JP4987685B2 - Double tube heat exchanger, method for manufacturing the same, and heat pump system including the same - Google Patents

Description

  TECHNICAL FIELD The present invention relates to a double-pipe heat exchanger used in a refrigeration apparatus that transfers heat from a high-temperature fluid to a low-temperature fluid by exchanging heat between the low-temperature fluid and the high-temperature fluid, a manufacturing method thereof, and a heat pump system including the same. It is.

  In a conventional double pipe heat exchanger, a cylindrical refrigerant circulation pipe having a large number of refrigerant circulation holes penetrating the inside of the wall is joined to the outer periphery of the water officer, And a bag-shaped header that is joined to the outer peripheral wall of the water pipe and provided at the end of the refrigerant flow pipe (see, for example, Patent Document 1).

JP 2002-213895 A

  In a conventional double tube heat exchanger, a large number of refrigerant flow holes are arranged in the circumferential direction and formed through the wall of the refrigerant flow tube, so that a gas-liquid two-phase refrigerant is circulated. In other words, after the refrigerant is supplied into the header, it is difficult to be uniformly distributed to each refrigerant circulation hole. In particular, when a conventional double tube heat exchanger is operated as an evaporator, the refrigerant in the gas-liquid two-phase state is unevenly distributed to the refrigerant circulation holes, and in the refrigerant circulation holes with a small liquid refrigerant distribution amount, All of the liquid refrigerant evaporates in the middle of the pipe line, and the excessive superheated area becomes longer, resulting in a problem that the heat transfer performance of the entire heat exchanger is extremely lowered.

  The present invention has been made to solve the above-described problems, and a double-tube heat exchanger that can evenly distribute a plurality of gas-liquid refrigerants even in a gas-liquid two-phase state, and its It aims at obtaining a manufacturing method and a heat pump provided with the same.

The double pipe heat exchanger of the present invention is manufactured in a cylindrical shape with a center hole formed at the axial center position, and a plurality of pipe lines through which the first refrigerant flows has their pipe centers parallel to the axis. A first tube formed in a circumferential direction, a cylinder that is inserted into the center hole of the first tube and is in close contact with the inner peripheral wall surface of the center hole of the first tube, and through which the second refrigerant flows. A cylindrical second pipe, formed in an annular cylindrical shape having a predetermined radial width and a predetermined axial length on one end side of the first pipe, and one end sides of the plurality of pipe lines are opened, A first header space that distributes the first refrigerant to the plurality of pipes, formed on the other end of the first pipe, the other end of the plurality of pipes opened, and circulated through the plurality of pipes A second header space for collecting the first refrigerant and first and second headers that cooperate with the first pipe to define the first and second header spaces. And a first and second pipe connected to each of the first and second header spaces, and a double pipe for heat exchange for exchanging heat between the first refrigerant and the second refrigerant. Yes. Then, the first pipe, the pipe center is positioned on a plane perpendicular to the axis of the first pipe, perpendicular to the該径direction displaced in the axial center radially outward of the first pipe As described above, the inner peripheral wall that is connected to the first header space and defines the first and second header spaces is configured by a cylindrical protruding portion that protrudes coaxially from both ends of the first pipe. The first refrigerant flowing through the first and second header spaces is separated from the second refrigerant flowing through the second pipe by the projecting portion and the second pipe .

  According to the present invention, the pipe center of the first pipe is located on a plane orthogonal to the axis of the first pipe, and is displaced radially outward from the axis of the first pipe and is orthogonal to the radial direction. Thus, the refrigerant in the gas-liquid two-phase state that has flowed into the first header space from the first pipe has a large swirl component in the circumferential direction. Therefore, the refrigerant becomes an annular flow of a substantially uniform liquid film and refrigerant vapor along the outer peripheral wall surface of the first header space by centrifugal force, and is evenly distributed to a plurality of pipe lines opened in the first header space.

Embodiment 1 FIG.
1 is a perspective view showing a heat exchange double pipe applied to a double pipe heat exchanger according to Embodiment 1 of the present invention, and FIG. 2 is a double pipe type according to Embodiment 1 of the present invention. FIG. 3 is a perspective view showing a state in which one header of a double pipe for heat exchange applied to a heat exchanger is omitted, and FIG. 3 shows heat applied to the double pipe heat exchanger according to Embodiment 1 of the present invention. FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3, FIG. 5 is a sectional view taken along the line V-V in FIG. 3, and FIG. 6 is a first embodiment of the present invention. FIG. 7 is a cross-sectional view for explaining the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe heat exchanger. FIG. 7 is a double pipe heat exchanger according to Embodiment 1 of the present invention. It is a longitudinal cross-sectional view explaining the refrigerant | coolant flow in the header of the double pipe for heat exchange applied to.

  1 to 5, a double tube 1 for heat exchange is produced by extruding an aluminum alloy into a cylindrical tube having a predetermined thickness with a center hole drilled at the axial center position. The outer pipe 2 as a first pipe through which the first refrigerant flows, for example, twelve are formed at an equiangular pitch on the same circumference through the wall with the hole direction parallel to the axis. It is made of a copper material in a cylindrical shape, is in close contact with the inner wall surface of the center hole of the outer tube 2 and is inserted coaxially with the outer tube 2 to serve as a second tube through which the second refrigerant flows. The inner tube 3 is made of aluminum alloy in a bottomed cylindrical shape, and the extending portions of the inner tube 3 from both ends of the outer tube 2 are inserted through the through holes 4a and 5a formed coaxially in the bottom portion, The inner wall surfaces of the through holes 4a and 5a are joined to the outer wall surface of the inner tube 3, and the opening end surface is joined to the radially outer end surface of the formation region of the pore 2a of the outer tube 2, First and second headers 4, 5 provided coaxially with the outer tube 2 at both ends of the tube 2, and the outer tube 2 is located on a plane whose center is perpendicular to the axis of the outer tube 2. First and second pipes 6 and 7 made of aluminum alloy connected to the bottom side of the first and second headers 4 and 5 so as to be orthogonal to the radial direction at positions shifted in the radial direction from the axis of Prepare.

  Here, the outer tube 2 and the inner tube 3 are formed by inserting the inner tube 3 into the central hole of the outer tube 2 and then expanding the inner tube 3 mechanically so that the outer wall surface of the inner tube 3 becomes the outer tube 2. It is in close contact with the inner wall surface of the center hole and is in close thermal contact. The outer tube 2 and the first and second headers 4 and 5 are joined by brazing. The inner tube 3 and the first and second headers 4 and 5 are joined to each other by brazing via a thin plate-like stainless alloy. Further, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5 by brazing. The first header space 9a is defined on one end side of the outer tube 2 by the outer tube 2, the inner tube 3, and the first header 4, and has an annular cylindrical shape having a predetermined radial width and a predetermined axial length. Is formed. Similarly, a second header space 9b is defined on the other end side of the outer tube 2 by the outer tube 2, the inner tube 3, and the second header 5, and has a predetermined radial width and a predetermined axial length. It is formed in an annular cylindrical shape. In order to prevent corrosion of the brazed part from moisture due to condensation or the like, an anticorrosion coating may be applied to the outer surface of the brazed part.

  In the double-pipe heat exchanger 10 according to the first embodiment, one heat exchange double pipe 1 configured as described above is not shown, for example, but the first pipe 6 is a first cooling / heating device. The second pipe 7 is connected to the suction pipe of the first cooling device, one end of the inner pipe 3 is connected to the discharge pipe of the second cooling device, and the other end of the inner pipe 3 is the second cooling heat. Connected to the equipment intake piping.

And the 1st refrigerant | coolant discharged from the 1st cooling / heating apparatus flows in in the 1st header 4 via the 1st piping 6, and is distributed to each pore 2a. The first refrigerant flows through each pore 2a, is collected in the second header 5, and is returned from the second pipe 7 to the first cooling / heating device.
On the other hand, the second refrigerant discharged from the second cooling / heating device flows through the inner pipe 3 and is returned to the second cooling / heating device. This second refrigerant exchanges heat with the first refrigerant flowing in the pores 2a while flowing in the inner pipe 3. The second refrigerant has a parallel flow with respect to the first refrigerant flowing in the pores 2a. However, when the second pipe 7 is connected to the discharge pipe of the first cooling device, the second refrigerant has the pores. It becomes a counterflow with respect to the 1st refrigerant | coolant which flows through in 2a. Alternatively, even when the connection direction of the inner pipe 3 and the second cooling / heating device is changed, the second refrigerant is opposed to the first refrigerant flowing in the pores 2a.

  In this double pipe heat exchanger 10, the first and second pipes 6 and 7 of the double pipe 1 for heat exchange are located on a plane whose pipe center is orthogonal to the axis of the outer pipe 2, It is connected to the bottom side of the first and second headers 4 and 5 so as to be orthogonal to the radial direction at a position shifted in the radial direction from the axis of the outer tube 2. Therefore, the first refrigerant 8 in the gas-liquid two-phase state in which the refrigerant liquid 8a and the refrigerant vapor 8b are mixed is introduced into the first header 4 from the first pipe 6 as indicated by an arrow in FIG. It has a turning component in the circumferential direction. And the 1st refrigerant | coolant 8 is a liquid film (refrigerant liquid 8a) of the substantially uniform thickness along the inner peripheral wall surface (the outer peripheral wall surface of the 1st header space 9a) of the 1st header 4 with the centrifugal force, and the refrigerant | coolant vapor | steam 8b. It becomes an annular flow. Then, as indicated by an arrow in FIG. 7, the first refrigerant 8 is accompanied by the refrigerant vapor 8b, reaches the end surface of the outer tube 2, and is evenly distributed to each pore 2a.

  When the double pipe heat exchanger 10 is operated as an evaporator, if the refrigerant liquid 8a is not evenly distributed to the respective pores 2a, the refrigerant liquid is reduced in the pores 2a with a small distribution amount of the refrigerant liquid 8a. All of 8a evaporates in the middle of the pore 2a. Therefore, an excessive overheating region becomes long, and the heat transfer performance of the entire heat exchanger is extremely lowered. In this double tube heat exchanger 10, since the refrigerant liquid 8a is evenly distributed to the respective pores 2a, it is possible to prevent the performance deterioration of the heat exchanger described above.

  Since the distribution of the first refrigerant in the first header 4 in the circumferential direction is affected by gravity due to the structure of the double tube 1 for heat exchange, the axis of the outer tube 2 is inclined with respect to the horizontal. Thus, it is preferable to arrange the heat exchange double pipe 1 and more preferably to arrange the heat exchange double pipe 1 so that the axis of the outer pipe 2 is vertical.

  Further, the refrigerant circle introduced into the first header 4 is displaced as the point perpendicular to the center of the first pipe 6 and the radial direction of the outer pipe 2 is displaced radially outward from the axis of the outer pipe 2. Since the swirl component in the circumferential direction becomes large, it is preferable that an orthogonal point between the pipe center of the first pipe 6 and the radial direction of the outer pipe 2 is located on the outer peripheral side of the outer pipe 2. In particular, it is more preferable that the center of the pipe line of the first pipe 6 is substantially coincident with the tangent line of the inner peripheral wall surface of the first header 4. That is, as shown in FIG. 5, the center of the pipe line of the first pipe 6 is located on a plane orthogonal to the axis of the outer pipe 2, is orthogonal to the radial direction of the outer pipe 2, and What is necessary is just to connect the 1st piping 6 to the 1st header 4 so that the tangent of an inner peripheral wall surface may intersect with the tangent line of the inner peripheral wall surface of the 1st header 4. FIG. It should be noted that the second header 5 and the second pipe 7 on the refrigerant discharge side, including the connection structure of both, have the same configuration, so that even if the first refrigerant flows in from the second pipe 7, it enters the pores 2a. Since it can distribute equally, the 1st header 4 and the 1st piping 6 are not specified to the inflow side, and the freedom degree of installation of double pipe 1 for heat exchange can be increased. Further, as will be described later, the double pipe heat exchanger 30 is formed by connecting the second pipes 7 of the plurality of adjacent double pipes 1 for heat exchange to the first pipe 6 of the double pipe 1 for adjacent heat exchange. The productivity in the case of manufacturing is also improved.

The inner pipe 3 is made of a copper material, but is not limited to this, and may be appropriately selected according to the second refrigerant. For example, if a stainless alloy having excellent corrosion resistance compared to copper is used. Therefore, the thickness can be reduced and the weight of the heat exchanger can be reduced.
The outer pipe 2, the first and second headers 4 and 5, and the first and second pipes 6 and 7 are made of aluminum alloy, but may be appropriately selected according to the first refrigerant. A stainless alloy, copper, or the like may be used.
Also, the outer tube 2 and the first and second headers 4 and 5 are joined by brazing, and the first and second headers 4 and 5 and the first and second pipes 6 and 7 are joined by brazing. However, pressure welding or eutectic bonding may be used instead of brazing. In particular, since copper pipes are mainly used for piping on the side of the refrigeration equipment, pressure welding other than brazing is used for joining the first and second pipes 6 and 7 made of aluminum alloy and the piping on the side of the refrigeration equipment. Bonding or eutectic bonding is preferred.

Next, a heat pump system using the double pipe heat exchanger 10 will be described.
Example 1.
FIG. 8 is a refrigerant circuit diagram showing Example 1 of the heat pump system using the double-pipe heat exchanger according to Embodiment 1 of the present invention.
In FIG. 8, a heat pump system 20A includes a compressor 21 for compressing the first refrigerant, an expansion valve 23, an outdoor heat exchanger 24, a use-side heat exchanger 25, and a pump 26 for pumping the second refrigerant. And the outdoor air exchanger 24 to supply heat to the outdoor heat exchanger 24 to exchange heat between the first refrigerant circulating in the outdoor heat exchanger 24 and the outside air, and to exchange heat between the first refrigerant and the second refrigerant. A heavy pipe heat exchanger 10. Here, R410A is used as the first refrigerant, and tap water is used as the second refrigerant.

  The refrigerant discharge port of the compressor 21 is connected to the first pipe 6 of the heat exchange double pipe 1 of the double pipe heat exchanger 10, and the second pipe 7 of the heat exchange double pipe 1 is an expansion valve. The outlet of the outdoor heat exchanger 24 is connected to the refrigerant suction port of the compressor 21 through the inlet 23 of the outdoor heat exchanger 24. The first refrigerant circulates in the first refrigerant circuit in the order of the compressor 21 → the pore 2 a of the outer pipe 2 of the double pipe 1 for heat exchange 1 → the expansion valve 23 → the outdoor heat exchanger 24 → the compressor 21. The refrigerant discharge port of the pump 26 is connected to one end of the inner tube 3 of the heat exchange double tube 1 of the double tube heat exchanger 10, and the other end of the inner tube 3 of the heat exchange double tube 1 is connected to the other end. The use side heat exchanger 25 is connected to the inlet, and the use side heat exchanger 25 has an outlet connected to the refrigerant inlet of the pump 26. The second refrigerant circulates in the second refrigerant circuit in the order of the pump 26 → the inner pipe 3 of the heat exchange double pipe 1 → the use-side heat exchanger 25 → the pump 26.

In this heat pump system 20A, the pump 26 is driven, and tap water circulates in the second refrigerant circuit. Then, the first refrigerant becomes a high-temperature and high-pressure refrigerant in the compressor 21 and is introduced into the first header 4 of the double tube 1 for heat exchange, and is distributed to the respective pores 2a. The first refrigerant exchanges heat with the second refrigerant flowing in the inner pipe 3 while flowing in the pores 2a. The first refrigerant is condensed by exchanging heat with the second refrigerant, decompressed by the expansion valve 23, and introduced into the outdoor heat exchanger 24. The second refrigerant introduced into the outdoor heat exchanger 24 is evaporated by exchanging heat with the air blown by the fan 29 and returned to the compressor 21. On the other hand, the second refrigerant heated by exchanging heat with the first refrigerant is returned to the use side heat exchanger 25, dissipated, and returned to the pump 26.
The heat pump system 20A is used as a heating system that uses, for example, a radiator, a floor heating heater, or the like for the use-side heat exchanger 2.

Example 2
FIG. 9 is a refrigerant circuit diagram showing Example 2 of the heat pump system using the double-pipe heat exchanger according to Embodiment 1 of the present invention.
In FIG. 9, the heat pump system 20 </ b> B includes a tank 28 that encloses the use side heat exchanger 25. The heat pump system 20B is configured in the same manner as the heat pump system 20A of the first embodiment, except that the tank 28 is provided.

In this heat pump system 20B, the fluid heated by the heat exchange with the second refrigerant supplied to the tank 28 and flowing through the use side heat exchanger 25 is taken and used for heating or hot water supply.
Therefore, the heating or hot water supply system using the heat pump system 20B has an energy saving effect as compared with the heating or hot water supply system using a conventional boiler as a heat source.

Example 3
FIG. 10 is a refrigerant circuit diagram showing Example 3 of the heat pump system using the double-pipe heat exchanger according to Embodiment 1 of the present invention.
In FIG. 10, in the heat pump system 20 </ b> C, the refrigerant discharge port of the compressor 21 is connected to the inlet of the outdoor heat exchanger 24, and the outlet of the outdoor heat exchanger 24 is connected to the double-tube heat exchanger 10 via the expansion valve 23. Are connected to the first pipe 6 of the double pipe 1 for heat exchange, and the second pipe 7 of the double pipe 1 for heat exchange is connected to the refrigerant suction port of the compressor 21. The first refrigerant circulates in the first refrigerant circuit in the order of the compressor 21 → the outdoor heat exchanger 24 → the expansion valve 23 → the pore 2 a of the outer pipe 2 of the double pipe 1 for heat exchange → the compressor 21. The heat pump system 20C is configured in the same manner as the heat pump system 20A of the first embodiment except that the flow direction of the first refrigerant flowing through the first refrigerant circuit is different.

In this heat pump system 20C, the pump 26 is driven, and tap water circulates in the second refrigerant circuit. Then, the first refrigerant becomes a high-temperature and high-pressure refrigerant in the compressor 21 and is introduced into the outdoor heat exchanger 24. The second refrigerant introduced into the outdoor heat exchanger 24 is condensed by exchanging heat with the air blown by the fan 29, decompressed by the expansion valve 23, and in the first header 4 of the double tube 1 for heat exchange. And distributed to each pore 2a. The first refrigerant exchanges heat with the second refrigerant flowing in the inner pipe 3 while flowing in the pores 2a. The first refrigerant evaporates by exchanging heat with the second refrigerant, and is returned to the compressor 21. On the other hand, the second refrigerant cooled by exchanging heat with the first refrigerant is returned to the use side heat exchanger 25.
The heat pump system 20C is used as, for example, a cooling system using an air heat exchanger as the use-side heat exchanger 2 or a radiant cooling system using a chilled water panel as the use-side heat exchanger 2.

Example 4
FIG. 11 is a refrigerant circuit diagram showing Example 4 of the heat pump system using the double-pipe heat exchanger according to Embodiment 1 of the present invention.
In FIG. 11, the heat pump system 20D includes a four-way valve 22 in the first refrigerant circuit, switches the four-way valve 22, and converts the first refrigerant compressed by the compressor 21 to the outdoor heat exchanger 24 or the double pipe heat exchange. It can be introduced into the vessel 10. The heat pump system 20D is configured in the same manner as the heat pump systems 20A and 20C of the first and third embodiments, except that the four-way valve 22 is provided in the first refrigerant circuit.

The heat pump system 20D operates as a heat pump system 20A by switching the four-way valve 22 so that the high-pressure and high-temperature first refrigerant compressed by the compressor 1 is introduced into the double-pipe heat exchanger 10. By switching the four-way valve 22 so that the high-pressure and high-temperature first refrigerant compressed by the machine 1 is introduced into the outdoor heat exchanger 24, the heat pump system 20C operates. As described above, by incorporating the four-way valve 22, it is possible to switch between warm and cold in one system.
Further, by incorporating the four-way valve 22 into the heat pump system 20B in the second embodiment, it becomes possible to switch between hot water supply and cold water.

  In each of the above embodiments, R410A is used as the first refrigerant, and tap water is used as the second refrigerant. However, the first and second refrigerants are not limited to this, and other examples of the first refrigerant include, for example, A CFC-based refrigerant or a natural refrigerant such as carbon dioxide or hydrocarbon may be used, and the same refrigerant as the brine or the first refrigerant may be used as the second refrigerant. Further, the circulation direction of the second refrigerant may be set in a timely manner so as to be parallel flow or counter-current with the first refrigerant flowing through the heat exchange double pipe 1.

Embodiment 2. FIG.
12 is a perspective view showing a double tube for heat exchange applied to a double tube heat exchanger according to Embodiment 2 of the present invention, and FIG. 13 is a double tube type according to Embodiment 2 of the present invention. FIG. 14 is a perspective view showing a state in which one header of a double pipe for heat exchange applied to a heat exchanger is omitted, and FIG. 14 shows heat applied to the double pipe heat exchanger according to Embodiment 2 of the present invention. FIG. 15 is a cross-sectional view illustrating the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe heat exchanger according to Embodiment 2 of the present invention. FIG. 16 is a longitudinal sectional view for explaining the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe heat exchanger according to Embodiment 2 of the present invention.

  12 to 14, an outer tube 11 as a first tube has a cylindrical large-diameter portion 11a having a predetermined thickness and a thin cylindrical small-diameter portion 11b projecting coaxially at both ends of the large-diameter portion 11a. The center hole is made of an aluminum alloy stepped tube having a central axis, and the pore 11c as a pipe passes through the large diameter portion 11a with the hole direction parallel to the axial center. For example, 12 pieces are formed on the same circumference at an equiangular pitch so as to open at the end face of the large diameter portion 11a. The first and second headers 4 and 5 are inserted into the through holes 4a and 5a through the small diameter portion 11b of the outer tube 11, and the inner wall surfaces of the through holes 4a and 5a are joined to the outer wall surface of the small diameter portion 11b. Are joined to the radially outer end face of the region where the pores 11c of the large diameter part 11a are formed, and are provided coaxially on both end parts of the outer tube 11, respectively. The heat exchanging double pipe 1A configured in this manner is the same as the heat exchanging double pipe 1 according to the first embodiment except that the outer pipe 11 is used instead of the outer pipe 2. It is configured.

  In the heat exchanging double pipe 1A, the first and second header spaces 9a and 9b are composed of first and second headers 4 and 5 and an outer pipe 11. That is, the inner peripheral walls of the first and second header spaces 9 a and 9 b are constituted by the small diameter portion 11 b that is a part of the outer tube 11. Therefore, even if the copper inner pipe 3 corrodes and cracks and pinholes occur in the inner pipe 3, the second refrigerant flowing in the inner pipe 3 flows into the first and second header spaces 9a and 9b. Is blocked by the small diameter portion 11b, and mixing of the first refrigerant and the second refrigerant is reliably prevented.

In the heat exchange double pipe 1A configured as described above, the first pipe 6 is connected to the discharge pipe of the first cooling / heating apparatus and the second pipe 7 is connected to the first cooling / heating apparatus, as in the first embodiment. Connected to the suction pipe, one end of the inner pipe 3 is connected to the discharge pipe of the second cooling device, the other end of the inner pipe 3 is connected to the suction pipe of the second cooling device, and the first refrigerant and the second refrigerant are It is applied as a double tube heat exchanger for heat exchange.
Also in this heat exchange double pipe 1A, as indicated by an arrow in FIG. 15, the first refrigerant 8 introduced into the first header 4 from the first pipe 6 has a swirl component in the circumferential direction. And the 1st refrigerant | coolant 8 becomes an annular flow of the liquid film (refrigerant liquid 8a) of the substantially uniform thickness along the inner peripheral wall surface of the 1st header 4, and the refrigerant | coolant vapor | steam 8b with a centrifugal force. Then, as indicated by arrows in FIG. 16, the first refrigerant 8 is accompanied by the refrigerant vapor 8b, reaches the end surface of the large diameter portion 11a of the outer tube 11, and is evenly distributed to the respective pores 11c. .

  Here, the outer tube 11 is made by, for example, extruding an aluminum alloy to produce a cylindrical tube having a predetermined thickness in which the pores 11c are formed, and then cutting the tube while rotating the tube around the axis. And the thickness of both ends of the tube body is reduced.

Embodiment 3 FIG.
FIG. 17 is a perspective view showing a heat exchange double pipe applied to a double pipe heat exchanger according to Embodiment 3 of the present invention, and FIG. 18 is a double pipe type according to Embodiment 3 of the present invention. FIG. 19 is a partially broken perspective view illustrating a header structure of a double pipe for heat exchange applied to a heat exchanger, and FIG. 19 is a heat exchange applied to a double pipe heat exchanger according to Embodiment 3 of the present invention. FIG. 20 is a cross-sectional view illustrating the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe heat exchanger according to Embodiment 3 of the present invention. 21 and 21 are longitudinal sectional views for explaining the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe heat exchanger according to Embodiment 3 of the present invention.

  17 to 19, an outer tube 12 as a first tube is made of a cylindrical tube body 12a having a predetermined thickness and made of an aluminum alloy having a center hole drilled at an axial center position. An annular groove 12b is coaxially recessed at both ends of the tube body 12a, and the pore 12c passes through the tube body 12a with the hole direction parallel to the axis and opens at the bottom of the groove 12b. Twelve, for example, are formed on the same circumference at an equiangular pitch. The 1st and 2nd piping 6 and 7 is joined to the outer peripheral wall surface of the both ends side of the pipe body 12a. The end plate 13 is made of an aluminum alloy disk having a through hole 13a drilled at the center position, joined to both end faces of the tube body 12a, and closes the opening of the concave groove 12b. The heat exchanging double pipe 1B configured as described above has the above-described first embodiment except that the outer pipe 12 is used instead of the outer pipe 2 and the first and second headers 4 and 5. It is comprised similarly to the double tube 1 for heat exchange by. The end plate 13 cooperates with the outer tube 12 to function as first and second headers that define the first and second header spaces 9a and 9b.

  In the heat exchange double pipe 1B, the first and second header spaces 9a and 9b are configured by closing the concave groove 12b of the pipe body 12a with the end plate 13. Therefore, the first and second header spaces 9a and 9b can be configured with a simple structure. Furthermore, even if the copper inner pipe 3 corrodes and cracks and pinholes occur in the inner pipe 3, the second refrigerant flowing in the inner pipe 3 flows into the first and second header spaces 9a and 9b. Is blocked by the outer tube 12, and mixing of the first refrigerant and the second refrigerant is reliably prevented.

In the double tube for heat exchange 1B configured as described above, the first pipe 6 is connected to the discharge pipe of the first cooling / heating device and the second pipe 7 is connected to the first cooling / heating device, as in the first embodiment. Connected to the suction pipe, one end of the inner pipe 3 is connected to the discharge pipe of the second cooling device, the other end of the inner pipe 3 is connected to the suction pipe of the second cooling device, and the first refrigerant and the second refrigerant are It is applied as a double tube heat exchanger for heat exchange.
Also in this double tube for heat exchange 1B, as indicated by an arrow in FIG. 20, the first refrigerant 8 introduced from the first pipe 6 into the concave groove 12b has a swirl component in the circumferential direction. And the 1st refrigerant | coolant 8 becomes an annular flow of the liquid film (refrigerant liquid 8a) of the substantially uniform thickness along the inner peripheral wall surface of the ditch | groove 12b, and the refrigerant | coolant vapor | steam 8b with a centrifugal force. Then, as indicated by arrows in FIG. 21, the first refrigerant 8 is accompanied by the refrigerant vapor 8b, reaches the bottom surface of the concave groove 12b of the outer tube 12, and is evenly distributed to the respective pores 12c.

  Here, the outer tube 12 is formed by, for example, extruding an aluminum alloy to produce a cylindrical tube 12a having a predetermined thickness in which the pores 12c are formed, and then rotating the tube 12a around the axis. Cutting is performed from the outside in the axial direction, and annular concave grooves 12b having a predetermined groove width are formed at both ends of the tube body 12a.

Embodiment 4 FIG.
22 is a longitudinal sectional view showing a double tube for heat exchange applied to a double tube heat exchanger according to Embodiment 4 of the present invention, and FIG. 23 is a sectional view taken along arrow XXIII-XXIII in FIG. .

  22 and FIG. 23, an outer tube 14 as a first tube is formed from a cylindrical large-diameter portion 14a having a predetermined thickness and a thin cylindrical small-diameter portion 14b that protrudes coaxially from both ends of the large-diameter portion 14a. The center hole 14d is made of an aluminum alloy stepped tube having an axial center, and the pore 14c passes through the large diameter portion 14a with the hole direction parallel to the axial center. Twelve, for example, are formed on the same circumference at an equiangular pitch so as to open at the end face of the same. A corrosion-resistant layer 15 is covered on the entire inner wall surface of the center hole 14 d of the outer tube 14. The first and second headers 4 and 5 are inserted into the through holes 4a and 5a through the small diameter portion 14b of the outer tube 14, and the inner wall surfaces of the through holes 4a and 5a are joined to the outer wall surface of the small diameter portion 14b. Are joined to the radially outer end face of the region where the pores 14c of the large diameter portion 14a are formed, and are coaxially provided at both ends of the large diameter portion 14a of the outer tube 14. The double tube for heat exchange 1C configured in this way is the double tube for heat exchange according to the first embodiment except that the outer tube 14 is used instead of the outer tube 2 and the inner tube 3. The configuration is the same as that of the tube 1.

  In the heat exchanging double pipe 1C configured as described above, the first pipe 6 is connected to the discharge pipe of the first cooling / heating apparatus and the second pipe 7 is connected to the first cooling / heating apparatus as in the first embodiment. Connected to the suction pipe, one small-diameter portion 14b of the outer pipe 14 is connected to the discharge pipe of the second cooling / heating device, and the other small-diameter portion 14b is connected to the suction piping of the second cooling / heating device. It is applied as a double tube heat exchanger that exchanges heat with a refrigerant.

Also in this double tube for heat exchange 1C, the first refrigerant can be evenly distributed to each pore 14c, as in the first embodiment.
Further, in this double tube for heat exchange 1C, the second refrigerant is circulated through the central hole 14d of the outer tube 14 in which the corrosion resistant layer 15 is coated on the entire inner peripheral wall surface, so that the inner tube 3 is not required, The weight of the heat exchanger can be reduced.

In addition, as the corrosion-resistant layer 15, a metal material that is electrochemically lower than the outer tube 14 that is a base material can be used. When the outer tube 14 is an aluminum alloy or aluminum, for example, magnesium is included. Metal materials can be used. Then, for example, the outer tube may be manufactured using a clad material formed by coating a metal material containing magnesium on the surface of an aluminum alloy or aluminum. In this case, a flat clad material provided with pores 14c may be formed into a cylindrical shape by roll forming or the like, and the seam may be connected by electro-sealing welding or the like. Moreover, after producing an outer tube | pipe with a base material, plating may be given to the inner peripheral wall surface of the center hole of an outer tube | pipe, and a corrosion-resistant layer may be formed.
Further, instead of the metal material, a resin such as polyethylene may be coated on the entire inner wall surface of the center hole 14d of the outer tube 14 to form a corrosion resistant layer.

Embodiment 5 FIG.
FIG. 24 is a longitudinal sectional view showing a double tube for heat exchange applied to a double tube heat exchanger according to Embodiment 5 of the present invention.

  In FIG. 24, the outer tube 16 as the first tube is composed of a cylindrical large-diameter portion 16a having a predetermined thickness and a thin cylindrical small-diameter portion 16b projecting coaxially from both ends of the large-diameter portion 16a. The center hole 16e is made of an aluminum alloy stepped tube having an axial center, and an annular groove 16c as an annular groove is formed concentrically at both ends of the large diameter portion 16a. For example, 12 pieces are formed at an equiangular pitch on the same circumference so that 16d penetrates the large diameter portion 16a with the hole direction parallel to the axis and opens at the bottom of the groove 16c. The 1st and 2nd piping 6 and 7 is joined to the outer peripheral wall surface of the both ends side of the large diameter part 16a. The end plate 13 is made of an aluminum alloy disc having a through hole 13a drilled at the center position, joined to both end faces of the large diameter portion 16a and the outer peripheral wall surface of the small diameter portion 16b, and opens the groove 16c. The mouth is closed. Further, the corrosion resistant layer 15 is covered on the entire inner peripheral wall surface of the center hole 16 e of the outer tube 16. Note that the double tube for heat exchange 1D configured in this way uses an outer tube 16 and an end plate 13 in place of the outer tube 2, the inner tube 3, and the first and second headers 4 and 5. Except for this, it is configured in the same manner as the heat exchanging double pipe 1 according to the first embodiment.

  In the heat exchange double pipe 1D configured in this way, the first pipe 6 is connected to the discharge pipe of the first cooling / heating apparatus and the second pipe 7 is connected to the first cooling / heating apparatus, as in the first embodiment. Connected to the suction pipe, one small-diameter portion 16b of the outer pipe 16 is connected to the discharge pipe of the second cooling / heating device, and the other small-diameter portion 16b is connected to the suction piping of the second cooling / heating device. It is applied as a double tube heat exchanger that exchanges heat with a refrigerant.

Also in this double tube for heat exchange 1D, similarly to the first embodiment, the first refrigerant can be evenly distributed to the respective pores 16d.
Further, in this double tube for heat exchange 1D, since the second refrigerant is circulated through the central hole 16e of the outer tube 16 in which the corrosion-resistant layer 15 is coated on the entire inner wall surface, the inner tube 3 is not required, The weight of the heat exchanger can be reduced.
Further, since the first and second header spaces 9a and 9b are configured by closing the concave grooves 16c of the large diameter portion 16a with the end plates 13, the first and second header spaces 9a and 9b have a simple structure. Can be configured.

Embodiment 6 FIG.
FIG. 25 is a side view showing a double-pipe heat exchanger according to Embodiment 6 of the present invention.
In FIG. 25, the double-pipe heat exchanger 30 includes an inner tube 3 in which four heat-exchange double tubes 1 connected by one inner tube 3 connect adjacent heat-exchange double tubes 1. Are bent into a U-shape, and the outer pipes 2 are arranged in a row adjacent to each other so that the first header 4 and the second header 5 face each other with the axial centers of the outer pipes 2 being parallel to each other on the same plane. The second pipe 7 of the heat exchange double pipe 1 is connected to the adjacent first pipe 6 of the heat exchange double pipe 1. Here, the double-pipe heat exchanger 30 is assumed to be composed of four heat-exchange double tubes 1, but the number of heat-exchange double tubes 1 is appropriately set according to the required heat exchange capacity. Is done.

In the double-pipe heat exchanger 30 configured as described above, the first pipe 6 of the first heat-exchange double pipe 1 in the arrangement direction is the discharge pipe of the first cooling device, as in the first embodiment. The second pipe 7 of the last heat exchange double pipe 1 in the arrangement direction is connected to the suction pipe of the first cooling device, and one end of the inner pipe 3 is connected to the discharge pipe of the second cooling device, The other end of the inner pipe 3 is connected to a suction pipe of a second cooling / heating device, and is applied as a double pipe heat exchanger for exchanging heat between the first refrigerant and the second refrigerant.
Then, the first refrigerant flows in from the first pipe 6 of the first heat exchange double pipe 1 in the arrangement direction, and sequentially flows through the pores 2a of the four heat exchange double pipes 1 to the last in the arrangement direction. It flows out from the second pipe 7 of the double pipe 1 for heat exchange. At this time, the first refrigerant is evenly distributed to the pores 2a of the heat exchange double tubes 1, and the heat transfer performance of the heat exchange heat exchanger 1 is prevented from being lowered.

Next, a method for manufacturing the double tube heat exchanger 30 will be described.
First, the outer tube 2, the inner tube 3, the first and second headers 4, 5, and the first and second pipes 6, 7 that are components of the double tube 1 for heat exchange are prepared. Then, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5. Next, the first and second headers 4 and 5 are joined to both ends of the outer tube 2 to produce a heat exchange main body 31 as shown in FIG. Next, the inner pipe 3 is inserted into the outer pipes 2 of the four heat exchange main body parts 31, and then the inner pipe 3 is expanded, and the four heat exchange main body parts 31 are connected to the outer pipes 2 as shown in FIG. A heat exchanger assembly 32 in which the inner tube 3 is brought into thermal contact with each other and connected integrally is manufactured. Next, the portion between the adjacent heat exchange main body portions 31 of the inner tube 3 of the heat exchanger assembly 32 is bent, and as shown in FIG. 25, the axes of the outer tube 2 are parallel to each other on the same plane, Four heat exchange main body portions 31 are arranged adjacent to each other so that the first header 4 and the second header 5 face each other. Then, the 2nd piping 7 of each heat exchange main-body part 31 is connected to the 1st piping 6 of the heat exchange main-body part 31 located adjacently, and the double pipe type heat exchanger 30 is produced.

According to this manufacturing method, since the diameter of the inner tube 3 is smaller than the diameter of the outer tube 2, the inner tube 3 can be bent with a small radius of curvature, and the same heat exchange length can be set to one heat exchange duplex. The size can be reduced as compared with the case where the tube 1 is used.
In addition, although the process of joining the first and second pipes 6 and 7 to the first and second headers 4 and 5 is described as the first process, this process does not need to be performed first, It may be performed prior to the connection step between the first pipe 6 and the second pipe 7 of the heat exchange main body 31 arranged adjacent to each other in one row.

  Here, in Embodiment 6 described above, the double-pipe heat exchanger 30 is configured such that the axial centers of the outer pipes 2 are parallel to each other on the same plane and the first header 4 and the second header 5 are opposed to each other. In addition, it is assumed that the double tubes for heat exchange 1 are arranged adjacent to each other in four rows and columns, but the arrangement of the double tubes for heat exchange 1 is not limited to this, for example, As shown in FIG. 28, the bending direction of the inner tube 3 is displaced by 90 degrees, the axes of the outer tube 2 are parallel to each other, and the first header 4 and the second header 5 are opposed to each other. The replacement double tubes 1 may be arranged adjacent to each other in two columns and two rows. In this way, by changing the bending direction and bending angle of the inner tube 3, the arrangement of the heat exchange double tubes 1 can be adjusted to the storage space. Therefore, according to this manufacturing method, the heat exchanger can be miniaturized, and a heat exchanger having a shape matched to the storage space can be easily manufactured. Moreover, the productivity of the connection process of the adjacent 1st piping 6 and the 2nd piping 7 improves by making the 1st header 4 and the 1st piping 6 and the 2nd header 5 and the 2nd piping 7 into the same structure.

Embodiment 7 FIG.
Although the double-pipe heat exchanger according to the seventh embodiment is not shown, the double-tube heat exchanger 1A according to the second embodiment is used in place of the double-tube 1 for heat exchange. Except for this, the configuration is the same as in the sixth embodiment.
Therefore, the double-pipe heat exchanger according to the seventh embodiment operates in the same manner as the double-pipe heat exchanger 30 according to the sixth embodiment and has the same effects.

Next, a method for manufacturing the double pipe heat exchanger will be described.
First, the outer tube 11, the inner tube 3, the first and second headers 4 and 5, and the first and second pipes 6 and 7 that are components of the heat exchange double tube 1 </ b> A are prepared. Then, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5. Next, the first and second headers 4 and 5 are joined to both ends of the outer tube 11 to produce a heat exchange main body. Next, four inner pipes 3 are inserted into the outer pipe 11 of the heat exchange main body, and then the inner pipe 3 is expanded, and the four heat exchange main bodies are brought into thermal contact with each of the outer pipe 11 and the inner pipe 3. Thus, a heat exchanger assembly connected integrally is produced. Next, a portion between adjacent heat exchange main body portions of the inner tube 3 of the heat exchanger assembly is bent so that the axes of the outer tube 11 are parallel to each other on the same plane, and the first header 4 and the second header 5 Are arranged so that the four heat exchange main body portions are adjacent to each other in four rows and one column. Then, the 2nd piping 7 of each heat exchange main-body part is connected to the 1st piping 6 of the heat exchange main-body part located next, and a double tube type heat exchanger is produced.

Also in this manufacturing method, since the diameter of the inner tube 3 is smaller than the diameter of the outer tube 2, the inner tube 3 can be bent with a small radius of curvature, and the same heat exchange length is set to one heat exchange double tube. The size can be reduced as compared with the case of 1A.
In addition, although the process of joining the first and second pipes 6 and 7 to the first and second headers 4 and 5 is described as the first process, this process does not need to be performed first, It may be performed prior to the connection step between the first pipe 6 and the second pipe 7 of the heat exchange main body 31 arranged adjacent to each other in one row.

Embodiment 8 FIG.
The double pipe heat exchanger according to the eighth embodiment is the same as that of the above embodiment except that the double pipe 1B for heat exchange according to the third embodiment is used instead of the double pipe 1 for heat exchange. The configuration is the same as in the sixth embodiment.
Therefore, the double-pipe heat exchanger according to the eighth embodiment operates in the same manner as the double-pipe heat exchanger 30 according to the sixth embodiment and has the same effects.

Next, a method for manufacturing the double pipe heat exchanger will be described.
First, the outer pipe 12, the inner pipe 3, the first and second pipes 6 and 7, and the end plate 13 which are components of the heat exchange double pipe 1B are prepared. Then, the first and second pipes 6 and 7 are joined to the outer pipe 12. Next, the end plate 13 is joined to both ends of the outer tube 12 to produce a heat exchange main body. Next, four inner tubes 3 are inserted into the outer tube 12 of the heat exchange main body, and then the inner tube 3 is expanded, and the four heat exchange main portions are brought into thermal contact with each outer tube 12 and the inner tube 3. Thus, a heat exchanger assembly connected integrally is produced. Next, a portion between adjacent heat exchange main body portions of the inner pipe 3 of the heat exchanger assembly is bent so that the axial centers of the outer pipes 12 are parallel to each other on the same plane, and the first pipe 6 and the second pipe 7 Are arranged so that the four heat exchange main body portions are adjacent to each other in four rows and one column. Then, the 2nd piping 7 of each heat exchange main-body part is connected to the 1st piping 6 of the heat exchange main-body part located next, and a double tube type heat exchanger is produced.

Also in this manufacturing method, since the diameter of the inner tube 3 is smaller than the diameter of the outer tube 2, the inner tube 3 can be bent with a small radius of curvature, and the same heat exchange length is set to one heat exchange double tube. The size can be reduced as compared with the case of 1B.
In addition, although the process of joining the first and second pipes 6 and 7 to the outer pipe 12 is described as the first process, this process does not need to be performed first and is adjacent to one line. It may be performed prior to the connecting step between the first pipe 6 and the second pipe 7 of the arranged heat exchange main body.

Embodiment 9 FIG.
FIG. 29 is a side view showing a double-pipe heat exchanger according to Embodiment 9 of the present invention.
In FIG. 29, a double-tube heat exchanger 35 includes two sets of heat exchangers in which two heat-exchange double tubes 1 are connected by a hairpin tube 36 bent into a U shape as an inner tube. Assemblies 38 are arranged in a row adjacent to each other so that the first header 4 and the second header 5 face each other with the axis of the outer tube 2 parallel to each other on the same plane. The other end and one end of the other hairpin pipe 36 are connected by a U vent pipe 37, and the second pipe 7 of the heat exchange double pipe 1 is connected to the adjacent first pipe 6 of the heat exchange double pipe 1. Configured. Here, it is assumed that the double-tube heat exchanger 35 is composed of four heat-exchange double tubes 1, but the number of heat-exchange double tubes 1 is appropriately set according to the required heat exchange capacity. Is done.

In the double-pipe heat exchanger 35 configured as described above, the first pipe 6 of the first heat-exchange double pipe 1 in the arrangement direction is the discharge pipe of the first cooling / heating device, as in the first embodiment. The second pipe 7 of the last heat exchange double pipe 1 in the arrangement direction is connected to the suction pipe of the first cooling device, and one end of the hairpin tube 36 is connected to the discharge pipe of the second cooling device, The other end of the hairpin tube 36 is connected to the suction pipe of the second cooling device, and is applied as a double tube heat exchanger that exchanges heat between the first refrigerant and the second refrigerant.
Then, the first refrigerant flows in from the first pipe 6 of the first heat exchange double pipe 1 in the arrangement direction, and sequentially flows through the pores 2a of the four heat exchange double pipes 1 to the last in the arrangement direction. It flows out from the second pipe 7 of the double pipe 1 for heat exchange. At this time, the first refrigerant is evenly distributed to the pores 2a of the heat exchange double tubes 1, and the heat transfer performance of the heat exchange heat exchanger 1 is prevented from being lowered.

Next, a method for manufacturing the double pipe heat exchanger 35 will be described.
First, the outer pipe 2, the hairpin pipe 36, the first and second headers 4 and 5, the first and second pipes 6 and 7, and the U vent pipe 37, which are constituent parts of the heat exchange double pipe 1, are prepared. . Then, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5. Next, the first and second headers 4 and 5 are joined to both ends of the outer tube 2 to produce the heat exchange main body 31. Next, the hairpin tubes 36 are inserted into the outer tubes 2 of the two heat exchange main body portions 31, and then the hairpin tubes 36 are expanded. The two heat exchange main body portions 31 thermally connect the outer tubes 2 and the hairpin tubes 36. The heat exchanger assembly 38 is manufactured in close contact with each other. Next, as shown in FIG. 30, the four heat exchange main body portions 31 are adjacent so that the axial centers of the outer tubes 2 are parallel to each other on the same plane and the first header 4 and the second header 5 face each other. The two heat exchanger assemblies 38 are arranged so that they are arranged in a row. Thereafter, the hairpin tubes 36 are connected to each other by a U vent tube 37, and the second pipe 7 of each heat exchange main body 31 is connected to the first pipe 6 of the heat exchange main body 31 located adjacent thereto, as shown in FIG. A double tube heat exchanger 35 is produced.

  According to this manufacturing method, since the diameter of the hairpin tube 36 and the U vent tube 37 as the inner tube is smaller than the diameter of the outer tube 2, the hairpin tube 36 and the U vent tube 37 can be bent with a small radius of curvature. As compared with the case where the same heat exchange length is constituted by one heat exchange double tube 1, the size can be reduced. Further, the hairpin tube 36 that is bent in advance is inserted into the outer tube 2 of the heat exchange main body 31, and the hairpin tubes 36 of the adjacent heat exchanger assemblies 38 are connected to each other using the U bend tube 37 that is bent in advance. Therefore, productivity improves more compared with the manufacturing method which bends the part between the adjacent heat exchange main-body parts 31 of the inner tube | pipe 3 of the heat exchanger assembly 32 described in the said Embodiment 6. FIG.

  In addition, although the process of joining the first and second pipes 6 and 7 to the first and second headers 4 and 5 is described as the first process, this process does not need to be performed first, It may be performed prior to the connecting step between the first pipe 6 and the second pipe 7 of the heat exchange main body 31 arranged adjacent to each other. Moreover, the connection process of the 1st piping 6 and the 2nd piping 7 of the heat exchange main-body part 31 in each heat exchanger assembly 38 may be implemented in which step of the said process. Moreover, the productivity of the connection process of the adjacent 1st piping 6 and the 2nd piping 7 improves by making the 1st header 4 and the 1st piping 6 and the 2nd header 5 and the 2nd piping 7 into the same structure.

  Here, in the ninth embodiment, the double-pipe heat exchanger 35 is configured so that the two heat exchanger assemblies 38 are parallel to each other, the axes of the outer tubes 2 are parallel to each other on the same plane, and It is assumed that the heat exchange double pipes 1 are arranged adjacent to each other in one column and four rows so that the first header 4 and the second header 5 face each other. For example, as shown in FIG. 31, the four heat exchanger assemblies 38 are parallel to each other, the axes of the outer tubes 2 are parallel to each other, and the first header is not limited thereto. The double tubes 1 for heat exchange may be arranged adjacent to each other in 2 columns and 4 rows so that 4 and the second header 5 face each other. In this way, by changing the arrangement of the heat exchanger assemblies 38, the arrangement of the heat exchange double tubes 1 can be adjusted to the storage space. Therefore, according to this manufacturing method, the heat exchanger can be miniaturized, and a heat exchanger having a shape matched to the storage space can be easily manufactured.

Embodiment 10 FIG.
The double pipe heat exchanger according to the tenth embodiment is the same as that of the above embodiment except that the double pipe 1A for heat exchange according to the second embodiment is used instead of the double pipe 1 for heat exchange. The configuration is the same as in the ninth embodiment.
Therefore, the double-pipe heat exchanger according to the tenth embodiment operates in the same manner as the double-pipe heat exchanger 35 according to the ninth embodiment and has the same effects.

Next, a method for manufacturing the double pipe heat exchanger will be described.
First, the outer tube 11, which is a component of the heat exchanging double tube 1A, the hairpin tube 36 as the inner tube, the first and second headers 4, 5, the first and second piping 6, 7, and the U vent tube 37 Is prepared. Then, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5. Next, the first and second headers 4 and 5 are joined to both ends of the outer tube 11 to produce a heat exchange main body. Next, the hairpin tube 36 is inserted into the outer tube 2 of the two heat exchange main body portions, and then the hairpin tube 36 is expanded, and the two heat exchange main body portions are brought into thermal contact with each outer tube 2 and the hairpin tube 36. Thus, a heat exchanger assembly connected integrally is produced. Next, the four heat exchange main body parts are arranged in a row adjacent to each other so that the axial centers of the outer pipes 2 are parallel to each other on the same plane, and the first header 4 and the second header 5 face each other. Line up two sets of heat exchanger assemblies. Thereafter, the hairpin pipes 36 are connected to each other by a U vent pipe 37, and the second pipe 7 of each heat exchange main body is connected to the first pipe 6 of the heat exchange main body located next to the double pipe heat exchanger. Is produced.

  According to this manufacturing method, since the diameter of the hairpin tube 36 and the U vent tube 37 as the inner tube is smaller than the diameter of the outer tube 2, the hairpin tube 36 and the U vent tube 37 can be bent with a small radius of curvature. As compared with the case where the same heat exchange length is constituted by one heat exchange double tube 1, the size can be reduced. Moreover, the hairpin tube 36 previously bent is inserted into the outer tube 11 of the heat exchange main body, and the hairpin tubes 36 of adjacent heat exchanger assemblies are connected to each other by using a U-bend tube 37 bent in advance. Therefore, productivity improves more compared with the manufacturing method which bends the part between the adjacent heat exchange main-body parts 31 of the inner tube | pipe 3 of the heat exchanger assembly 32 described in the said Embodiment 6. FIG.

  In addition, although the process of joining the first and second pipes 6 and 7 to the first and second headers 4 and 5 is described as the first process, this process does not need to be performed first, What is necessary is just to be implemented prior to the connection process of the 1st piping 6 and the 2nd piping 7 of the heat exchange main-body part arranged adjacently. Moreover, the connection process of the 1st piping 6 and the 2nd piping 7 of the heat exchange main-body part in each set of heat exchanger assembly may be implemented in any step of the said process. Moreover, the productivity of the connection process of the adjacent 1st piping 6 and the 2nd piping 7 improves by making the 1st header 4 and the 1st piping 6 and the 2nd header 5 and the 2nd piping 7 into the same structure.

Embodiment 11 FIG.
The double-pipe heat exchanger according to the eleventh embodiment is the same as that of the above embodiment except that the double-tube 1B for heat exchange according to the third embodiment is used instead of the double tube 1 for heat exchange. The configuration is the same as in the ninth embodiment.
Therefore, the double-pipe heat exchanger according to the eleventh embodiment operates in the same manner as the double-pipe heat exchanger 35 according to the ninth embodiment and has the same effects.

Next, a method for manufacturing the double pipe heat exchanger will be described.
First, the outer tube 12, which is a component of the heat exchanging double tube 1B, the hairpin tube 36 as the inner tube, the first and second pipes 6 and 7, the end plate 13, and the U vent tube 37 are prepared. Then, the first and second pipes 6 and 7 are joined to the outer pipe 12. Next, the end plate 13 is joined to both ends of the outer tube 12 to produce a heat exchange main body. Next, the hairpin tube 36 is inserted into the outer tube 2 of the two heat exchange main body portions, and then the hairpin tube 36 is expanded, and the two heat exchange main body portions are brought into thermal contact with each outer tube 2 and the hairpin tube 36. Thus, a heat exchanger assembly connected integrally is produced. Next, the four heat exchange main body parts are arranged in a row adjacent to each other so that the axial centers of the outer pipes 2 are parallel to each other on the same plane, and the first header 4 and the second header 5 face each other. Line up two sets of heat exchanger assemblies. Thereafter, the hairpin pipes 36 are connected to each other by a U vent pipe 37, and the second pipe 7 of each heat exchange main body is connected to the first pipe 6 of the heat exchange main body located next to the double pipe heat exchanger. Is produced.

  According to this manufacturing method, since the diameter of the hairpin tube 36 and the U vent tube 37 as the inner tube is smaller than the diameter of the outer tube 2, the hairpin tube 36 and the U vent tube 37 can be bent with a small radius of curvature. As compared with the case where the same heat exchange length is constituted by one heat exchange double tube 1, the size can be reduced. In addition, the hairpin tube 36 that is bent in advance is inserted into the outer tube 12 of the heat exchange main body, and the hairpin tubes 36 of the adjacent heat exchanger assemblies are connected to each other using a U-bend tube 37 that is bent in advance. Therefore, productivity improves more compared with the manufacturing method which bends the part between the adjacent heat exchange main-body parts 31 of the inner tube | pipe 3 of the heat exchanger assembly 32 described in the said Embodiment 6. FIG.

  In addition, although the process of joining the first and second pipes 6 and 7 to the first and second headers 4 and 5 is described as the first process, this process does not need to be performed first, What is necessary is just to be implemented prior to the connection process of the 1st piping 6 and the 2nd piping 7 of the heat exchange main-body part arranged adjacently. Moreover, the connection process of the 1st piping 6 and the 2nd piping 7 of the heat exchange main-body part in each set of heat exchanger assembly may be implemented in any step of the said process.

Embodiment 12 FIG.
In the ninth embodiment, a double-tube heat exchanger 35 is configured by arranging two heat exchanger assemblies 38 formed by connecting two heat-exchange double tubes 1 with hairpin tubes 36. However, in this twelfth embodiment, two sets of heat exchanger assemblies 38A formed by connecting four heat exchange double tubes 1 with hairpin tubes 36 are arranged to form a double tube heat exchanger 35A. Is configured.

  In the twelfth embodiment, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5. Next, the first and second headers 4 and 5 are joined to both ends of the outer tube 2 to produce the heat exchange main body 31. Next, the hairpin tubes 36 are inserted into the outer tubes 2 of the four heat exchange main body portions 31, and then the hairpin tubes 36 are expanded. The four heat exchange main body portions 31 thermally connect the outer tubes 2 and the hairpin tubes 36. The heat exchanger assembly 38A that is brought into close contact with each other is manufactured. Next, as shown in FIG. 33, the eight heat exchange main body portions 31 are adjacent so that the axial centers of the outer pipes 2 are parallel to each other on the same plane and the first header 4 and the second header 5 face each other. The two sets of heat exchanger assemblies 38A are arranged so that they are arranged in a row. Thereafter, the hairpin tubes 36 are connected to each other by a U vent tube 37, and the second pipe 7 of each heat exchange main body portion 31 is connected to the first pipe 6 of the heat exchange main body portion 31 located adjacent thereto, as shown in FIG. A double tube heat exchanger 35A is produced.

  The double-tube heat exchanger 35A configured in this way has two sets of heat formed by connecting four heat-exchange double tubes 1 with U-shaped hairpin tubes 36 as inner tubes. The exchanger assembly 38A is arranged in a row adjacent to each other so that the first header 4 and the second header 5 face each other with the axis of the outer tube 2 parallel to each other on the same plane, and one hairpin tube The other end of 36 and one end of the other hairpin pipe 36 are connected by a U vent pipe 37, and the second pipe 7 of the heat exchange double pipe 1 is connected to the adjacent first pipe 6 of the heat exchange double pipe 1. It is connected.

Therefore, this double tube heat exchanger 35A can increase the number of heat exchange double tubes 1 and increase the heat exchange capacity compared to the double tube heat exchanger 35 according to the ninth embodiment. can do.
Also in the twelfth embodiment, the heat exchange double pipes 1A and 1B can be used in place of the heat exchange double pipe 1, and the number of heat exchange double pipes 1 and the heat exchanger assembly By changing the arrangement of the three-dimensional body 38A, it is possible to easily manufacture a heat exchanger that matches the required heat exchange capacity and storage space.

Embodiment 13 FIG.
FIG. 34 is a side view showing a double-pipe heat exchanger according to Embodiment 13 of the present invention.
In FIG. 34, a double pipe heat exchanger 40 has four heat exchange double pipes 1 such that the axis of the outer pipe 2 is parallel to each other on the same plane, and the first header 4 and the second header 5 Of the inner pipes 3 of the adjacent heat exchange double pipes 1 so that the first and second refrigerants flow in series through the four heat exchange double pipes 1 so as to face each other. The ends and the first pipe 6 and the second pipe 7 are connected to each other.

In the double-pipe heat exchanger 40 configured as described above, the first pipe 6 of the first heat-exchange double pipe 1 in the arrangement direction is the discharge pipe of the first refrigeration equipment, as in the first embodiment. , The second pipe 7 of the last heat exchange double pipe 1 in the arrangement direction is connected to the suction pipe of the first refrigeration equipment, and one end of the inner pipe 3 connected in series is discharged from the second refrigeration equipment. Connected to the pipe, the other end of the inner pipe 3 is connected to the suction pipe of the second cooling / heating device, and is applied as a double pipe heat exchanger for exchanging heat between the first refrigerant and the second refrigerant.
Then, the first refrigerant flows in from the first pipe 6 of the first heat exchange double pipe 1 in the arrangement direction, and sequentially flows through the pores 2a of the four heat exchange double pipes 1 to the last in the arrangement direction. It flows out from the second pipe 7 of the double pipe 1 for heat exchange. At this time, the first refrigerant is evenly distributed to the pores 2a of the heat exchange double tubes 1, and the heat transfer performance of the heat exchange heat exchanger 1 is prevented from being lowered.

Next, a method for manufacturing the double tube heat exchanger 40 will be described.
First, the outer tube 2, the inner tube 3, the first and second headers 4 and 5, the first and second pipes 6 and 7, and the U vent tube 37, which are components of the double tube 1 for heat exchange, are prepared. . Then, the first and second pipes 6 and 7 are joined to the first and second headers 4 and 5. Next, the first and second headers 4 and 5 are joined to both ends of the outer tube 2 to produce a heat exchange main body 31 as shown in FIG. Next, as shown in FIG. 36, the inner tube 3 is inserted into the outer tube 2 of one heat exchange main body 31, and then the inner tube 3 is expanded, so that the heat exchange main body 31 is connected to the outer tube 2 and the inner tube 3. Are made in close contact with each other and the heat exchanger assembly 41, ie, the double tube 1 for heat exchange, is produced.

  Next, the four heat exchange main body portions 31 are arranged in a row adjacent to each other so that the axial centers of the outer pipes 2 are parallel to each other on the same plane and the first header 4 and the second header 5 face each other. Four sets of heat exchanger assemblies 41 are arranged. Thereafter, the inner pipes 3 are connected to each other by a U vent pipe 37, and the second pipe 7 of each heat exchange main body 31 is connected to the first pipe 6 of the heat exchange main body 31 located adjacent thereto, as shown in FIG. A double tube heat exchanger 40 is produced.

  According to this manufacturing method, since the diameter of the U vent pipe 37 is smaller than the diameter of the outer pipe 2, the U vent pipe 37 can be bent with a small radius of curvature, and the same heat exchange length can be used for one heat exchange. As compared with the case where the double tube 1 is used, the size can be reduced. Further, since the inner pipes 3 of the adjacent heat exchanger assemblies 41 are connected using the U-bend pipe 37 bent in advance, the inner pipe of the heat exchanger assembly 32 described in the sixth embodiment. Compared with the manufacturing method which bends the part between 3 adjacent heat exchange main-body parts 31, the heat exchanger suitable for the storage space requested | required can be manufactured easily, and productivity improves. Moreover, since the hairpin tube 36 described in the ninth embodiment is not necessary, there is an effect that the number of parts can be reduced.

  In addition, although the process of joining the first and second pipes 6 and 7 to the first and second headers 4 and 5 is described as the first process, this process does not need to be performed first, It may be performed prior to the connecting step between the first pipe 6 and the second pipe 7 of the heat exchange main body 31 arranged adjacent to each other. Moreover, the productivity of the connection process of the adjacent 1st piping 6 and the 2nd piping 7 improves by making the 1st header 4 and the 1st piping 6 and the 2nd header 5 and the 2nd piping 7 into the same structure.

Here, in the thirteenth embodiment, the double pipe heat exchanger 40 is configured such that the axial centers of the outer pipes 2 are parallel to each other on the same plane and the first header 4 and the second header 5 are opposed to each other. In addition, the double tubes 1 for heat exchange (heat exchanger assemblies 41) are arranged adjacent to each other in one column and four rows. For example, as shown in FIG. 37, the heat exchanging duplex is made so that the axes of the outer tube 2 are parallel to each other and the first header 4 and the second header 5 are opposed to each other. The tubes 1 (heat exchanger assemblies 41) may be arranged adjacent to each other in 2 columns and 4 rows. In this way, by changing the number and arrangement of the heat exchange double tubes 1 (heat exchanger assemblies 41), it is possible to easily manufacture a heat exchanger suitable for the required heat exchange capacity and storage space. it can.
Also in the thirteenth embodiment, the heat exchange double tubes 1A and 1B can be used in place of the heat exchange double tube 1.

It is a perspective view which shows the double tube for heat exchange applied to the double tube type heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the state which omitted one header of the double pipe for heat exchange applied to the double pipe heat exchanger which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 1 of this invention. FIG. 4 is a cross-sectional view taken along arrow IV-IV in FIG. 3. It is a VV arrow directional cross-sectional view of FIG. It is a transverse cross section explaining the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe heat exchanger concerning Embodiment 1 of this invention. It is a longitudinal cross-sectional view explaining the refrigerant | coolant flow in the header of the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 1 of this invention. It is a refrigerant circuit diagram which shows Example 1 of the heat pump system using the double tube | pipe type heat exchanger which concerns on Embodiment 1 of this invention. It is a refrigerant circuit figure which shows Example 2 of the heat pump system using the double tube | pipe type heat exchanger which concerns on Embodiment 1 of this invention. It is a refrigerant circuit figure which shows Example 3 of the heat pump system using the double tube | pipe type heat exchanger which concerns on Embodiment 1 of this invention. It is a refrigerant circuit figure which shows Example 4 of the heat pump system using the double tube | pipe type heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view which shows the double tube for heat exchange applied to the double tube type heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the state which omitted one header of the double pipe for heat exchange applied to the double pipe heat exchanger which concerns on Embodiment 2 of this invention. It is a longitudinal cross-sectional view which shows the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 2 of this invention. It is a transverse cross section explaining the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe type heat exchanger concerning Embodiment 2 of this invention. It is a longitudinal cross-sectional view explaining the refrigerant | coolant flow in the header of the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 2 of this invention. It is a perspective view which shows the double tube for heat exchange applied to the double tube type heat exchanger which concerns on Embodiment 3 of this invention. It is a partially broken perspective view explaining the header structure of the double pipe for heat exchange applied to the double pipe type heat exchanger concerning Embodiment 3 of this invention. It is a longitudinal cross-sectional view which shows the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 3 of this invention. It is a transverse cross section explaining the refrigerant flow in the header of the double pipe for heat exchange applied to the double pipe type heat exchanger concerning Embodiment 3 of this invention. It is a longitudinal cross-sectional view explaining the refrigerant | coolant flow in the header of the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 3 of this invention. It is a longitudinal cross-sectional view which shows the double tube for heat exchange applied to the double tube type heat exchanger which concerns on Embodiment 4 of this invention. It is XXIII-XXIII arrow sectional drawing of FIG. It is a longitudinal cross-sectional view which shows the double pipe for heat exchange applied to the double pipe type heat exchanger which concerns on Embodiment 5 of this invention. It is a side view which shows the double tube type heat exchanger which concerns on Embodiment 6 of this invention. It is a top view explaining the manufacturing method of the double pipe type heat exchanger which concerns on Embodiment 6 of this invention. It is a top view explaining the manufacturing method of the double pipe type heat exchanger which concerns on Embodiment 6 of this invention. It is a perspective view which shows the embodiment of the double tube type heat exchanger which concerns on Embodiment 6 of this invention. It is a side view which shows the double tube type heat exchanger which concerns on Embodiment 9 of this invention. It is a top view explaining the manufacturing method of the double-pipe heat exchanger which concerns on Embodiment 9 of this invention. It is a perspective view which shows the embodiment of the double pipe type heat exchanger which concerns on Embodiment 9 of this invention. It is a side view which shows the double tube type heat exchanger which concerns on Embodiment 12 of this invention. It is a top view explaining the manufacturing method of the double pipe | tube type heat exchanger which concerns on Embodiment 12 of this invention. It is a side view which shows the double tube type heat exchanger which concerns on Embodiment 13 of this invention. It is a top view explaining the manufacturing method of the double tube type heat exchanger which concerns on Embodiment 13 of this invention. It is a top view explaining the manufacturing method of the double tube type heat exchanger which concerns on Embodiment 13 of this invention. It is a perspective view which shows the embodiment of the double pipe | tube type heat exchanger which concerns on Embodiment 13 of this invention.

Explanation of symbols

  1, 1A, 1B, 1C, 1D, 30, 35, 35A, 40 Double tube for heat exchange, 2, 11, 12, 14, 16 Outer tube (first tube), 2a, 11c, 12c, 14c, 16d Pore (pipe), 3 Inner pipe (second pipe), 4 1st header, 5 2nd header, 6 1st pipe, 7 2nd pipe, 9a 1st header space, 9b 2nd header space, 10 2 Heavy tube heat exchanger, 12b, 16c Groove (annular groove), 13 End plate (first and second header), 14a, 16a Large diameter part, 14b, 16b Small diameter part, 14d, 16e Center hole, 15 Corrosion resistance Layer, 20A, 20B, 20C, 20D heat pump system, 31 heat exchange body, 32, 38, 38A, 41 heat exchanger assembly, 36 hairpin tube, 37 U vent tube.

Claims (11)

A first tube formed in a cylindrical shape having a central hole formed at the axial center, and a plurality of conduits through which the first refrigerant flows are arranged in the circumferential direction with the conduit centers being parallel to the axial center. A cylindrical second pipe that is inserted into the center hole of the first pipe and is in close contact with the inner peripheral wall surface of the center hole of the first pipe and through which the second refrigerant flows, and one end of the first pipe Is formed in an annular cylindrical shape having a predetermined radial width and a predetermined axial length on the same side, one end side of the plurality of pipes is opened, and the first refrigerant is distributed to the plurality of pipes A first header space formed on the other end side of the first pipe, the other end side of the plurality of pipe lines being opened, and a second header space for collecting the first refrigerant flowing through the plurality of pipe lines, First and second headers defining the first and second header spaces in cooperation with the first pipe, and the first and second headers; Having first and second pipe connected to each of the header space, in the double-pipe heat exchanger and the first refrigerant and the second refrigerant having a heat exchange double tube for heat exchange,
The first pipe, so that the pipe center is positioned on a plane perpendicular to the axis of the first pipe, perpendicular to the該径direction displaced in the axial center radially outward of the first pipe Connected to the first header space,
The inner peripheral wall that defines the first and second header spaces is composed of a cylindrical projecting portion that projects coaxially from both ends of the first pipe ,
The first refrigerant flowing through the first and second header spaces is separated from the second refrigerant flowing through the second pipe by the projecting portion and the second pipe. Double pipe heat exchanger. The first and second headers are composed of ring-shaped end plates,
The first and second header spaces have annular grooves recessed coaxially at both ends of the first tube, and the end plates are formed at both ends of the first tube so as to close the openings of the annular groove. The double-tube heat exchanger according to claim 1, wherein the double-tube heat exchanger is joined. Said second pipe, so that the pipe center is positioned on a plane perpendicular to the axis of the first pipe, perpendicular to the該径direction displaced in the axial center radially outward of the first pipe The double pipe heat exchanger according to claim 1, wherein the double pipe heat exchanger is connected to the second header space. 4. The first pipe according to claim 1, wherein a center of the pipe is perpendicular to a radial direction of the first pipe on a radially outer peripheral side of the first header space. 5. A double-tube heat exchanger as described in the paragraph.   The said 1st piping is connected to the said 1st header space so that the tangent of the inner peripheral wall surface of the pipe line may be orthogonal to the tangent of the outer peripheral wall surface of the said 1st header space. Double tube heat exchanger.   The double pipe according to any one of claims 1 to 5, wherein the double pipe for heat exchange is arranged such that an axis of the first pipe is inclined with respect to the horizontal. Tube heat exchanger.   The double pipe heat exchanger according to claim 6, wherein the double pipe for heat exchange is arranged so that an axis of the first pipe is vertical. A method of manufacturing a double-pipe heat exchanger according to any one of claims 1 to 7, wherein the double-pipe heat exchanger includes a plurality of the double tubes for heat exchange. There,
Joining the first and second headers to the first pipe to produce a plurality of heat exchange body parts;
The second pipe formed of a single straight pipe is inserted into the center hole of each of the first pipes of the plurality of heat exchange main body portions, and then the second pipe is expanded so that each of the first pipes is Producing a heat exchanger assembly fixed in close contact with the second pipe, wherein the plurality of heat exchange main body portions are connected to the second pipe at predetermined intervals;
Bending the portion of the second pipe between the adjacent heat exchange main body portions of the heat exchanger assembly; and
A method for manufacturing a double-pipe heat exchanger. A method of manufacturing a double-pipe heat exchanger according to any one of claims 1 to 7, wherein the double-pipe heat exchanger includes a plurality of the double tubes for heat exchange. There,
Joining the first and second headers to the first pipe to produce a plurality of heat exchange body parts;
The second pipe bent into a U-shape is inserted into the center hole of each of the first pipes of the plurality of heat exchange main body portions, and then the second pipe is expanded so that each of the first pipes is expanded. Producing a plurality of sets of heat exchanger assemblies fixed in close contact with the second pipe, wherein the plurality of heat exchange main body portions are connected to the second pipe at predetermined intervals;
Joining the ends of the second tubes of the plurality of sets of heat exchanger assemblies with a tube, and connecting the second tubes of the plurality of sets of heat exchanger assemblies in series;
A method for manufacturing a double-pipe heat exchanger. A method of manufacturing a double-pipe heat exchanger according to any one of claims 1 to 7, wherein the double-pipe heat exchanger includes a plurality of the double tubes for heat exchange. There,
Joining the first and second headers to the first pipe to produce a plurality of heat exchange body parts;
One of the second tubes is inserted into the center hole of each of the first tubes of each of the plurality of heat exchange main body portions, and then the second tube is expanded so that the first tube is in close contact with the second tube. Producing a plurality of heat exchanger assemblies, wherein the plurality of heat exchange main body portions are respectively secured to the second pipe;
Joining the ends of the second tubes of the plurality of heat exchanger assemblies with a tube, and connecting the second tubes of the plurality of heat exchanger assemblies in series;
A method for manufacturing a double-pipe heat exchanger.   A heat pump system comprising the double-pipe heat exchanger according to any one of claims 1 to 7.

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