JP2013145066A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger enabling further reduction in size.SOLUTION: The heat exchanger 1A is provided with: a structure 3 which forms a first flow passage 2 for allowing a first fluid to flow therethrough; and a plurality of pipes 5 which form second flow passages 4 for allowing a second fluid to flow therethrough and which are arranged in a predetermined direction within the first flow passage 2. Each of the pipes 5 includes a serpentine section 51 which serpentines in the predetermined direction so that adjacent pipes 5 approach and separate from each other. As a result of this configuration, the cross-sectional area of the first flow passage 2 is small in comparison to that of conventional heat exchangers because the arrangement direction of the pipes 5 and the serpentine direction coincide with each other. Consequently, the heat exchanger is compact in comparison to the conventional heat exchangers.

Description

  The present invention relates to a heat exchanger that performs heat exchange between a first fluid and a second fluid.

  Conventionally, in heat pump devices such as a heat pump type hot water heater, an air conditioner, and a floor heating device, a heat exchanger that performs heat exchange between two types of fluids (for example, water and refrigerant, air and refrigerant) has been used. . For example, Patent Document 1 discloses a heat exchanger 100 that performs heat exchange between water and a refrigerant as shown in FIG.

  The heat exchanger 100 includes a structure 115 that forms a first flow path 110 through which water flows, and a pair of refrigerant tubes 120 that form a second flow path through which a refrigerant flows. The structure 115 has a rectangular plate shape, and the first flow path 110 is a serpentine-type flow path having a plurality of straight portions arranged in the width direction of the structure 115. The pair of refrigerant tubes 120 are stacked in the thickness direction of the structure body 115 and meander in the width direction of the structure body 115 so as to cross each other on the center line of the straight line portion in each straight line portion of the first flow path 110. ing.

International Publication No. 2007/108240

  In the heat exchanger 100 as shown in FIG. 13, the width of the first flow path 110 is set to be relatively large in order to accommodate the pair of refrigerant tubes 120 meandering in the width direction of the structure 115. In heat exchangers, further downsizing is required.

  An object of this invention is to provide the heat exchanger which can be further reduced in size.

  In order to solve the above problems, a heat exchanger according to the present invention is a heat exchanger that performs heat exchange between a first fluid and a second fluid, and is a structure that forms a first flow path through which the first fluid flows. And a plurality of pipes arranged in a predetermined direction in the first flow path that form a second flow path through which the second fluid flows, and each of the plurality of pipes is adjacent to the adjacent pipes And a meandering portion that meanders in the predetermined direction so as to move away from or away from the subject.

  According to said structure, since the arrangement direction of several piping and the meandering direction correspond, the cross-sectional area of a 1st flow path can be made smaller than before. Therefore, the heat exchanger can be made smaller than before.

The whole perspective view of the heat exchanger concerning a first embodiment of the present invention. Sectional drawing which shows the internal structure of the heat exchanger shown in FIG. Cross section of structure only (A) is sectional drawing along the IV-IV line of FIG. 2, (b) is the partially expanded view. Sectional view along line VV in FIG. (A) And (b) is a figure explaining the meander part of a modification. (A) And (b) is a figure explaining the meander part of another modification. Sectional drawing which shows the internal structure of the heat exchanger which concerns on 2nd embodiment of this invention. (A) is sectional drawing along the IX-IX line of FIG. 8, (b) is the partially expanded view. Sectional drawing which shows the internal structure of the heat exchanger which concerns on 3rd Embodiment of this invention. (A) is sectional drawing along the XI-XI line of FIG. 10, (b) is the partially expanded view. Configuration of twist type heat exchanger Configuration diagram of conventional heat exchanger

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. However, the present invention is not limited to the following embodiments.

  In the following embodiments, a heat exchanger that is used in a heat pump apparatus such as a heat pump type hot water heater and performs heat exchange between water as a first fluid and a refrigerant as a second fluid will be described as an example. The refrigerant circulates through the heat pump circuit, and for example, carbon dioxide is used as the refrigerant. However, the first fluid and the second fluid are not limited to these. For example, instead of water, oil, brine or the like can be used as the first fluid. Further, both the first fluid and the second fluid may be liquid or gas.

(First embodiment)
FIG. 1 shows the appearance of the heat exchanger 1A of the present embodiment, and FIG. 2 shows the internal structure of the heat exchanger 1A. 1 A of this heat exchanger is provided with the structure 11 which forms the 1st flow path 2 through which water flows, and the multiple (2 in this embodiment) piping 5 which forms the 2nd flow path 4 through which a refrigerant | coolant flows. . Most of the piping 5 is accommodated in the structure 3.

  The water flowing through the first flow path 2 and the refrigerant flowing through the second flow path 5 flow opposite to each other. If it is such a structure, the heat exchange efficiency of water and a refrigerant | coolant can be improved.

  The structure 3 has a rectangular flat plate shape in plan view, and the inside is hollow. That is, the first flow path 2 is configured by the internal space of the structure 3. In addition, both the main surfaces in the thickness direction of the structure 3 may be uneven so that a portion corresponding to the water flow path 2 is raised.

  Hereinafter, for convenience of explanation, the length direction of the structure 3 is referred to as a Y direction, the width direction is referred to as an X direction, and the thickness direction is referred to as a Z direction. In the present embodiment, the Z direction is a vertical direction, and the X direction and the Y direction are horizontal directions. However, the X, Y, and Z directions are not limited to this, and can be appropriately selected according to the installation location of the heat exchanger 1A.

  More specifically, the structure 3 includes a box 3A made up of a peripheral wall, a bottom wall, and a ceiling wall, and a plurality of partition plates 3B arranged in the box 3A. At one end in the Y direction of the box 3 </ b> A, a first fluid inlet 31 for flowing water into the first flow path 2 and a first fluid outlet 32 for flowing water out of the first flow path 2. Are spaced apart from each other in the X direction. Both ends of the pipe 5 forming the second flow path 4 pass through the box 3A in the vicinity of the first fluid inlet 31 and in the vicinity of the first fluid outlet 32, respectively.

  FIG. 3 is a cross-sectional view of only the structure 3. The partition plates 3B arranged in the box 3A are arranged at equal intervals in the X direction, and are alternately connected to one and the other of the short sides facing the Y direction in the peripheral wall of the box 3A. . That is, the partition plate 3B partially partitions the space surrounded by the peripheral wall, and forms the main flow path 2 that is the internal space of the structure 3 into a serpentine-type flow path (meandering flow path). In other words, the main flow path 2 has a plurality of linear portions 21 arranged in parallel with each other in the X direction and a bent portion 22 that connects the ends of the linear portions 21 to each other. The first fluid inlet 31 and the first fluid outlet 32 described above open at the end opposite to the bent portion 22 of the linear portion 21 located on the outermost side, and the flow direction of water is alternately 180 in the linear portion 21. It is the opposite direction. The serpentine type flow path is advantageous for saving a useless space in the structure 3. Note that the structures 3 may be stacked in a plurality of stages in the Z direction.

  The structure 3 is made of resin. Examples of such a resin include polyphenylene sulfide, polyether ether ketone, polytetrafluoroethylene, polysulfone, polyether sulfone, polyarylate, polyamideimide, polyetherimide, liquid crystal polymer, and polypropylene. Resins generally have the advantage of being lighter than metal materials. Also, the resin is generally less expensive than the metal material. However, the structure 3 may be made of metal.

  The structure 3 can be produced, for example, by welding the divided bodies obtained by dividing the structure 3 in half in the Z direction by a method such as vibration welding. Alternatively, the structure 3 is divided into a short side portion through which the pipe 5 of the box 3A passes, a lid portion made up of the partition plate 3B connected thereto, and other portions into which the lid portion can be inserted. And it is also possible to fasten a cover part and a container part via a sealing member.

  Returning to FIG. 2, the pipes 5 are arranged in the Z direction in the first flow path 2. That is, the Z direction corresponds to the predetermined direction of the present invention, and the X direction corresponds to the orthogonal direction of the present invention. A high-temperature and high-pressure refrigerant is led from an unillustrated compressor or the like to the end portion of the pipe 5 near the first fluid outlet 32, and heat is radiated to water from the end of the pipe 5 near the first fluid inlet 31. The refrigerant is guided to an expansion mechanism (not shown).

  Each pipe 5 includes a meandering part 51 disposed in each straight line part 21 of the first flow path 2 and a connecting part 52 that connects the end parts of the meandering part 51 along the bent part 22 of the first flow path 2. . The length of the meandering portion 51 is substantially equal to the length of the straight portion 21. The both ends of each pipe 5 mentioned above are the part which extended the meandering part 51 located in the outermost straight.

  The pipe 5 is made of a metal having good thermal conductivity. As the pipe 5, it is preferable to employ a double pipe (leakage detection pipe) having a structure in which a small diameter pipe is covered with a large diameter inner grooved pipe. According to such a double pipe, even if the small-diameter pipe is broken, the refrigerant containing the lubricating oil is released to the outside of the first flow path 2 through the groove of the outer grooved pipe on the outside. It is possible to prevent the lubricating oil in the refrigerant from being mixed into the water.

  Next, the shapes of the first flow path 2 and the pipe 5 will be described in detail with reference to FIGS. 4 (a) and 4 (b) and FIG.

  The meandering portion 51 of each pipe 5 meanders in the Z direction so that the adjacent pipes 5 approach or move away from each other. In other words, the centers of the meandering portions 51 of both pipes 5 are located on the same plane parallel to the Y direction and the Z direction.

  The meandering shape of the meandering part 51 has periodicity and has a sinusoidal shape. By adopting such a meandering shape, the ratio of the total length of the pipe 5 to the total length of the first flow path 2 can be increased, which is advantageous for downsizing the heat exchanger 1A. The meandering shapes of the meandering portions 51 of both pipes 5 are symmetric with respect to the center line of the first flow path 2 with respect to the Z direction, and the wavelengths P1 of the meandering parts 51 of both the pipes 5 are the same. For this reason, the bending shape of the meander part 51 can be made common in both the piping 5, and the piping 5 can be produced easily. Further, since the entire structure is simplified, it becomes easy to optimize design conditions such as the bending shape of the meandering portion 51 and the width of the first flow path 2 by, for example, computer simulation.

  Further, the relative positions of the meandering portions 51 of both pipes 5 are determined so that the vertices of the meandering portions 51 are in point contact with each other. That is, the phases of the meandering portions 51 of both pipes 5 are shifted by 180 degrees. Thus, if it avoids that the contact of meandering parts 51 continues in a line shape, a comparatively big gap can be secured between meandering parts 51, activation of three-dimensional flow, The effect of preventing an increase in water pressure loss can be expected.

  The structure 3 has a tubular surface 35 that defines the first flow path 2. In the present embodiment, the basic shape in the cross section of the tubular surface 35 is a circular shape having a diameter D1. The tubular surface 35 has a basic shape at the bent portion 22 and a shape deformed from the basic shape at the straight portion 21. However, the basic shape of the tubular surface 35 may be, for example, a rectangular shape with rounded corners.

  The maximum gap (gap) G in the Z direction between the meandering parts 51 of the adjacent pipes 5 is equal to twice the amplitude γ of the meandering part 51 in this embodiment. This maximum gap G is preferably larger than the minimum clearance C1 in the Z direction between the tubular surface 35 and the pipe 5 (clearance at the position where the meandering portions 51 are farthest from each other). At the position where the meandering portions 51 are in contact with each other, the distance from the tubular surface 35 to the pipe 5 in the Z direction is C1 + 0.5 × G.

  The tubular surface 35 that defines the first flow path 2 has a facing region 36 that faces the meandering portion 51 of the pipe 5 in the X direction. A pair of opposing regions 36 exist in all the straight portions 21. As shown in FIG. 3, a plurality of convex portions 37 that form a wave shape that undulates in the X direction along the axial direction of the tubular surface 35 are provided in the facing region 36 of each linear portion 21. The wave shapes of both opposing regions 36 in each linear portion 21 are symmetric with respect to the center line with respect to the X direction of the first flow path 2, and the wavelengths P2 of both wave shapes match.

  Moreover, the convex part 37 on one opposing area | region 36 and the convex part 37 on the other opposing area | region 36 in each linear part 21 are located in a line in the Y direction so that both waveform phase may correspond. In other words, the width of the straight line portion 21 is the same everywhere when viewed from the Z direction. For this reason, the water flows while undulating the straight portion 21 of the first flow path 2 in the X direction.

  The convex portion 37 has a triangular shape when viewed from the Z direction. The tips of the convex portions 37 on both opposing regions 36 in each linear portion 21 are closest to the pipe 5 at a position where the meandering portions 51 are most separated from each other. That is, P2 = 2 × P1. The clearance C2 in the X direction from the tip of the convex portion 37 to the pipe 5 is about the same as the minimum clearance C1 in the Z direction.

  In the heat exchanger 1A of the present embodiment, since the arrangement direction of the pipes 5 and the meandering direction coincide with each other, it is not necessary to ensure a large width of the first flow path 2 in the direction orthogonal to those directions. Therefore, the cross-sectional area of the first flow path 2 can be made smaller than before, and the heat exchanger can be made smaller than before.

  Then, the effect | action of 1 A of heat exchangers of this embodiment is demonstrated.

  The water flowing into the first flow path 2 from the first fluid inlet 31 flows through the first flow path 2 toward the first fluid outlet 32 on the downstream side. In each straight portion 21, the water is guided by the convex portion 37, and thus undulates in the X direction between the meandering portions 51 and between the meandering portion 51 and the tubular surface 35 so as to cross the pipe 5 many times. While flowing. Thereafter, the water flows out from the first fluid outlet 32.

  By the way, when water flows straight along the axial direction of the pipe 5 outside the pipe 5, since the stirring action received from the pipe 5 is small, the water has a relatively large temperature boundary layer near the surface of the pipe 5. It flows while forming.

  On the other hand, in this embodiment, water flows while undulating in the X direction so as to cross the pipe 5 many times by the convex portions 37 provided in both opposing regions 36 in each straight line portion 21. The temperature boundary layer formed in the vicinity of the surface is less likely to grow as compared to the case where the above-described water flows straight along the axial direction of the pipe 5. By actively creating such a flow, it is possible to prevent the temperature boundary layer from becoming thick, and thus to perform more efficient heat exchange.

  Moreover, in this embodiment, since water flows while colliding with the surface of both the pipes 5, the surface of the pipe 5 can be used effectively as a heat transfer surface. In addition, the dead water area can be reduced. As the dead water area becomes smaller, the heat transfer area increases, so the heat exchange efficiency increases.

  Next, the simulation performed in order to confirm the effect of 1 A of heat exchangers of this embodiment is demonstrated.

  In this simulation, analysis software “Fluent” was used. As analysis conditions, the flow rate of water was 0.0058 kg / s, the temperature of water was 40 ° C., and the temperature of the piping through which the refrigerant flows was 45 ° C.

  First, as comparison targets, reference models 1 and 2 that are twist type heat exchangers 6 as shown in FIG. 12 were created. In the twist type heat exchanger 6, a pair of refrigerant pipes 62 and 63 are arranged in close contact with each other inside a water pipe 61 having a circular cross section. In the reference model 1, the inner diameter of the water pipe 61 is 8.6 mm, the outer diameter of the refrigerant pipes 62 and 63 is 3.9 mm, the clearance between the water pipe 61 and the refrigerant pipes 62 and 63 is 0.4 mm, and the refrigerant pipes 62 and 63 The twist pitch was 40 mm. The reference model 2 is obtained by changing the twist pitch of the refrigerant tubes 62 and 63 from the reference model 1 to 30 mm.

  Next, an implementation model 1 corresponding to the heat exchanger 1A of the present embodiment was created. In the implementation model 1, the diameter D1 of the tubular surface 35 is 10.6 mm, the outer diameter D2 of the pipe 5 is 3.9 mm, the minimum clearance C1 in the Z direction and the minimum clearance C2 in the X direction are 0.4 mm, and between the meandering portions 51 The maximum gap G in the Z direction was 2 mm, the wavelength P1 of the meandering part 51 was 10 mm, and the wave-shaped wavelength P2 formed by the convex part 37 was 20 mm.

  The heat transfer coefficient and pressure loss were analyzed for the reference models 1 and 2 and the implementation model 1. Table 1 shows the analysis results. In Table 1, the cross-sectional area through which water flows (in the implementation model 1, the area obtained by subtracting the area occupied by both pipes 5 from the cross-sectional area of the straight portion 21 of the first flow path 2) is described as the water-side cross-sectional area. .

In the reference model 2 in which the twist pitch of the refrigerant pipe is shortened from 40 mm to 30 mm with respect to the reference model 1, the effect of suppressing the development of the temperature boundary layer of water in the vicinity of the surface of the refrigerant pipe is obtained by promoting the stirring. The heat transfer rate from water to water is improved from 2855 W / m ² K to 4120 W / m ² K. However, the pressure loss also increases from 1.31 kPa / m to 1.56 kPa / m. On the other hand, in the implementation model 1, similarly to the reference model 2, the heat transfer rate from the pipe 5 to the water can be improved to 4663 W / m ² K, and the pressure loss is also equivalent to the reference model 1. It can be suppressed to a certain 1.31 kPa / m. Furthermore, the implementation model 1, the water side cross-sectional area of about 1.4 times larger than the 34 mm ² of 47 mm ² and the reference model 2. For this reason, when water containing metal ions such as calcium ions is heated, even if a scale that is likely to be generated in a region of 60 ° C. or higher is deposited, the first flow path 2 is less likely to be blocked, and the scale resistance is improved. improves.

  According to the heat exchanger 1A of the present embodiment, it is possible not only to improve the heat transfer coefficient but also to achieve both reduction of pressure loss and securing of scale resistance. Therefore, it is possible to provide a heat exchanger 1A that is excellent in heat exchange efficiency and can be further reduced in size.

<Modification>
The diameter D of the tubular surface 35 that defines the first flow path 2 does not need to be constant over the entire length of the first flow path 2. For example, the diameter D of the tubular surface 35 may be larger on the downstream side than on the upstream side of the first flow path 2. When water containing a large amount of metal ions such as calcium ions is heated, scale is likely to precipitate in a region of 60 ° C. or higher. If the portion close to the first fluid outlet 4 in the first flow path 2 is designed to be slightly wide, an increase in pressure loss due to scale deposition can be suppressed.

  Moreover, in the said embodiment, although the phase of the meander part 51 of both the piping 5 shifted | deviated 180 degree | times, the shift | offset | difference of the phase of the meander part 51 does not necessarily need to be 180 degree | times. For example, as shown in FIGS. 6A and 6B, the meandering portion 51 of one pipe 5 moves from the state shown in FIG. 5 by ΔP (for example, ΔP = (1/4) P1) in the Y direction. It may be. In this case, the meandering parts 51 do not contact each other (for example, only the connecting parts 52 may contact each other). Even with this configuration, the significant effects described in the above embodiment can be obtained. Alternatively, as shown in FIGS. 7A and 7B, both the pipes 5 may be moved in the Z direction from the state shown in FIG. In this case, the maximum gap G in the Z direction between the meandering portions 51 is smaller than twice the amplitude γ of the meandering portion 51.

  In the embodiment, the pipes 5 are arranged in the Z direction. However, the pipes 5 are not necessarily arranged in the Z direction. For example, when headers are provided on both sides in the Y direction of the structure 3 and a plurality of linear first flow paths 2 are provided in the structure 3 so as to connect the headers, the pipes 5 are arranged in the X direction. It is also possible.

(Second embodiment)
Next, with reference to FIG. 8 and FIG. 9 (a) and (b), the heat exchanger 1B which concerns on 2nd embodiment of this invention is demonstrated. In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof may be omitted. This is the same in the third embodiment described later.

  In the present embodiment, a plurality of convex portions 37 are provided in one opposing region 36 in each linear portion 21, but the other opposing region 36 is a plane parallel to the Z direction and close to the pipe 5. Yes. In other words, in each straight line portion 21, the distance from the facing region 36 to the pipe 5 is different, and the convex portion 37 is provided in the facing region 36 farther from the pipe 5.

  The clearance C3 in the X direction from the opposed region 36, which is a flat surface, to the pipe 5 is approximately the same as the minimum clearance C1 in the Z direction and the clearance C2 in the X direction from the tip of the convex portion 37 to the pipe 5.

  Then, the effect | action of the heat exchanger 1B of this embodiment is demonstrated.

  The water flowing into the first flow path 2 from the first fluid inlet 31 flows through the first flow path 2 toward the first fluid outlet 32 on the downstream side. In each straight portion 21, water is guided by the convex portion 37, so that the water protrudes many times from the vicinity of the pipe 5 and between the meandering portions 51 and between the meandering portion 51 and the tubular surface 35 in the X direction. It flows while repeating reduction and enlargement. Thereafter, the water flows out from the first fluid outlet 32.

  Also in the heat exchanger 1B of the present embodiment, the temperature boundary layer can be prevented from becoming thick and the dead water area can be reduced, so that the same effect as the heat exchanger 1A of the first embodiment can be obtained.

  Needless to say, the modification described in the first embodiment is also applicable to this embodiment.

(Third embodiment)
Next, with reference to FIG. 10 and FIG. 11 (a) and (b), 1 C of heat exchangers which concern on 3rd embodiment of this invention are demonstrated.

  In the present embodiment, both of the facing regions 36 in each linear portion 21 are planes parallel to the Z direction and are close to the pipe 5. That is, the cross-sectional shape of the tubular surface 35 is extended in the Z direction in each linear portion 21.

  In the opposing region 36 in each straight line portion 21, a protruding portion 38 extending in the axial direction of the tubular surface 35 is provided so as to separate a space for individually accommodating the meandering portions 51 of both pipes 5. The protruding portion 38 is continuously formed over substantially the entire length of the linear portion 21.

  The cross-sectional shape of the protruding portion 38 may be a rectangular shape, but is preferably a tapered shape such as a trapezoidal shape or a triangular shape. Moreover, it is preferable that the both sides | surfaces of the protrusion part 38 are curved surfaces which have a center of curvature on the plane which passes through the center of both piping 5. As shown in FIG. On the other hand, the region between the opposing regions 36 in the tubular surface 35 is also preferably a curved surface having a center of curvature on a plane passing through the centers of both pipes 5.

  The height of the protruding portion 38 is preferably larger than the clearance C3 in the X direction from the facing region 36 to the pipe 5.

  In the present embodiment, it is preferable that the meandering portions 51 do not contact each other (see FIG. 6B). The phase shift of the meandering portions 51 of both pipes 5 may be 180 degrees. In this case, it is preferable to separately support both pipes 5 so as not to contact each other. With such a positional relationship between the meandering parts 51, water can smoothly flow into a relatively large gap formed between the meandering parts 51. As in the first embodiment, three-dimensional The effect of activating the flow and preventing the increase in water pressure loss can be expected.

  In the heat exchanger 1C of this embodiment, since the arrangement direction of the pipes 5 and the meandering direction coincide with each other, it is not necessary to ensure a large width of the first flow path 2 in the direction orthogonal to these directions. Therefore, the cross-sectional area of the first flow path 2 can be made smaller than before, and the heat exchanger can be made smaller than before.

  Then, the effect | action of 1 C of heat exchangers of this embodiment is demonstrated.

  The water flowing into the first flow path 2 from the first fluid inlet 31 flows through the first flow path 2 toward the first fluid outlet 32 on the downstream side. In each straight line portion 21, the meandering portion is configured so that water crosses the meandering shape of the meandering portion 51 through both sides of each pipe 5 in the X direction by restricting the flow of water in the Z direction by the protrusions 38. The wide space between 51 and the wide space between the meandering part 51 and the tubular surface 35 are passed. Thereafter, the water flows out from the first fluid outlet 32.

  By the way, when water flows straight along the axial direction of the pipe 5 outside the pipe 5, since the stirring action received from the pipe 5 is small, the water has a relatively large temperature boundary layer near the surface of the pipe 5. It flows while forming.

  On the other hand, in this embodiment, water flows while undulating in the Z direction along the surface of each pipe 5 by the protrusions 38 provided in both opposing regions 36 in each linear part 21. The temperature boundary layer formed in the vicinity of the surface is less likely to grow as compared to the case where the above-described water flows straight along the axial direction of the pipe 5. By actively creating such a flow, it is possible to prevent the temperature boundary layer from becoming thick, and thus to perform more efficient heat exchange.

  Moreover, in this embodiment, since water flows along the surface of both the pipes 5, the surface of the pipe 5 can be effectively used as a heat transfer surface. In addition, the dead water area can be reduced. As the dead water area becomes smaller, the heat transfer area increases, so the heat exchange efficiency increases.

  Next, the simulation performed in order to confirm the effect of 1 C of heat exchangers of this embodiment is demonstrated. The analysis software and analysis conditions are the same as the simulation performed to confirm the effect of the first embodiment.

  First, as a comparison target, a reference model 3 as a twist type heat exchanger 6 as shown in FIG. 12 was created. The reference model 3 is obtained by changing the twist pitch of the refrigerant tubes 62 and 63 to 20 mm from the reference model 1 described in the first embodiment.

  Next, an implementation model 2 corresponding to the heat exchanger 1C of the present embodiment was created. In the implementation model 2, the height of the tubular surface 35 in the Z direction (the height on the plane passing through the centers of both pipes 5) is 10.6 mm, the outer diameter D2 of the pipe 5 is 3.9 mm, and the minimum in the Z direction. The clearance C1 and the clearance C3 in the X direction from the facing region 36 to the pipe 5 are 0.4 mm, the maximum gap G in the Z direction between the meandering portions 51 is 2 mm, the wavelength P1 of the meandering portion 51 is 10 mm, and the phase of the meandering portion 51 is shifted. Was 90 degrees. Further, the curvature radius R1 of the region between the opposing regions 36 in the tubular surface 35 is 2.35 mm, the curvature radius R2 of both side surfaces which are curved surfaces of the protrusions 38 is 2.35 mm, and the curvature centers of the curvature radii R1 and R2 are the same. The distance H between them was 2.73 mm, and the distance δ between the virtual surfaces obtained by extending both side surfaces of the protrusion 38 was 0.2 mm.

  The heat transfer coefficient and pressure loss were analyzed for reference model 3 and implementation model 2. Table 2 shows the analysis results. In Table 2, the cross-sectional area through which water flows (in the implementation model 2, the area obtained by subtracting the area occupied by both pipes 5 from the cross-sectional area of the straight portion 21 of the first flow path 2) is described as the water-side cross-sectional area. . Table 2 also shows the analysis result of the reference model 1.

In the reference model 3 in which the twist pitch of the refrigerant pipe is shortened from 40 mm to 20 mm with respect to the reference model 1, the effect of suppressing the development of the water temperature boundary layer in the vicinity of the surface of the refrigerant pipe can be obtained by promoting stirring. The heat transfer rate from water to water is improved from 2855 W / m ² K to 5183 W / m ² K. However, the pressure loss also increases from 1.31 kPa / m to 2.27 kPa / m. On the other hand, in the implementation model 2, similarly to the reference model 3, the heat transfer rate from the pipe 5 to the water can be improved to 5486 W / m ² K, and the pressure loss is also lower than that of the reference model 2. 2.19 kPa / m can be suppressed. Furthermore, in the implementation model 2, the water-side cross-sectional area is 45 mm ^2, which is about 1.3 times larger than the 34 mm ² of the reference models 1 and 3. For this reason, when water containing metal ions such as calcium ions is heated, even if a scale that is likely to be generated in a region of 60 ° C. or higher is deposited, the first flow path 2 is less likely to be blocked, and the scale resistance is improved. improves.

  According to the heat exchanger 1C of the present embodiment, not only an improvement in heat transfer coefficient but also a reduction in pressure loss and securing of scale resistance can be achieved at the same time. Therefore, it is possible to provide a heat exchanger 1C that is excellent in heat exchange efficiency and can be further reduced in size.

  In addition, in the heat exchanger 1B of the second embodiment, it is also possible to provide the protruding portion 38 described in the present embodiment in the facing region 36 where the convex portion 37 is not provided.

  The heat exchanger of the present invention has excellent heat exchange performance and is particularly useful as a heat exchanger for a heat pump type hot water heater using a refrigerant.

DESCRIPTION OF SYMBOLS 1A-1C Heat exchanger 2 1st flow path 21 Linear part 3 Structure 35 Tubular surface 36 Opposite area 37 Convex part 38 Projection part 4 Second flow path 5 Piping 51 Meandering part

Claims (9)

A heat exchanger for exchanging heat between the first fluid and the second fluid,
A structure forming a first flow path through which the first fluid flows;
Forming a second flow path through which the second fluid flows, and a plurality of pipes arranged in a predetermined direction in the first flow path,
Each of the plurality of pipes includes a meandering section that meanders in the predetermined direction so that the adjacent pipes approach or move away from each other.   The maximum gap in the predetermined direction between the meandering portions of the adjacent pipes is larger than a minimum clearance in the predetermined direction between the tubular surface defining the first flow path of the structure and the plurality of pipes. The heat exchanger according to 1. The tubular surface defining the first flow path of the structure has an opposing region facing each other across the meandering portions of the plurality of pipes in an orthogonal direction orthogonal to the predetermined direction,
The heat exchanger according to claim 1 or 2, wherein at least one of the opposing regions is provided with a plurality of convex portions that form a wave shape that undulates in the orthogonal direction along the axial direction of the tubular surface.   4. The heat exchanger according to claim 3, wherein the plurality of convex portions are provided in both of the facing regions so that the first fluid flows while undulating the first flow path in the orthogonal direction. The plurality of convex portions are provided in one of the opposing regions,
The heat exchanger according to claim 3, wherein the other of the opposed regions is a plane parallel to the predetermined direction and is close to the plurality of pipes. The tubular surface defining the first flow path of the structure has an opposing region facing each other across the meandering portions of the plurality of pipes in an orthogonal direction orthogonal to the predetermined direction,
The facing region is a plane parallel to the predetermined direction and is close to the plurality of pipes,
Each of the said opposing area | region is provided with the protrusion part extended in the axial direction of the said tubular surface so that the space which accommodates the meander part of these piping separately may be provided. Heat exchanger.   The first flow path is a serpentine-type flow path having a plurality of linear portions arranged in parallel with each other in an orthogonal direction orthogonal to the predetermined direction, and the meandering portion is disposed inside each of the plurality of linear portions. The heat exchanger according to any one of claims 1 to 6.   The said structure is a heat exchanger as described in any one of Claims 1-7 comprised with resin.   The heat exchanger according to any one of claims 1 to 8, wherein the first fluid is water and the second fluid is a refrigerant circulating in the heat pump circuit.

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