embodiment mainly describes a case where a heat exchanger 3 functions as a condenser 3A, as shown in Fig. 4. Heat exchanger unit 100 is placed outdoors or in a machine chamber or the like, for example, and is connected with an indoor unit 400 via a pipe 410 and a pipe 420. Pipe 410 is a pipe through which a liquid refrigerant flows, and pipe 420 is a pipe through which a gas refrigerant flows. Indoor unit 400 is, for example, a unit cooler provided on the inside of a room, such as a warehouse, to cool the inside of the room. Indoor unit 400 may be a unit provided in a showcase to cool the inside of the showcase. Indoor unit 400 has an expansion valve 402 and an evaporator 404. Expansion valve 402 expands refrigerant. Evaporator 404 evaporates the refrigerant by heat exchange between the refrigerant and air. A fan 406 is provided in the vicinity of evaporator 404. When fan 406 is operated, air is taken in from a cooling space into indoor unit 400, the taken-in air passes through evaporator 404 and is subjected to heat exchange, and then cool air is blown out to the cooling space.

[0011] [Heat Exchanger Unit] As shown in Figs. 1 and 2, heat exchanger unit 100 has a case 110 including a heat exchange chamber 10 and a machine chamber 20 partitioned by a partition plate 25. In heat exchange chamber 10, heat exchanger 3 and a liquid reservoir 54 are provided.

Heat exchanger 3 exchanges heat between the refrigerant and air. Since heat exchanger 3 is provided in heat exchange chamber 10 partitioned from machine chamber 20 by partition plate 25, heat exchanger 3 can perform heat exchange efficiently. Liquid reservoir 54 separates a gas-liquid two-phase refrigerant into a gas refrigerant and a liquid refrigerant, reserves the gas refrigerant, and causes the liquid refrigerant to flow out. Liquid reservoir 54 is provided at a lower part inside heat exchange chamber 10. Since liquid reservoir 54 is provided at a position having a low temperature inside heat exchange chamber 10, evaporation of the liquid refrigerant can be suppressed. It should be noted that liquid reservoir 54 may be provided in machine chamber 20.

[0012] As shown in Fig. 1, a first blower 14 and a second blower 18 are provided in a forward part of heat exchange chamber 10. First blower 14 and second blower 18 form an air flow passing through heat exchanger 3. First blower 14 or second blower 18 corresponds to the "blower" of the present invention. First blower 14 is provided closer to a first heat exchanger 31 than to a second heat exchanger 32. Second blower 18 is provided below first blower 14 and closer to second heat exchanger 32 than to first heat exchanger 31. A first fan guard 12 is provided in front of first blower 14, and a second fan guard 16 is provided in front of second blower 18. Heat exchanger unit 100 is provided with air suction parts in a left side part and a back surface part of case 110, for example, and can suction the air from the left side part and the back surface part. As shown in Fig. 5, when first blower 14 or second blower 18 is operated, the air is taken in from a back surface and a left side surface of heat exchanger 3, passes through heat exchanger 3, and then is blown out of a front surface. That is, heat exchanger unit 100 in the example of the present embodiment is a side flow-type heat source machine that blows out the air in a direction intersecting an up/down direction. It should be noted that, although the present embodiment describes a case where heat exchanger unit 100 has two blowers, i.e., first blower 14 and second blower 18, heat exchanger unit 100 may have only first blower 14, with second blower 18 being omitted. In addition, heat exchanger unit 100 may have three or more blowers including first blower 14, second blower 18, and another blower (not shown).

[0013] In machine chamber 20, a compressor 52, an electrical component box 210, refrigerant circuit components (not shown) such as connecting pipes for controlling a flow of the refrigerant, and the like are provided. Electrical component box 210 is attached to, for example, partition plate 25 that partitions machine chamber 20 from heat exchange chamber 10. For example, a surface of electrical component box 210 provided with a heat dissipation promotion part 212 forms a portion of partition plate 25. Electrical component box 210 is provided above compressor 52. Since electrical component box 210 is provided above, convenience of maintenance and the like is improved. Since compressor 52 is provided below, influence of vibration of compressor 52 can be reduced.

[0014] In electrical component box 210, electrical component 213, a temperature sensor 213a, a control device 220, and the like are accommodated. Electrical component 213 is an element that generates a large amount of heat, among the elements accommodated in electrical component box 210. Electrical component 213 includes, for example, an inverter that drives compressor 52 or first blower 14 or second blower 18, or the like. In electrical component box 210, heat dissipation promotion part 212 is provided. Heat dissipation promotion part 212 promotes heat dissipation of electrical component 213, and is, for example, a heat sink formed of a material having a good heat conductivity such as aluminum. Heat dissipation promotion part 212 is indirectly attached to electrical component 213, for example, via a substrate (not shown) provided with electrical component 213. It should be noted that heat dissipation promotion part 212 may be directly attached to electrical component 213. Heat dissipation promotion part 212 enters heat exchange chamber 10, and is exposed to heat exchange chamber 10. Heat generated by electrical component 213 and the like is exhausted to heat exchange chamber 10 via heat dissipation promotion part 212. Temperature sensor 213a detects the temperature of electrical component 213 directly or indirectly. Control device 220 controls an entire refrigeration cycle device 101 shown in Fig. 4, and is composed of, for example, a microcomputer or the like. It should be noted that control device 220 may control refrigeration cycle device 101 together with a centralized controller (not shown) provided outside heat exchanger unit 100 or a control device (not shown) provided in indoor unit 400.

[0015] [Heat Exchanger] As shown in Fig. 5, heat exchanger 3 has a shape with a single bend, for example, and can perform heat exchange efficiently in a space-saving manner. It should be noted that heat exchanger 3 may have a shape with two or more bends, or may have a shape with no bend. As shown in Figs. 2 and 3, heat exchanger 3 has first heat exchanger 31 and second heat exchanger 32. First heat exchanger 31 and second heat exchanger 32 are connected by a second connecting pipe 34. Second connecting pipe 34 is formed of a circular pipe having a flow path with a circular cross section. The refrigerant subjected to heat exchange in first heat exchanger 31 passes through second connecting pipe 34, and is subjected to heat exchange in second heat exchanger 32. First heat exchanger 31 is provided above second heat exchanger 32. It should be noted that first heat exchanger 31 and second heat exchanger 32 may be integrally formed.

[0016] First heat exchanger 31 and second heat exchanger 32 are formed to include refrigerant pipes which have a flat shape and through which the refrigerant flows, and a corrugated fin which has a wave shape and which connects the refrigerant pipes. Heat exchanger 3 in the example of the present embodiment is, for example, an aluminum flat pipe/corrugated fin heat exchanger in which flat pipes and a corrugated fin are made of aluminum, achieving weight saving, cost reduction, downsizing, and the like. Since the refrigerant pipes of heat exchanger 3 have a flat shape, efficiency of heat exchange between the refrigerant and the air is improved, and further, air path resistance can be reduced. Further, since the refrigerant pipes of heat exchanger 3 have a flat shape, heat exchanger 3 can be downsized and the filling amount of the refrigerant can be reduced. Further, since the fin is a corrugated fin having a wave shape, a heat transfer area can be enlarged.

[0017] First heat exchanger 31 has a first heat exchange part 31A and a second heat exchange part 31B. Second heat exchange part 31B is provided above first heat exchange part 31A First heat exchange part 31A and second heat exchange part 31B have a plurality of flow paths through which the refrigerant flows in parallel. In first heat exchanger 31, a first inflow/outflow header 310 is attached to one end, and a first connecting pipe 312 is attached to the other end. First inflow/outflow header 310 is formed of a circular pipe having a flow path with a circular cross section. First inflow/outflow header 310 has a first inflow part 310A and a first outflow part 310B. First inflow part 310A and first outflow part 310B are partitioned by a first partition part 31 OC. A first inflow pipe 311 is attached to first inflow part 310A, and a first outflow pipe 313 is attached to first outflow part 310B. First connecting pipe 312 is formed of a circular pipe having a flow path with a circular cross section. First connecting pipe 312 has a pipe diameter larger than a diameter of 10 mm. The refrigerant flowing in from first inflow pipe 311 is distributed in first inflow part 310A, and the distributed refrigerants flow through first heat exchange part 31A in parallel.

The refrigerants flowing out of first heat exchange part 31A join together in first connecting pipe 312, the joined refrigerant is distributed, and the distributed refrigerants flow through second heat exchange part 31B in parallel. The refrigerants flowing out of second heat exchange part 31B join together in first outflow part 310B, and the joined refrigerant flows out of first outflow pipe 313.

[0018] In the example of the present embodiment, since electrical component box 210 is provided closer to second heat exchange part 31B than to first heat exchange part 31A as shown in Figs. 1 and 2, electrical component box 210 can dissipate heat efficiently. This is because second heat exchange part 31B has a temperature lower than that of first heat exchange part 31A. Further, in the example of the present embodiment, since electrical component box 210 is provided closer to first outflow part 310B serving as a refrigerant outflow part of second heat exchange part 31 B, than to first connecting pipe 312 serving as a refrigerant inflow part of second heat exchange part 31B, electrical component box 210 can dissipate heat efficiently. This is because the refrigerant outflow part of second heat exchange part 31B has a temperature lower than that of the refrigerant inflow part of second heat exchange part 31B.

[0019] As shown in Figs. 2 and 3, second heat exchanger 32 has a third heat exchange part 32A and a fourth heat exchange part 32B. Third heat exchange part 32A is provided above fourth heat exchange part 32B. Third heat exchange part 32A and fourth heat exchange part 32B have a plurality of flow paths through which the refrigerant flows in parallel. In second heat exchanger 32, a second inflow/outflow header 320 is attached to one end, and a third connecting pipe 322 is attached to the other end. Second inflow/outflow header 320 is formed of a circular pipe having a flow path with a circular cross section. Second inflow/outflow header 320 has a second inflow part 320A and a second outflow part 320B. Second inflow part 320A and second outflow part 320B are partitioned by a second partition part 312C. A second inflow pipe 321 is attached to second inflow part 320A, and a second outflow pipe 323 is attached to second outflow part 320B. Third connecting pipe 322 is formed of a circular pipe having a flow path with a circular cross section. The refrigerant flowing in from second inflow pipe 321 is distributed in second inflow part 320A, and the distributed refrigerants flow through third heat exchange part 32A in parallel. The refrigerants flowing out of third heat exchange part 32A join together in third connecting pipe 322, the joined refrigerant is distributed, and the distributed refrigerants flow through fourth heat exchange part 32B in parallel. The refrigerants flowing out of fourth heat exchange part 32B join together in second outflow part 320B, and the joined refrigerant flows out of second outflow pipe 323.

[0020] [Flow of Refrigerant in Condenser] Next, a flow of refrigerant in condenser 3A will be described. A gas refrigerant having a high temperature and a high pressure compressed by compressor 52 shown in Fig. 4 passes through first inflow pipe 311 and first inflow part 310A shown in Fig. 3, and flows into first heat exchange part 31A. The refrigerant exchanges heat with the air while flowing through first heat exchange part 31A in the direction intersecting the up/down direction, and then passes through first connecting pipe 312 and flows into second heat exchange part 31 B above first heat exchange part 31A. The refrigerant having exchanged heat with the air in first heat exchange part 31A becomes a gas refrigerant or a gas-liquid two-phase refrigerant having a high ratio of a gas refrigerant. Since the gas refrigerant or the gas-liquid two-phase refrigerant having a high ratio of the gas refrigerant flows upward through first connecting pipe 312 in the present embodiment, influence of pressure loss is reduced, and further, distribution of the refrigerant to second heat exchange part 31B is equalized, when compared with a case where a liquid refrigerant or a gas-liquid two-phase refrigerant having a high ratio of a liquid refrigerant flows upward through first connecting pipe 312. This is because the gas refrigerant has a density lower than that of the liquid refrigerant. In addition, since first connecting pipe 312 is formed of a circular pipe having a pipe diameter larger than a diameter of 10 mm, for example, in the present embodiment, influence of pressure loss is reduced. It should be noted that the ratio of a liquid refrigerant flowing into first connecting pipe 312 can be reduced for example by forming first heat exchange part 31A to have an area smaller than that of second heat exchange part 31B, and thereby influence of pressure loss can be further reduced, and distribution of the refrigerant to second heat exchange part 31 B can be further equalized.

[0021] The refrigerant exchanges heat with the air while flowing through second heat exchange part 31B in the direction intersecting the up/down direction, and then passes through first outflow part 310B, first outflow pipe 313, second connecting pipe 34, second inflow pipe 321, and second inflow part 320A, and flows into third heat exchange part 32A below first heat exchange part 31A and second heat exchange part 31 B. The refrigerant having exchanged heat with the air in second heat exchange part 31B becomes a gas-liquid two-phase refrigerant having a high ratio of a liquid refrigerant. In the present embodiment, since first heat exchange part 31A is provided between second heat exchange part 31B and third heat exchange part 32A, a height difference between second heat exchange part 31B and third heat exchange part 32A can be increased. By increasing the height difference between second heat exchange part 31 B and third heat exchange part 32A, the flow velocity of the refrigerant flowing into second inflow part 320A can be increased, and thereby distribution of the refrigerant flowing into third heat exchange part 32A can be equalized. By equalizing the gas-liquid two-phase refrigerant flowing into third heat exchange part 32A, efficiency of heat exchange in third heat exchange part 32A is improved.

[0022] The refrigerant exchanges heat with the air while flowing through third heat exchange part 32A in the direction intersecting the up/down direction, and then passes through third connecting pipe 322 and flows into fourth heat exchange part 32B. The refrigerant having exchanged heat with the air in third heat exchange part 32A becomes a gas-liquid two-phase refrigerant having a higher ratio of a liquid refrigerant. By causing the gas-liquid two-phase refrigerant having a high ratio of the liquid refrigerant to flow downward, influence of pressure loss can be reduced, and thereby the refrigerant can flow efficiently. The refrigerant exchanges heat with the air while flowing through fourth heat exchange part 32B in the direction intersecting the up/down direction, and then passes through second outflow part 320B and flows out of second outflow pipe 323.

[0023] [Refrigeration Cycle Device] As shown in Fig. 4, refrigeration cycle device 101 in the example of the present embodiment has a refrigerant circulation circuit 102 through which the refrigerant circulates, and an injection flow path 103 which returns the condensed refrigerant to compressor 52. The refrigerant applied to refrigeration cycle device 101 in the present embodiment is a refrigerant having a low global warming potential (GWP) such as R410A, R32, or CO2, for example, and may also be a mixed refrigerant containing at least one of these refrigerants, or a refrigerant of another type different from these refrigerants. Further, refrigeration cycle device 101 in the example of the present embodiment can also use a non-azeotropic refrigerant mixture. The non-azeotropic refrigerant mixture is, for example, R407C or R448A. The non-azeotropic refrigerant mixture may be any refrigerant that is a mixed refrigerant containing R32, R125, R 134a, R1234yf, and CO), and satisfies all of a condition that a ratio XR32 (wt%) of R32 is 33<XR32<39, a condition that a ratio XR125 (wt%) of R125 is 27<XR125<33, a condition that a ratio XR134a (wt%) of R134a is 11<XR134a<17, a condition that a ratio XR1234yf (wt%) of R1234yf is 11<XR1234yf<17, a condition that a ratio XCO2 (wt%) of CO2 is 3<XCO2<9, and a condition that a total sum of XR32, XR125, XR134a, XR1234yf, and XCO2 is 100.

[0024] Refrigerant circulation circuit 102 is constituted by connecting compressor 52, condenser 3A, liquid reservoir 54, a supercooler 56, expansion valve 402, and evaporator 404 using pipes. Compressor 52 compresses the suctioned refrigerant and discharges the refrigerant in a high-temperature and high-pressure state. Compressor 52 is, for example, an inverter compressor in which control is performed by an inverter, and its capacity (the amount of discharging the refrigerant per unit time) can be changed by arbitrarily changing an operation frequency. Compressor 52 may be a constant-speed compressor operated at a constant operation frequency. Although the example of the present embodiment describes a case where refrigerant circulation circuit 102 has one compressor 52, compressor 52 may have a plurality of compressors connected in parallel or in series. Condenser 3A condenses the refrigerant by heat exchange between the refrigerant and the air. Liquid reservoir 54 is a container for reserving the refrigerant.

[0025] Supercooler 56 supercools the refrigerant flowing through refrigerant circulation circuit 102 by heat exchange between the refrigerant flowing through refrigerant circulation circuit 102 and the refrigerant flowing through injection flow path 103. Supercooler 56 is formed of, for example, a plate-type heat exchanger, a double pipe heat exchanger, or the like, and may be any element that performs heat exchange between the refrigerant flowing through refrigerant circulation circuit 102 and the refrigerant flowing through injection flow path 103. It should be noted that, although supercooler 56 may be omitted, the degree of supercooling can be increased by providing supercooler 56, and thus supercooler 56 can increase refrigeration capacity of refrigeration cycle device 101.

[0026] Expansion valve 402 expands the refrigerant. Expansion valve 402 is formed of, for example, an electronic expansion valve, a temperature-type expansion valve, or the like in which the degree of opening is adjustable, and may also be formed of a capillary tube or the like in which the degree of opening is not adjustable. It should be noted that expansion valve 402 can also be formed of a combination of a plurality of flow paths in which capillary tubes having different lengths are connected in parallel, and an opening/closing valve provided to at least one of the plurality of flow paths.

Evaporator 404 evaporates the refrigerant. Evaporator 404 is, for example, a fin tube-type heat exchanger formed to include a tube through which refrigerant flows, and a fin attached to the tube.

[0027] Injection flow path 103 returns a portion of the refrigerant condensed by condenser 3A to compressor 52. Injection flow path 103 is formed of a pipe that connects a pipe connecting between supercooler 56 and expansion valves 402 to a compression chamber (not shown) at an intermediate pressure in compressor 52. Injection flow path 103 may be a pipe that connects a pipe connecting between supercooler 56 and expansion valves 402 to a low pressure side of compressor 52.

Injection flow path 103 is provided with an injection expansion valve 58. Injection expansion valve 58 expands the refrigerant flowing into injection flow path 103. Injection expansion valve 58 is formed of, for example, an electronic expansion valve, a temperature-type expansion valve, or the like in which the degree of opening is adjustable, and may also be formed of a capillary tube or the like in which the degree of opening is not adjustable. Further, injection expansion valve 58 can also be formed of a combination of a plurality of flow paths in which capillary tubes having different lengths are connected in parallel, and an opening/closing valve provided to at least one of the plurality of flow paths.

[0028] [Operation of Refrigeration Cycle Device] Next, an operation of refrigeration cycle device 101 will be described. The refrigerant compressed by compressor 52 is condensed by condenser 3A. The refrigerant condensed by condenser 3A passes through liquid reservoir 54 and is cooled by supercooler 56. The refrigerant cooled by supercooler 56 is expanded by expansion valve 402. The refrigerant expanded by expansion valve 402 is evaporated by evaporator 404. The refrigerant evaporated by evaporator 404 is suctioned into compressor 52 and is compressed again. A portion of the refrigerant cooled by supercooler 56 is expanded by injection expansion valve 58 in injection flow path 103, passes through supercooler 56 in injection flow path 103, and is returned to compressor 52.

[0029] [Cooling Structure for Electrical Component Box] As shown in Fig. 5, heat dissipation promotion part 212 exposed to heat exchange chamber 10 is provided more downstream of an air flow than heat exchanger 3. Specifically, heat dissipation promotion part 212 is provided at a position higher than first partition part 310C shown in Fig. 3, and is provided at a position through which the air having passed through second heat exchange part 31B passes. By causing the air having passed through heat exchanger 3 to pass through heat dissipation promotion part 212, a cooling structure for electrical component box 210 can be simplified. By simplifying the cooling structure for electrical component box 210, heat exchanger unit 100 can be downsized. Further, since the air passing through heat dissipation promotion part 212 is the air having passed through second heat exchange part 31B, the air having a temperature lower than that of the air having passed through first heat exchange part 31A passes. Further, since the air passing through heat dissipation promotion part 212 is the air having passed through the vicinity of first outflow part 310B that is close to the refrigerant outflow part of second heat exchange part 31B, the air having a temperature lower than that of the air having passed through the vicinity of first connecting pipe 312 that is close to the refrigerant inflow part of second heat exchange part 31B passes. Since the air passing through heat dissipation promotion part 212 has a low temperature, heat dissipation in heat dissipation promotion part 212 can be performed efficiently. It should be noted that, in a refrigeration device or the like in which heat exchanger 3 functions as condenser 3A, the temperature of the refrigerant flowing into heat exchanger 3 may be more than or equal to 100 degrees. In such a case, by composing heat exchanger 3 such that the temperature of the refrigerant passing through first outflow part 3108 is less than 60 degrees, heat exchanger 3 can have a good heat exchange efficiency, and heat dissipation in heat dissipation promotion part 212 can be performed efficiently. [0030] [Operation of Control Device] Fig. 6 is a view showing an example of a configuration of the control device shown in Fig. 1, and Fig. 7 is a view showing an example of an operation of the control device shown in Fig. 6. As shown in Fig. 6, control device 220 controls first blower 14, second blower 18, compressor 52, injection expansion valve 58, expansion valve 402, fan 406, or the like. It should be noted that, when indoor unit 400 shown in Fig. 4 includes a control device (not shown), it is possible to adopt a configuration in which control device 220 controls first blower 14, second blower 18, compressor 52, or injection expansion valve 58 of heat exchanger unit 100, and the control device (not shown) of indoor unit 400 controls expansion valve 402 or fan 406 of indoor unit 400. For example, control device 220 controls first blower 14, second blower 18, or compressor 52 by utilizing the temperature of electrical component 213 detected by temperature sensor 213a. As shown in Fig. 7, in step S02, refrigeration cycle device 101 shown in Fig. 3 performs a normal operation.

[0031] In step SO4 in Fig. 7, it is determined whether the temperature of electrical component 213 detected by temperature sensor 213a is more than or equal to a first threshold value. When the temperature of electrical component 213 detected by temperature sensor 213a is lower than the first threshold value, the processing returns to step S02. When the temperature of electrical component 213 detected by temperature sensor 213a is more than or equal to the first threshold value in step SO4, an air volume of first blower 14 shown in Fig. 5 is increased and an air volume of second blower 18 is maintained in step 806. By increasing the air volume of first blower 14, an air volume passing through heat dissipation promotion part 212 is increased, and thereby heat dissipation of electrical component 213 is promoted. In the present embodiment, when electrical component 213 has a high temperature, it is only necessary to increase only the air volume of first blower 14, among first blower 14 and second blower 18. Thus, low power consumption can be achieved. Further, when the temperature of electrical component 213 is more than or equal to the first threshold value, the number of revolutions of compressor 52 is not decreased, or compressor 52 is not stopped. Thus, an increase in the temperature of the cooling space is suppressed.

[0032] In step S08 in Fig. 7, it is determined whether the temperature of electrical component 213 detected by temperature sensor 213a is more than or equal to a second threshold value. The second threshold value is a value corresponding to a temperature higher than the first threshold value. When the temperature of electrical component 213 detected by temperature sensor 213a is lower than the second threshold value, the processing returns to step 504. When the temperature of electrical component 213 detected by temperature sensor 213a is more than or equal to the second threshold value in step 508, the number of revolutions of compressor 52 is decreased in step S10. By decreasing the number of revolutions of compressor 52, heat generation of electrical component 213 is suppressed. In the present embodiment, when the temperature of electrical component 213 is more than or equal to the second threshold value, compressor 52 is not stopped and the number of revolutions of compressor 52 is decreased, and thereby an increase in the temperature of the cooling space is suppressed. [0033] In step S12, it is determined whether the temperature of electrical component 213 detected by temperature sensor 213a is more than or equal to a third threshold value. The third threshold value is a value corresponding to a temperature higher than the second threshold value. When the temperature of electrical component 213 detected by temperature sensor 213a is lower than the third threshold value, the processing returns to step SO8. When the temperature of electrical component 213 detected by temperature sensor 213a is more than or equal to the third threshold value in step S12, compressor 52 is stopped in step S14. By stopping compressor 52, heat generation of electrical component 213 is suppressed. In the present embodiment, when the temperature of electrical component 213 is more than or equal to the third threshold value, compressor 52 is stopped, and thereby deterioration of or damage to electrical component 213 is suppressed. Further, since compressor 52 is stopped when the temperature of electrical component 213 is more than or equal to the third threshold value, a failure or the like in refrigeration cycle device 101 due to an abnormality in first blower 14 can be suppressed.

[0034] As described above, in the example of the present embodiment, since cooling of electrical component box 210 is promoted, electrical component 213 is suppressed from having a high temperature that is more than or equal to the first threshold value. Therefore, protection control that eliminates a high temperature state of electrical component 213 is less to be performed. Further, in the example of the present embodiment, when the temperature of electrical component 213 is more than or equal to the first threshold value, the number of revolutions of compressor 52 is not decreased or compressor 52 is not stopped, and thereby an increase in the temperature of the cooling space is suppressed. Further, in the example of the present embodiment, when the temperature of electrical component 213 is more than or equal to the second threshold value, compressor 52 is not stopped and the number of revolutions of compressor 52 is decreased, and thereby an increase in the temperature of the cooling space is suppressed. Therefore, according to the present embodiment, deterioration of an object to be cooled that is accommodated in the cooling space can be suppressed. [0035] As described above, heat exchanger unit 100 in the example of the present embodiment includes: heat exchanger 3 having first heat exchange part 31A to perform heat exchange on refrigerant and second heat exchange part 31B to perform heat exchange on the refrigerant subjected to heat exchange in first heat exchange part 31A; blower 14 to form an air flow that causes air to pass through heat exchanger 3; and electrical component box 210 to accommodate electrical component 213, electrical component box 210 being provided closer to second heat exchange part 31B than to first heat exchange part 31A. In addition, refrigeration cycle device 101 in the example of the present embodiment includes: refrigerant circulation circuit 102 in which compressor 52, condenser 3A, expansion valve 402, and evaporator 404 are connected, and through which refrigerant circulates; and electrical component box 210 to accommodate electrical component 213, condenser 3A having heat exchanger 3 having first heat exchange part 31A to perform heat exchange on the refrigerant and second heat exchange part 31B to perform heat exchange on the refrigerant subjected to heat exchange in first heat exchange part 31A, electrical component box 210 being provided closer to second heat exchange part 31B than to first heat exchange part 31A.

In the example of the present embodiment, since electrical component box 210 is provided closer to second heat exchange part 31B having a temperature lower than that of first heat exchange part 31A, electrical component box 210 can dissipate heat efficiently.

[0036] For example, second heat exchange part 31 B has a plurality of flow paths through which the refrigerant flows in parallel. Utilizing the air around second heat exchange part 31B having a temperature lower than that of first heat exchange part 31A, electrical component box 210 can dissipate heat efficiently.

[0037] In addition, for example, since electrical component box 210 is provided closer to the refrigerant outflow part than to the refrigerant inflow part of second heat exchange part 31B, electrical component box 210 can dissipate heat efficiently, utilizing the air around the refrigerant outflow part having a temperature lower than that of the refrigerant inflow part of second heat exchange part 31B.

[0038] In addition, for example, heat exchanger unit 100 includes heat dissipation promotion part 212 provided at a position through which the air having passed through second heat exchange part 31B passes, to promote heat dissipation of electrical component 213. By causing the air having passed through second heat exchange part 31B to pass through heat dissipation promotion part 212, the cooling structure for electrical component box 210 can be simplified. By simplifying the cooling structure for electrical component box 210, heat exchanger unit 100 can be downsized.

[0039] In addition, for example, case 110 has heat exchange chamber 10 in which heat exchanger 3 is accommodated and machine chamber 20 in which electrical component box 210 is accommodated, and heat dissipation promotion part 212 is exposed to heat exchange chamber 10. Since heat exchanger 3 is provided in heat exchange chamber 10, heat exchange in heat exchanger 3 becomes more efficient. Further, since heat dissipation promotion part 212 is exposed to heat exchange chamber 10, heat dissipation in heat dissipation promotion part 212 can be performed efficiently. [0040] In addition, for example, second heat exchange part 31B is provided above first heat exchange part 31A, and electrical component box 210 is provided at a position higher than first heat exchange part 31 A. Since electrical component box 210 is provided at a high position, convenience of maintenance and the like is improved. [0041] In addition, for example, when heat exchanger 3 functions as condenser 3A and second heat exchange part 31B is provided above first heat exchange part 31A, influence of pressure loss can be reduced by adopting first connecting pipe 312, which connects first heat exchange part 31A and second heat exchange part 31B, formed of a circular pipe. First connecting pipe 312 is preferably formed of a pipe having a pipe diameter larger than a diameter of 10 mm, for example.

[0042] In addition, for example, when heat exchanger 3 functions as condenser 3A and second heat exchange part 31B is provided above first heat exchange part 31A, a height difference between second heat exchange part 31B and third heat exchange part 32A can be increased by providing third heat exchange part 32A below first heat exchange part 31A. Third heat exchange part 32A has a plurality of flow paths through which the refrigerant flows in parallel. By increasing the height difference between second heat exchange part 31B and third heat exchange part 32A, the flow velocity of the refrigerant flowing into second connecting pipe 34 can be increased, and distribution of the refrigerant flowing into third heat exchange part 32A can be equalized. Further, since heat exchanger 3 has first heat exchange part 31A, second heat exchange part 31B, and third heat exchange part 32A, the refrigerant having passed through first heat exchange part 31A can become a gas refrigerant or a gas-liquid two-phase refrigerant having a high ratio of a gas refrigerant. Since the refrigerant flowing through first connecting pipe 312, which connects first heat exchange part 31 A and second heat exchange part 31B, becomes the gas refrigerant or the gas-liquid two-phase refrigerant having a high ratio of the gas refrigerant, influence of pressure loss can be reduced.

[0043] In addition, for example, blower 14 has first blower 14 to perform air blowing to second heat exchange part 31B, and second blower 18 to perform air blowing to third heat exchange part 32A. Since blower 14 has first blower 14 and second blower 18, heat exchange can be efficiently performed on the refrigerant by adjusting a heat exchange amount in second heat exchange part 31B and a heat exchange amount in third heat exchange part 32A.

[0044] In addition, for example, when the temperature detected by temperature sensor 213a is more than or equal to the first threshold value, the air volume of second blower 18 is maintained and the air volume of first blower 14 is increased. Thereby, heat dissipation in heat dissipation promotion part 212 is promoted. When electrical component 213 has a high temperature, it is only necessary to increase only the air volume of first blower 14, among first blower 14 and second blower 18. Thus, low power consumption can be achieved. Further, when the temperature detected by temperature sensor 213a is more than or equal to the second threshold value corresponding to a temperature higher than the first threshold value, the number of revolutions of compressor 52 is decreased, and when the temperature detected by temperature sensor 213a is more than or equal to the third threshold value corresponding to a temperature higher than the second threshold value, compressor 52 is stopped. In the example of the present embodiment, even when the temperature of electrical component 213 increases, the number of revolutions of compressor 52 is not decreased immediately or the compressor is not stopped immediately. Thus, an increase in the temperature of the cooling space can be suppressed.

[0045] In addition, for example, since heat exchanger 3 has a refrigerant pipe formed in a flat shape, air path resistance can be reduced, heat exchange efficiency can be improved, and heat exchanger 3 can be downsized.

[0046] In addition, for example, since liquid reservoir 54 is provided at a position having a low temperature at a lower part inside heat exchange chamber 10, evaporation of the liquid refrigerant can be suppressed.

[0047] It should be noted that, in the present embodiment, the above effect is remarkable when heat exchanger 3 functions as condenser 3A. This is because, in the refrigeration device or the like in which heat exchanger 3 functions as condenser 3A, the temperature of the refrigerant flowing into heat exchanger 3 may be more than or equal to 100 degrees. By providing electrical component box 210 at a position where it is less affected by hot air having exchanged heat with the refrigerant having a temperature of more than or equal to 100 degrees, the cooling structure for electrical component box 210 can be simplified.

[0048] In addition, in the present embodiment, the above effect is remarkable when the refrigerant is a non-azeotropic refrigerant mixture. This is because the non-azeotropic refrigerant mixture has a temperature gradient, and thus a temperature difference between the temperature of the refrigerant passing through first heat exchange part 31A and the temperature of the refrigerant passing through second heat exchange part 31 B is increased.

[0049] As described above, according to the present embodiment, since heat dissipation in heat dissipation promotion part 212 becomes more efficient, heat dissipation promotion part 212 can be downsized. By downsizing heat dissipation promotion part 212, the cost of heat dissipation promotion part 212 can be reduced, pressure loss in an air path can be reduced, and refrigeration cycle device 101 can be downsized.

[0050] It should be noted that the present embodiment is not limited to the above

description.

[0051] [First Variation] For example, Fig. 8 is a view showing a first variation of Fig. 5, and Fig. 9 is a view of a heat exchanger, an air path formation part, and a heat dissipation promotion part in Fig. 8, viewed from a side. In Fig. 8, components identical to those in Fig. 5 will be designated by the same reference numerals, and the description thereof will be omitted or simplified. As shown in Figs. 8 and 9, the first variation has an air path formation part 214. Air path formation part 214 forms an air path that causes the air having passed through heat exchanger 3 to pass through heat dissipation promotion part 212. Air path formation part 214 is provided on the lee side of first heat exchange part 31A, and is attached to partition plate 25 or electrical component box 210, for example. Air path formation part 214 has a shape that allows the air passing through heat dissipation promotion part 212 to have a flow velocity faster than a flow velocity of the air passing through heat exchanger 3. For example, air path formation part 214 has a trumpet shape in which an opening of its air intake part located upstream of an air flow has an area larger than that on a downstream side. By forming the air intake part of air path formation part 214 to be large, much air can be taken in, and much air can pass through heat dissipation promotion part 212. Heat dissipation promotion part 212 is provided at a position higher than first partition part 310C in Fig. 3. The air intake part of air path formation part 214 is formed within a range of second heat exchange part 31B, and can take in the air having passed through second heat exchange part 31 B. By causing the air having passed through second heat exchange part 31B to pass through heat dissipation promotion part 212, heat dissipation in heat dissipation promotion part 212 can be performed efficiently. For example, the opening of the air intake part of air path formation part 214 is preferably formed to be twice or more larger than the cross-sectional area of heat dissipation promotion part 212. In the first variation, since air path formation part 214 is included, the amount of the air passing through heat dissipation promotion part 212 can be increased, and the velocity of the air passing through heat dissipation promotion part 212 can be increased. Thus, heat dissipation in heat dissipation promotion part 212 can be promoted. In addition, in the first variation, since air path formation part 214 is provided, heat dissipation promotion part 212 can be downsized.

[0052] [Second Variation] In addition, for example, Fig. 10 is a view showing a second variation of Fig. 8, and Fig. 11 is a view of a heat exchanger, an air path formation part, and a heat dissipation promotion part in Fig. 10, viewed from a side. It should be noted that, in Fig. 10, components identical to those in Fig. 8 will be designated by the same reference numerals, and the description thereof will be omitted or simplified. As shown in Figs. 10 and 11, in the second variation, air path formation part 214 has an air passage part 214A to cover at least a portion of heat dissipation promotion part 212. Air passage part 214A is provided so as not to come into contact with heat dissipation promotion part 212, and is formed such that heat can be dissipated from an outer surface of heat dissipation promotion part 212. A gap of 1 to 3 mm, for example, is provided between air passage part 214A and heat dissipation promotion part 212. By providing air passage part 214A, air blowing to heat dissipation promotion part 212 can be ensured. In addition, by providing air passage part 214A, hot air having passed through first heat exchange part 31A can be suppressed from passing through heat dissipation promotion part 212, and thus heat dissipation in heat dissipation promotion part 212 becomes more efficient. Although it is only necessary for air passage part 214A to have a shape covering at least a portion of heat dissipation promotion part 212, when air passage part 214A has a shape covering entire heat dissipation promotion part 212, air blowing to heat dissipation promotion part 212 can be further ensured. It should be noted that air passage part 214A is preferably formed such that the air passing through heat dissipation promotion part 212 has a velocity of more than or equal to 3 m/sec. By forming air passage part 214A such that the air passing through heat dissipation promotion part 212 has a velocity of more than or equal to 3 m/sec, heat dissipation in heat dissipation promotion part 212 becomes more efficient. When the air passing through heat dissipation promotion part 212 has a velocity of less than 3 m/sec as a result of forming air passage part 214A, air passage part 214A may be omitted as in the first variation. This is because, when the air passing through heat dissipation promotion part 212 has a velocity of less than 3 m/sec, hot air subjected to heat exchange in heat dissipation promotion part 212 may remain in air passage part 214A. Further, this is because, when the air passing through heat dissipation promotion part 212 has a velocity of less than 3 m/sec, air passage part 214A may be heated by the hot air having passed through first heat exchange part 31A, and heat dissipation in heat dissipation promotion part 212 may be impeded.

[0053] Second Embodiment Fig. 12 is a view showing an example of a refrigeration cycle device in accordance with a second embodiment of the present invention. It should be noted that, in Fig. 12, components identical to those in Fig. 4 will be designated by the same reference numerals, and the description thereof will be omitted or simplified. In addition, in the second embodiment, the description of components identical to those in the first embodiment will be omitted or simplified. As shown in Fig. 12, in a heat exchanger unit 100A of a refrigeration cycle device 101A in the example of the present embodiment, a liquid reservoir 54A is provided between first heat exchanger 31 and second heat exchanger 32. A gas-liquid two-phase refrigerant flowing out of first heat exchanger 31 is separated into a gas refrigerant and a liquid refrigerant in liquid reservoir 54A, and the liquid refrigerant flows out of liquid reservoir 54A. The liquid refrigerant flowing out of liquid reservoir 54A is subjected to heat exchange in second heat exchanger 32. In the example of the present embodiment, since the liquid refrigerant flowing out of liquid reservoir 54A is subjected to heat exchange in second heat exchanger 32, the degree of supercooling of the refrigerant flowing out of heat exchanger 3 can be increased. Therefore, according to the example of the present embodiment, refrigeration capacity of refrigeration cycle device 101A can be increased. [0054] Electrical component box 210 is provided closer to second heat exchanger 32 than to first heat exchanger 31. It should be noted that, in the second embodiment, first heat exchanger 31 corresponds to the "first heat exchange part" of the present invention, and second heat exchanger 32 corresponds to the "second heat exchange part" of the present invention. Since the liquid refrigerant from which the gas refrigerant has been separated in liquid reservoir 54A flows into second heat exchanger 32, electrical component box 210 can dissipate heat efficiently by providing electrical component box 210 closer to second heat exchanger 32. This is because the liquid refrigerant from which the gas refrigerant has been separated and which has exchanged heat with the air has a temperature lower than that of the gas-liquid two-phase refrigerant. Heat dissipation promotion part 212 is provided at a position through which the air having passed through second heat exchanger 32 passes, and heat dissipation in heat dissipation promotion part 212 can be performed efficiently.

[0055] The present invention is not limited to the embodiments described above, and can be modified in various manners within the scope of the present invention. That is, the configuration of each embodiment described above may be improved as appropriate, or at least a portion thereof may be replaced by another configuration. Further, a constituent feature whose arrangement is not particularly limited is not limited to be arranged at the position disclosed in an embodiment, and can be arranged at any position where it can perform its function.

[0056] For example, through a combination of the first embodiment and the second embodiment, a liquid reservoir can be provided between first heat exchange part 31A and second heat exchange part 31B of the first embodiment shown in Fig. 3. Further, a liquid reservoir can be provided between first heat exchanger 31 and second heat exchanger 32 of the first embodiment shown in Fig. 3, and electrical component box 210 can be provided closer to second heat exchanger 32 than to first heat exchanger 31. [0057] In addition, for example, although the first embodiment and the second embodiment have provided description about the refrigeration cycle device to be applied to a large-sized refrigeration device for cooling the inside of a cold storage warehouse or the like, the refrigeration cycle device is applicable to a small-sized refrigeration device such as a refrigerator. Further, the refrigeration cycle device is also applicable to an air conditioning device that cools or heats the inside of a room, and a heating device that heats water or the like.

[0058] In addition, for example, although the first embodiment has described the case where heat exchanger 3 functions as a condenser, heat exchanger 3 may function as an evaporator.

[0059] In addition, for example, although the first embodiment has provided description about heat exchanger 3 having first heat exchanger 31 and second heat exchanger 32 provided below first heat exchanger 31, the first embodiment is not limited thereto. For example, heat exchanger 3 can have only first heat exchanger 31, with second heat exchanger 32 being omitted, or can have three or more heat exchangers including first heat exchanger 31, second heat exchanger 32, and another heat exchanger.

[0060] In addition, for example, although the first embodiment has provided description about heat exchanger 3 having first heat exchanger 31 that has first heat exchange part 3 IA and second heat exchange part 31B, and third heat exchange part 32A and fourth heat exchange part 32B, first heat exchange part 31A, second heat exchange part 31B, third heat exchange part 32A, and fourth heat exchange part 32B may be formed separately.

REFERENCE SIGNS LIST

[0061] 3: heat exchanger; 3A: condenser; 10: heat exchange chamber; 12: first fan guard; 14: first blower; 16: second fan guard; 18: second blower; 20: machine chamber; 25: partition plate; 31: first heat exchanger; 31A: first heat exchange part; 31B: second heat exchange part; 32: second heat exchanger; 32A: third heat exchange part; 32B: fourth heat exchange part; 34: second connecting pipe; 52: compressor; 54: liquid reservoir; 54A: liquid reservoir; 56: supercooler; 58: injection expansion valve; 100: heat exchanger unit; 100A: heat exchanger unit; 101: refrigeration cycle device; 101A: refrigeration cycle device; 102: refrigerant circulation circuit; 103: injection flow path; 110: case; 210: electrical component box; 212: heat dissipation promotion part; 213: electrical component; 213a: temperature sensor; 214: air path formation part; 214A: air passage part; 220: control device; 310: first inflow/outflow header; 310A: first inflow part; 310B: first outflow part; 310C: first partition part; 311: first inflow pipe; 312: first connecting pipe; 312C: second partition part; 313: first outflow pipe; 320: second inflow/outflow header; 320A: second inflow part; 320B: second outflow part; 321: second inflow pipe; 322: third connecting pipe; 323: second outflow pipe; 400: indoor unit; 402: expansion valve; 404: evaporator; 406: fan; 410: pipe; 420: pipe.

Claims

CLAIMS1. A heat exchanger unit comprising: a heat exchanger having a first heat exchange part to perform heat exchange on refrigerant and a second heat exchange part to perform heat exchange on the refrigerant subjected to heat exchange in the first heat exchange part; a blower to form an air flow that causes air to pass through the heat exchanger; and an electrical component box to accommodate an electrical component, the electrical component box being provided closer to the second heat exchange part than to the first heat exchange part.
2. The heat exchanger unit according to claim 1, comprising a liquid reservoir provided between the first heat exchange part and the second heat exchange part.
3. The heat exchanger unit according to claim 1 or 2, wherein the second heat exchange part has a plurality of flow paths through which the refrigerant flows in parallel.
4. The heat exchanger unit according to any one of claims 1 to 3, wherein the electrical component box is provided closer to a refrigerant outflow part than to a refrigerant inflow part of the second heat exchange part.
5. The heat exchanger unit according to any one of claims I to 4, comprising a heat dissipation promotion part provided at a position through which air having passed through the second heat exchange part passes, to promote heat dissipation of the electrical component.
6. The heat exchanger unit according to claim 5, comprising a case having a -26 -heat exchange chamber in which the heat exchanger is accommodated and a machine chamber in which the electrical component box is accommodated, wherein the heat dissipation promotion part is exposed to the heat exchange chamber.
7. The heat exchanger unit according to claim 5 or 6, comprising an air path formation part to form an air path that causes the air having passed through the heat exchanger to pass through the heat dissipation promotion part, wherein the air path formation part has a shape that allows the air passing through the heat dissipation promotion part to have a flow velocity faster than a flow velocity of the air passing through the heat exchanger.
8. The heat exchanger unit according to claim 7, wherein the air path formation part has an intake part to take in air within a range through which the air having passed through the second heat exchange part passes.
9. The heat exchanger unit according to claim 7 or 8, wherein the air path formation part has an air passage part to cover at least a portion of the heat dissipation promotion part.
10. The heat exchanger unit according to any one of claims 1 to 9, wherein the second heat exchange part is provided above the first heat exchange part.
11. The heat exchanger unit according to claim 10, wherein the electrical component box is provided at a position higher than the first heat exchange part.
12. The heat exchanger unit according to claim 10 or 11, wherein the heat exchanger has a first connecting pipe that is a pipe to allow the refrigerant flowing out of the first heat exchange part to flow into the second heat exchange part, and is formed of a circular pipe having a circular flow path.-27 -
13. The heat exchanger unit according to claim 12, wherein the first connecting pipe has a pipe diameter larger than a diameter of 10 mm
14. The heat exchanger unit according to any one of claims 1 to 13, wherein the heat exchanger has a third heat exchange part provided below the first heat exchange part to perform heat exchange on the refrigerant subjected to heat exchange in the second heat exchange part.
15. The heat exchanger unit according to claim 14, wherein the third heat exchange part has a plurality of flow paths through which the refrigerant flows in parallel.
16. The heat exchanger unit according to claim 14 or 15, wherein the blower has a first blower to perform air blowing to the second heat exchange part, and a second blower to perform air blowing to the third heat exchange part.
17. The heat exchanger unit according to claim 16, comprising a temperature sensor to detect a temperature of the electrical component, wherein when the temperature detected by the temperature sensor is more than or equal to a first threshold value, an air volume of the second blower is maintained and an air volume of the first blower is increased.
18. The heat exchanger unit according to claim 17, comprising a compressor to compress the refrigerant, wherein when the temperature detected by the temperature sensor is more than or equal to a second threshold value corresponding to a temperature higher than the first threshold value, a number of revolutions of the compressor is decreased, and when the temperature detected by the temperature sensor is more than or equal -28 -to a third threshold value corresponding to a temperature higher than the second threshold value, the compressor is stopped.
19. The heat exchanger unit according to any one of claims 1 to 18, wherein the heat exchanger has a refrigerant pipe formed in a flat shape.
20. The heat exchanger unit according to any one of claims 1 to 19, wherein the heat exchanger functions as a condenser.
21. The heat exchanger unit according to claim 20 referring to claim 6, comprising a liquid reservoir provided at a lower part inside the heat exchange chamber to reserve the refrigerant subjected to heat exchange in the heat exchanger.
22. The heat exchanger unit according to any one of claims 1 to 21, wherein the refrigerant is a non-azeotropic refrigerant mixture.
23. A refrigeration cycle device comprising: a refrigerant circulation circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected, and through which refrigerant circulates; and an electrical component box to accommodate an electrical component, the condenser having a heat exchanger having a first heat exchange part to perform heat exchange on the refrigerant and a second heat exchange part to perform heat exchange on the refrigerant subjected to heat exchange in the first heat exchange part, the electrical component box being provided closer to the second heat exchange part than to the first heat exchange part.-29 -