JP2000055574A - Heat-exchanging device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact heat-exchanging device that has a coil-shaped pipeline and high heat exchange capability. SOLUTION: First and second cylindrical channels 21 and 22 are composed of a cylindrical chiller drum 10 and external and internal shells 13 and 14, and a cooling pipe 6 being wound in a coil shape is installed inside. The cooling pipe 6 is formed in the coil shape by arranging tubes 5a, 5b, and 5c in parallel in the axis direction of a coil, and a refrigerant 2 is allowed to flow into the tubes for cooling water 7 flowing in the channels 21 and 22 by a tube with a small bore. Since the tubes have the small bore, thermal conductivity becomes high, and heat exchange capability is increased. On the other hand, three tubes are adopted, thus preventing pressure loss caused by reducing the bore from being increased, and hence providing a compact heat-exchanging device with high heat exchange capability.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchange device used for a cooler or the like.

[0002]

2. Description of the Related Art As a cooling device for generating cold water by exchanging heat with a refrigerant, a helically wound cooling pipe through which the refrigerant is passed is installed in a casing having an appropriate capacity so that water passes through the casing. A coil-type cooler is known. In this coil-type cooler, the pipe diameter of the cooling pipe is determined so that the pressure loss of the refrigerant falls below a certain value. Usually, only a very small pressure loss is recognized, so the pipe diameter becomes relatively large. However, when the pipe diameter is increased, the degree of contact of the refrigerant (refrigerant unit contact area) decreases. Therefore, the cooling pipe becomes long in order to secure an area required for heat transfer. Then, as the cooling pipe becomes longer, the pressure loss increases, and accordingly, the pipe diameter further increases. In addition, when the diameter of the cooling pipe is large, the cooling pipe tends to be distorted when bent. Therefore, in order to process the pipe into a coil shape while suppressing the flatness, the coil diameter becomes large.
Therefore, in the coil-type cooler, it is difficult to increase the heat exchange efficiency when trying to suppress the pressure loss to an allowable range. Furthermore, since the size of the coil-shaped cooling pipe through which the refrigerant flows increases, the size of the cooler itself also increases,
Manufacturing costs also increase.

On the other hand, Japanese Patent Application Laid-Open No. Hei 8-54192 discloses a heat transfer method in which a plurality of coils having different winding diameters are concentrically arranged so as to communicate a header on a refrigerant introduction pipe side and a header on a discharge pipe side. An exchange coil is disclosed. This heat exchange coil has a small pressure loss because the inlet pipe and the outlet pipe are connected by a plurality of independent coils. Furthermore, by arranging a plurality of coils concentrically, it is possible to provide a small-sized heat exchange coil having a high heat exchange capacity, which can increase the heat transfer area without increasing the space occupied by these coils.

[0004]

However, in a heat exchange coil in which a plurality of coils having different winding diameters are arranged concentrically, a coil arranged outside and a coil arranged inside are among these coils. Have different winding diameters, so that the pressure loss differs even if the pipe diameters are the same. Therefore, in order to make the pressure loss of these coils uniform and to flow the refrigerant in a well-balanced manner, it is necessary to adjust the pressure loss by changing the number of windings and balance the flow rates. Therefore, this heat exchange coil requires a plurality of coils having different numbers of windings as well as winding diameters, so that the number of parts is large and the assembling process is complicated.
Therefore, the manufacturing cost is high. Further, since the header or a pipe connecting the header and each coil is attached to the heat exchange coil in order to divide the heat into a plurality of coils, the heat exchange coil becomes large, and the size of the heat exchange device containing the coil becomes large.

Therefore, in the present invention, the pressure loss can be kept low, the heat exchange capacity is high,
It is another object of the present invention to provide a heat exchange device that can be manufactured at low cost.

[0006]

For this reason, in the heat exchange apparatus of the present invention, a cylindrical flow path is formed, and a spiral (coil-shaped) heat exchange tube is provided in this flow path by a plurality of shafts. By arranging them side by side, the pressure loss can be reduced and the heat transfer efficiency between the inside and outside of the tube can be increased. That is, the heat exchange device of the present invention has a cylindrical flow path formed by an outer partition and an inner partition arranged coaxially, and a pipe spirally arranged in the flow path. This conduit is characterized by comprising a plurality of tubes arranged in parallel in the axial direction.

[0007] By forming a spiral pipe by arranging a plurality of tubes in parallel in the axial direction, it is possible to prevent an increase in pressure loss in the entire pipe even if the diameter of each tube is reduced. . Therefore, the heat transfer efficiency can be improved by increasing the degree of contact of the fluid on the pipeline side. Further, since the plurality of tubes constituting the pipeline are arranged in parallel in the axial direction, the winding diameter is the same, and the pressure loss does not change, so that the flow rate can be balanced as it is. Further, since the tube diameter is reduced, it is easy to process the coil into a small-diameter coil, and a plurality of tubes can be integrally formed into a spiral having a small coil diameter. Therefore, it is possible to provide a heat exchange device that is small, has a high heat exchange capability, and can be manufactured at low cost.

Further, in the heat exchange device of the present invention,
Since the flow path is also cylindrical so that the fluid flows along the spiral coil, the degree of contact on the flow path side is increased, and the heat transfer efficiency can be improved. Also, since the channel is cylindrical,
A plurality of flow paths can be coaxially combined, and a conduit can be arranged in each flow path. Therefore, it is possible to provide a heat exchange device in which a plurality of heat exchange devices are integrally housed. Alternatively, a plurality of flow paths and conduits are connected at one end, and the connected conduits are reversed in the direction of travel of each spiral, so that one flow path and one conduit are combined coaxially. It is possible to configure a heat exchange device, and it is possible to provide a heat exchange device that is smaller and has higher heat exchange capability.

In a heat exchange device in which a plurality of flow paths are coaxially combined, an even number of flow paths arranged coaxially are connected to each other so that a side for introducing a fluid into the tube and a side for discharging the tube are heated. This makes it possible to align one of the exchange devices. Conversely, by connecting the odd number of flow paths arranged coaxially, it is also possible to arrange the introduction side and the extraction side at both ends of the heat exchange device. Therefore, it is possible to provide a heat exchange device having an inlet side and an outlet side in a direction that matches the piping system in which the heat exchange device is installed, and it is possible to provide a piping system including the heat exchange device, an air conditioner, or a chilled water supply. Devices and the like can be compactly assembled.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A heat exchanger according to the present invention will be described below with reference to the drawings. 1 is a coil-type cooler according to the present invention capable of cooling water 7 through a cooling pipe 6 assembled in a coil shape and supplying the coolant 2 as cold water 8. is there. A coil-type cooler (hereinafter, a cooler) 1 of the present example includes a chiller drum 10 having a cylindrical shape and an upper end closed by an upper wall 11, and is formed in a spiral shape (coil shape) inside the chiller drum 10. The cooling pipe 6 forms a conduit. Further, inside the chiller drum 10, a cylindrical outer shell 13 and an inner shell 14 are coaxially arranged at an appropriate distance from each other.
Is closed by a bottom plate 12. Therefore, the chiller drum 10 and the outer shell 13 form a cylindrical first flow path 21, and the outer shell 13 and the inner shell 14 form a cylindrical second flow path 22. The outer shell 13 is shorter in the axial direction than the chiller drum 10, and includes first and second flow paths 21.
And 22 are connected on the side of the upper wall 11. The inner shell 14 is also shorter in the axial direction than the chiller drum 10, and the bottom plate 12 is a bottom wall 15. For this reason, a chamber 16 for outputting the cold water 8 is formed between the bottom plate 12 and the bottom wall 15.

The cooling pipe 6 housed inside the chiller drum 10 is composed of a combination of three tubes 5a, 5b and 5c. These three tubes are arranged adjacent to each other in parallel in the axial direction of the chiller drum 10, and these three tubes 5a, 5b and 5c are wound with equal diameters to form a coil-shaped cooling tube 6. These three
The cooling pipe 6 in which the tubes 5a, 5b, and 5c are combined is spirally aligned so that the refrigerant 2 flows upward in FIG. 1 along the second flow path 22 inside the second flow path 22. Are combined. In this example, these tubes 5a, 5b and 5c are connected from the bottom plate 12 to the upper wall 1
It is processed into a coil shape (spiral shape) that turns clockwise with respect to the traveling direction of the refrigerant 2 so that the refrigerant 2 flows toward 1. Then, as shown in FIG.
Nozzles 3a, 3b, and 3c for introducing the refrigerant 2 are provided on the inner diameter side of the bottom plate 12 of each of the above.
a, 5b and 5c are connected.

When the tubes 5a, 5b and 5c reach the upper wall 11 of the second flow path 22, the winding diameter of the tubes 5a, 5b and 5c is enlarged, and the first flow path from the inner second flow path 22 to the outer first flow path 22 is formed. It enters the inside of the road 21. Inside the first flow path 21, these tubes 5 a, 5 b, and 5 c rotate counterclockwise with respect to the traveling direction of the refrigerant 2 so that the refrigerant 2 flows from the upper wall 11 toward the bottom plate 12. Assembled in a coil shape. Then, the leading ends of these tubes 5a, 5b and 5c are arranged on the outer diameter side of the bottom plate 12, and the outlet nozzles 4a, 4b
And 4c, so that the refrigerant 2 can be discharged from the chiller drum 10.

As described above, in the cooler 1 of the present embodiment,
Three tubes 5a, 5b and 5 constituting the cooling pipe 6
c is overlapped and wound in the axial direction (vertical direction in FIG. 1) inside the inner second flow path 22, and is folded when it reaches the upper wall 11. After the inside is wound with a reverse inclination, it comes out of the bottom plate 12. Therefore, the introduction pipe header installed outside the cooler 1 and the introduction nozzles 3a, 3b and 3c are connected, and the extraction pipe header and the extraction nozzles 4a, 4b and 4 are connected.
c, the refrigerant 2 supplied from the supply source to the cooler 1 is divided into three tubes 5a, 5b, and 5c and flows at a substantially equal flow rate. Can be returned.

On the other hand, water 7 cooled by the refrigerant 2 in the cooler 1 is supplied from a supply port 17 provided on the outer peripheral surface of the chiller drum 10 on the side of the bottom plate 12 to the first flow path 2.
1 is supplied. The water 7 supplied to the first flow path 21 flows through the first flow path 21 through the tube 5 of the refrigerant 2.
a, 5b and 5c while contacting the bottom plate 12
Flows toward the upper wall 11. Further, the water 7 that has reached the upper wall 11 is separated from the second flow path 2 that is continuous on the side of the upper wall 11.
2 flows from the upper wall 11 to the bottom plate 12 while contacting the tubes 5a, 5b and 5c again, and is collected in the chamber 16. In this manner, the cold water 8 is produced by flowing the water 7 from the inside to the outside in the direction opposite to the refrigerant 2 flowing inside the cooling pipe 6, and the cold water 8 is output from the discharge port 18 provided substantially at the center of the bottom plate 12. It has become so.

The bottom plate 12 has a fastening bolt 31
The bottom plate 12 and the chiller drum 10 are attached so as to be detachable from the chiller drum 10.
An O-ring 35 is interposed between the chiller drum 10 and the flange surface 10a so that the inside of the chiller drum 10 is sealed. An outer shell 13 is attached to the bottom plate 12 so as to separate the first flow path 21 and the second flow path 22 by welding or brazing. further,
The inner shell 14 is attached to a predetermined position of the upper wall 11 of the chiller drum 10 by welding or brazing so as to form a second flow path 22. For this reason, the cooler 1 of the present example is provided with the three tubes 5a, 5b and 5c assembled in a coil shape as described above inside the chiller drum 10 to which the inner shell 14 is attached, and further, the outside. Bottom plate 12 with shell 13 attached
It can be assembled by attaching. Then, the chiller drum 1 is tightened by tightening the tightening bolts 31.
0 is sealed, and the above-described first and second flow paths 21 and 22 are formed. Therefore, the cooler 1 of the present embodiment requires a small number of parts and is very easy to assemble, so that it can be manufactured and supplied at low cost. Also,
Since disassembly and assembly can be performed simply by removing the fastening bolt 31, maintenance after installation is also very simple.

In such a coil-type cooler 1, a small-sized cooler having a large heat exchange amount Q and high heat exchange efficiency is desired. The heat exchange amount Q in the heat exchanger is generally represented by the following equation (1).

Q = K × A × Δt (1) where A is the total surface area of the tube of the coiled cooler, and Δt is the temperature difference between the liquid temperature on the high temperature side and the liquid temperature on the low temperature side ( In this example, the temperature difference between the refrigerant and the water is shown. Also,
K is a coefficient indicating the ease of passing heat with respect to the entire temperature difference, called a heat transmittance, and is represented by the following equation (2).

K = 1 / {(1 / h1) + (L / λ) + (1 / h2)} (2) where h1 is the heat transfer coefficient of the inner surface of the tube, and h2
Is the heat transfer coefficient of the outer surface of the tube. L indicates the thickness of the tube, and λ indicates the heat transfer coefficient of the tube.

According to the equation (1), in order to reduce the size of the cooler 1, it is necessary to reduce the total surface area A of the tube under the condition that the heat exchange amount Q and the temperature difference Δt are the same. It is necessary to increase the heat transmittance K.
In order to increase the heat transfer rate K, it is important to increase h1 and h2 while minimizing the flow loss inside and outside the tube.

First, in the cooler 1 of the present embodiment, the heat transfer coefficient h1 on the inner surface of the tube is improved by reducing the diameter of the tube. That is, in the cooler 1 of the present embodiment, the cooling pipe 6 is constituted by three combinations of the plurality of tubes 5a, 5b and 5c, so that even if the total cross-sectional area as the cooling pipe 6 is the same, The tube diameter of the tube can be reduced, the degree of contact C1 between the refrigerant and the inner surface of the tube is increased, and the heat transfer coefficient h of the inner surface of the tube is increased.
1 can be improved. The degree of contact C1 is represented by the ratio of the inner surface area of the tube per unit length to the cross-sectional area of the tube. For example, a cooling tube composed of one tube having an inner diameter of 16 mm and a cooling tube composed of three tubes having an inner diameter of 9.2 mm are compared. A tube having an inner diameter of 16 mm has a cross-sectional area of 201 mm ² , and a surface area of 50 mm per 10 cm.
266 mm ² , the ratio of the surface area to the cross-sectional area is 250. On the other hand, a tube having an inner diameter of 9.2 mm has a cross-sectional area of 67 mm ² and a surface area of 289 per 10 cm.
03 mm ² , and the ratio of the surface area to the cross-sectional area is 435. Therefore, when a cooling tube is constituted by three tubes having an inner diameter of 9.2 mm, the total cross-sectional area in the tube is the same as that of a tube having an inner diameter of 16 mm, so that the cooler 1 can be provided with the same pressure loss. When the tube is used, the ratio of the surface area to the sectional area (contact degree C1) is 1.7
Since it is four times, the heat transmission rate K can be greatly improved. For example, if the heat transfer coefficient h1 of the inner surface of the tube is improved by 74% under the condition that other elements of the heat transfer rate K are not changed, the surface area A of the tube can be reduced by 16%, and cooling is accordingly performed. The size of the cooler 1 can be reduced without changing the capacity.

Further, in the cooler 1 of the present embodiment, the outer shell 13 and the inner shell 14 are provided inside the chiller drum 10 to provide first and second cylindrical flow paths 21 and 22. The fluid is caused to flow along the coil-shaped cooling pipe 6 in the insides 21 and 22. Therefore, as compared with a cooler in which a coiled cooling pipe is installed in a water tank as shown in JP-A-8-45192 cited above, the ratio of the liquid in contact with the tube on the outer surface of the tube is greatly increased. It can be enhanced. For this reason, in the cooler 1 of the present example, the heat transfer coefficient h2 on the outer surface of the tube is also improved. Therefore, due to these factors, the cooler 1 of the present embodiment can significantly improve the heat transfer rate K, and can provide a compact cooler having a high heat exchange capacity.

Further, by reducing the diameter of the tube, the size can be reduced in terms of production technology. That is, when the tube is processed into a coil shape, the minimum coil outer diameter is limited by the outer diameter of the tube in order to prevent a reduction in cross-sectional area due to deformation of the tube at the bent portion. Generally, it is recommended that the minimum coil outer diameter be eight times or more the tube outer diameter. A tube having a tube inner diameter of 16 mm as described above,
Taking the 9.2 mm tube as an example, the effects on processing by making the tube thinner are compared as follows. Assuming that the tube thickness of a tube having a tube inner diameter of 16 mm is 0.8 mm and the tube thickness of a tube having a tube inner diameter of 9.2 mm is 0.7 mm, the outer diameter of each tube is 17.6 mm and 1 mm.
0.6 mm. Therefore, the minimum coil outer diameter of a tube having an outer diameter of 17.6 mm is 140.8 mm. Here, assuming a cooler having a surface area A of 1 m ² required for heat exchange, a tube length of 18.1 m is required, and a coil having a minimum outer diameter of 140.8 mm results in a coil of 40.9 turns. . Furthermore, when a tube of this length is wound up in close contact, the height (length in the axial direction) is 720.6 mm.
And the volume is 0.0112 m ³ . In contrast, if the tube has a tube inner diameter of 9.2 mm, the required surface area A is reduced by 16% by improving the heat transfer coefficient h1 by reducing the tube inner diameter as described above. . Therefore, the required pipe length is 25 m. Furthermore, a tube of this length has a minimum outer diameter of 84.8.
It can be processed into a coil of 94 mm, so that it becomes a 94-wound coil.
Becomes Therefore, the volume occupied by the coil is 0.005
Since the inner diameter of the tube is 6 m ³ , the inner diameter of the tube is reduced from 16 mm to 9.
By reducing the size to 2 mm, the volume of the coil-shaped cooling pipe can be reduced to about half. Further, the pressure loss is increased by reducing the inner diameter of the tube, which can be solved by winding up three tubes in parallel as described above.

As described above, in the cooler of the present embodiment, the coil diameter can be reduced by reducing the tube diameter, so that the cooler 1 can be further compacted. Furthermore, a plurality of tubes are combined so that the pressure loss does not increase, so that the total cross-sectional area as a cooling pipe can be sufficiently secured, and these tubes are arranged in parallel in the coil-shaped axial direction. I have. For this reason, the coil diameters of the plurality of tubes 5a, 5b and 5c are the same, and the respective tube lengths inside the chiller drum 10 can be made the same. Therefore, the pressure loss in each tube can be made uniform without changing the shape of each tube, changing its length, or adjusting the pressure balance by installing an orifice or the like. For this reason, the fluid can be uniformly flowed to each of the tubes in a well-balanced manner, and problems due to unbalanced flow rates such as a temperature difference between the tubes can be prevented. Also, by arranging a plurality of tubes in the axial direction of the coil, these tubes can be housed in the cylindrical flow path, so that the heat transfer efficiency h2 of the outer surface of the tubes is improved as described above. be able to.

Further, the cooler 1 of the present embodiment is provided with first and second flow paths 21 and 22 coaxially, and these are connected to form one flow path. Therefore, these flow paths 21
The coil-shaped cooling pipe 6 can be folded back and installed at and 22, so that the coil length calculated above can be further reduced to about half. When the coil is folded and wound in this manner, the volume is not reduced to half of the above calculated value because the outer diameter of the outer coil needs to be increased, but the coil-shaped cooling pipe 6 is installed without being folded. It can be smaller in size than a cooler. Further, in the cooler 1 of the present embodiment, since the coil-shaped cooling pipe 6 is folded back, the inlet 3 and the outlet 4 of the refrigerant 2 can be provided to be aligned with the bottom plate 12 side. Therefore, it is possible to install the inlet pipe header and the outlet pipe header in the same direction with respect to the cooler 1, and the layout of the pipes is facilitated.

Of course, a third flow path is provided coaxially inside the second flow path 22 and connected to the second flow path 22.
It is also possible to manufacture the coiled cooling pipe 6 by folding it back again and to make the first to third flow paths function as one heat exchanger. By increasing the number of channels, the height of the coil can be reduced, and a thin and compact cooler 1 can be realized. In addition, since the coil-shaped cooling pipe is folded back, the inlet and the outlet can be provided on both sides of the chiller drum. Therefore, the cooler having such an odd number of flow paths is suitable for a piping system in which the inlet pipe header and the outlet pipe header are located on both sides of the chiller drum. On the other hand, when the number of the flow paths is even, the inlet and the outlet are aligned in one direction as described above, so that this is suitable for a piping arrangement in which the inlet pipe header and the outlet pipe header are installed adjacent to each other.

The first and second flow paths 21 and 2
2 can be completely separated by the outer shell 13 without being continuous, and the coil-shaped cooling pipe 6 can be disposed in each of the first and second flow paths 21 and 22. In this way, a cooler in which two coolers are integrated into one can be provided. Therefore, a system that requires a plurality of coolers can be integrated in a compact manner. Further, in the cooler 1 of the present embodiment, since the coil-shaped cooling pipe 6 and the cylindrical flow paths 21 and 22 are arranged along the outer periphery of the chiller drum 10, a space in the center of the chiller drum can be made available. This space can be used as a space for installing piping or other equipment.

In the above description, the coolant 2 passes through the inside of the coil-shaped cooling pipe 6 from the side of the second flow path 22 to face the flow of water passing through the first and second flow paths 21 and 22, and Although the present invention has been described by taking the cooler 1 capable of generating and supplying water as an example, the present invention is not limited to this type of heat exchange between a refrigerant and water, and the present invention can be provided to a heat exchange device between appropriate fluids. Of course. Although the refrigerant is passed through the coil-shaped cooling pipe, it is needless to say that cold water may be passed through the coil-shaped cooling pipe depending on conditions such as pressure. Further, in this example, the cooling pipe is constituted by a combination of three tubes, but it is a matter of course that a combination of two or four or more tubes may be adopted in consideration of pressure loss and the like. . However, if the number of tubes is increased and the inner diameter of each tube becomes too small, the ratio of the tube plate thickness to the cross-sectional area of the tube increases, so that the weight increases. Therefore, it is desirable to combine about 2 to 5 tubes to form one coiled cooling pipe.

The winding direction of the coiled cooling tube is not limited to the above example, and the cooling tube can be wound in the opposite direction. Further, in the above description, the cooler in which the axis of the coil-shaped cooling pipe is installed in the vertical direction is described as an example, but the axis of the coil-shaped cooling pipe is installed in the horizontal direction, that is, the chiller drum is placed in the horizontal direction. Needless to say, a cooler or a heat exchange device extending to the end may be used.

[0029]

As described above, in the present invention, a pipe such as a cooling pipe is spirally arranged in a cylindrical flow path, and the pipes are arranged in parallel in the axial direction of the spiral. And a plurality of tubes. For this reason, by flowing a fluid through these plural tubes, a heat exchange device having a high heat exchange capability while preventing a pressure loss from increasing compared to a tube constituted by a single tube having a large diameter is provided. can do. Furthermore, since the tubes are arranged in a spiral in the axial direction and arranged in a spiral, the winding diameters of these tubes are the same, and the fluid can be substantially applied to a plurality of tubes without adjusting the pressure loss of each tube. It becomes possible to flow uniformly. Therefore, it is possible to provide a heat exchange device that is small, has high heat exchange capability, is easy to assemble, and can be manufactured at low cost.

Further, it is possible to arrange a plurality of flow paths coaxially, and to connect a plurality of flow paths by connecting a plurality of flow paths or a heat exchange device in which a plurality of heat exchange functions are integrated.
It is possible to provide a more compact heat exchange device. In addition, by connecting a plurality of flow paths, it is possible to freely adjust the direction of introduction and exit of the tube, and the length of the piping that connects the header and the tube to the piping system where the heat exchange device is installed. And a heat exchange device capable of compactly integrating the entire system can be provided.

[Brief description of the drawings]

FIG. 1 is a diagram showing a configuration of a heat exchange device according to an embodiment of the present invention using a partial cross section.

FIG. 2 is a view showing a state where the heat exchange device shown in FIG. 1 is viewed from a bottom plate side.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Heat exchange apparatus (cooler) 2 Refrigerant 3 Inlet 4 Outlet 5a, 5b, 5c Tube 6 Cooling pipe (pipe) 7 Water 8 Cold water 10 Chiller drum 11 Top wall 12 Bottom plate 13 External shell 14 Inner shell 15 Bottom wall Reference Signs List 16 chamber 17 supply port 18 discharge port 21 first flow path 22 second flow path 31 fastening bolt 35 O-ring

Continued on the front page (72) Inventor Profit Aizawa 246 Sachika, Osaka, Suzaka City, Nagano F-term in Orion Machinery Co., Ltd. (Reference) 3L103 AA01 AA05 AA17 AA18 CC02 DD05 DD42 DD62

Claims (3)

[Claims] The present invention has a cylindrical flow path formed by an outer partition and an inner partition arranged coaxially, and a pipe spirally arranged in the flow path. A heat exchange device comprising a plurality of tubes arranged in parallel in a direction. 2. The heat exchange device according to claim 1, further comprising: a plurality of the coaxially arranged flow paths; and a plurality of the pipelines respectively arranged in the plurality of flow paths. . 3. The method according to claim 2, wherein the plurality of flow paths and the conduits are connected at one end, respectively, and further, the connected conduits have the spiral direction reversed. And heat exchanger.