WO2024069861A1

WO2024069861A1 - Heat exchange device and cooling device

Info

Publication number: WO2024069861A1
Application number: PCT/JP2022/036467
Authority: WO
Inventors: 真弘蜂矢; 正樹千葉; 健司山崎; 善則宮本
Original assignee: 日本電気株式会社
Priority date: 2022-09-29
Filing date: 2022-09-29
Publication date: 2024-04-04

Abstract

The purpose of the present invention is to improve the heat exchange efficiency of a heat exchange device.　A heat exchange device comprises heat exchangers (2) that exchange heat between a coolant and air which flows through a flow path (1) in the vertical direction, a supply duct (3) that supplies the coolant subject to heat exchange by the heat exchangers (2), and a discharge duct (4) that is for discharging the coolant which has been subjected to heat exchange by the heat exchangers (2), said heat exchange device being characterized in that: a plurality of the heat exchangers (2) are disposed along a direction intersecting the flow path (1) of the air; and at least one of the supply duct (3) and the discharge duct (4) is constituted by a main pipe (5) that is disposed below a region in which the plurality of heat exchangers (2) are disposed and parallel to the direction along which the heat exchangers (2) are arranged and which is indicated by the arrow (W) in the drawing, and branch pipes (6) that respectively connect the main pipe (5) and the plurality of heat exchangers (2).

Description

Heat exchange and cooling equipment

The present invention relates to a heat exchange device and a cooling device.

2. Description of the Related Art Conventionally, in data centers or the like that are equipped with a large number of servers, the server rooms in which the servers are installed are maintained at an optimum temperature for the operation of the servers by air conditioning devices.
The air conditioning unit has as its main components a heat receiver that receives heat from the air exhausted from the server, a compressor that compresses the refrigerant whose heat has been received by the heat receiver, a radiator that radiates heat from the refrigerant compressed by the compressor, and an expansion section constituted, for example, by a valve.
The heat receiver is equipped with a heat exchanger (radiator) for heat exchange between the exhaust air of the server to be cooled and a refrigerant, and the heat sink is equipped with a heat exchanger (radiator) for heat exchange between the refrigerant compressed by the compressor and the atmosphere (cooling air).

Patent document 1 related to the present invention discloses a technology in which a heat exchanger used in the above-mentioned radiator is arranged at an angle to the air flow path of the cooling air (generally vertically), thereby ensuring a large contact area (heat dissipation area) between the heat dissipation fins of the heat exchanger and the air in a cross section perpendicular to the cooling air flow path.
Patent Document 2, which is related to the present invention, discloses a technology for improving heat exchange performance by using multiple heat exchangers to ensure the heat dissipation area required for one heat exchanger and individually adjusting the flow rate of refrigerant supplied to the multiple heat exchangers.

JP 2014-163530 A JP 2022-046305 A

In recent years, due to consideration of the environmental impact, the refrigerants used in the above-mentioned refrigeration cycle have been switched from the high-pressure hydrofluorocarbons (HFCs), which have a difference between evaporation pressure and condensation pressure of the order of 1000 kPa, to low-pressure hydrofluoroolefins (HFOs), which have a difference between evaporation pressure and condensation pressure of about 100 kPa and a maximum vapor pressure of 1000 kPa or less.

In cooling systems that use low-pressure HFOs as refrigerants, the heat transfer capacity per unit volume is smaller than that of high-pressure refrigerants, so in a refrigeration cycle of the same volume, it is necessary to circulate a larger volume of refrigerant than in the case of high-pressure refrigerants. Furthermore, as the circulation volume (flow rate) of the refrigerant increases, the flow rate increases, and an increase in pressure loss due to the faster flow rate is unavoidable. Therefore, in order to obtain the necessary cooling capacity while avoiding the need to increase the size of the equipment, such as by expanding the piping diameter, the heat exchanger is required to have the performance to exchange heat more efficiently than in the case of high-pressure refrigerants.

However, in the technology disclosed in Patent Document 1, the following problems arise due to the configuration in which the heat exchanger is disposed at an angle.
(1) The distance from the fan that generates the cooling air flow to the heat exchanger varies depending on the height position (upstream and downstream of the cooling air flow path) in the same heat exchanger. In other words, since the pressure generated by the fan differs in the height direction, the wind speed varies in the height direction, and the heat transfer coefficient becomes uneven, which reduces the heat exchange performance of the heat exchanger as a whole.
(2) The radiator is structured such that a tank for receiving the refrigerant after heat exchange is stored in a housing together with the heat exchanger, and the large-sized heat exchanger arranged at an angle extends above and below the housing, occupying space. As a result, the height of the tank is arranged to be almost the same as the lower end of the heat exchanger, and the liquid level in the refrigerant pipe constituting the heat exchanger (the height of the refrigerant that has become liquid due to heat dissipation) may become the same as the liquid level in the tank connected thereto. When a liquid phase portion occurs in the refrigerant pipe of the heat exchanger in this way, below this liquid level, heat dissipation due to the phase change of the refrigerant from the gas phase to the liquid phase does not occur, and the heat exchange performance of the heat exchanger decreases.

In addition, since Patent Document 2 requires control of the heat exchange load of each heat exchanger, the cost of a control system added to the refrigeration cycle is incurred, and there is also the disadvantage of adding a control system, which creates a risk of failure. Furthermore, Patent Document 2 does not disclose any specific configuration for improving the efficiency of the heat exchangers themselves, such as the arrangement of a tank that receives and stores the refrigerant discharged after heat exchange in multiple heat exchangers, or the piping paths that introduce the refrigerant from each heat exchanger to the tank.

The purpose of this invention is to improve the heat exchange performance of a heat exchanger and a cooling device that uses the same.

In order to solve the above problems, the heat exchange device of the present invention is a heat exchange device that includes a heat exchanger that exchanges heat between air flowing in an up-down flow path and a refrigerant, a supply line that supplies the refrigerant that is heat exchanged in the heat exchanger, and a discharge line that discharges the refrigerant that has been heat exchanged in the heat exchanger, and is characterized in that the heat exchangers are arranged in a line in a direction that intersects with the air flow path, and at least one of the supply line and the discharge line is composed of a trunk pipe that is arranged parallel to the arrangement direction of the heat exchangers below the area in which the multiple heat exchangers are arranged, and branch pipes that connect the trunk pipe to each of the multiple heat exchangers.

The present invention can improve the heat exchange efficiency of heat exchange devices and cooling devices.

FIG. 2 is a front view of a heat exchanger according to a minimum configuration example of the present invention. 1 is a schematic diagram of a piping system of a cooling device including a heat exchanger device according to an embodiment of the present invention. 1 is a perspective view of a heat exchanger according to an embodiment, as viewed obliquely from below. FIG. FIG. 2 is a front view of a heat exchange device according to one embodiment. FIG. 4 is a right side view of the heat exchange device of FIG. 3 . FIG. 4 is a rear view of the heat exchange device of FIG. 3 . FIG. 4 is a schematic diagram of a piping system of the heat exchanger of FIG. 3 . 13 is a cross-sectional view of a modified example of a connection portion between a tank and a liquid branch pipe. FIG.

The configuration of a cooling device according to a minimum configuration of the present invention will be described with reference to FIG.
This heat exchange device comprises a heat exchanger 2 which exchanges heat between the air flowing in a vertical flow path 1 and a refrigerant, a supply pipeline 3 which supplies the refrigerant which is heat exchanged in the heat exchanger 2, and a discharge pipeline 4 which discharges the refrigerant which has been heat exchanged in the heat exchanger 2, and is characterized in that the heat exchangers 2 are arranged in a row in a direction intersecting the air flow path, and at least one of the supply pipeline 3 and the discharge pipeline 4 is composed of a trunk pipe 5 which is arranged below the area in which the multiple heat exchangers 2 are arranged and parallel to the arrangement direction of the heat exchangers 2 as indicated by the arrow W in the figure, and branch pipes 6 which connect the trunk pipe 5 to each of the multiple heat exchangers 2.

With the above configuration, since the main pipe 5 is disposed below each of the heat exchangers 2, a configuration mainly consisting of straight pipes is adopted as the branch pipes 6 connecting the heat exchanger 2 to the main pipe 5 at the corresponding position, and the heat exchanger 2 and the main pipe 5 can be connected with a flow path with low resistance and with a short flow path length, and the flow path resistance to the supply pipe 3 or the discharge pipe 4 can be made small and constant. As a result, the heat exchange load of each of the heat exchangers 2 can be made uniform, and the heat exchange efficiency of the entire heat exchange device can be increased.

With reference to FIG. 2, an overview of a cooling device including a heat sink according to an embodiment will be described.
This cooling device is basically composed of a heat dissipation section 20 having a heat exchanger 22 according to one embodiment, a heat receiving section 30 that receives heat from the exhaust air of a server unit to be cooled, a compressor 40 that receives the refrigerant that has received heat at the heat receiving section 30 via a pipe L1 and compresses it at a predetermined compression rate, and an expansion section 50 that is, for example, configured with a valve. The heat receiving section 30 has a heat exchanger (evaporator) 31 that receives heat from high-temperature air exhausted from a server to be cooled, which is arranged in a server room (not shown) (more specifically, exhaust air that is higher in temperature than the room temperature of the server room and is sucked into the server as cooling air). That is, the air discharged from the server to the server room is cooled by the heat of evaporation when the refrigerant flowing through the heat exchanger 31 changes from a liquid phase to a gas phase, and then discharged to the server room and taken into the server as cooling air.

The refrigerant compressed by the compressor 40 is supplied to the heat dissipation section 20 via pipe L2. The heat exchanger 22 of the heat dissipation section 20 condenses the refrigerant compressed by the compressor 40 and heated by exchanging heat with outside air. The liquid-phase refrigerant condensed by heat dissipation in the heat dissipation section 20 is sent to the expansion section 50 via pipe L3 and cooled as it expands, then enters the heat receiving section 30 via pipe L4, and circulates through the refrigeration cycle shown in FIG. 2 by cooling the exhaust air of the server in the heat exchanger 31. The heat dissipation section 20 is installed outdoors as a so-called outdoor unit, and the heat receiving section 30, compressor 40, and expansion section 50 are installed inside a building such as a data center as so-called indoor units.

The heat exchanger 22 constituting the heat dissipation section 20 will be described in detail with reference to FIGS.
The heat exchanger 22 is a so-called radiator, and has refrigerant pipes through which a refrigerant flows, and a heat sink for increasing the contact area between the refrigerant pipes and the cooling air. A serpentine type in which the refrigerant pipes are repeatedly bent within a plane and distributed over the entire plane, or a parallel flow type in which a large number of refrigerant pipes are connected in parallel between a supply header that supplies the refrigerant and a discharge header that discharges the refrigerant, is adopted.
These heat exchangers 22 have a flat plate-like appearance, and as shown in Figures 3 to 6, are arranged in six pairs, each pair forming an inverted V shape with the inclination directions opposite to each other, in a horizontal line inside a housing 60 that houses the entire heat dissipation unit 20. This arrangement direction is, in a broad sense, a direction intersecting the air flow path, and in one embodiment, they are arranged in a horizontal direction perpendicular to the up-down (vertical) air flow path.

A fan 70 is disposed above the heat exchangers 22 to supply cooling air to the heat exchangers 22. Two fans 70 are disposed in parallel in the horizontal direction to uniformly supply air to the heat exchangers 22. Three pairs of heat exchangers 22 are disposed below each fan 70. In one embodiment, the fan 70 is an axial flow fan that generates an air flow in the direction of a shaft 71 that is the center of rotation (vertically upward in the illustrated example).
In the illustrated example, three pairs of heat exchangers 22 are arranged at equal intervals below each fan 70, but it is also effective to change the arrangement density of the heat exchangers 22 (the mutual spacing of the heat exchangers 22) depending on the radial distribution of air volume of the fans 70 (for example, characteristics such as faster flow velocity and higher air pressure due to faster circumferential speed of the fan blades toward the outside in the radial direction) to make the heat exchange volume in each heat exchanger 22 more uniform.

The supply pipes for supplying the gas-phase refrigerant to the heat exchangers 22 will now be described.
The upper portions of the plurality of heat exchangers 22 are branched and connected by vapor branch pipes 23 to a manifold 24 that distributes the vapor-phase refrigerant supplied from the compressor 40 via a pipe L2.
The steam branch pipe 23 is connected to a refrigerant pipe built in the heat exchanger 22 at an upper portion of the heat exchanger 22, and is drawn out to one side of the heat exchanger 22, as shown in Fig. 5, passes between the heat exchanger 22 and the inner surface on one side of the housing 60, and is connected to the manifold 24 arranged below the heat exchanger 22. The manifold 24 is connected to the pipe L2 via a steam main pipe 25 at a lower portion of the approximate center thereof, and is supplied with a gas-phase refrigerant. The manifold 24 is arranged along the arrangement direction of the plurality of heat exchangers 22 along the width direction of the housing 60 (W direction in Fig. 1), over almost the entire area in which the plurality of heat exchangers 22 are present.

Each of the steam branch pipes 23 is connected to the upper part of the heat exchanger 22, extends linearly downward from the side of the heat exchanger 22, and is connected to the manifold 24 at a position substantially directly below the heat exchanger 22. The steam branch pipe 23 is mainly composed of a straight pipe section 23a, is connected to the upper part of the heat exchanger 22 from the side via a curved pipe section 23b provided at the upper end, and is connected to the manifold 24 via a curved pipe section 23c provided at the lower end. Since each of the steam branch pipes 23 is connected to the manifold 24 at a position substantially directly below the heat exchanger 22, the pipe length can be shortened as much as possible. In addition, in order to connect to the manifold 24 at a position substantially directly below the steam branch pipes 23, the steam branch pipes 23 are composed of the straight pipe section 23a of the same shape and the

curved pipe sections

23b and 23c of the same shape.
In one embodiment, the manifold 24 is disposed below the area in which the heat exchangers 22 are disposed, and is generally tubular extending in the arrangement direction of the heat exchangers 22, with the lower ends of each of the steam branch pipes 23 connected to the sides thereof.

The discharge pipe for discharging the refrigerant that has become liquid due to heat dissipation in the heat exchangers 22 will be described.
The lower portions of the heat exchangers 22 are connected by liquid branch pipes 26 to a tank 27 that discharges the refrigerant to the expansion section 50 via a pipe line L3 so as to join the tank 27. The tank 27 is a manifold in which liquid-phase refrigerant joins, and is disposed over almost the entire area in which the heat exchangers 22 are arranged along the arrangement direction of the heat exchangers 22 (W direction in FIG. 1) in a plan view.
Each of the liquid branch pipes 26 is connected to the lower part of the heat exchanger 22, extends linearly downward from the side of the heat exchanger 22, and is connected to the tank 27 located directly below the heat exchanger 22. That is, each of the liquid branch pipes 26 is generally composed of two

straight pipe sections

26a, 26b and three

curved pipe sections

26c, 26d, 26e, and is connected to the lower part of the heat exchanger 22 from the lateral direction via the curved pipe section 26c provided at the upper end of the vertically oriented straight pipe section 26a, is connected to the horizontally oriented straight pipe section 26b by the curved pipe section 26d provided at the lower end of the straight pipe section 26a, and is further connected to the bottom of the tank 27 by the curved pipe section 26e. Each of the liquid branch pipes 26 is configured to have the same shape as a whole by combining the

straight pipe sections

26a, 26b of the same standard and the

curved pipe sections

26c, 26d, 26e of the same standard.
In one embodiment, the tank 27 is positioned below the area in which the heat exchangers 22 are arranged, and is generally tubular extending in the arrangement direction of the heat exchangers 22, with the lower ends of each of the liquid branch pipes 26 connected to its bottom.

In the illustrated example, a pipe L3 leading to the expansion section 50 is connected to the bottom of the tank 27, and a pump 28 is provided midway along the pipe. This pump 28 is located below the tank 27 and pumps the liquid refrigerant it has drawn into the expansion section 50. The liquid refrigerant is supplied to the heat receiving section 30 against the flow resistance of the pipes L3 and L4, but if the head difference between the tank 27 and the heat receiving section 30 (gravity acting on the liquid refrigerant based on the difference in potential energy between them) is sufficiently large, the pump 28 may be omitted.

The operation of the cooling device including the heat exchanger according to one embodiment will be described with reference to FIGS.
The refrigerant compressed by the compressor 40 and raised in temperature reaches the steam main pipe 25 through the pipe line L2, flows into the approximate center of the manifold 24, and is distributed to each heat exchanger 22 through each steam branch pipe 23 arranged on the left and right. In one embodiment, the manifold 24 is present in almost the entire area where the heat exchangers 22 are present, so that the steam branch pipes 23 from the manifold 24 to the heat exchangers 22 are approximately straight, connected to the manifold 24 at a position directly below each heat exchanger 22, and configured with the same shape. Therefore, the resistance of the flow path from the manifold 24 to each heat exchanger 22 becomes uniform, and the refrigerant is distributed evenly, allowing each heat exchanger 22 to efficiently exchange heat.

The heat exchanger 22 cools the refrigerant flowing through the internal heat exchange pipes by heat exchange with the cooling air supplied by the fan 70, and the refrigerant that has become liquid due to this heat dissipation flows downward through the liquid branch pipe 26 due to gravity and flows into and joins the tank 27.
In one embodiment, since the tank 27 is present throughout the entire area where the heat exchangers 22 are located, the liquid branch pipes 26 are configured to be straight and have the same diameter and length, so that the flow resistance on the refrigerant discharge side of each heat exchanger 22 can be minimized and made uniform, and the refrigerant can be discharged evenly and merged in the tank 27.
In one embodiment, the lower end of the liquid branch pipe 26 is connected to the bottom (lowest point) of the tank 27 having a circular cross section. In the tank 27, the liquid phase refrigerant may evaporate or the gas phase refrigerant that has not been condensed in the heat exchanger 22 may flow in, so that the gas phase refrigerant may also be present in the tank 27. However, by setting the outlet of the liquid branch pipe 26 below the liquid level in the tank 27, it is possible to prevent uneven distribution of the refrigerant caused by the gas phase refrigerant flowing back through the liquid branch pipe 26.
In the embodiment, the liquid branch pipe 26 is connected to the bottom of the tank 27. However, when it is necessary to connect the liquid branch pipe 26 to an upper part of the tank 27 due to the installation conditions of the liquid branch pipe 26 and the tank 27, it is preferable to insert the liquid branch pipe 26 close to the bottom of the tank 27 as shown in a modified example in FIG. 8 to ensure that the liquid-phase refrigerant flows below the liquid level L of the liquid-phase refrigerant.

Furthermore, the liquid-phase refrigerant flowing into the tank 27 is sucked into the pump 28 and sent to the pipe L3. Here, by arranging the heat exchanger 22 at the top of the housing 60, arranging the tank 27 below the heat exchanger 22, and further arranging the pump 28 below it, the NPSH (Net Positive Suction Head), which depends on the height difference from the heat exchanger 22 (the liquid level of the internal liquid-phase refrigerant) to the inlet of the pump 28 and the internal pressure, can be maintained at an appropriate suction pressure with good discharge efficiency on the performance characteristic curve of the pump 28, and operational abnormalities such as cavitation can be prevented. In addition, since the tank 27 is arranged below the heat exchanger 22, a sufficiently large height difference is secured between them, so that the liquid level of the liquid-phase refrigerant in the tank 27 does not rise to the inside of the heat exchanger 22, and all of the refrigerant flowing through the heat exchanger 22 can change phase from gas phase to liquid phase and release heat.

In this way, in one embodiment, the flow resistance of the flow path of the refrigerant flowing in and out of each of the multiple heat exchangers 22 can be made uniform, making the heat exchange load in each heat exchanger 22 uniform. In addition, since the heat exchangers 22 are arranged horizontally with alternating inclinations in opposite directions, unevenness in the amount of heat exchanged in the vertical direction of each heat exchanger 22 can be reduced, and the heat exchange efficiency can be improved as much as possible when used in a refrigeration cycle that uses a low-pressure refrigerant with a large refrigerant flow rate relative to the heat dissipation capacity, particularly when used in a refrigeration cycle that uses a low-pressure refrigerant with a large refrigerant flow rate relative to the heat dissipation capacity, when exchanging heat with a large amount of refrigerant flowing at high speed.

In the above embodiment, an example has been described in which the heat exchanger 22 is used as a heat dissipation part, but the heat exchanger 22 can also be used as a heat receiving part. In this case, it is sufficient to connect a refrigerant supply pipe and a refrigerant discharge pipe as described below.
That is, in the heat receiving section 30, the liquid-phase refrigerant supplied from the pipe L4 as a supply pipe becomes gaseous due to the heat of the cooling object such as the exhaust gas of the server, and therefore, instead of the tank 27, a manifold is provided to distribute the liquid-phase refrigerant from the pipe L4 as a supply pipe to the liquid branch pipe 26, and the liquid branch pipe 26 is branched from this manifold into a straight pipe section and supplied to each of the heat exchangers 22 directly above. Also, the gas-phase refrigerant that absorbs the heat of the cooling object in the heat exchanger 22 is merged into the manifold 24 by the straight pipe section of the vapor branch pipe 23, and the gas-phase refrigerant is supplied to the compressor 40 via the pipe L1 as a discharge pipe. The gas-phase refrigerant is compressed at a predetermined compression ratio by the compressor 40, dissipates heat in the heat dissipation section 20, and is circulated to the heat receiving section 30 again, thereby realizing a refrigeration cycle.

The shape of the branch pipe, specifically, the number of straight pipe sections, the length, the number of curved pipe sections, and the orientation are not limited to one embodiment, and may of course be changed depending on the number and arrangement of heat exchangers, and the relative positional relationship of the main pipe to the heat exchangers, etc.
In one embodiment, the flow of cooling air and the flow of refrigerant are described as being approximately vertical, but this is not limited to being vertical, and as long as the refrigerant can flow due to the action of gravity, it is not limited to being vertical.
The shape, size, and number of the fan and the heat exchanger are not limited to those in the embodiment, and it is desirable to select an optimal combination according to the installation conditions of the heat dissipation unit and the amount of heat dissipation. For example, the inclination direction of the heat exchangers is not limited to an arrangement in which they are inclined in opposite directions alternately, and for example, a plurality of heat exchangers may be arranged horizontally inclined in the same direction. In addition, the arrangement direction of the heat exchangers is not limited to horizontal, and as long as it is not the same direction as the airflow of the cooling air but is a direction that crosses it, it is possible to obtain the effect of reducing unevenness in the wind pressure and air volume of the cooling air.
The arrangement and shapes of the manifold, tank, steam branch pipes, and liquid branch pipes relative to the heat exchanger are not limited to those in the embodiment, and may of course be changed as appropriate depending on the installation conditions.
In one embodiment, a frame-like structure is used as the housing, but a structure that surrounds the periphery of each part, or a structure in which part of the cooling air flow path is used as the housing may also be used.
Furthermore, the object of cooling according to the present invention is not limited to the server of the embodiment, but can be used to cool various heat generating devices such as power supplies and other electronic devices.

　Although an embodiment of the present invention has been described above in detail with reference to the drawings, the specific configuration is not limited to this embodiment, and design changes and the like that do not deviate from the gist of the present invention are also included.

The present invention can be used in the heat dissipation and heat receiving parts of a cooling device.

REFERENCE SIGNS LIST 1 Flow path 2 Heat exchanger 3 Supply pipe 4 Discharge pipe 5 Trunk pipe 6 Branch pipe 20 Heat dissipation section 21 Heat exchanger 23 Steam branch pipe 23a

Straight pipe section

23b, 23c Curved pipe section 24 Manifold 25 Steam main pipe 26

Liquid branch pipe

26a, 26b

Straight pipe section

26c, 26d, 26e Curved pipe section 27 Tank 28 Pump 30 Heat receiving section 31 Heat exchanger 40 Compressor 50 Expansion section 60 Housing 70 Fan 71 Shaft L1, L2, L3, L4 Pipe line L Liquid level

Claims

a heat exchanger that exchanges heat between air flowing in a vertical flow path and a refrigerant;
a supply pipe for supplying a refrigerant to be heat exchanged in the heat exchanger;
a discharge pipe for discharging the refrigerant that has been heat exchanged in the heat exchanger;
A heat exchange device comprising:
The heat exchanger is arranged in a plurality of units in a direction intersecting the air flow path,
At least one of the supply pipe and the discharge pipe is
a trunk pipe arranged below an area in which the plurality of heat exchangers are arranged and parallel to an arrangement direction of the heat exchangers;
branch pipes connecting the trunk pipe and each of the heat exchangers;
It is composed of
A heat exchange device characterized by:
The plurality of branch pipes have the same shape.
The heat exchange device of claim 1 .
The plurality of branch pipes have straight pipe portions, and the straight pipe portions are arranged in a vertical direction and parallel to each other.
The heat exchange device according to claim 2.
The supply pipe is connected to a branching manifold that distributes a gas-phase refrigerant to the plurality of heat exchangers, and the discharge pipe is connected to a merging manifold that merges the liquid-phase refrigerant that has been heat exchanged in the plurality of heat exchangers.
The heat exchange device of claim 1 .
The supply pipe is connected to a branching manifold that distributes a liquid-phase refrigerant to the plurality of heat exchangers, and the discharge pipe is connected to a merging manifold that merges the gas-phase refrigerant that has been heat exchanged in the plurality of heat exchangers.
The heat exchange device of claim 1 .
A cooling device in which a refrigerant that has received heat at a heat receiving section is compressed by a compressor, and the compressed refrigerant is radiated heat at a heat radiating section and circulated to the heat receiving section,
A cooling device comprising the heat exchange device according to claim 1 in at least one of the heat receiving portion and the heat radiating portion.