JP2008116096A - Water heat exchanger for water heater - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a water heat exchanger, improving heat exchange performance in comparatively simple and compact structure, improving heat transfer acceleration on the water side, and restraining adhesion of scales in a water side passage. <P>SOLUTION: An inner pipe 14 having a small diameter for circulating a heat exchange medium in the pipe is inserted in an outer pipe 12 having a large diameter, and supported in contact with a plurality of portions on the inner peripheral surface of the outer pipe 12 by a plurality of support legs 16 provided to project from the outer peripheral surface of the inner pipe 14 outward in the radial direction and extend in the axial direction. A plurality of spaces formed between the inner peripheral surface of the outer pipe 12 and the outer peripheral surface of the inner pipe 14 by contact supporting at the plurality of portions have an inner surface shape enclosed in a smooth curve as a whole and projecting outward, including a plurality of corner parts curved or making an obtuse angle. Thus, a passage 20 for water to be heat-exchanged is constructed. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a water heat exchanger for a water heater that performs heat exchange between a heat exchange medium and water, and in particular, for heat exchange between this and water using a refrigerant mainly composed of carbon dioxide as a heat exchange medium. The present invention relates to a water heat exchanger for water heaters.

  Conventionally, as a water heat exchanger for a hot water heater for exchanging heat between a heat exchange medium (refrigerant) and water, a flow path for circulating such a refrigerant (refrigerant side flow path) and a flow path for circulating water (water side flow path) Are used in combination with two heat transfer tubes, and various types of water heat exchangers that exchange heat between the water and the refrigerant have been used.

  In addition, as a heat exchange medium (refrigerant) used in such a water heat exchanger, a natural refrigerant having a low warming coefficient is used in place of the conventional chlorofluorocarbon refrigerant from the viewpoint of protecting the ozone layer and preventing global warming. In recent years, heat exchangers using this natural refrigerant have been developed. Among such natural refrigerants, when carbon dioxide gas is used, it is particularly attracting attention because high-temperature and high-pressure gas conditions can be obtained.

  By the way, as a heat exchanger of such a system that performs heat exchange between the refrigerant mainly composed of carbon dioxide gas and water, the refrigerant internally is disclosed as disclosed in Patent Documents 1 to 4. Various proposals have been made in which one heat exchanger is configured by combining a heat transfer tube through which water is circulated and a heat transfer tube through which water is circulated.

  For example, in Japanese Patent Application Laid-Open No. 2003-214778 (Patent Document 1), a hollow portion is formed along the axial direction on the peripheral wall of a first heat exchange pipe through which the heat exchange liquid flows, and the inside of the hollow portion In addition, a second heat exchange pipe through which a predetermined heat medium flows is disposed inside, and the first heat exchange pipe and the second heat exchange pipe are brazed and integrated to form a gap between the two. The heat of the heat medium flowing in the second heat exchange pipe is transmitted to the heat exchange liquid flowing in the first heat exchange pipe via the brazing material, so that the heat exchange is performed. Things have been revealed.

  On the other hand, in Japanese Patent Application Laid-Open No. 2003-202194 (Patent Document 2), a plurality of small-diameter thin tubes constituting the refrigerant passage are provided on the inner wall of the core tube on the inner peripheral surface of the large-diameter core tube constituting the water passage. A heat exchanger is disclosed that is arranged in parallel to the longitudinal direction along the longitudinal direction and integrally assembled by brazing or the like. Further, in Japanese Patent Laid-Open No. 2002-122390 (Patent Document 3), a large number of fine tubes in which a refrigerant is circulated are arranged coaxially in a water tube in which water to be heat-exchanged is circulated. A so-called double tube heat exchanger has been clarified.

  Moreover, as what can improve the heat-transfer acceleration | stimulation effect of such a double pipe type heat exchanger, in JP 2001-201275 A (patent documents 4), a double pipe which consists of an inner pipe and an outer pipe In the heat exchanger of the type, a heat transfer facilitator that interposes the flow path formed between the inner pipe and the outer pipe in a spiral manner is interposed to increase the flow path length of the flow path and to flow the fluid A double-tube heat exchanger that increases the flow rate and turbulence of the pipe to facilitate heat transfer from the fluid flowing in the inner pipe to the fluid flowing between the inner pipe and the outer pipe. Has been.

  However, among those proposed technologies, for example, the one disclosed in Patent Document 1 is a recess for fitting the second heat exchange pipe that is the refrigerant side flow path into the first heat exchange pipe that is the water side flow path. The problem is that the pressure loss on the water side increases because the outer wall portion of the first heat exchange pipe protrudes into the water side flow path. Further, even in the one disclosed in Patent Document 2, a small-diameter thin tube serving as a refrigerant passage is brazed and integrated on the inner peripheral surface of a large-diameter core tube serving as a water passage. As with the heat exchanger disclosed in Patent Document 1, the pressure loss on the water side increases. And as the pressure loss on the water side increases in this way, it is necessary to increase the capacity of the water supply pump for the countermeasure, since there is a possibility that the head of the water supply pump will be insufficient. As a result, the problem of causing an increase in production cost as a whole of the hot water heater is newly induced.

  In addition, as in the heat exchangers disclosed in Patent Document 1 and Patent Document 2, the pipe body serving as the water-side flow path and the pipe body serving as the refrigerant-side flow path are joined by brazing, and the heat exchanger is In the configuration, due to such a brazing failure in the brazing portion, there is a drawback that the contact area between the refrigerant-side flow path and the water-side flow path is likely to be insufficient, resulting in performance variations. Furthermore, there is a problem that the yield is likely to decrease due to poor brazing and the production cost is increased.

  On the other hand, in the double-pipe heat exchanger disclosed in Patent Document 3, the coolant channel on the high temperature side is completely enclosed in the water channel on the low temperature side. Therefore, it is possible to suppress the heat of the refrigerant from being released to the outside air, as compared with the configuration in which the water-side channel tube and the refrigerant-side channel tube are joined by brazing. However, in order to increase the heat transfer area to the water side, there is a problem that it is difficult to reduce the size of the heat exchanger because it is necessary to increase the flow path length.

  Thus, as a method for enhancing the water-side heat transfer enhancement effect of such a double-tube heat exchanger, in Patent Document 4, a water-side channel (outer tube) and a refrigerant-side channel (inner tube) ), A structure in which a spiral heat transfer facilitator is interposed is clarified. However, in the heat exchanger disclosed in such a document, a problem that a problem of scale formation in the water-side flow path is likely to be newly generated. In other words, by using the heat exchanger for a long period of time, components such as calcium contained in tap water precipitate as scales in the water flow channel, adhere to the flow channel wall, and the amount of adhesion (thickness) As the time increases with time, the channel will eventually be blocked. Therefore, when the scale adheres to some extent, it is necessary to remove the adhered scale. However, the existence of a spiral heat transfer facilitator interposed in the water-side flow path is necessary. This makes it very difficult to do that. For this reason, in reality, the entire heat exchanger is replaced, and this inherently has a problem that leads to a deterioration in operation costs.

  In addition, in such a double-pipe heat exchanger, if there are corners or acute-angled recesses in the water-side flow passage formed in the interior of the double-tube heat exchanger, the water flow in that part stagnates, so that heat transfer is performed to other parts. It will deteriorate more. Moreover, in such a corner | angular part, peeling flow, such as a secondary vortex, arises, and the peeling flow also causes the fall of the local heat transfer coefficient in a corner | angular part. And in the area | region where the local heat transfer rate fell, the wall surface superheat degree will increase and the concentration of the scale component in water will advance in the part, As a result, components, such as calcium contained in tap water, However, it becomes easy to precipitate as a scale, and this also increases the above-mentioned problem.

JP 2003-214778 A JP 2003-202194 A JP 2002-122390 A JP 2001-201275 A

  Here, the present invention has been made in the background of such circumstances, and the problem to be solved is that the heat exchange performance is greatly improved with a relatively simple and compact structure. It is to provide a water heat exchanger for hot water heaters that can be produced, and another object is to effectively improve the heat transfer on the water side and to effectively adhere the scale in the water side flow path. There is also the provision of a water heat exchanger that can be suppressed in a controlled manner.

  And in this invention, in order to solve such a subject, one thin inner pipe | tube through which the predetermined heat exchange medium distribute | circulates the inside of a pipe | tube is separate from the inside of a large diameter outer pipe | tube. Inserted into the outer peripheral surface of the inner tube and supported in contact with the inner peripheral surface of the outer tube at a plurality of locations by a plurality of support legs that protrude radially outward from the outer peripheral surface and extend in the axial direction. As a whole, a plurality of spaces formed between the inner peripheral surface of the outer tube and the outer peripheral surface of the inner tube by contact support at a location are configured to include a plurality of corner portions having a curved shape or an obtuse angle. The gist is a water heat exchanger for a hot water heater, characterized in that it is formed as an outwardly convex inner surface shape surrounded by, and is configured as a flow path of water to be heat exchanged.

  In addition, according to one of the desirable aspects of the water heat exchanger for a hot water heater according to the present invention, as the inner pipe, a heat transfer pipe provided with heat transfer promotion means on its inner surface is advantageously used. As the outer tube, a heat transfer tube provided with heat transfer promoting means on its inner surface is used.

  Moreover, according to the other one of the desirable aspects of the water heat exchanger for water heaters according to this invention, it is desirable that the said inner pipe | tube is comprised with copper or a copper alloy.

  Furthermore, according to another desirable aspect of the present invention, a refrigerant mainly composed of carbon dioxide gas is used as the heat exchange medium.

  As described above, in the water heat exchanger for a water heater according to the present invention, an inner tube with a single small diameter is placed in a large-diameter outer tube so that the inner surface of the outer tube contacts a plurality of locations. By being inserted and formed, the heat exchange medium side flow path and the water side flow path can be advantageously formed in a relatively simple and compact structure, and the heat exchange medium side flow The partition wall between the channel and the low-temperature water-side channel has no crimping part or brazing part, so that heat loss during heat transfer between them can be effectively suppressed. The effect of promoting heat transfer to the side can be advantageously increased.

  Moreover, in the water heat exchanger for a hot water heater according to the present invention, a plurality of spaces formed between the outer peripheral surface of the outer tube and the outer peripheral surface of the inner tube are surrounded by a smooth curve that is convex outward. It is possible to effectively suppress the generation of secondary vortices, which is a major factor in scale generation, because it is formed in the inner surface shape that gives the cross-sectional shape to be formed and is configured as a water-side flow path. Therefore, the generation of scale in the water side channel is effectively suppressed or prevented, and the heat loss due to the generation of such scale is advantageously suppressed, and the heat exchange performance is greatly improved. It can be achieved effectively.

  Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

  First, FIG.1 and FIG.2 shows one Embodiment of the water heat exchanger according to this invention. 1 shows such a water heat exchanger in the form of a cross-sectional view, and FIG. 2 shows the water heat exchanger shown in FIG. 1 in a longitudinal cross-sectional view (A-A cross section in FIG. 1). In the form, each is shown. As is clear from these drawings, the water heat exchanger 10 has a thin inner tube 14 having a substantially rectangular cross-sectional shape that is separate from the outer tube 12 having a large diameter. Each of the support legs 16 extending outward from the four corners is coaxially supported and fixedly positioned.

  More specifically, the outer tube 12 is formed using a predetermined metal material such as copper or copper alloy, and generally has an outer diameter of about 8 to 20 mm and a wall thickness of about 0.3 to 1.0 mm. It is composed of a pipe body having a circular cross section. Similarly to the outer tube 12, the inner tube 14 is formed in a rectangular tube shape having a substantially rectangular cross-sectional shape using a predetermined metal material such as copper or copper alloy, and each corner is formed. The portions are respectively configured as support legs 16 that protrude outward in the pipe radial direction and extend in the axial direction. In addition, the outer peripheral surface of each side of the inner tube 14 is a curved surface 18 provided by a smooth continuous curved surface that is recessed inward in the radial direction together with the side surfaces of the support legs 16 and 16 located on both sides in the circumferential direction. It is composed of. On the other hand, as shown in FIG. 1, each of the inner pipes 14 has apexes (singular points) inside the integrally provided support legs 16, and each apex is inward. An inner hole having a substantially rectangular cross-sectional shape connected by a concave curve is formed. Further, the tip end portions of the support legs 16 integrally provided at the respective corner portions of the inner tube 14 are formed so as to exhibit a fan-shaped shape that curves and spreads outward on both side surfaces thereof. It is.

  Then, by using the outer tube 12 and the inner tube 14 formed separately, the inner tube 14 is inserted into the outer tube 12, and the outer tube 12 is reduced in diameter by drawing or the like. The tips of the four support legs 16 of the tube 14 are brought into contact with and closely attached to the inner peripheral surface of the outer tube 12, so that the inner peripheral surface of the outer tube 12 and the outer peripheral surface of the inner tube 14 are The space between the two is divided into four, and independent water-side flow paths 20 are formed in the direction of the pipe axis, while the inside of the inner pipe 14 is a flow path 22 of a predetermined heat exchange medium. The double-pipe structure water heat exchanger 10 is configured. Moreover, in such a water heat exchanger 10, the side surface of the distal end portion of the support leg 16 is configured in a curved shape, and is thus connected in a continuous form to the inner surface of the outer tube 12. The four water-side flow paths 20 formed between the inner pipe 14 and the inner pipe 14 are all substantially elliptical cross-sections, and are outwardly convex inner surfaces (inner sides) surrounded by a smooth curve as a whole. In other words, it is configured so as to exhibit a shape in which no convex portion exists.

  Therefore, in the water heat exchanger 10 having such a structure, a predetermined high-temperature heat exchange medium, in particular, a refrigerant mainly composed of carbon dioxide gas is circulated in the pipe internal flow path 22 of the inner pipe 14. Low-temperature water to be heated is circulated in the four substantially elliptical water-side flow paths 20 formed between the outer tube 12 and the inner tube 14. The flow path 20 is configured in an inner surface shape surrounded by a curved smooth curve that protrudes outward in the cross-sectional shape thereof, and does not exhibit a complicated cross-sectional shape, thereby effectively suppressing heat loss. On the other hand, the generation of secondary vortices, which is a major factor in scale generation, can be advantageously suppressed or prevented, so that scale adhesion in the water-side channel 20 is effectively suppressed. Because it is supposed to be .

  In short, due to the long-term use of heat exchangers, components such as calcium contained in tap water precipitate as scales, adhere to the flow channel walls, accumulate, and block the flow channel. In the water heat exchanger 10 according to the embodiment, since the water-side flow path 20 has a substantially elliptical smooth curve in its cross-sectional shape, generation of secondary vortices is effectively suppressed. Therefore, even if the scale is generated, it is easy to remove the scale because of the shape of the inner surface constituted by a smooth curve. For example, by adopting a means such as washing with a normal pipe cleaning agent, it is possible to cope with it sufficiently.

  Further, in the water heat exchanger 10 having such a configuration, a single small-diameter inner tube 14 is provided on the inner peripheral surface of the outer tube 12 at a plurality of locations ( Here, since it is inserted and configured so as to be in contact at four locations), it can be formed compactly with a relatively simple structure, and the heat exchange medium flow path 22 and the low-temperature water-side flow path can be formed. There is no crimping part or brazing part in the partition between 20 and the conventional water heat exchanger, so that it is possible to effectively suppress heat loss. .

  Here, by using copper or a copper alloy having high thermal conductivity as the material of the outer tube 12 or the inner tube 14, the heat of the heat exchange medium circulated in the inner tube 14 is changed to the outer tube. 12 can be effectively transmitted to the water circulated in the outer water-side flow path 20 formed between the inner pipe 14 and the inner pipe 14. The heat exchange efficiency can be effectively improved.

  Furthermore, by using a refrigerant mainly composed of carbon dioxide as a heat exchange medium that can be circulated through the flow path 22 in the inner pipe 14, there is a risk of ozone layer destruction as in the case of conventional chlorofluorocarbon refrigerants. Since the problem of global warming can be advantageously eliminated and high-temperature and high-pressure gas conditions can be obtained, even when such a water heat exchanger is used as a single-stage heat exchanger, The advantage that can be obtained can also be enjoyed.

  By the way, the water heat exchanger 10 having such a structure in which the tips of the plurality of support legs 16 extending integrally from the outer peripheral surface of the inner tube 14 are brought into contact with the inner peripheral surface of the outer tube 12 as described above. For example, it is manufactured by the following method.

  First, as the outer tube 12 and the elementary tube that gives the inner tube 14, tubes having simple circular cross sections are prepared. Here, as an example, a tube having a simple cylindrical cross section with an outer diameter of 9.52 mm and a wall thickness of 0.5 mm is prepared as the outer tube 12, while the raw tube that provides the inner tube 14 has an outer diameter. A tube having a simple circular cross section with a thickness of 7.00 mm and a thickness of 0.5 mm is prepared. Note that the materials of these two pipes are both phosphorous deoxidized copper (JIS H 3300 C1220).

  Then, a plurality of dies having convex portions having curved surfaces are pressed against the outer surface (outer peripheral surface) of the simple circular cross-section element tube that gives the inner tube 14, and the distance between the dies is gradually reduced. Thus, a plurality of (here, four) concave portions (18) made of a curved surface are formed on the outer surface symmetrically in the circumferential direction, and the connecting portions of the adjacent concave portions project outward as support legs 16 The formed deformed tube is manufactured. The size of the deformed tube is such that it is approximately inscribed in the inner peripheral surface of the tubular body that gives the outer tube 12, in other words, can be inserted smoothly, and as much as possible with the inner peripheral surface. The dimensions are such that the gap between them is small.

  Subsequently, the deformed tube (inner tube 14) thus obtained was inserted into the tube body as the outer tube 12, and one end of the tube (outer tube) and the deformed tube (inner tube) was fixed. In this state, the tip end portion of the support leg 16 of the inner tube 14 made of a deformed tube is brought into close contact with the inner peripheral surface of the outer tube 12 constituted by such a tube body by drawing using a diameter reducing die. By doing so, the water heat exchanger 10 in which four of the substantially elliptical water-side flow paths 20 as shown in the figure are formed is completed. In addition, in the case of using the outer tube or the inner tube for the above-described size, the elliptical shape of the water-side flow path 20 formed in the water heat exchanger 10 has a major axis of about 5.5 mm and a minor axis of about 5. It is about 2.3 mm.

  Further, in the water heat exchanger 10 having such a configuration, the space between the inner tube 14 and the outer tube 12 is formed at a plurality of locations by the support legs 16 extending integrally from the inner tube 14. The plurality of water-side flow paths (20) that are formed in the transverse cross-section have a substantially elliptical shape as illustrated, or a circular shape, which indicates that secondary vortices are generated in the water-side flow path (20). For this reason, the curved surface 18 has a smooth curve at the abutting portion of the distal end portion of the support leg 16 of the inner tube 14 with respect to the inner peripheral surface of the outer tube 12. It is desirable to have a curved (R) shape as shown in FIG. 1 so as to be connected to the inner peripheral surface of the tube 12. 3A to 3C show various connection forms with the inner surface of the outer tube 12 at the tip of the support leg 16, and in FIG. 3A, the connection is made with a curved (R) shape. Moreover, in (b), it is formed including a plurality of corners that make an obtuse angle, and in (c), it is connected with corners that make an acute angle.

  And in the connection form with respect to the inner peripheral surface of the outer tube 12 as shown in FIG. 3, the secondary vortex suppressing effect in the water side flow path (20) is (b), compared with the connection structure of (c), In the present invention, the connection structure (a) or (b) is advantageously employed because the connection structure (a) becomes better in order. Further, even in such a connection structure as shown in (a), since the radius of curvature of the R shape becomes better as the radius of curvature increases, in the present invention, an R shape having a radius of curvature as large as possible is obtained. , Will be advantageously employed. Further, the side surface shape of the support leg 16 in the inner tube 14 with respect to the inner peripheral surface of the outer tube 12 is selected so that the R shape shown in (a) and the polygonal shape shown in (b) are selected, and the outer tube The assembly and integration of 12 and the inner pipe 14 are performed.

  As described above, one of the representative embodiments of the present invention has been described in detail. However, this is merely an example, and the present invention is not limited by the specific description according to such an embodiment. It should be understood that this is not to be construed as limiting.

  For example, in the above-described embodiment, four water-side flow paths 20 are formed between the outer pipe 12 and the inner pipe 14, but the number of such water-side flow paths 20 is any number. For example, as shown in FIG. 4, even if three water-side channels 20 are formed, as shown in FIGS. 5 and 6, eight water-side channels 20 are formed. Even if it is done, there is no problem. Furthermore, the shape of the flow path 22 of the heat exchange medium formed in the inner pipe 14 is not limited to the shape of the water side flow path 20, and various cross-sectional shapes can be adopted. Even if it is a circular cross-sectional shape as shown, even if it is a flow path 22 having a shape protruding inward corresponding to the water side flow path 20 as shown in FIG. 6, there is no problem. .

  And even if it exists in the external shape of the outer tube | pipe 12, it is also possible to comprise the target water heat exchanger 10 as a rectangular shape as shown in FIG. 7 besides the circular shape as shown in FIGS. It is.

  Further, in the water heat exchanger 10 according to the present invention, in order to advantageously realize heat exchange between the heat exchange medium and the water via the inner tube 14, the inner surface of the inner tube 14 is Similarly, it is effective to increase the heat transfer area on the heat exchange medium side by providing grooves and protrusions or providing a fine structure surface, an example of which is shown in FIG. In this case, a large number of protrusions 24 are integrally provided on the inner peripheral surface of the inner tube 14 so as to be brought into contact with a heat exchange medium circulated in the flow path 22.

  Furthermore, as a method for increasing the heat transfer area on the water side, as shown in FIG. 9, a protrusion 26 is provided integrally on the inner surface of the outer tube 12, or a groove is provided instead of such a protrusion 26. It is also possible to provide a fine structure surface. In particular, by forming the projections 26 as shown in FIG. 9 on the inner surface of the outer tube 12, it is possible to exert an action of peeling the scales when they reach a certain amount.

  In addition, in the above-described embodiment, a heat transfer tube having a simple structure that allows a predetermined heat exchange medium to flow through the tube is used as the inner tube 14, but for example, as shown in FIG. It is also possible to employ a heat transfer tube having a structure in which a leakage detection function 28 is provided on the inner peripheral surface. In addition, about the structure of the inner tube | pipe 14 as such a heat exchanger tube which has such a leak detection function, since the well-known structure clarified in Unexamined-Japanese-Patent No. 2005-69620 etc. can be employ | adopted as it is. The details are omitted here.

  In addition, even in the flow direction of the water that flows through the flow path 20 and the heat exchange medium that flows through the flow path 22, as shown in FIG. It goes without saying that it can be distributed.

  In addition, although not enumerated one by one, the present invention is carried out in a mode to which various changes, modifications, improvements, etc. are added based on the knowledge of those skilled in the art. It goes without saying that any one of them falls within the scope of the present invention without departing from the spirit of the present invention.

It is explanatory drawing of the cross section used as the cross section of the direction perpendicular | vertical to a pipe axis which shows an example of the water heat exchanger for water heaters according to this invention. It is AA cross-section explanatory drawing in FIG. It is sectional explanatory drawing which shows the form by which the front-end | tip part of the support leg extended from an inner pipe is connected to the inner surface of an outer pipe, Comprising: (a)-(c) has shown the different connection form, respectively. It is sectional explanatory drawing corresponding to FIG. 1 which shows another example of the water heat exchanger according to this invention. It is a section explanatory view corresponding to Drawing 1 showing still another example of the water heat exchanger according to the present invention. It is sectional explanatory drawing corresponding to FIG. 1 which shows another example of the water heat exchanger according to this invention. It is sectional explanatory drawing corresponding to FIG. 1 which shows another example of the water heat exchanger according to this invention. It is sectional explanatory drawing corresponding to FIG. 1 which shows a different example of the water heat exchanger according to this invention. It is sectional explanatory drawing corresponding to FIG. 1 which shows a further different example of the water heat exchanger according to this invention. It is sectional explanatory drawing corresponding to FIG. 1 which shows another example from which the water heat exchanger according to this invention differs.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Water heat exchanger 12 Outer tube 14 Inner tube 16 Support leg 18 Curved surface 20 Water side channel 22 Channel 24, 26 Protrusion 28 Leak detection function

Claims (5)

  One thin inner tube through which a predetermined heat exchange medium is allowed to flow is inserted into a large outer tube separate from the inner tube, and protrudes radially outward from the outer peripheral surface of the inner tube; A plurality of support legs extending in the axial direction are supported by being brought into contact with the inner peripheral surface of the outer tube at a plurality of locations, and between the inner peripheral surface of the outer tube and the outer peripheral surface of the inner tube by contact support at the plurality of locations. The plurality of spaces formed in the shape of the curved surface or the plurality of corners having an obtuse angle are formed into an outwardly convex inner surface shape surrounded by a smooth curve as a whole, and are subjected to heat exchange. A water heat exchanger for a hot water heater, characterized by being configured as a flow path for water.   The water heat exchanger for a hot water heater according to claim 1, wherein the inner pipe is a heat transfer pipe having an inner surface provided with heat transfer promoting means.   The water heat exchanger for a hot water heater according to claim 1 or 2, wherein the outer pipe is a heat transfer pipe having an inner surface provided with heat transfer promotion means.   The water heat exchanger for a hot water heater according to any one of claims 1 to 3, wherein the inner pipe is made of copper or a copper alloy. The water heat exchanger for a hot water heater according to any one of claims 1 to 4, wherein the heat exchange medium is a refrigerant mainly composed of carbon dioxide gas.

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