JP2020159681A - Heat exchanger - Google Patents

Abstract

To provide a heat exchanger capable of simplifying a structure and reducing a manufacturing cost.SOLUTION: A heat exchanger 10 comprises: a plurality of flat perforated pipes 34 having a flow passage 34a in which a plurality of holes 34b through which first fluid flows is arranged in parallel; a first inlet header 36 that allows inlets of the flow passages 34a of the plurality of flat perforated pipes 34 to communicate with each other and allows the first fluid to flow into the flow passage 34a of each flat perforated pipe 34; a first outlet header 37 that allows outlets of the flow passages 34a of the plurality of flat perforated pipes 34 to communicate with each other, and through which the first fluid flowing out from the flow passage 34a of each flat perforated pipe 34 flows; a storage chamber 32a that houses the plurality of flat perforated pipes 34; and a pressure container having an inlet port 40 that allows second fluid to flow into the storage chamber 32a, and an outlet port 41 that allows the second fluid to flow out from the storage chamber 32a.SELECTED DRAWING: Figure 2

Description

The present invention relates to a heat exchanger that exchanges heat between two fluids.

Conventionally, in a refrigerating cycle apparatus or the like, a heat exchanger that exchanges heat between two fluids is widely used. For example, in Patent Document 1, as a heat exchanger for heat exchange between water and a refrigerant, a plurality of flat pipes communicating with each other via a communication portion and a plurality of flat porous pipes communicating with each other via a header are provided. The provided configuration is disclosed. In this heat exchanger, the flat pipes and the flat porous pipes are alternately laminated to exchange heat between the water flowing through the flat pipes and the refrigerant flowing through the flat porous pipes.

Japanese Patent No. 5790730

In the configuration of Patent Document 1, since flat tubes having different structures and flat porous tubes are alternately laminated, not only the overall structure is complicated, but also the structure of the header that communicates the flat porous tubes is complicated. The manufacturing cost is high.

The present invention has been made in consideration of the above-mentioned problems of the prior art, and an object of the present invention is to provide a heat exchanger capable of simplifying the structure and reducing the manufacturing cost.

The heat exchanger according to the first aspect of the present invention is a heat exchanger that exchanges heat between the first fluid and the second fluid, and has a flow path in which a plurality of holes through which the first fluid flows are arranged in parallel. A plurality of flat porous tubes, a first inlet header that communicates with each other at the inlets of the flow paths of the plurality of flat porous tubes, and allows the first fluid to flow into the flow paths of each flat porous tube. The first outlet header through which the first fluid flowing out of the flow path of each flat porous tube is communicated with each other, and the plurality of flat porous tubes are accommodated. It is characterized by comprising a chamber, an inlet port for allowing the second fluid to flow into the containment chamber, and a pressure vessel having an outlet port for allowing the second fluid to flow out of the containment chamber.

The second fluid flows into the containment chamber in a gas-liquid two-phase flow state, faces the inlet port in the containment chamber, and flows into the containment chamber from the inlet port. A baffle member that obstructs the flow of the second fluid flowing into the accommodation chamber from the inlet port by being arranged so as to intersect the direction may be provided.

The flat perforated tube may also be used as the baffle member.

The plurality of flat perforated pipes have at least one long side having a cross section orthogonal to the longitudinal direction thereof arranged along a direction orthogonal to the inflow direction of the second fluid from the inlet port into the accommodation chamber. The flat perforated tube may be configured to face the inlet port.

The pressure vessel has a cylindrical shape, the first inlet header is provided at the upper end of the pressure vessel, the first outlet header is provided at the lower end of the pressure vessel, and the inlet port is provided. The outlet port is provided at the lower part of the outer peripheral surface of the pressure vessel, the outlet port is provided at the upper part of the outer peripheral surface of the pressure vessel, and is further provided so as to collectively surround the plurality of flat porous tubes in the accommodation chamber. A spacer member may be provided to fill the gap between the flat perforated tube and the inner wall surface of the pressure vessel.

In the plurality of flat perforated pipes, the short sides in the cross section orthogonal to the longitudinal direction of the adjacent flat perforated pipes are arranged to face each other, and the long sides in the cross section are the first inlet header and the first. 1 The configuration may be such that the exit headers are lined up in a row along the longitudinal direction.

A plurality of units in which the plurality of flat perforated tubes are connected by the first inlet header and the first outlet header are provided, and the long sides of the flat perforated tubes are arranged to face each other among the adjacent units. Further, the first inlet header of each unit is communicated with each other, and the second inlet header for allowing the first fluid to flow into each first inlet header is communicated with each other, and the first outlet header of each unit is communicated with each other. The configuration may include a second outlet header through which the first fluid flowing out of the first outlet header flows.

In the pressure vessel, the inflow direction of the second fluid from the inlet port to the storage chamber is in the direction along the longitudinal direction of the first inlet header or in the longitudinal direction of the flat porous tube. There is also a configuration in which the outflow direction of the second fluid from the storage chamber to the outlet port is a direction along the longitudinal direction of the first inlet header or a direction along the longitudinal direction of the flat perforated pipe. Good.

The second fluid may have a higher pressure than atmospheric pressure, and the first fluid may have a higher pressure than the second fluid.

The flat perforated pipe may have a concave-convex shape portion at least a part of an outer surface corresponding to a long side in a cross section orthogonal to the longitudinal direction.

The outer surface of the flat porous tube is provided with a first region located at least on the inlet port side and a second region located on the outlet port side in the longitudinal direction thereof, and at least the second region is provided. , The groove portions along the longitudinal direction of the flat perforated pipe may be provided side by side.

A fin member may be provided in contact with the outer surface of the flat perforated tube.

The pressure vessel has a cylindrical shape, the first inlet header and the first outlet header are provided along the axial direction of the pressure vessel, and the flat porous tube is gradually bent along the longitudinal direction thereof. It may be configured to have a spiral shape.

According to the above aspect of the present invention, the structure of the heat exchanger can be simplified and the manufacturing cost can be reduced.

FIG. 1 is an overall configuration diagram of a refrigeration cycle apparatus using the heat exchanger according to the first embodiment. FIG. 2 is a perspective view schematically showing the configuration of the heat exchanger according to the first embodiment. FIG. 3 is a plan sectional view of the heat exchanger shown in FIG. FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. FIG. 5 (A) is a front view showing a configuration example of a flat porous tube according to the first modification, and FIG. 5 (B) is a cross-sectional view taken along the line VB-VB in FIG. 5 (A). .. FIG. 6 (A) is a front view showing a configuration example of a flat perforated tube according to a second modification, and FIG. 6 (B) is a cross-sectional view taken along the VIB-VIB line in FIG. 6 (A). .. FIG. 7A is an explanatory view schematically showing a fluid flow state on the outer surface of the flat porous tube provided with the groove, and FIG. 7B is an explanatory view on the outer surface of the flat porous tube not provided with the groove. It is explanatory drawing which shows typically the flow state of a fluid. FIG. 8 (A) is a front view showing a configuration example of the flat porous tube according to the third modification, and FIG. 8 (B) is a cross-sectional view taken along the line VIIIB-VIIIB in FIG. 8 (A). .. FIG. 9 is a front view showing a configuration example of the flat porous tube according to the fourth modification. FIG. 10 is a cross-sectional view schematically showing the internal structure of a flat perforated pipe having an uneven shape portion in the flow path. FIG. 11 is a partially exploded perspective view schematically showing the configuration of the heat exchanger according to the second embodiment. FIG. 12 is a cross-sectional view taken along the line XII-XII in FIG. 13 (A) is a configuration diagram of the unit shown in FIG. 11, and FIG. 13 (B) is a configuration diagram of a state in which a fin member is attached to the unit shown in FIG. 13 (A). FIG. 14 is a perspective view schematically showing the configuration of the heat exchanger according to the third embodiment. FIG. 15 is a vertical cross-sectional view schematically showing the internal structure of the heat exchanger shown in FIG. FIG. 16 is a schematic cross-sectional view of the heat exchanger shown in FIG. 15 cut at the position of the inlet port. FIG. 17 is an enlarged perspective view of the lower end portion of the spacer member. FIG. 18 is an explanatory view of a configuration example in which a baffle member is installed in the heat exchanger shown in FIG.

Hereinafter, a preferred embodiment of the heat exchanger according to the present invention will be described and described in detail with reference to the accompanying drawings.

FIG. 1 is an overall configuration diagram of a refrigeration cycle apparatus 12 using the heat exchanger 10 according to the first embodiment. First, prior to the specific description of the heat exchanger 10 of the present embodiment, the refrigeration cycle apparatus 12 as an application example of the heat exchanger 10 will be described.

The refrigeration cycle apparatus 12 includes two refrigeration cycles, a first refrigeration cycle 14 in which the first fluid circulates and a second refrigeration cycle 16 in which the second fluid circulates, and the first fluid as one refrigerant and the other. This is a dual refrigeration cycle configured to exchange heat with the second fluid, which is the refrigerant of the above, by the heat exchanger 10. The refrigeration cycle device 12 can use, for example, the cold heat generated by the evaporator 21 of the first refrigeration cycle 14 for various refrigeration equipment such as air conditioners and showcases.

The first refrigeration cycle 14 has a configuration in which the compressor 18, the condenser 19, the heat exchanger 10, the expansion device 20, and the evaporator 21 are connected in order by piping. The second refrigeration cycle 16 has a configuration in which the compressor 22, the condenser 23, the expansion device 24, and the heat exchanger 10 are connected in order by piping. The heat exchanger 10 exchanges heat between the high-pressure first fluid that has passed through the condenser 19 of the first refrigeration cycle 14 and the low-pressure second fluid that has passed through the expansion device 24 of the second refrigeration cycle 16. It is a vessel. In the heat exchanger 10, the first fluid condenses and the second fluid evaporates. The configurations of the refrigeration cycles 14 and 16 can be changed as appropriate. The heat exchanger 10 may be used in addition to the intermediate heat exchanger of such a dual refrigeration cycle.

The first fluid and the second fluid, which are the refrigerants that circulate in the refrigeration cycles 14 and 16, are, for example, natural refrigerants, alternative CFC refrigerants, and the like. In the case of the present embodiment, the second fluid of the second refrigeration cycle 16 has a higher pressure than the atmospheric pressure when flowing into the heat exchanger 10, and the first fluid of the first refrigeration cycle 14 has a higher pressure than the second fluid. It flows into the heat exchanger 10 in this state.

Next, a specific configuration example of the heat exchanger 10 will be described. FIG. 2 is a perspective view schematically showing the configuration of the heat exchanger 10 according to the first embodiment. FIG. 3 is a plan sectional view of the heat exchanger 10 shown in FIG. FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG.

As shown in FIGS. 2 to 4, the heat exchanger 10 includes a plurality of units 30 arranged in parallel so as to be stacked, and a pressure vessel 32 having a storage chamber 32a for accommodating each unit 30.

Each unit 30 is connected to the piping of the first refrigeration cycle 14 when the heat exchanger 10 is mounted on the refrigeration cycle device 12 shown in FIG. 1, and is a portion through which the high-pressure first fluid circulating therethrough flows. is there. The storage chamber 32a of the pressure vessel 32 is a portion connected to the piping of the second refrigeration cycle 16 and through which a second fluid having a lower pressure than the first fluid circulating therethrough flows. During normal operation, the accommodation chamber 32a is filled with the second fluid. The second fluid is introduced into the storage chamber 32a in a gas-liquid two-phase flow state. In the heat exchanger 10, the first fluid and the second fluid exchange heat, the first fluid dissipates heat and condenses, and the second fluid absorbs heat and evaporates.

Hereinafter, with reference to the heat exchanger 10 shown in FIG. 2, the front-rear direction from the front side to the back side is referred to as the Y direction, the vertical direction from the upper surface side to the lower surface side is referred to as the Z direction, and the left-right width direction is referred to as the X direction. To do.

Each unit 30 has a plurality of flat perforated pipes 34, a first inlet header 36 connecting the upper end portions of the flat perforated pipes 34, and a first outlet header 37 connecting the lower end portions of the flat perforated pipes 34. Have.

As shown in FIG. 2, the heat exchanger 10 of the present embodiment has a configuration in which 10 sets of units 30 in which four flat perforated tubes 34 arranged in the X direction are connected by headers 36 and 37 are arranged in the Y direction. Is. In addition, in FIGS. 3 and 4, in order to ensure the legibility of the drawing, one unit 30 is composed of two flat perforated pipes 34, and six units are arranged in the Y direction. .. The number of flat perforated tubes 34 constituting each unit 30 can be changed as appropriate. The number of installations of each unit 30 can be changed as appropriate, and may be composed of only one unit 30.

As shown in FIGS. 2 to 4, the flat perforated pipes 34 of each unit 30 are strip-shaped flat plate-shaped members, which are arranged in parallel along the X direction. The flat perforated pipe 34 has a flow path 34a inside. The flow path 34a has a plurality of holes 34b formed through the flat porous tube 34 along the longitudinal direction (Z direction), and a plurality of the holes 34b are arranged in parallel in the width direction (X direction). .. Each hole 34b is a fine path called a so-called mini channel or micro channel, whereby the flow path 34a has sufficient pressure resistance to a high-pressure first fluid.

In the flat perforated pipe 34 constituting one unit 30, the short sides 34c of the adjacent flat perforated pipes 34 are arranged to face each other, and the long sides 34d thereof are in the longitudinal direction (X direction) of the headers 36 and 37. They are lined up in a row in a straight line. As a result, the thickness of each unit 30 in the Y direction is minimized. In the adjacent units 30, the long sides 34d of the flat perforated pipes 34 are arranged to face each other, so that the units 30 are stacked in the Y direction at predetermined intervals.

The first inlet header 36 is, for example, a cylindrical metal pipe extending along the X direction. The first inlet header 36 is formed with a distribution flow path 36a (see FIG. 4) that communicates with the inlets (upper end openings) of the flow paths 34a of the flat perforated pipes 34 constituting one unit 30.

The first outlet header 37 is, for example, a cylindrical metal pipe, which extends along the X direction. The first outlet header 37 is formed with a collective flow path 37a (see FIG. 4) that communicates the outlets (lower end openings) of the flow paths 34a of the flat perforated pipes 34 constituting one unit 30.

As shown in FIGS. 2 to 4, between the units 30, the first inlet headers 36 of each other are connected by the second inlet header 38, and the first outlet headers 37 of each other are connected by the second outlet header 39. Has been done.

The second inlet header 38 is, for example, a cylindrical metal pipe extending along the Y direction. The second entrance header 38 connects one ends of the first entrance header 36 of each unit 30 to each other. The second inlet header 38 is formed with an inlet flow path 38a (see FIG. 4) that communicates the distribution flow paths 36a of the first inlet header 36 of each unit 30 with each other.

The second outlet header 39 is, for example, a cylindrical metal pipe, which extends along the Y direction. The second exit header 39 connects, for example, one ends of the first exit header 37 of each unit 30 to each other. The second outlet header 39 is formed with an outlet flow path 39a (see FIG. 4) that communicates with each other the gathering flow paths 37a of the first outlet header 37 of each unit 30. In the present embodiment, a configuration in which the headers 38 and 39 are arranged vertically in the Y direction is illustrated, but the second entrance header 38 and the second entrance header 38 and the second entrance header 38 are shown as shown by the two-dot chain line in FIG. 2 The configuration may be such that the exit header 39 is arranged diagonally.

As shown in FIGS. 2 to 4, the pressure vessel 32 is a pressure vessel made of metal, and the internal space thereof serves as a storage chamber 32a for accommodating each unit 30. In the present embodiment, a rectangular parallelepiped shape is exemplified as the pressure vessel 32, but a cylindrical shape or the like that makes it easier to secure pressure resistance performance may be used.

An inlet port 40 and an outlet port 41 are connected to one side surface (YZ surface on one side) of the pressure vessel 32. The inlet port 40 is provided, for example, in the lower center of one side surface, and the exit port 41 is provided, for example, in the upper center of one side surface. As a result, the inflow direction of the second fluid from the inlet port 40 to the accommodating chamber 32a is the extending direction of the first inlet header 36 of each unit 30, that is, the arranging direction of the flat perforated pipes 34 constituting each unit 30 (X). The direction is along the direction). The outflow direction of the second fluid from the accommodation chamber 32a to the outlet port 41 is opposite to that of the inlet port 40. In this embodiment, the configuration in which the inlet port 40 and the outlet port 41 are provided on the same side surface of the pressure vessel 32 is illustrated, but the outlet port 41 is provided as shown by the two-dot chain line in FIG. It may be configured to be provided on a side surface (YZ surface on the other side) different from the inlet port 40.

Although not shown, one or both of the inlet port 40 and the outlet port 41 may be connected to the upper surface or the lower surface (XY surface) of the pressure vessel 32. In this case, the inflow direction of the second fluid from the inlet port 40 to the accommodation chamber 32a is the direction along the longitudinal direction of the flat perforated pipe 34 of each unit 30, and the outlet port 41 is in the opposite direction or the same direction.

Therefore, the first fluid introduced from the outside is distributed from the second inlet header 38 to each first inlet header 36, flows through each flow path 34a of each flat perforated pipe 34 from top to bottom, and then each. It is derived from the first exit header 37 to the outside via the second exit header 39. On the other hand, the second fluid introduced from the outside flows from the inlet port 40 into the accommodation chamber 32a of the pressure vessel 32, and then is led out from the outlet port 41 to the outside. At that time, when the second fluid circulates between the units 30 or in the gap G1 (see FIGS. 3 and 4) between the units 30 and the inner wall surface of the pressure vessel 32, the second fluid is on the long side 34d side of each flat porous tube 34. It flows along the outer surface 34d while being in contact with the surface (hereinafter referred to as “outer surface 34d”), and exchanges heat with the first fluid flowing through the flow path 34a.

In this way, the heat exchanger 10 directly accommodates the flat perforated pipe 34 through which the first fluid flows in the pressure vessel 32 through which the second fluid flows. As a result, the second fluid directly contacts and exchanges heat with the flat perforated pipe 34 through which the first fluid flows, so that high heat exchange performance can be obtained. Further, in the heat exchanger 10, since a flat tube or the like for circulating the second fluid as in the above-mentioned prior art is not required, the component cost is reduced. Further, a complicated design regarding the arrangement relationship between the flat pipe through which the second fluid flows and the flat perforated pipe 34 through which the first fluid flows becomes unnecessary. Therefore, the structure can be further simplified and at the same time compacted, and the manufacturing cost can be reduced. Moreover, since the heat exchanger 10 realizes a multipath flow in which the first fluid is diverted to each unit 30 and further to each flat perforated pipe 34 of each unit 30, the pressure loss is small and heat exchange occurs. Efficiency is further improved.

In the heat exchanger 10, since the flat perforated tube 34 through which the first fluid flows is composed of a plurality of units 30, the manufacturing efficiency is high and the manufacturing cost can be further reduced. Since the number of laminated units 30 can be easily changed, the configuration can be easily changed according to the desired heat exchange capacity. At least one unit 30 may be provided, and in this case, the second inlet header 38 and the second exit header 39 may be omitted.

In the pressure vessel 32, the inflow direction of the second fluid from the inlet port 40 to the accommodation chamber 32a is along the longitudinal direction of the first inlet header 36 (X direction) or along the longitudinal direction of the flat porous pipe 34. The direction in which the second fluid flows out from the storage chamber 32a to the outlet port 41 is the direction along the longitudinal direction (X direction) of the first inlet header 36, or the flat porous pipe 34. It is a direction (Z direction) along the longitudinal direction. Therefore, when the second fluid flows into the accommodating chamber 32a, it does not collide straight with the outer surface 34d of the flat porous tube 34, and its smooth flow is not hindered, and higher heat exchange performance can be obtained. Moreover, since a gap G1 through which the second fluid can smoothly pass is formed between the first inlet headers 36 between the units 30, the second fluid flows more smoothly in the accommodating chamber 32a.

In the heat exchanger 10, a high-pressure first fluid flows through the flow path 34a of the flat perforated pipe 34 arranged inside the pressure vessel 32, and a second fluid lower than the first fluid flows outside the flow path 34a. To do. That is, the heat exchanger 10 has a double pressure-resistant structure in which a second fluid having an intermediate pressure flows between the first fluid having a high pressure and the outside (atmospheric pressure) of the pressure vessel 32. As a result, the pressure resistance design of the outermost pressure-resistant portion, that is, the outer wall of the pressure vessel 32 is relaxed as compared with the configuration in which the pressure of the first fluid is directly received, so that the manufacturing cost is further reduced.

FIG. 5 (A) is a front view showing a configuration example of the flat porous tube 34A according to the first modification, and FIG. 5 (B) is a cross-sectional view taken along the line VB-VB in FIG. 5 (A). is there.

The outer surface 34d of the flat perforated pipe 34 described above is formed of a flat surface. On the other hand, the flat perforated pipe 34A shown in FIGS. 5 (A) and 5 (B) has a configuration in which the uneven shape portion 44 is provided on the outer surface 34d. The concave-convex shape portion 44 has a configuration in which a plurality of protrusions 44a are arranged on the outer surface 34d in the X direction and the Z direction. As a result, in the flat porous tube 34A, the surface area of the outer surface 34d is expanded by the protrusions 44a to promote heat transfer, so that evaporation is promoted.

FIG. 6A is a front view showing a configuration example of the flat perforated tube 34B according to the second modification, and FIG. 6B is a cross-sectional view taken along the line VIB-VIB in FIG. 6A. is there.

The flat porous tube 34B shown in FIGS. 6 (A) and 6 (B) has a concave-convex shape portion 46 having a different shape from the concave-convex shape portion 44 shown in FIGS. 5 (A) and 5 (B) on the outer surface 34d. .. The concave-convex shape portion 46 has a configuration in which a plurality of groove portions 46a along the Z direction are arranged in the X direction on the outer surface 34d. The groove portion 46a is a valley-shaped groove portion formed in a V shape on the outer surface 34d. The groove portion 46a may be a rectangular groove portion.

Here, for example, as shown in FIG. 7A, when the outer surface 34d is a flat surface, the bubbles coalesce with each other to generate large bubbles, although it depends on the type, temperature, flow velocity, etc. of the second fluid. , The heat exchange efficiency may decrease. On the other hand, in the flat perforated tube 34B shown in FIG. 7B, when the second fluid flowing along the outer surface 34d exchanges heat with the first fluid and evaporates, the generated bubbles form a plug along the groove 46a. Since it flows, it is suppressed that the bubbles are combined into a large bubble. As a result, in the flat perforated tube 34B, it is prevented that the bubbles generated on the outer surface 34d become large and hinder heat exchange, and the surface area of the outer surface 34d also increases, so that high heat transfer efficiency can be obtained.

FIG. 8A is a front view showing a configuration example of the flat porous tube 34C according to the third modification, and FIG. 8B is a cross-sectional view taken along the line VIIIB-VIIIB in FIG. 8A. is there.

The flat perforated pipe 34C shown in FIGS. 8 (A) and 8 (B) is composed of a groove portion 48a having a shape different from that of the groove portion 46a of the concave-convex shape portion 46 shown in FIGS. 6 (A) and 6 (B). It has an uneven shape portion 48. The concave-convex shape portion 48 is formed by forming a groove portion 48a between the protrusions 48b formed on the outer surface 34d along the Z direction.

FIG. 9 is a front view showing a configuration example of the flat porous tube 34D according to the fourth modification.

The flat perforated tube 34D shown in FIG. 9 has a first region R1 and a second region R2 on the outer surface 34d. The first region R1 is formed on the inlet port 40 side in the longitudinal direction (Z direction) of the outer surface 34d, that is, on the upstream side in the flow direction of the second fluid. The second region R2 is formed on the outlet port 41 side in the longitudinal direction (Z direction) of the outer surface 34d, that is, on the downstream side in the flow direction of the second fluid. The first region R1 is provided with, for example, a concave-convex shape portion 44 (see FIGS. 5A and 5B) formed by protrusions 44a. The second region R2 of the outer surface 34d is provided with, for example, a concave-convex shape portion 48 (see FIGS. 8A and 8B) formed by the groove portion 48a. As a result, the uneven shape of the outer surface 34d of the flat perforated pipe 34D changes in the flow direction of the second fluid.

By the way, since the second fluid is heated and evaporated on the outer surface 34d of the flat porous tube 34D, the upstream side (first region R1) has a larger proportion of liquid than the gas in the distribution direction, and the downstream side (second region). R2) has a higher proportion of gas than liquid. Therefore, in the first region R1 on the upstream side, the surface area of the outer surface 34d is expanded by the protrusion 44a to promote heat transfer, so that evaporation is promoted. Further, in the second region R2 on the downstream side, air bubbles smoothly escape due to the groove portion 48a, so that the generation of large air bubbles can be suppressed and the amount of heat exchange can be increased. For the second region R2, for example, the uneven shape portion 46 formed by the groove portion 46a described above may be used. The first region R1 may be a flat surface, or the uneven shape portions 46 and 48 described above may be provided. The outer surface 34d may be provided with three or more regions and the surface shape may be changed in each region, but even in this case, at least the most downstream region may be configured to have groove portions 46a and 48a. preferable.

As shown in FIG. 10, the flat perforated pipes 34, 34A to 34D have formed a concave-convex shape portion 49 having, for example, a protrusion on the inner surface of each hole portion 34b of the flow path 34a to further improve the heat transfer efficiency. It may be configured.

FIG. 11 is a partially exploded perspective view schematically showing the configuration of the heat exchanger 10A according to the second embodiment. FIG. 12 is a cross-sectional view taken along the line XII-XII in FIG. In the heat exchanger 10A according to the second embodiment, the same reference numerals are given to elements having the same or similar functions and effects as the heat exchanger 10 according to the first embodiment, and detailed description thereof will be given. Omit.

As shown in FIGS. 11 and 12, the heat exchanger 10A includes a unit 50 having a structure in which the unit 30 shown in FIG. 2 is formed in a spiral shape, a pressure vessel 52 in which the unit 50 is housed in the storage chamber 52a, and a fin member. It includes 54.

The pressure vessel 52 is a metal pressure vessel in which a storage chamber 52a in which the unit 50 and the fin member 54 are housed is formed. The pressure vessel 52 is a cylindrical container composed of a cylindrical portion 52b, a lid portion 52c that closes the upper end opening of the cylindrical portion 52b, and a bottom portion 52d that closes the lower end opening of the cylindrical portion 52b. In the pressure vessel 52, an inlet port 40 is connected to the side surface of the bottom portion 52d, and an outlet port 41 is connected to the lid portion 52c. The inner diameter of the cylindrical portion 52b is set to, for example, 160 mm or less.

FIG. 13A is a configuration diagram of the unit 50 shown in FIG. FIG. 13B is a configuration diagram showing a state in which the fin member 54 is attached to the unit 50 shown in FIG. 13A.

As shown in FIG. 13A, the unit 50 is obtained by changing the installation posture of the unit 30 and the shape of the flat perforated pipe 34 described above. Specifically, the unit 50 arranges the first outlet header 37 at the center of the spiral, arranges the first inlet header 36 outside the spiral, and arranges the flat perforated pipes 34 connected to the headers 36 and 37. It is a structure that is gradually bent in a spiral shape along its longitudinal direction.

In the unit 50, the headers 36 and 37 are housed in the pressure vessel 52 in a posture along the flow direction (Z direction) of the second fluid in the storage chamber 52a. The upper end opening of the first inlet header 36 that penetrates the lid portion 52c from the accommodating chamber 52a serves as the inlet for the first fluid. The lower end opening of the first outlet header 37 penetrating the side surface of the bottom portion 52d from the storage chamber 52a serves as the outlet for the first fluid.

As shown in FIG. 13B, the fin member 54 is formed by bending and deforming a metal plate bent in a corrugated shape in a spiral shape and inserting the metal plates into the spiral unit 50 so as to be alternately laminated. The top of the corrugated fin member 54 is in contact with the outer surface 34d of the flat perforated tube 34. The connection portion between the flat perforated pipe 34 and the headers 36 and 37, the contact portion between the fin member 54 and the flat perforated pipe 34, and the like are joined by, for example, vacuum brazing. The fin member 54 may be applied to the heat exchanger 10 of FIG. 2, in which case, for example, it is inserted between adjacent units 30 and installed in contact with the outer surface 34d of the flat perforated pipe 34 of each unit 30. do it.

Therefore, the first fluid introduced from the outside is distributed from the first inlet header 36 to the flow path 34a of each flat perforated tube 34, flows through each flow path 34a in the longitudinal direction (swirl direction), and then. It is derived to the outside via the first exit header 37. On the other hand, the second fluid introduced from the outside flows from the inlet port 40 into the storage chamber 52a of the bottom 52d of the pressure vessel 52, and then flows from the bottom to the top along the storage chamber 52a of the cylindrical portion 52b. It is led out to the outside from the outlet port 41 provided in the lid portion 52c. At that time, the second fluid exchanges heat with the first fluid flowing through the flow path 34a when the inner and outer portions of the spiral of each flat porous tube 34 flow while contacting the outer surface 34d. Further, the second fluid also comes into contact with the fin member 54, so that heat exchange with the first fluid is promoted via the fin member 54.

As described above, also in the heat exchanger 10A, the flat perforated pipe 34 through which the first fluid flows is directly housed in the pressure vessel 32 through which the second fluid flows. As a result, the second fluid directly contacts and exchanges heat with the flat perforated pipe 34 through which the first fluid flows, so that high heat exchange performance can be obtained. Further, in the heat exchanger 10A, the pressure vessel 52 has a cylindrical shape, so that the pressure resistance can be easily ensured. Therefore, the pressure resistance design of the pressure vessel 52 is further relaxed, and the manufacturing cost can be further reduced.

The flat perforated pipe 34 constituting the heat exchanger 10A may be provided with an uneven shape portion 49 similar to that shown in FIG. 10 in each hole portion 34b of the flow path 34a. In such a configuration, it is preferable that the uneven shape portion 49 has at least a pair of protrusions facing each other along the plate thickness direction (Y direction) of the flat porous tube 34 in FIG. That is, a protrusion may be provided on the inner wall surface of the flow path 34a with the radial direction of the spiral of the flat porous tube 34 as the normal direction. Then, when the flat perforated pipe 34 is bent and deformed in a spiral shape, it is possible to prevent the internal hole 34b from being crushed and the flow path 34a from being blocked.

In the heat exchanger 10A, two or more units 50 may be housed in the pressure vessel 52, and a plurality of headers 36 and 37 for inflow and outflow of the first fluid may be provided, respectively. In this case, each unit 50 may be provided. By circulating another fluid, it may be used for three or more types of heat exchange.

By the way, in the heat exchanger 10 according to the first embodiment described above, the direction in which the second fluid flows into the accommodation chamber 32a from the inlet port 40 and the extending direction of the long side 34d of the flat porous tube 34 are one. We are doing it (X direction in Fig. 3). As a result, as described above, the heat exchanger 10 makes it possible for the second fluid to smoothly circulate in the accommodating chamber 32a and obtain high heat exchange performance.

However, as a result of further experiments, it was found that the configuration of the heat exchanger 10 may cause the following problems depending on the properties of the second fluid, the flow rate, and the like. That is, the second fluid flows into the accommodation chamber 32a in a gas-liquid two-phase flow. Therefore, in the heat exchanger 10, after the second fluid enters the accommodation chamber 32a from the inlet port 40, the gas component gradually floats in the accommodation chamber 32a, which is a so-called dry-out phenomenon. As a result, in the accommodation chamber 32a, a gas-rich region (dry-out region) in which the gas component of the second fluid spreads from the outlet of the inlet port 40 like a delta and a liquid-rich region are formed. Here, since the second fluid exchanges heat with the first fluid by utilizing the latent heat of evaporation of the liquid component in the storage chamber 32a and exhibits high heat exchange performance, most of the gas component is used for heat exchange. Does not contribute. From the above, it has been found that in the heat exchanger 10, the dryout region that does not contribute to heat exchange has a large range in the accommodation chamber 32a, and there is a concern that the heat exchange performance may deteriorate.

Therefore, next, the heat exchanger 10B according to the third embodiment, which can suppress the deterioration of the heat exchange performance due to such a dryout phenomenon, will be described.

FIG. 14 is a perspective view schematically showing the configuration of the heat exchanger 10B according to the third embodiment. FIG. 15 is a vertical cross-sectional view schematically showing the internal structure of the heat exchanger 10B shown in FIG. FIG. 16 is a schematic cross-sectional view of the heat exchanger 10B shown in FIG. 15 cut at the position of the inlet port 40. Also in the heat exchanger 10B according to the third embodiment, the same reference numerals are given to elements that have the same or similar functions and effects as the heat exchangers 10 and 10A according to the first and second embodiments. However, detailed description will be omitted.

As shown in FIGS. 14 to 16, the heat exchanger 10B includes a plurality of flat perforated pipes 34, a baffle member 60, and a pressure vessel 62 in which the flat perforated pipe 34 and the baffle member 60 are housed in the storage chamber 62a. ..

The pressure vessel 62 is a metal pressure vessel in which a first inlet header 36, a storage chamber 62a, and a first outlet header 37 are formed therein. The pressure vessel 62 is a cylindrical container composed of a cylindrical portion 62b, a lid portion 62c that closes the upper end opening of the cylindrical portion 62b, and a bottom portion 62d that closes the lower end opening of the cylindrical portion 62b. The inner diameter of the cylindrical portion 62b is set to, for example, 160 mm or less.

The internal space of the cylindrical portion 62b is the accommodation chamber 62a. In the cylindrical portion 62b, the inlet port 40 is connected to the lower part of the outer peripheral surface, and the outlet port 41 is connected to the upper part of the outer peripheral surface. The inlet port 40 and the outlet port 41 are opposite to each other in the radial direction of the cylindrical portion 62b. The lid portion 62c has a dome shape, and the internal space thereof functions as the first entrance header 36. A second inlet header 38 is connected to the top of the lid 62c. The bottom portion 62d has a dome shape, and its internal space functions as a first exit header 37. A second exit header 39 is connected to the top of the bottom 62d.

As shown in FIGS. 15 and 16, each flat perforated pipe 34 has a long side 34d (outer surface 34d) orthogonal to the longitudinal direction of the inlet port 40 (in the inflow direction of the second fluid into the accommodation chamber 62a). They are arranged in a cross-shaped arrangement. The number and arrangement of flat perforated pipes 34 and the installation posture can be changed as appropriate.

The baffle member 60 is a member that obstructs the flow of the second fluid that has flowed into the accommodation chamber 62a from the inlet port 40. In the configuration example shown in FIG. 16, the baffle member 60 is also used as the flat perforated pipe 34 located closest to the inlet port 40. The baffle member 60 is arranged to face the outlet of the inlet port 40, and the outer surface 34d is orthogonal to the inflow direction of the second fluid. The baffle member 60 is not also used as the flat perforated pipe 34, and may have a configuration in which a metal plate or the like different from the flat perforated pipe 34 is arranged to face the inlet port 40.

As shown in FIG. 15, the first entrance header 36 is separated from the storage chamber 62a by the support disk 64 and the ring-shaped member 66. The support disk 64 is a circular metal plate. The support disk 64 is formed with a plurality of through holes 64a into which each flat perforated tube 34 is inserted in the plate thickness direction. The peripheral edge of the through hole 64a of the support disk 64 and the outer peripheral surface of the flat perforated tube 34 are joined by vacuum brazing or the like to be airtight. The ring-shaped member 66 is a ring-shaped metal member. The ring-shaped member 66 is joined to the inner peripheral surface of the cylindrical portion 62b and the end surface of the support disk 64 on the accommodation chamber 62a side by vacuum brazing or the like, and is airtight. As a result, the first entrance header 36 is airtightly partitioned from the storage chamber 62a. The upper end of the flow path 34a of each flat perforated tube 34 is open in the first inlet header 36.

As shown in FIG. 15, the first outlet header 37 has substantially the same configuration as the first inlet header 36 except that it has a substantially upside-down structure. That is, the first outlet header 37 is also airtightly separated from the accommodation chamber 62a by the support disk 64 and the ring-shaped member 66. Since the configurations of the support disk 64 and the ring-shaped member 66 are the same as those on the first entrance header 36 side, the same or similar configurations are designated by the same reference numerals and detailed description thereof will be omitted. The lower end of the flow path 34a of each flat perforated pipe 34 is open in the first outlet header 37.

As shown in FIGS. 15 and 16, a spacer member 68 is installed in the accommodation chamber 62a. FIG. 17 is an enlarged perspective view of the lower end portion of the spacer member 68.

As shown in FIGS. 16 and 17, the spacer member 68 has an inlet side portion 68a and an outlet side portion 68b, and is divided into an inlet port 40 side and an outlet port 41 side with the center line of the cylindrical portion 62b interposed therebetween. It has a structured structure. The spacer member 68 extends from the lower end to the upper end of the cylindrical portion 62b, and has a substantially cylindrical shape as a whole. The spacer member 68 may have an integral structure in which the respective portions 68a and 68b are integrally formed.

The outlet side portion 68b is provided so as to connect both ends of the stepped portion 70 and the stepped portion 70 forming a plurality of concave spaces in the accommodation chamber 62a in the plan view shown in FIG. 16, and is inside the cylindrical portion 62b. It is composed of an arc portion 71 extending in a semicircular shape along the peripheral surface and a lid plate 72. The step portion 70 of the present embodiment has two steps in the outer peripheral direction from the center of the storage chamber 62a, and the number of steps may be one or three or more. The arc portion 71 extends with almost no gap between the arc portion 71 and the inner peripheral surface of the cylindrical portion 62b. The lid plate 72 closes the lower end edge of the space S1 surrounded by the step portion 70 and the arc portion 71. That is, in the space S1 of the exit side portion 68b, only the upper end edge is open.

The inlet side portion 68a has a symmetrical structure with the outlet side portion 68b, but the point is that an opening 70a is formed in the step portion 70, an opening 71a is formed in the arc portion 71, and the lid plate 72 closes the upper end edge. It is different from the outlet side part 68b. The inlet side portion 68a has the same or the same configuration as the outlet side portion 68b with the same reference numerals, and detailed description thereof will be omitted. The openings 70a and 71a are notched so as to extend from the lower end surface of the inlet side portion 68a to a height position exceeding at least the inlet port 40, and are formed in an arch shape at a position overlapping on the extension line of the inlet port 40. It is an opening. The lid plate 72 closes the upper end edge of the space S1 surrounded by the step portion 70 and the arc portion 71 (see FIG. 15). That is, in the space S1 of the entrance side portion 68a, only the upper end edge is open.

The spacer members 68 are arranged so that the stepped portions 70, 70 of the respective portions 68a, 68b face each other, and a space S2 having a substantially cross-shaped cross section is formed between the stepped portions 70, 70. Each flat perforated tube 34 is arranged in this space S2.

As shown in FIGS. 15 and 16, the spacer member 68 has an opening at the lower end edge of the space S1 of the inlet side portion 68a. Therefore, in the spacer member 68, a plurality of gaps G2 having a substantially triangular shape in a plan view are formed between the step portion 70 of the inlet side portion 68a, the arc portion 71, and the ring-shaped member 66. The gap G2 communicates with the inlet port 40 through the opening 71a of the arc portion 71.

On the other hand, as shown in FIG. 15, the spacer member 68 has an opening at the upper end edge of the space S1 of the outlet side portion 68b. Therefore, in the spacer member 68, a plurality of gaps G2 similar to those of the inlet side portion 68a are formed between the step portion 70 of the outlet side portion 68b and the arc portion 71 and the ring-shaped member 66. The gap G2 communicates with the outlet port 41 through the opening 71a of the arc portion 71.

Therefore, as shown in FIG. 15, in the heat exchanger 10B, the first fluid introduced from the outside flows from the second inlet header 38 to the flow path 34a of each flat porous tube 34 via the first inlet header 36. After being distributed and flowing through each flow path 34a in the longitudinal direction (swirl direction), the fluid is led out to the outside via the first outlet header 37 and the second outlet header 39.

On the other hand, when the second fluid introduced from the outside flows into the accommodation chamber 62a from the inlet port 40, it first flows through the space S1 of the inlet side portion 68a, and then supports the ring-shaped member 66 below from the gap G2. It flows into the space S3 formed by the disk 64 (see FIG. 15). Here, since the lower end edge of the outlet side portion 68b is closed by the lid plate 72, the second fluid rises from the space S3 to the space S2, and finally the gap G2 above the outlet side portion 68b. It is led out from the exit port 41 through the outlet port 41. At that time, the second fluid comes into contact with the outer surface 34d and the short side 34c of each flat porous pipe 34, and exchanges heat with the first fluid flowing through the flow path 34a in each flat porous pipe 34.

Here, the heat exchanger 10B includes a baffle member 60 facing the inlet port 40. Therefore, the second fluid collides with the outer surface 34d of the baffle member 60 immediately after flowing into the accommodation chamber 62a from the inlet port 40, and the gas component is separated from the liquid component. That is, immediately after the second fluid in the gas-liquid two-phase flow state flows into the storage chamber 62a, the gas-liquid is separated by the collision action with the baffle member 60. The separated gas component intensively rises in the vicinity of the inlet port 40 in the space S2 of the inlet side portion 68a, and finally passes through the gap G2 above the outlet side portion 68b from the outlet port 41 to the outside. Derived. On the other hand, since the separated liquid component has a higher specific gravity than the gas component, it flows down from the gap G2 into the space S3 and spreads in the space S3 as described above. Then, this liquid component rises from the space S3 to the space S2, and is led out from the outlet port 41 to the outside while exchanging heat with the first fluid in the flat porous tube 34 in the rising process.

As described above, the heat exchanger 10B includes the baffle member 60 at a position facing the inlet port 40 in the accommodation chamber 62a. Therefore, the gas component of the second fluid flowing into the accommodation chamber 62a from the inlet port 40 is positively separated by the collision with the baffle member 60, and as it is, it rises in a narrow range near the inlet port 40 of the space S2 one after another. To do. That is, in the heat exchanger 10B, the gas-rich portion (dryout region) of the second fluid is limited to a narrow region near the inlet port 40. As a result, since almost only the liquid component of the second fluid circulates around the flat porous tube 34, high heat exchange performance can be obtained. In other words, the heat exchanger 10B positively creates a dryout region of the second fluid by the baffle member 60, and at the same time limits the range to a narrow range. As a result, the range of the liquid component is relatively expanded, and the heat exchange performance is improved. The baffle member 60 may be composed of, for example, two flat perforated tubes 34.

Also in the heat exchanger 10B, the flat perforated pipe 34 through which the first fluid flows is directly housed in the pressure vessel 32 through which the second fluid flows. As a result, the second fluid directly contacts and exchanges heat with the flat perforated pipe 34 through which the first fluid flows, so that high heat exchange performance can be obtained. Further, also in the heat exchanger 10B, the pressure resistance can be easily ensured because the pressure vessel 62 has a cylindrical shape. Therefore, the pressure resistance design of the pressure vessel 62 is further relaxed, and the manufacturing cost can be further reduced.

The heat exchanger 10B is provided so as to collectively surround each of the flat perforated tubes 34 in the accommodating chamber 62a, and includes a spacer member 68 that fills a gap between the flat perforated tube 34 and the inner wall surface of the pressure vessel 62. Therefore, in the heat exchanger 10B, the liquid component of the second fluid that flows into the accommodating chamber 62a from the inlet port 40 and is separated by the baffle member 60 is between the flat porous tube 34 having a small pressure loss and the cylindrical portion 62b. It surely flows into the space S2 around the flat perforated tube 34, not the space. Therefore, the heat exchanger 10B has further improved heat exchange performance. The spacer member 68 is also applicable to the heat exchanger 10 according to the first embodiment.

In the heat exchanger 10B, since the baffle member 60 is also used as the flat perforated pipe 34, it is possible to prevent an increase in the number of parts. Moreover, since the baffle member 60 is composed of the flat porous tube 34, heat exchange of the flat porous tube 34 that functions as the baffle member 60 can be expected, and the heat exchange performance is further improved.

In the heat exchanger 10B, the installation posture of the flat perforated pipe 34 may be changed as appropriate. Further, even if the baffle member 60 is applied to the heat exchanger 10 according to the first embodiment as shown in FIG. 18, the effect of improving the heat exchange performance can be expected as in the heat exchanger 10B. As the flat porous tube 34 of the heat exchanger 10B, the flat porous tubes 34A to 34D according to each of the above-described modifications may be used.

It should be noted that the present invention is not limited to the above-described embodiment, and it goes without saying that the present invention can be freely changed without departing from the gist of the present invention.

10,10A, 10B Heat exchanger 12 Refrigeration cycle device 14 First refrigeration cycle 16 Second refrigeration cycle 30,50 units 32,52,62 Pressure vessel 32a, 52a Storage chamber 34,34A-34D Flat perforated pipe 34a Channel 34b Hole 34c Short side 34d Long side (outer surface)
36 1st inlet header 37 1st exit header 38 2nd inlet header 39 2nd exit header 40 Inlet port 41 Exit port 44, 46, 48, 49 Concavo-convex shape part 46a, 48a Groove part 54 Fin member 60 Baffle member 68 Spacer member R1 1st area R2 2nd area

Claims (13)

A heat exchanger that exchanges heat between the first fluid and the second fluid.
A plurality of flat perforated pipes having a flow path in which a plurality of holes through which the first fluid flows are arranged in parallel,
A first inlet header that communicates the inlets of the flow paths of the plurality of flat porous pipes and allows the first fluid to flow into the flow paths of the flat porous pipes.
A first outlet header in which the outlets of the flow paths of the plurality of flat perforated pipes are communicated with each other and the first fluid flowing out from the flow paths of the flat perforated pipes flows through.
A pressure vessel having a storage chamber in which the plurality of flat perforated pipes are housed, an inlet port for allowing the second fluid to flow into the storage chamber, and an outlet port for discharging the second fluid from the storage chamber.
A heat exchanger characterized by being equipped with. The heat exchanger according to claim 1.
The second fluid flows into the storage chamber in a gas-liquid two-phase flow state.
The first fluid that has flowed into the containment chamber from the inlet port is arranged so as to face the inlet port in the containment chamber and intersect the inflow direction of the second fluid from the inlet port into the containment chamber. 2 A heat exchanger comprising a baffle member that obstructs the flow of a fluid. The heat exchanger according to claim 2.
A heat exchanger characterized in that the flat perforated tube is also used as the baffle member. The heat exchanger according to claim 3.
The plurality of flat perforated pipes are arranged such that their long sides in a cross section orthogonal to the longitudinal direction are arranged along a direction orthogonal to the inflow direction of the second fluid from the inlet port into the accommodation chamber.
A heat exchanger characterized in that at least one of the flat perforated tubes faces the inlet port. The heat exchanger according to any one of claims 1 to 4.
The pressure vessel has a cylindrical shape and has a cylindrical shape.
The first inlet header is provided at the upper end of the pressure vessel.
The first outlet header is provided at the lower end of the pressure vessel.
The inlet port is provided at the bottom of the outer peripheral surface of the pressure vessel.
The outlet port is provided on the upper part of the outer peripheral surface of the pressure vessel.
Further, the heat is provided in the accommodation chamber so as to surround the plurality of flat porous tubes together, and includes a spacer member that fills the gap between the flat porous tubes and the inner wall surface of the pressure vessel. Exchanger. The heat exchanger according to claim 1.
In the plurality of flat perforated pipes, the short sides in the cross section orthogonal to the longitudinal direction of the adjacent flat perforated pipes are arranged to face each other, and the long sides in the cross section are the first inlet header and the first. 1 A heat exchanger characterized in that it is lined up in a row along the longitudinal direction of the outlet header. The heat exchanger according to claim 6.
A plurality of units in which the plurality of flat perforated pipes are connected by the first inlet header and the first outlet header are provided, and the long sides of the flat perforated pipes are arranged to face each other among the adjacent units.
Further, a second inlet header that communicates the first inlet headers of each unit and allows the first fluid to flow into each first inlet header.
A heat exchanger characterized in that the first outlet headers of each unit are communicated with each other, and a second outlet header through which the first fluid flowing out from each first outlet header flows is provided. The heat exchanger according to claim 1, 6 or 7.
In the pressure vessel, the inflow direction of the second fluid from the inlet port to the accommodating chamber is in the direction along the longitudinal direction of the first inlet header or in the longitudinal direction of the flat porous tube. Yes,
The flow direction of the second fluid from the storage chamber to the outlet port is a direction along the longitudinal direction of the first inlet header or a direction along the longitudinal direction of the flat porous tube. Heat exchanger. The heat exchanger according to any one of claims 1 to 8.
The second fluid has a pressure higher than atmospheric pressure and is
The first fluid is a heat exchanger characterized in that the pressure is higher than that of the second fluid. The heat exchanger according to any one of claims 1 to 9.
The flat perforated tube is a heat exchanger characterized by having an uneven shape portion on at least a part of an outer surface corresponding to a long side in a cross section orthogonal to the longitudinal direction. The heat exchanger according to claim 10.
The outer surface of the flat perforated tube is provided with a first region located at least on the inlet port side and a second region located on the outlet port side in the longitudinal direction thereof.
A heat exchanger characterized in that, at least in the second region, groove portions along the longitudinal direction of the flat porous tube are provided side by side. The heat exchanger according to any one of claims 1 to 11.
A heat exchanger comprising a fin member in contact with the outer surface of the flat porous tube. The heat exchanger according to claim 1 or 6.
The pressure vessel has a cylindrical shape and has a cylindrical shape.
The first inlet header and the first outlet header are provided along the axial direction of the pressure vessel.
The flat perforated tube is a heat exchanger characterized by having a spiral shape gradually bent along the longitudinal direction thereof.

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