JP6888102B2 - Heat exchanger unit and refrigeration cycle equipment - Google Patents

Description

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

Conventionally, a heat exchanger unit provided with an electric component box has been known (see, for example, Patent Document 1). In Patent Document 1, a heat sink attached to an electric component box is exposed in a heat exchange chamber, and the heat sink is cooled by the wind flowing in the heat exchange chamber.

Japanese Unexamined Patent Publication No. 2016-166734

However, in Patent Document 1, heat dissipation of the electric component box may be insufficient depending on the positional relationship between the heat sink and the heat exchange chamber. Insufficient heat dissipation from the electrical component box may result in deterioration or damage to the electrical components contained in the electrical component box.

The present invention has been made in view of the above problems, and an object of the present invention is to obtain a heat exchanger unit capable of efficiently dissipating heat from an electric component box.

The heat exchanger unit according to the present invention has heat having a first heat exchange unit that exchanges heat with the refrigerant and a second heat exchange unit that exchanges heat with the refrigerant heat exchanged by the first heat exchange unit. It is provided between the exchanger, the blower that forms an air flow that allows air to pass through the heat exchanger, the electrical component box that houses the electrical components, and the first heat exchange section and the second heat exchange section. The heat exchanger is provided with a liquid reservoir , and the heat exchanger has an inflow section for flowing the refrigerant compressed by the compressor into the first heat exchanger having a plurality of parallel flow paths, and a first heat exchange section from the inflow section. A connection pipe for flowing out the refrigerant flowing into the second heat exchange section having a plurality of parallel flow paths, and an outflow section for flowing out the heat exchanged refrigerant in the second heat exchange section. The electrical component box is provided closer to the second heat exchange section than the first heat exchange section, and closer to the outflow section which is the refrigerant outflow section of the second heat exchange section than the connection pipe. It is a thing.

According to the present invention, it is possible to obtain a heat exchanger unit capable of efficiently dissipating heat from an electric component box.

It is a figure which looked at the heat exchanger unit which concerns on Embodiment 1 of this invention from the front. It is a figure which shows an example of the inside of the heat exchanger unit shown in FIG. It is a figure which shows an example of the heat exchanger described in FIG. It is a figure which shows an example of the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention. FIG. 2 is a view of the heat exchange chamber shown in FIG. 2 as viewed from above. It is a figure which shows an example of the structure of the control device shown in FIG. It is a figure which shows an example of the operation of the control device shown in FIG. It is a figure which shows the modification 1 of FIG. FIG. 8 is a side view of the heat exchanger, the air passage forming portion, and the heat dissipation promoting portion of FIG. It is a figure which shows the modification 2 of FIG. FIG. 10 is a side view of the heat exchanger, the air passage forming portion, and the heat dissipation promoting portion of FIG. It is a figure which shows an example of the refrigeration cycle apparatus which concerns on Embodiment 2 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each figure, the same or corresponding parts are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, etc. of the configurations shown in each figure can be appropriately changed within the scope of the present invention.

Embodiment 1.
FIG. 1 is a front view of the heat exchanger unit according to the first embodiment of the present invention, and FIG. 2 is a diagram showing an example of the inside of the heat exchanger unit shown in FIG. 3 is a diagram showing an example of the heat exchanger described in FIG. 2, FIG. 4 is a diagram showing an example of a refrigeration cycle apparatus according to the first embodiment of the present invention, and FIG. 5 is a diagram showing an example of the heat exchanger. It is the figure which looked at the heat exchange chamber described from above. The heat exchanger unit 100 shown in FIG. 1 is an outdoor unit provided outside the room. As shown in FIG. 4, in this embodiment, an example in which the heat exchanger 3 functions as the condenser 3A will be mainly described. The heat exchanger unit 100 is installed, for example, outdoors or in a machine room, and is connected to the indoor unit 400 via pipes 410 and 420. The pipe 410 is for flowing the liquid refrigerant, and the pipe 420 is for flowing the gas refrigerant. The indoor unit 400 is, for example, a unit cooler provided inside a room such as a warehouse to cool the inside of the room. The indoor unit 400 may be provided in the showcase and cool the inside of the showcase. The indoor unit 400 has an expansion valve 402 and an evaporator 404. The expansion valve 402 expands the refrigerant. The evaporator 404 heat-exchanges the refrigerant with air to evaporate the refrigerant. A fan 406 is provided in the vicinity of the evaporator 404. When the fan 406 operates, air is taken into the indoor unit 400 from the cooling space, the taken-in air passes through the evaporator 404, and the heat-exchanged cold air is blown out to the cooling space through the evaporator 404. To.

[Heat exchanger unit]
As shown in FIGS. 1 and 2, the heat exchanger unit 100 has a housing 110 in which the heat exchange chamber 10 and the machine room 20 are partitioned by a partition plate 25. The heat exchange chamber 10 is provided with a heat exchanger 3 and a liquid reservoir 54. The heat exchanger 3 exchanges heat with air for the refrigerant. Since the heat exchanger 3 is provided in the heat exchange chamber 10 partitioned by the machine room 20 and the partition plate 25, the heat exchanger 3 can efficiently perform heat exchange. The liquid reservoir 54 separates the gas-liquid two-phase refrigerant into a gas refrigerant and a liquid refrigerant, stores the liquid refrigerant, and causes the gas refrigerant to flow out. The liquid reservoir 54 is provided in the lower part inside the heat exchange chamber 10. By providing the liquid reservoir 54 at a position where the temperature inside the heat exchange chamber 10 is low, evaporation of the liquid refrigerant can be suppressed. The liquid reservoir 54 may be provided in the machine room 20.

As shown in FIG. 1, a first blower 14 and a second blower 18 are provided in front of the heat exchange chamber 10. The first blower 14 and the second blower 18 form an air flow to be passed through the heat exchanger 3. The first blower 14 or the second blower 18 corresponds to the "blower" of the present invention. The first blower 14 is provided closer to the first heat exchanger 31 than the second heat exchanger 32. The second blower 18 is provided below the first blower 14 and closer to the second heat exchanger 32 than the first heat exchanger 31. A first fan guard 12 is provided in front of the first blower 14, and a second fan guard 16 is provided in front of the second blower 18. The heat exchanger unit 100 is provided with air suction portions on the left side portion and the back surface portion of the housing 110, for example, and can suck air from the left side portion and the back surface portion. As shown in FIG. 5, by operating the first blower 14 or the second blower 18, air is taken in from the back surface and the left side surface of the heat exchanger 3, and the air passing through the heat exchanger 3 is taken in from the front. Blow out. That is, the heat exchanger unit 100 of the example of this embodiment is a side flow type heat source machine that blows air in a direction intersecting the vertical direction. In this embodiment, an example having two blowers, a first blower 14 and a second blower 18, will be described, but the second blower 18 is omitted and only the first blower 14 is provided. It may be configured. Further, the configuration may include three or more blowers having a first blower 14, a second blower 18, and another blower (not shown).

The machine room 20 is provided with a compressor 52, an electric component box 210, and refrigerant circuit parts (not shown) such as connection pipes for controlling the flow of the refrigerant. The electrical component box 210 is attached to, for example, a partition plate 25 that separates the heat exchange chamber 10 and the machine chamber 20. For example, the surface of the electrical component box 210 provided with the heat dissipation promoting portion 212 forms a part of the partition plate 25. The electrical component box 210 is provided above the compressor 52. By providing the electrical component box 210 at the upper part, convenience such as maintenance is improved. By providing the compressor 52 at the lower part, the influence of the vibration of the compressor 52 can be reduced.

The electrical product box 210 houses the electrical product 213, the temperature sensor 213a, the control device 220, and the like. The electric product 213 has a large calorific value among the elements housed in the electric product box 210. The electrical product 213 includes, for example, a compressor 52, an inverter for driving a first blower 14 or a second blower 18, and the like. The electric component box 210 is provided with a heat dissipation promoting unit 212. The heat dissipation promoting unit 212 promotes heat dissipation of the electric product 213, and is a heat sink made of a material having good thermal conductivity such as aluminum. The heat dissipation promotion unit 212 is indirectly attached to the electric product 213 via, for example, a substrate (not shown) provided with the electric product 213. The heat dissipation promotion unit 212 may be directly attached to the electrical product 213. The heat dissipation promotion unit 212 enters the heat exchange chamber 10 and is exposed to the heat exchange chamber 10. The heat generated by the electric product 213 and the like is exhausted to the heat exchange chamber 10 via the heat dissipation promoting unit 212. The temperature sensor 213a directly or indirectly detects the temperature of the electrical product 213. The control device 220 controls the entire refrigeration cycle device 101 shown in FIG. 4, and is composed of, for example, a microcomputer or the like. The control device 220 controls the refrigeration cycle device 101 together with a centralized controller (not shown) provided outside the heat exchanger unit 100 or a control device (not shown) provided in the indoor unit 400. It may be a thing.

[Heat exchanger]
As shown in FIG. 5, the heat exchanger 3 has, for example, a once-bent shape, and can efficiently exchange heat in a small space. The heat exchanger 3 may have a bending shape of two or more times, or may not have a bending shape. As shown in FIGS. 2 and 3, the heat exchanger 3 has a first heat exchanger 31 and a second heat exchanger 32. The first heat exchanger 31 and the second heat exchanger 32 are connected by a second connecting pipe 34. The second connecting pipe 34 is formed of a circular pipe having a flow path having a circular cross section. The refrigerant heat-exchanged in the first heat exchanger 31 passes through the second connecting pipe 34 and is heat-exchanged in the second heat exchanger 32. The first heat exchanger 31 is provided above the second heat exchanger 32. The first heat exchanger 31 and the second heat exchanger 32 may be integrally formed.

The first heat exchanger 31 and the second heat exchanger 32 are formed to include a refrigerant pipe having a flat shape and flowing a refrigerant inside, and a corrugated fin having a wave shape and connecting the refrigerant pipes to each other. ing. The heat exchanger 3 of the example of this embodiment is, for example, an aluminum flat tube corrugated fin heat exchanger in which a flat tube and a corrugated fin are formed of aluminum, and weight reduction, cost reduction, miniaturization, and the like are realized. ing. Since the refrigerant pipe of the heat exchanger 3 has a flat shape, the heat exchange efficiency between the refrigerant and the air can be improved, and the air passage resistance can be further reduced. Further, since the refrigerant pipe of the heat exchanger 3 has a flat shape, the heat exchanger 3 can be miniaturized and the amount of the refrigerant filled can be reduced. Further, since the fin is a corrugated fin having a wavy shape, the heat transfer area can be increased.

The first heat exchanger 31 has a first heat exchange unit 31A and a second heat exchange unit 31B. The second heat exchange unit 31B is provided above the first heat exchange unit 31A. The first heat exchange unit 31A and the second heat exchange unit 31B have a plurality of flow paths through which the refrigerant flows in parallel. The first heat exchanger 31 has a first inflow / outflow header 310 attached to one end and a first connecting pipe 312 attached to the other end. The first inflow / outflow header 310 is formed of a circular tube having a flow path having a circular cross section. The first inflow / out header 310 has a first inflow portion 310A and a first outflow portion 310B. The first inflow portion 310A and the first outflow portion 310B are partitioned by a first partition portion 310C. A first inflow pipe 311 is attached to the first inflow portion 310A, and a first outflow pipe 313 is attached to the first outflow portion 310B. The first connecting pipe 312 is formed of a circular pipe having a flow path having a circular cross section. The first connecting pipe 312 has a pipe diameter larger than 10 mm in diameter. The refrigerant flowing in from the first inflow pipe 311 is distributed by the first inflow portion 310A and flows in parallel through the first heat exchange portion 31A. The refrigerant flowing out from the first heat exchange section 31A joins and is distributed at the first connecting pipe 312, and flows in parallel through the second heat exchange section 31B. The refrigerant flowing out from the second heat exchange section 31B merges at the first outflow section 310B and flows out from the first outflow pipe 313.

In the example of this embodiment, as shown in FIGS. 1 and 2, since the electric component box 210 is provided closer to the second heat exchange section 31B than the first heat exchange section 31A, the electric component box 210 is provided. The box 210 can efficiently dissipate heat. This is because the temperature of the second heat exchange unit 31B is lower than that of the first heat exchange unit 31A. Further, in the example of this embodiment, the electric component box 210 is more closely connected to the refrigerant outflow portion of the second heat exchange portion 31B than the first connection pipe 312 which is the refrigerant inflow portion of the second heat exchange portion 31B. Since it is provided close to the first outflow portion 310B, the electric component box 210 can efficiently dissipate heat. This is because the temperature of the refrigerant outflow section of the second heat exchange section 31B is lower than that of the refrigerant inflow section of the second heat exchange section 31B.

As shown in FIGS. 2 and 3, the second heat exchanger 32 has a third heat exchange unit 32A and a fourth heat exchange unit 32B. The third heat exchange unit 32A is provided above the fourth heat exchange unit 32B. The third heat exchange unit 32A and the fourth heat exchange unit 32B have a plurality of flow paths through which the refrigerant flows in parallel. A second inflow / outflow header 320 is attached to one end of the second heat exchanger 32, and a third connecting pipe 322 is attached to the other end. The second inflow / outflow header 320 is formed of a circular tube having a flow path having a circular cross section. The second inflow / outflow header 320 has a second inflow portion 320A and a second outflow portion 320B. The second inlet 320A and the second outlet portion 320B, are partitioned by the second partition portion 3 20 C. A second inflow pipe 321 is attached to the second inflow portion 320A, and a second outflow pipe 323 is attached to the second outflow portion 320B. The third connecting pipe 322 is formed of a circular pipe having a flow path having a circular cross section. The refrigerant flowing in from the second inflow pipe 321 is distributed by the second inflow portion 320A and flows in parallel through the third heat exchange portion 32A. The refrigerant flowing out from the third heat exchange section 32A joins and is distributed at the third connecting pipe 322, and flows in parallel through the fourth heat exchange section 32B. The refrigerant flowing out from the fourth heat exchange section 32B merges at the second outflow section 320B and flows out from the second outflow pipe 323.

[Refrigerant flow in the condenser]
Next, the flow of the refrigerant in the condenser 3A will be described. The high-temperature and high-pressure gas refrigerant compressed by the compressor 52 shown in FIG. 4 passes through the first inflow pipe 311 and the first inflow section 310A shown in FIG. 3 to the first heat exchange section 31A. Inflow. The refrigerant that has exchanged heat with air while flowing in the direction intersecting the vertical direction of the first heat exchange unit 31A exchanges heat with the air through the first connecting pipe 312, and exchanges heat with the second upper part of the first heat exchange unit 31A. It flows into the part 31B. The refrigerant that has exchanged heat with air in the first heat exchange unit 31A is a gas refrigerant or a gas-liquid two-phase refrigerant having a high ratio of the gas refrigerant. In this embodiment, since the gas-liquid two-phase refrigerant having a high ratio of the gas refrigerant or the gas refrigerant flows while rising up the first connecting pipe 312, the gas-liquid having a high ratio of the liquid refrigerant or the liquid refrigerant flows. Compared with the case where the two-phase refrigerant flows while rising through the first connecting pipe 312, the influence of the pressure loss is reduced, and the distribution of the refrigerant to the second heat exchange section 31B is made uniform. This is because the gas refrigerant has a lower density than the liquid refrigerant. Further, in this embodiment, since the first connecting pipe 312 is formed of, for example, a circular pipe having a pipe diameter larger than 10 mm in diameter, the influence of pressure loss is reduced. For example, by forming the area of the first heat exchange section 31A smaller than the area of the second heat exchange section 31B, the ratio of the liquid refrigerant flowing through the first connecting pipe 312 can be reduced. Therefore, the influence of the pressure loss can be further reduced, and the distribution of the refrigerant to the second heat exchange unit 31B can be further made uniform.

The refrigerant that has exchanged heat with air while flowing through the second heat exchange section 31B in the direction intersecting the vertical direction is the first outflow section 310B, the first outflow pipe 313, the second connection pipe 34, and the second inflow. It flows into the third heat exchange section 32A below the first heat exchange section 31A and the second heat exchange section 31B through the pipe 321 and the second inflow section 320A. The refrigerant that has exchanged heat with air in the second heat exchange unit 31B is a gas-liquid two-phase refrigerant having a high ratio of liquid refrigerant. In this embodiment, since the first heat exchange unit 31A is provided between the second heat exchange unit 31B and the third heat exchange unit 32A, the second heat exchange unit 31B and the third heat exchange unit 31B are provided. The height difference from the heat exchange unit 32A can be increased. By increasing the height difference between the second heat exchange unit 31B and the third heat exchange unit 32A, the flow velocity of the refrigerant flowing into the second inflow unit 320A can be increased, so that the third heat exchange unit The distribution of the refrigerant flowing into 32A can be made uniform. By homogenizing the gas-liquid two-phase refrigerant flowing into the third heat exchange unit 32A, the heat exchange efficiency in the third heat exchange unit 32A is improved.

The refrigerant that has exchanged heat with air while flowing in the direction intersecting the vertical direction of the third heat exchange unit 32A flows into the fourth heat exchange unit 32B via the third connecting pipe 322. The refrigerant that has exchanged heat with air in the third heat exchange unit 32A becomes a gas-liquid two-phase refrigerant in which the ratio of the liquid refrigerant is further increased. By configuring the gas-liquid two-phase refrigerant having a high ratio of the liquid refrigerant to flow downward, the influence of the pressure loss can be reduced, so that the refrigerant can flow efficiently. The refrigerant that has exchanged heat with air while flowing in the direction intersecting the vertical direction through the fourth heat exchange section 32B flows out from the second outflow pipe 323 via the second outflow section 320B.

[Refrigeration cycle equipment]
As shown in FIG. 4, the refrigerating cycle device 101 of the example of this embodiment has a refrigerant circulation circuit 102 in which the refrigerant circulates, and an injection flow path 103 that returns the condensed refrigerant to the compressor 52. .. The refrigerant applied to the refrigeration cycle apparatus 101 of this embodiment is, for example, a refrigerant having a low global warming potential (GWP) such as _{R410A, R32 or CO 2, but contains at least one of them.} It may be a mixed refrigerant or another kind of refrigerant different from these. Further, the refrigeration cycle apparatus 101 of the example of this embodiment can also use a non-azeotropic mixed refrigerant. The non-azeotropic mixed refrigerant is, for example, R407C or R448A. The non-co-boiling mixed refrigerant is a mixed refrigerant of R32, R125, R134a, R1234yf, and CO ₂ , and the condition that the ratio XR32 (wt%) of R32 is 33 <XR32 <39 and the ratio XR125 of R125. The condition that (wt%) is 27 <XR125 <33, the condition that the ratio of R134a XR134a (wt%) is 11 <XR134a <17, and the condition that the ratio of R1234yf XR1234yf (wt%) is 11 <XR1234yf <17. there condition and a condition rate _XCO 2 of CO ₂ (wt%) is 3 _<XCO 2 <9, refrigerant that satisfies all the conditions sum of XR32 and XR125 and XR134a and XR1234yf and XCO ₂ is 100, the You may.

In the refrigerant circulation circuit 102, the compressor 52, the condenser 3A, the liquid reservoir 54, the supercooler 56, the expansion valve 402, and the evaporator 404 are connected by piping. The compressor 52 compresses the sucked refrigerant to bring the refrigerant into a high temperature and high pressure state and discharges the refrigerant. The compressor 52 is, for example, an inverter compressor controlled by an inverter, and the operating frequency can be arbitrarily changed to change the capacity (the amount of refrigerant delivered per unit time). The compressor 52 may be a constant speed compressor that operates at a constant operating frequency. In the example of this embodiment, an example having one compressor 52 will be described, but the compressor 52 may have a plurality of compressors connected in parallel or in series. The condenser 3A heat-exchanges the refrigerant with air to condense the refrigerant. The liquid reservoir 54 is a container for storing the refrigerant.

The supercooler 56 supercools the refrigerant flowing in the refrigerant circulation circuit 102 by exchanging heat between the refrigerant flowing in the refrigerant circulation circuit 102 and the refrigerant flowing in the injection flow path 103. The supercooler 56 is formed of, for example, a plate-type heat exchanger, a double-tube heat exchanger, or the like, and exchanges heat between the refrigerant flowing in the refrigerant circulation circuit 102 and the refrigerant flowing in the injection flow path 103. All you need is. Although the supercooler 56 may be omitted, the degree of supercooling can be increased by the configuration having the supercooler 56, so that the refrigerating capacity of the refrigeration cycle device 101 can be increased. ..

The expansion valve 402 expands the refrigerant. The expansion valve 402 is formed of, for example, an electronic expansion valve whose opening degree can be adjusted, a temperature type expansion valve, or the like, but may be formed of a capillary tube or the like whose opening degree cannot be adjusted. The expansion valve 402 may be formed by a combination of a plurality of flow paths in which capillary tubes having different lengths are connected in parallel and an on-off valve provided in at least one of the plurality of flow paths. it can. The evaporator 404 evaporates the refrigerant. The evaporator 404 is a fin tube type heat exchanger formed including, for example, a pipe through which a refrigerant flows and fins attached to the pipe.

The injection flow path 103 returns a part of the refrigerant condensed by the condenser 3A to the compressor 52. The injection flow path 103 is formed of a pipe connecting the supercooler 56 and the expansion valve 402 and a compression chamber (not shown) having an intermediate pressure of the compressor 52. The injection flow path 103 may be a pipe connecting the supercooler 56 and the expansion valve 402 and the low pressure side of the compressor 52. The injection flow path 103 is provided with an injection expansion valve 58. The injection expansion valve 58 expands the refrigerant that has flowed into the injection flow path 103. The injection expansion valve 58 is formed of, for example, an electronic expansion valve whose opening degree can be adjusted, a temperature type expansion valve, or the like, but may be formed of a capillary tube or the like whose opening degree cannot be adjusted. Further, the injection expansion valve 58 is formed by a combination of a plurality of flow paths in which capillary tubes having different lengths are connected in parallel and an on-off valve provided in at least one of the plurality of flow paths. You can also.

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

[Cooling structure of electrical equipment box]
As shown in FIG. 5, the heat dissipation promoting portion 212 exposed to the heat exchange chamber 10 is provided downstream of the heat exchanger 3 in the air flow. Specifically, the heat dissipation promoting portion 212 is provided at a position higher than the first partition portion 310C shown in FIG. 3, and is provided at a position where the air that has passed through the second heat exchange portion 31B passes. ing. The cooling structure of the electrical component box 210 can be simplified by configuring the air that has passed through the heat exchanger 3 to pass through the heat dissipation promoting unit 212. By simplifying the cooling structure of the electrical component box 210, the heat exchanger unit 100 can be miniaturized. Further, since the air passing through the heat dissipation promoting section 212 becomes the air passing through the second heat exchange section 31B, the air having a lower temperature passes than the air passing through the first heat exchange section 31A. It will be. Further, since the air passing through the heat dissipation promoting section 212 becomes the air passing near the first outflow section 310B close to the refrigerant outflow section of the second heat exchange section 31B, the refrigerant of the second heat exchange section 31B Compared to the air that has passed near the first connecting pipe 312 near the inflow portion, the air having a lower temperature will pass through. Since the temperature of the air passing through the heat dissipation promoting section 212 is low, the heat dissipation of the heat dissipation promoting section 212 can be efficiently performed. In a refrigerating apparatus or the like in which the heat exchanger 3 functions as the condenser 3A, the temperature of the refrigerant flowing into the heat exchanger 3 may be 100 degrees or higher. In such a case, by configuring the heat exchanger 3 so that the temperature of the refrigerant passing through the first outflow portion 310B is less than 60 degrees, the heat exchange efficiency of the heat exchanger 3 becomes good, and the heat exchange efficiency is improved. The heat dissipation promotion unit 212 can efficiently dissipate heat.

[Control device operation]
FIG. 6 is a diagram showing an example of the configuration of the control device shown in FIG. 1, and FIG. 7 is a diagram showing an example of the operation of the control device shown in FIG. As shown in FIG. 6, the control device 220 controls the first blower 14, the second blower 18, the compressor 52, the injection expansion valve 58, the expansion valve 402, the fan 406, and the like. When the indoor unit 400 shown in FIG. 4 is provided with a control device (not shown), the control device 220 is the first blower 14, the second blower 18, and the compressor 52 of the heat exchanger unit 100. , Or the injection expansion valve 58 may be controlled, and the control device (not shown) of the indoor unit 400 may control the expansion valve 402 or the fan 406 of the indoor unit 400. For example, the control device 220 controls the first blower 14, the second blower 18, or the compressor 52 by using the temperature of the electric product 213 detected by the temperature sensor 213a. As shown in FIG. 7, in step S02, the refrigeration cycle apparatus 101 shown in FIG. 4 is performing a normal operation.

In step S04 of FIG. 7, it is determined whether the temperature of the electric product 213 detected by the temperature sensor 213a is equal to or higher than the first threshold value. When the temperature of the electric product 213 detected by the temperature sensor 213a is lower than the first threshold value, the process returns to step S02. When the temperature of the electric product 213 detected by the temperature sensor 213a in step S04 becomes equal to or higher than the first threshold value, the air volume of the first blower 14 shown in FIG. 5 is increased in step S06 to increase the air volume of the second blower 14. The air volume of the blower 18 is maintained. By increasing the air volume of the first blower 14, the air volume passing through the heat dissipation promoting unit 212 is increased, so that the heat dissipation of the electric product 213 is promoted. In this embodiment, when the temperature of the electric product 213 becomes high, the air volume of only the first blower 14 of the first blower 14 and the second blower 18 needs to be increased, so that the power consumption is low. It is possible to realize power consumption. Further, when the temperature of the electric product 213 becomes equal to or higher than the first threshold value, the rotation speed of the compressor 52 is not reduced or the compressor 52 is not stopped, so that the temperature rise of the cooling space is suppressed.

In step S08 of FIG. 7, it is determined whether or not the temperature of the electric product 213 detected by the temperature sensor 213a is equal to or higher than the second threshold value. The second threshold is a value corresponding to a temperature higher than the first threshold. When the temperature of the electric product 213 detected by the temperature sensor 213a is lower than the second threshold value, the process returns to step S04. When the temperature of the electric product 213 detected by the temperature sensor 213a in step S08 becomes equal to or higher than the second threshold value, the rotation speed of the compressor 52 is reduced in step S10. By reducing the rotation speed of the compressor 52, the heat generation of the electric product 213 is suppressed. In this embodiment, when the temperature of the electric product 213 becomes equal to or higher than the second threshold value, the compressor 52 is not stopped and the rotation speed of the compressor 52 is lowered to suppress the temperature rise in the cooling space. doing.

In step S12, it is determined whether the temperature of the electric product 213 detected by the temperature sensor 213a is equal to or higher than the third threshold value. The third threshold value is a value corresponding to a temperature higher than the second threshold value. When the temperature of the electric product 213 detected by the temperature sensor 213a is lower than the third threshold value, the process returns to step S08. When the temperature of the electric product 213 detected by the temperature sensor 213a in step S12 becomes equal to or higher than the third threshold value, the compressor 52 is stopped in step S14. By stopping the compressor 52, the heat generation of the electric product 213 is suppressed. In this embodiment, when the temperature of the electric product 213 becomes equal to or higher than the third threshold value, the compressor 52 is stopped, so that the deterioration or damage of the electric product 213 is suppressed. Further, by stopping the compressor 52 when the temperature of the electric product 213 becomes equal to or higher than the third threshold value, it is possible to suppress a failure of the refrigeration cycle device 101 due to an abnormality of the first blower 14.

As described above, in the example of this embodiment, since the electric product box 210 is configured to promote cooling, it is suppressed that the electric product 213 has a high temperature equal to or higher than the first threshold value. Therefore, it is difficult to execute the protection control for eliminating the high temperature state of the electric product 213. Further, in the example of this embodiment, when the temperature of the electric product 213 becomes equal to or higher than the first threshold value, the rotation speed of the compressor 52 is not lowered or the compressor 52 is not stopped. The temperature rise is suppressed. Further, in the example of this embodiment, when the temperature of the electric product 213 becomes equal to or higher than the second threshold value, the compressor 52 is not stopped and the rotation speed of the compressor 52 is lowered to create a cooling space. The temperature rise is suppressed. Therefore, according to this embodiment, deterioration of the object to be cooled housed in the cooling space can be suppressed.

As described above, the heat exchanger unit 100 of the example of this embodiment heat exchanges the heat exchanged refrigerant between the first heat exchange unit 31A that exchanges heat with the refrigerant and the first heat exchange unit 31A. A heat exchanger 3 having a second heat exchange section 31B, a blower 14 for forming an air flow for passing air through the heat exchanger 3, and an electrical component box 210 containing electrical components 213 are provided. The electrical component box 210 is provided closer to the second heat exchange section 31B than to the first heat exchange section 31A. Further, the refrigeration cycle device 101 of the example of this embodiment accommodates a refrigerant circulation circuit 102 in which a compressor 52, a condenser 3A, an expansion valve 402, and an evaporator 404 are connected to circulate the refrigerant, and an electric product 213. The condenser 3A includes a first heat exchange unit 31A that exchanges heat with the refrigerant, and a second heat exchange heat exchange between the first heat exchange unit 31A and the second heat exchanged refrigerant. It has a heat exchanger 3 having an exchange unit 31B, and the electrical component box 210 is provided closer to the second heat exchange unit 31B than the first heat exchange unit 31A. In the example of this embodiment, since the electric component box 210 is provided close to the second heat exchange section 31B whose temperature is lower than that of the first heat exchange section 31A, the electric component box 210 efficiently dissipates heat. It can be performed.

For example, the second heat exchange unit 31B includes a plurality of flow paths through which the refrigerant flows in parallel, and uses the air around the second heat exchange unit 31B whose temperature is lower than that of the first heat exchange unit 31A. As a result, the electrical component box 210 can efficiently dissipate heat.

Further, for example, since the electric component box 210 is provided closer to the refrigerant outflow portion than the refrigerant inflow portion of the second heat exchange portion 31B, the temperature is higher than that of the refrigerant inflow portion of the second heat exchange portion 31B. The electric component box 210 can efficiently dissipate heat by utilizing the air around the low refrigerant outflow portion.

Further, for example, a heat dissipation promoting unit 212 is provided at a position where air passing through the second heat exchange unit 31B passes and promotes heat dissipation of the electric product 213. The cooling structure of the electrical component box 210 can be simplified by allowing the air that has passed through the second heat exchange section 31B to pass through the heat dissipation promoting section 212. By simplifying the cooling structure of the electrical component box 210, the heat exchanger unit 100 can be miniaturized.

Further, for example, the housing 110 has a heat exchange chamber 10 in which the heat exchanger 3 is housed and a machine room 20 in which the electrical component box 210 is housed. Is exposed to. By providing the heat exchanger 3 in the heat exchange chamber 10, the heat exchange of the heat exchanger 3 is made more efficient, and further, since the heat dissipation promoting unit 212 is exposed in the heat exchange chamber 10, the heat dissipation promoting unit 212 It is possible to efficiently dissipate heat in.

Further, for example, the second heat exchange unit 31B is provided above the first heat exchange unit 31A, and the electrical component box 210 is provided at a position higher than the first heat exchange unit 31A. .. By providing the electrical component box 210 at a high position, convenience such as maintenance is improved.

Further, for example, when the heat exchanger 3 functions as the condenser 3A and the second heat exchange unit 31B is provided above the first heat exchange unit 31A, the first heat exchange unit 31A and the second heat exchange unit 31A are provided. By forming the first connecting pipe 312 connecting the second heat exchange portion 31B with a circular pipe, the influence of pressure loss can be reduced. The first connecting pipe 312 may be formed of, for example, one having a pipe diameter larger than 10 mm in diameter.

Further, for example, when the heat exchanger 3 functions as the condenser 3A and the second heat exchange unit 31B is provided above the first heat exchange unit 31A, the third heat exchange unit 32A By being provided below the first heat exchange unit 31A, the height difference between the second heat exchange unit 31B and the third heat exchange unit 32A can be increased. The third heat exchange section 32A has a plurality of flow paths through which the refrigerant flows in parallel, and by increasing the height difference between the second heat exchange section 31B and the third heat exchange section 32A, the third heat exchange section 32A has a third flow path. The flow velocity of the refrigerant flowing through the connecting pipe 34 of 2 can be increased to make the distribution of the refrigerant flowing into the third heat exchange unit 32A uniform. Further, by having a configuration having a first heat exchange unit 31A, a second heat exchange unit 31B, and a third heat exchange unit 32A, the refrigerant that has passed through the first heat exchange unit 31A can be used as a gas refrigerant or It can be a gas-liquid two-phase refrigerant having a high ratio of gas refrigerant. The refrigerant flowing through the first connecting pipe 312 connecting the first heat exchange unit 31A and the second heat exchange unit 31B becomes a gas refrigerant or a gas-liquid two-phase refrigerant having a high ratio of the gas refrigerant, so that the pressure is increased. The effect of loss can be reduced.

Further, for example, the blower 14 has a first blower 14 that blows air to the second heat exchange unit 31B and a second blower 18 that blows air to the third heat exchange unit 32A. There is. By having the first blower 14 and the second blower 18, for example, the amount of heat exchanged by the second heat exchange unit 31B and the amount of heat exchanged by the third heat exchange unit 32A can be adjusted. Therefore, the heat exchange of the refrigerant can be performed efficiently.

Further, for example, when the temperature detected by the temperature sensor 213a becomes equal to or higher than the first threshold value, the air volume of the second blower 18 is maintained and the air volume of the first blower 14 is increased, so that the heat dissipation promotion unit 212 Promotes heat dissipation. When the temperature of the electric product 213 becomes high, the air volume of only the first blower 14 of the first blower 14 and the second blower 18 needs to be increased, so that low power consumption can be realized. Can be done. Further, when the temperature detected by the temperature sensor 213a becomes equal to or higher than the second threshold value corresponding to the temperature higher than the first threshold value, the rotation speed of the compressor 52 is lowered, and the temperature detected by the temperature sensor 213a becomes the second threshold value. When the temperature becomes equal to or higher than the third threshold value corresponding to the temperature higher than the threshold value, the compressor 52 is stopped. In the example of this embodiment, even when the temperature of the electric product 213 rises, the rotation speed of the compressor 52 is not immediately lowered or the compressor is not stopped, so that the temperature rise of the cooling space is suppressed. be able to.

Further, for example, since the refrigerant pipe of the heat exchanger 3 has a flat shape, the air passage resistance can be reduced, the heat exchange efficiency can be improved, and the heat exchanger 3 can be miniaturized.

Further, for example, by providing the liquid reservoir 54 at a position where the temperature of the lower part inside the heat exchange chamber 10 is low, evaporation of the liquid refrigerant can be suppressed.

In this embodiment, the above effect becomes remarkable when the heat exchanger 3 functions as the condenser 3A. This is because, in a refrigerating apparatus or the like in which the heat exchanger 3 functions as the condenser 3A, the temperature of the refrigerant flowing into the heat exchanger 3 may be 100 degrees or higher. The cooling structure of the electrical component box 210 can be simplified by providing the electrical component box 210 at a position where the influence of high-temperature air that has exchanged heat with the refrigerant of 100 ° C. or higher is small.

Further, in this embodiment, the above effect becomes remarkable when the refrigerant is a non-azeotropic mixed refrigerant. Since the non-co-boiling mixed refrigerant has a temperature gradient, the temperature difference between the temperature of the refrigerant passing through the first heat exchange section 31A and the temperature of the refrigerant passing through the second heat exchange section 31B becomes large. Is.

As described above, according to this embodiment, since the heat radiation in the heat radiation promoting unit 212 is efficient, the heat radiation promoting unit 212 can be miniaturized. By downsizing the heat dissipation promotion unit 212, the cost of the heat dissipation promotion unit 212 can be reduced, the pressure loss in the air passage can be reduced, and the refrigeration cycle device 101 can be downsized.

It should be noted that this embodiment is not limited to that described above.

[Modification 1]
For example, FIG. 8 is a diagram showing a modification 1 of FIG. 5, and FIG. 9 is a side view of the heat exchanger, the air passage forming portion, and the heat dissipation promoting portion of FIG. In FIG. 8, the same configurations as those in FIG. 5 are designated by the same reference numerals, and the description thereof will be omitted or simplified. As shown in FIGS. 8 and 9, the modified example 1 has an air passage forming portion 214. The air passage forming unit 214 forms an air passage that allows the air that has passed through the heat exchanger 3 to pass through the heat dissipation promoting unit 212. The air passage forming portion 214 is provided on the leeward side of the first heat exchange portion 31A, and is attached to, for example, a partition plate 25 or an electric component box 210. The air passage forming portion 214 has a shape in which the flow velocity of the air passing through the heat dissipation promoting portion 212 is faster than the flow velocity of the air passing through the heat exchanger 3. For example, the air passage forming portion 214 has a trumpet shape in which the opening area of the air intake portion upstream of the air flow is formed larger than that on the downstream side. By forming a large air intake portion of the air passage forming portion 214, a large amount of air can be taken in and a large amount of air can be passed through the heat dissipation promoting portion 212. The heat dissipation promoting portion 212 is provided at a position higher than the first partition portion 310C in FIG. The air intake portion of the air passage forming portion 214 is formed within the range of the second heat exchange portion 31B, and can take in the air that has passed through the second heat exchange portion 31B. By passing the air that has passed through the second heat exchange section 31B through the heat dissipation promoting section 212, the heat dissipation in the heat dissipation promoting section 212 can be efficiently performed. For example, the opening of the air intake portion of the air passage forming portion 214 may be formed to be at least twice as large as the cross-sectional area of the heat dissipation promoting portion 212. In the first modification, since the air passage forming section 214 is provided, the amount of air passing through the heat dissipation promoting section 212 can be increased, and the speed of the air passing through the heat dissipation promoting section 212 can be increased, so that the heat dissipation is promoted. It is possible to promote heat dissipation in the unit 212. Further, in the first modification, since the air passage forming portion 214 is provided, the heat dissipation promoting portion 212 can be miniaturized.

[Modification 2]
Further, for example, FIG. 10 is a diagram showing a modified example 2 of FIG. 8, and FIG. 11 is a view of the heat exchanger, the air passage forming portion, and the heat dissipation promoting portion of FIG. 10 as viewed from the side. In FIG. 10, the same configurations as those in FIG. 8 are 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 modification, the air passage forming portion 214 has a ventilation portion 214A that covers at least a part of the heat dissipation promoting portion 212. The ventilation portion 214A is provided so as not to come into contact with the heat dissipation promoting portion 212, so that heat can be dissipated from the outer surface of the heat dissipation promoting portion 212. A gap of, for example, 1 to 3 mm is provided between the ventilation portion 214A and the heat dissipation promoting portion 212. By providing the ventilation portion 214A, it is possible to ensure the ventilation to the heat dissipation promoting portion 212. Further, by providing the ventilation unit 214A, it is possible to prevent the high temperature air that has passed through the first heat exchange unit 31A from passing through the heat dissipation promotion unit 212, so that the heat radiation in the heat dissipation promotion unit 212 is efficient. Be transformed. The ventilation portion 214A may have a shape that covers at least a part of the heat dissipation promoting portion 212, but by forming the shape that covers the entire heat radiation promoting portion 212, it is possible to further ensure the ventilation to the heat dissipation promoting portion 212. .. The ventilation portion 214A may be formed so that the speed of the air passing through the heat dissipation promoting portion 212 is 3 m / sec or more. By forming the ventilation section 214A so that the speed of the air passing through the heat dissipation promoting section 212 is 3 m / sec or more, the heat dissipation in the heat dissipation promoting section 212 is made efficient. When the velocity of the air passing through the heat dissipation promoting portion 212 is less than 3 m / sec by forming the ventilation portion 214A, the ventilation portion 214A may be omitted as in the first modification. This is because when the speed of the air passing through the heat radiation promoting unit 212 is less than 3 m / sec, the high temperature air heat exchanged by the heat radiation promoting unit 212 may stay in the ventilation unit 214A. Further, when the speed of the air passing through the heat dissipation promoting section 212 is less than 3 m / sec, the ventilation section 214A is heated by the high temperature air passing through the first heat exchange section 31A, and the heat dissipation promoting section 212 This is because heat dissipation may be hindered.

Embodiment 2.
FIG. 12 is a diagram showing an example of a refrigeration cycle device according to the second embodiment of the present invention. In FIG. 12, the same configurations as those in FIG. 4 are designated by the same reference numerals, and the description thereof will be omitted or simplified. Further, in the second embodiment, the description of the same configuration as that of the first embodiment will be omitted or simplified. As shown in FIG. 12, in the heat exchanger unit 100A of the refrigeration cycle device 101A of the example of this embodiment, a liquid reservoir 54A is provided between the first heat exchanger 31 and the second heat exchanger 32. It is provided. The gas-liquid two-phase refrigerant flowing out of the first heat exchanger 31 is separated into a gas refrigerant and a liquid refrigerant in the liquid reservoir 54A, and the liquid refrigerant flows out from the liquid reservoir 54A. The liquid refrigerant flowing out of the liquid reservoir 54A is heat-exchanged by the second heat exchanger 32. In the example of this embodiment, since the liquid refrigerant flowing out of the liquid reservoir 54A is heat-exchanged by the second heat exchanger 32, the degree of supercooling of the refrigerant flowing out from the heat exchanger 3 can be increased. Therefore, according to the example of this embodiment, the refrigerating capacity of the refrigerating cycle apparatus 101A can be increased.

The electrical component box 210 is provided closer to the second heat exchanger 32 than to the first heat exchanger 31. In the second embodiment, the first heat exchanger 31 corresponds to the "first heat exchange unit" of the present invention, and the second heat exchanger 32 is the "second heat exchange" of the present invention. Corresponds to "part". Since the liquid refrigerant from which the gas refrigerant is separated in the liquid reservoir 54A flows through the second heat exchanger 32, the electric component box 210 can be provided by providing the electric component box 210 close to the second heat exchanger 32. Efficient heat dissipation can be performed. This is because the temperature of the liquid refrigerant in which the gas refrigerant is separated and heat exchanged with air is lower than that of the gas-liquid two-phase refrigerant. The heat dissipation promotion unit 212 is provided at a position where the air that has passed through the second heat exchanger 32 passes, so that the heat dissipation promotion unit 212 can efficiently dissipate heat.

The present invention is not limited to the above-described embodiment, and can be variously modified within the scope of the present invention. That is, the configuration of the above embodiment may be appropriately improved, or at least a part thereof may be replaced with another configuration. Further, the configuration requirements without particular limitation on the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at a position where the function can be achieved.

For example, the first embodiment and the second embodiment may be combined to provide a liquid reservoir between the first heat exchange section 31A and the second heat exchange section 31B of the first embodiment shown in FIG. it can. Further, a liquid reservoir is provided between the first heat exchanger 31 and the second heat exchanger 32 of the first embodiment shown in FIG. 3, and the electric component box 210 is more than the first heat exchanger 31. It can be provided close to the heat exchanger 32 of 2.

Further, for example, in the first embodiment and the second embodiment, the refrigerating cycle device applied to a large refrigerating device for cooling the inside of a freezing warehouse or the like has been described, but the refrigerating cycle device is a refrigerator or the like. It can be applied to small refrigeration equipment. Further, the refrigeration cycle device can also be applied to an air conditioner for cooling or heating the inside of a room, and a heating device for heating water or the like.

Further, for example, in the first embodiment, the example in which the heat exchanger 3 functions as a condenser has been described, but the heat exchanger 3 may function as an evaporator.

Further, for example, in the first embodiment, the heat exchanger 3 having the first heat exchanger 31 and the second heat exchanger 32 provided below the first heat exchanger 31 will be described. However, the first embodiment is not limited to such a thing. For example, the heat exchanger 3 may omit the second heat exchanger 32 and have only the first heat exchanger 31 or the first heat exchanger 31 and the second heat exchange. It may be configured to have three or more heat exchangers having a vessel 32 and an additional heat exchanger.

Further, for example, in the first embodiment, the first heat exchanger 31 having the first heat exchange unit 31A and the second heat exchange unit 31B, the third heat exchange unit 32A, and the fourth heat exchange unit Although the heat exchanger 3 having the parts 32B has been described, the first heat exchange part 31A, the second heat exchange part 31B, the third heat exchange part 32A, and the fourth heat exchange part 32B have been described. May be formed separately from each other.

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 room, 25 partition plate, 31st 1 heat exchanger, 31A first heat exchange unit, 31B second heat exchange unit, 32 second heat exchanger, 32A third heat exchange unit, 32B fourth heat exchange unit, 34 second heat exchanger Connection 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 housing, 210 electrical parts box, 212 heat dissipation promotion part, 213 electric parts, 213a temperature sensor, 214 air passage forming part, 214A ventilation part, 220 control device, 310 first inflow / outflow header , 310A 1st inflow section, 310B 1st outflow section, 310C 1st partition section, 311 1st inflow pipe, 312 1st connection pipe , 3 13 1st outflow pipe, 320 2nd inflow / outflow Header, 320A 2nd inflow section, 320B 2nd outflow section, 320C 2nd partition section, 321 2nd inflow pipe, 322 3rd connection pipe, 323 2nd outflow pipe, 400 indoor unit, 402 expansion Valves, 404 evaporators, 406 fans, 410 pipes, 420 pipes.

Claims (20)

A heat exchanger having a first heat exchange unit for heat exchange of the refrigerant and a second heat exchange unit for heat exchange of the refrigerant heat exchanged in the first heat exchange unit.
A blower that forms an air flow that allows air to pass through the heat exchanger,
And the electrical component box that houses the electric equipment,
A liquid reservoir provided between the first heat exchange section and the second heat exchange section is provided.
The heat exchanger is
An inflow section that allows the refrigerant compressed by the compressor to flow into the first heat exchange section having a plurality of parallel flow paths, and an inflow section.
A connecting pipe that allows the refrigerant that has flowed into the first heat exchange section from the inflow section to flow out to the second heat exchange section having a plurality of parallel flow paths.
It is provided with an outflow portion that allows the refrigerant heat exchanged in the second heat exchange portion to flow out.
The electrical component box is provided closer to the second heat exchange section than the first heat exchange section, and is a refrigerant outflow section of the second heat exchange section rather than the connection pipe. It was set up close to the part,
Heat exchanger unit. It is provided at a position where air that has passed through the second heat exchange section passes, and is provided with a heat dissipation promoting section that promotes heat dissipation of the electrical product.
The heat exchanger unit according to claim 1. A housing having a heat exchange chamber in which the heat exchanger is housed and a machine room in which the electrical component box is housed is provided.
The heat dissipation promoting portion is exposed in the heat exchange chamber.
The heat exchanger unit according to claim 2. A wind passage forming portion for forming an air passage for passing air that has passed through the heat exchanger to the heat dissipation promoting portion is provided.
The air passage forming portion has a shape in which the flow velocity of air passing through the heat dissipation promoting portion is faster than the flow velocity of air passing through the heat exchanger.
The heat exchanger unit according to claim 2 or 3. The air passage forming portion has a take-in portion that takes in air within a range through which the air that has passed through the second heat exchange portion passes.
The heat exchanger unit according to claim 4. The air passage forming portion has a ventilation portion that covers at least a part of the heat dissipation promoting portion.
The heat exchanger unit according to claim 4 or 5. The second heat exchange section is provided above the first heat exchange section.
The heat exchanger unit according to any one of claims 1 to 6. The electrical component box is provided at a position higher than the first heat exchange section.
The heat exchanger unit according to claim 7. The heat exchanger is a pipe that allows the refrigerant flowing out of the first heat exchange section to flow into the second heat exchange section, and is a first connecting pipe formed of a circular pipe having a circular flow path. Have, have
The heat exchanger unit according to claim 7 or 8. The first connecting pipe has a pipe diameter larger than 10 mm in diameter.
The heat exchanger unit according to claim 9. The heat exchanger has a third heat exchange unit that is provided below the first heat exchange unit and exchanges heat with the refrigerant that has been heat exchanged by the second heat exchange unit.
The heat exchanger unit according to any one of claims 1 to 10. The third heat exchange unit has a plurality of flow paths through which the refrigerant flows in parallel.
The heat exchanger unit according to claim 11. The blower includes a first blower that blows air to the second heat exchange unit and a second blower that blows air to the third heat exchange unit.
The heat exchanger unit according to claim 11 or 12. It is equipped with a temperature sensor that detects the temperature of the electrical product.
When the temperature detected by the temperature sensor becomes equal to or higher than the first threshold value, the air volume of the second blower is maintained and the air volume of the first blower is increased.
The heat exchanger unit according to claim 13. Equipped with the compressor that compresses the refrigerant
When the temperature detected by the temperature sensor becomes equal to or higher than the second threshold value corresponding to the temperature higher than the first threshold value, the rotation speed of the compressor is lowered.
When the temperature detected by the temperature sensor becomes equal to or higher than the third threshold value corresponding to the temperature higher than the second threshold value, the compressor is stopped.
The heat exchanger unit according to claim 14. The heat exchanger has a refrigerant pipe formed in a flat shape.
The heat exchanger unit according to any one of claims 1 to 15. The heat exchanger functions as a condenser,
The heat exchanger unit according to any one of claims 1 to 16. A liquid reservoir provided in the lower part of the inside of the heat exchange chamber and storing the refrigerant heat exchanged by the heat exchanger is provided.
The heat exchanger unit according to claim 17 , which cites claim 3. The refrigerant is a non-azeotropic mixed refrigerant,
The heat exchanger unit according to any one of claims 1 to 18. A refrigerant circulation circuit in which a compressor, a condenser, an expansion valve, and an evaporator are connected and a refrigerant circulates,
Equipped with an electrical box containing electrical products,
The condenser has a heat exchanger having a first heat exchange section for heat exchange of the refrigerant and a second heat exchange section for heat exchange of the refrigerant heat exchanged in the first heat exchange section. And
A liquid reservoir provided between the first heat exchange section and the second heat exchange section is provided.
The heat exchanger is
An inflow section that allows the refrigerant compressed by the compressor to flow into the first heat exchange section having a plurality of parallel flow paths, and an inflow section.
A connecting pipe that allows the refrigerant that has flowed into the first heat exchange section from the inflow section to flow out to the second heat exchange section having a plurality of parallel flow paths.
It is provided with an outflow portion for flowing out the refrigerant heat exchanged in the second heat exchange portion.
The electrical component box is provided closer to the second heat exchange section than the first heat exchange section, and is a refrigerant outflow section of the second heat exchange section rather than the connection pipe. It was set up close to the part,
Refrigeration cycle equipment.

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