JP4729973B2 - Heat exchanger and hot water device provided with the same - Google Patents

Description

  The present invention relates to a heat exchanger used for recovering heat from combustion gas, and a hot water apparatus including the heat exchanger.

  Conventional examples of heat exchangers include those described in Patent Documents 1 and 2. As shown in FIG. 36, the heat exchanger described in Patent Document 1 has a configuration in which a coiled tubular portion 40e for heat exchange is arranged in a can body 2e. The bottom of the space 3e surrounded by the coiled tubular body 40e is closed by a partition member 6e. In this heat exchanger, when combustion gas is introduced from the upper portion of the can body 2e, the combustion gas flows from the space portion 3e to the outside through the gap between the coiled tube portion 40e, and then the can body. 2e is discharged to the outside through the lower opening. On the other hand, a medium is supplied to one end of the coiled tube body 40e, and this medium is heated by the combustion gas. This heated medium flows out from the other end of the coiled tube 40e. In this heat exchanger, the coiled tube portion 40e is composed of one spiral tube, and the structure thereof is, for example, compared to a heat exchanger of a type using a number of finned tubes. It's pretty simple. Therefore, it is suitable for reducing the manufacturing cost and reducing the overall size.

  On the other hand, as shown in FIG. 37, the heat exchanger described in Patent Document 2 has a configuration in which a coiled water tube 96 is provided in a can body 91A in which a burner 90A is disposed at the bottom. . A baffle 97A for preventing the passage of combustion gas to the inside of the loop portion 96a and a passage of the combustion gas to the gap around the outer periphery of the loop portion 96a are provided in the plurality of loop portions 96a of the water pipe 96 and its outer periphery. The baffles 97B are alternately provided. According to such a configuration, the combustion gas alternately proceeds inward and outward for each loop portion 60 a of the water pipe 96, and the heat transfer amount of the combustion gas to the water pipe 96 can be increased.

  However, the prior art described above has the following problems.

  That is, in the prior art shown in FIG. 36, the coiled tube part 40e for heat exchange is merely formed by using one spiral tube, and thus is introduced into the space 3e. The degree to which the combustion gas contacts the coiled tube body 40e is small. In particular, the degree of contact when the combustion gas passes through the gap between the coiled tube portions 40e is small, and the amount of heat transfer at that time is small. Therefore, in the prior art, the heat exchange efficiency is low. In recent years, there has been a strong demand to increase the heat exchange efficiency of heat exchangers from the viewpoints of environmental protection by saving fuel, reduction of running costs, and various other aspects. As an effective means for improving the heat exchange efficiency, in addition to recovering sensible heat from the combustion gas, it is conceivable to recover latent heat (more accurately, the latent heat of water vapor in the combustion gas is recovered). However, according to the prior art, such latent heat recovery is difficult.

  On the other hand, the prior art shown in FIG. 37 has a complicated structure in which a large number of baffles 97A and 97B are provided in the can body 91A in the same number as the loop portion 96a. In addition, the plurality of baffles 97A and 97B have a diameter equal to or greater than that of the loop portion 96a and are large in size. Therefore, the manufacturing cost is expensive. Further, the plurality of baffles 97A and 97B cause a loss of absorbing heat from the combustion gas by contact with the combustion gas. If the number of these baffles is large, the overall heat capacity in the can 91A increases. . In this case, for example, the rising speed of the water temperature in the water pipe 96 at the start of hot water supply is slow, and the ability when used in an instantaneous hot water apparatus is inferior. Furthermore, since the water pipe 96 is formed by using only one spiral tube body as in the prior art shown in FIG. 36, a high heat exchange efficiency is achieved for a complicated overall structure. It was difficult to get.

Japanese Utility Model Publication No. 61-69676 JP 59-66646 A

  The present invention has been conceived under such circumstances, and a heat exchanger and hot water that can increase the efficiency of heat exchange while simplifying and downsizing the entire structure The problem is to provide an apparatus.

  In order to solve the above-described problems, the present invention takes the following technical means.

The heat exchanger provided by the first aspect of the present invention has a cylindrical peripheral wall portion, and a can body in which an opening for a combustor and a combustion gas outlet are formed at both ends in the axial length direction, A coiled tube part for heat exchange having a plurality of loop parts arranged in the can body so as to be arranged in the axial length direction through a gap, and surrounded by the coiled tube part, and One end of the combustion gas formed between the space communicating with the combustor opening, the coiled tube body, and the peripheral wall of the can body is guided to the combustion gas outlet. A heat exchanger, comprising: at least one additional coiled tube portion having a different diameter or width of each loop portion from the coiled tube portion; and A plurality of loop portions are arranged in the axial length direction and the direction intersecting with the axial length direction. In addition, the tubular body wrapping structure portion in which the plurality of coiled tubular body portions are overlapped and a middle portion in the axial length direction of the space portion are closed to thereby make the space portion first in the axial length direction. And a partition member that divides the tubular body winding structure portion into first and second heat exchange portions that surround the first and second regions, The combustion gas introduced or generated in the first region passes through the gap in the first heat exchange section from the first region and proceeds to the combustion gas passage, and then the second heat exchange. The plurality of coiled tube parts are not uniform in diameter, and the innermost coiled part of the plurality of coiled tube parts is configured to pass through the gaps of the parts. The tube diameter of the tube portion is maximized, and the amount of water flow in the innermost coiled tube portion In addition to being increased, a step is formed in each gap between the innermost coiled tube part and the outer coiled tube part, and the combustion gas is the innermost coiled tube part. It is characterized by being configured to collide with the outer coiled tubular part after passing through the gap of the body part .

  According to the present invention, the following effects can be obtained.

  First, when combustion gas is introduced into the first region of the space portion surrounded by the tubular body winding structure portion or combustion gas is generated in the first region, the combustion gas is converted into the first region. In addition to heating the first heat exchange part of the tubular body winding structure part surrounding the region, the process of passing through the gap of the first heat exchange part and proceeding to the combustion gas path, In each of the proceeding process and the process of passing through the gap of the second heat exchange section after passing through the combustion gas passage, heat transfer is performed in contact with the plurality of coiled tube sections. In particular, when the combustion gas passes through the gap between the first and second heat exchange parts, it sequentially passes between a plurality of loop parts arranged in a direction intersecting the axial length direction. Therefore, the number of times that the combustion gas comes into contact with the plurality of coiled tube portions is increased, and the degree of contact thereof is increased, so that the amount of heat transfer at that time can be increased. For this reason, it is possible to increase the heat exchange efficiency as compared with the prior art.

  Secondly, since the tubular body winding structure part is divided into the first and second heat exchange parts, for example, the sensible heat is recovered from the combustion gas by the first heat exchange part, and the second heat exchange part. The latent heat can be recovered by the unit. As a result, the heat exchange efficiency can be further increased, and the drain associated with the latent heat recovery can be intensively generated in the second heat exchanging portion to facilitate the drain recovery.

  Thirdly, the first and second heat exchanges have a very simple configuration in which the space surrounded by the tubular body winding structure is partitioned into first and second regions using a partition member. Compared with the prior art in which many baffles of the same number as the loop part of the coiled tube part are used, the configuration is much simpler. Therefore, the manufacturing cost can be reduced. Further, if it is not necessary to provide a large number of baffles, the heat capacity in the can body becomes uselessly large, and the problem that the rising speed of the water temperature at the start of hot water supply is slowed down. It will be a thing.

Fourthly, in the present invention, although the number of coiled tube parts is increased as compared with the prior art, the plurality of coiled tube parts are provided in an overlapping manner. For this reason, it is possible to reduce the size of the entire heat exchanger by preventing the entire coiled tube part from becoming extremely large compared to the size of the coiled tube part of the prior art. It is.
Further, the innermost coiled tube portion of the tubular body winding structure surrounds the first region where the combustion gas is introduced or the combustion gas is generated, and this portion has the highest temperature by the combustion gas. This is the part that is heated. In the present invention, the tube diameter of the portion is the maximum, and the amount of water passing through the portion can be increased, so that the amount of heat recovered from the combustion gas is increased and the heat exchange efficiency is increased. Is preferred. Furthermore, in the present invention, the degree of contact between the coiled tube portion and the combustion gas is increased, and the heat exchange efficiency is further increased.

  In a preferred embodiment of the present invention, each of the coiled tube portions is configured using a spiral tube body in which the plurality of loop portions are spirally connected.

  According to such a configuration, it is possible to easily manufacture each coiled tube portion. Moreover, the structure for allowing each coil-shaped tube part to pass water can also be simplified.

  In a preferred embodiment of the present invention, the first and second heat exchange parts are partitioned by the partition member or a member separate from the partition member.

  According to such a configuration, when the combustion gas enters the vicinity of the boundary with the second heat exchange portion in the first heat exchange portion, the combustion gas does not flow out into the combustion gas passage as it is. It can prevent appropriately passing through the inside of the 2nd heat exchange part, and progressing to the 2nd field. As a result, the amount of combustion gas that travels through an appropriate path with respect to the gap of the second heat exchange section can be increased.

  In a preferred embodiment of the present invention, the combustor opening in the combustion gas passage is closed from the first region to the space between the end portion of the tubular body winding structure and the can body. A combustion gas stopper portion is provided that suppresses advancing directly to the close start end portion.

  According to such a configuration, the amount of the combustion gas that progresses in a short circuit toward the start end portion of the combustion gas passage without passing through the gap of the first heat exchange portion from the first region is eliminated or reduced, It is possible to increase the amount of combustion gas that travels through an appropriate path with respect to the gap of the first heat exchange section.

  In a preferred embodiment of the present invention, the combustion gas passage is formed in a series across the outer periphery of each of the first and second heat exchange parts, And a combustion gas stopper portion that blocks the end portion near the combustion gas outlet and suppresses the combustion gas that has reached the end portion from directly proceeding to the second region.

  According to such a configuration, the amount of combustion gas that progresses in a short-circuited manner with respect to the combustion gas outlet without passing through the gap between the end portion of the combustion gas passage and the second heat exchange portion is reduced or reduced, It is possible to increase the amount of combustion gas that travels along an appropriate route with respect to the second heat exchange unit.

  In a preferred embodiment of the present invention, each of the second heat exchange portion and the combustion gas passage is divided into two divided portions in the axial length direction, and the first heat is out of the combustion gas passages. A first auxiliary partition member that guides the combustion gas that has passed through the periphery of the exchanging portion to the second region by advancing through a gap in one divided portion of the second heat exchanging portion; and the second region The second auxiliary partition that suppresses the combustion gas introduced to the combustion gas outlet from proceeding to the combustion gas outlet and advances the combustion gas to the gap of the other one divided portion of the second heat exchange portion. And a member.

  According to such a configuration, the tubular body winding structure portion is substantially divided into three portions (the two divided portions of the first heat exchange portion and the second heat exchange portion) in the axial length direction of the can body. It is subdivided, and the combustion gas can be appropriately applied to each of the subdivided portions. Therefore, it is possible to cause the combustion gas to uniformly act on the entire area of the tubular body winding structure and further increase the heat exchange efficiency. In addition, if the tubular wrapping structure is subdivided, the combustion gas flow passage area of the subdivided portion is reduced, and the flow velocity of the combustion gas can be increased. Is improved.

  In a preferred embodiment of the present invention, the tubular body winding structure portion is further extended closer to the combustion gas outlet than the second auxiliary partition member, and of the combustion gas passage, The combustion gas that has traveled to the portion surrounding the extended portion is configured to further pass through the gap between the extended portions.

  According to such a configuration, the tubular body winding structure is subdivided into more parts, and the combustion gas acts uniformly on these parts, so that the heat exchange efficiency can be further improved. It becomes possible.

  In a preferred embodiment of the present invention, the water entering the plurality of coiled tube sections is made to the second heat exchange section, and the water that has passed through the second heat exchange section is then the first heat exchange section. It is set as the structure which flows into the heat exchange part.

  According to such a configuration, since the non-heated relatively low-temperature water is supplied to the second heat exchange unit, the amount of heat recovered by the second heat exchange unit is increased, and this portion This is suitable for recovering latent heat.

  In a preferred embodiment of the present invention, the first and second heat exchanging portions are configured such that the sizes of the gaps are different.

  According to such a configuration, for example, the ratio of the heat recovery amounts of the first and second heat exchange units can be easily set to a desired ratio.

The hot water device provided by the second aspect of the present invention is a hot water device comprising a combustor and a heat exchanger for performing heat recovery from the combustion gas generated by the combustor. ,
As the heat exchanger, the heat exchanger provided by the first aspect of the present invention is used.

  According to such a configuration, the same effect as described for the heat exchanger provided by the first aspect of the present invention can be obtained.

  In a preferred embodiment of the present invention, the heat exchanger is provided in a posture in which the opening for the combustor is higher than the combustion gas outlet, and the combustor is connected to an upper portion of the heat exchanger. And a bottom casing for connecting the combustion gas that has passed downward through the combustion gas outlet to the exhaust port is connected to the lower part of the heat exchanger. .

  The hot water apparatus having the above configuration is a so-called reverse combustion type, and the basic flow direction of the combustion gas is downward. Therefore, when a drain is generated in the tubular body winding structure, the drain can be made to actively flow downward due to the flow of gravity and combustion gas. As a result, the drain is easily collected at the bottom of the can body and processed.

  In a preferred embodiment of the present invention, a drain receiving portion provided in the can of the heat exchanger and receiving a drain flowing down from the tubular body winding structure portion, and a drain received by the drain receiving portion are provided. Drain discharge means for discharging to the outside of the heat exchanger so as not to flow into the bottom casing.

  According to such a configuration, the drain discharge process can be performed so that the inside of the bottom casing is not contaminated by the drain.

  In a preferred embodiment of the present invention, the heat exchanger is configured to guide a drain flowing down from the tubular body winding structure portion to the combustion gas outlet, and the combustion gas is disposed in the bottom casing. A drain receiving member is provided for receiving the drain flowing down from the outlet and discharging it to the outside of the bottom casing.

  According to such a configuration, the combustion gas outlet is effectively used as the drain outlet, which is suitable when it is desired to simplify the configuration of the heat exchanger. Further, since the drain is received and discharged using a drain receiving member provided in the bottom casing, the inside of the bottom casing can also be prevented from being contaminated by the drain.

  In a preferred embodiment of the present invention, the heat exchanger is configured to guide a drain flowing down from the tubular body winding structure portion to the combustion gas outlet, and the bottom casing includes the combustion gas outlet. A bottom wall for receiving the drain flowing down from the bottom wall, and a discharge port for discharging the drain received on the bottom wall to the outside.

  According to such a configuration, the bottom casing is used as the drain receiving member, and there is no need to separately provide a dedicated member for receiving the drain. Therefore, it is suitable for reducing the total number of parts.

  In a preferred embodiment of the present invention, the heat exchanger is provided in a posture in which the opening for the combustor is lower than the combustion gas outlet, and the combustor is connected to a lower portion of the combustor. In addition, the heat exchanger is configured to burn the fuel upward, and the heat exchanger includes a drain receiving portion that receives a drain that flows down from the tubular body winding structure portion, and a drain that is received by the drain receiving portion. A drain discharge means for discharging the heat exchanger to the outside so as not to flow down on the combustor is provided.

  The hot water apparatus having the above configuration is a so-called positive combustion type, and as the combustor, a general gas combustor that burns fuel upward and other various combustors can be widely used. Moreover, according to the said structure, the discharge process can be performed appropriately so that a drain does not flow down on a combustor.

  In a preferred embodiment of the present invention, each loop portion of the tubular body winding structure portion has a hollow rectangular shape, and the peripheral wall portion of the can body of the heat exchanger is a rectangular tube surrounding each loop portion. Is.

  There are various types of positive combustion type combustors, but the combustion region of the fuel is often rectangular. According to the said structure, it is suitable when using such a combustor.

  Other features and advantages of the present invention will become more apparent from the following description of embodiments of the present invention with reference to the accompanying drawings.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings.

FIG. 1 shows an example of a heat exchanger and a hot water supply apparatus including the heat exchanger. 2 to 8 show the heat exchanger of FIG. 1 and the configuration related thereto. As clearly shown in FIG. 2, the heat exchanger A <b> 1 of this embodiment includes a can body 2, a plurality of water pipes 4, a pair of headers 5 for entering and discharging water, and a partition member 6. The plurality of water tubes 4 form a tubular body winding structure portion SC in which a plurality of coiled tubular body portions 40 are arranged in an overlapping manner.

  The can body 2 has a substantially cylindrical peripheral wall portion 20 and a pair of cover bodies 21A and 21B attached to the upper and lower portions of the peripheral wall portion 20. These are made of stainless steel, for example, and are not easily corroded due to the drain generated when the latent heat is recovered from the combustion gas using each water pipe 4. When latent heat recovery is performed from combustion gas, water vapor in the combustion gas is condensed and a drain (condensed water) is generated, which is generally oxidized by sulfur oxides or nitrogen oxides in the combustion gas. It becomes a strong acidity of about PH3 that absorbs substances. For this reason, the can 2 is made of a material excellent in acid resistance. This also applies to each water pipe 4 and the like. As will be described later, the peripheral wall portion 20 is formed by bending a substantially rectangular stainless steel plate into a cylindrical shape and then joining a pair of end edges 20a shown in FIG. At each end edge 20a, a protruding piece 20a 'protruding outward in the radial direction of the peripheral wall portion 20 is bent, and these protruding pieces 20a' are overlapped and welded. One or a plurality of brackets 23 for attaching the can 2 to other desired portions are welded to the lower outer peripheral surface of the peripheral wall portion 20.

  2 and 3, the cover body 21A has a substantially disc shape with an opening 22A formed at the center. The opening 22 </ b> A is used as a combustion gas inlet for introducing combustion gas into the can body 2, or used as a part for allowing a part of the combustor to enter the can body 2. The opening 22A is a burring hole having an annular wall 220 protruding downward at the periphery thereof. The cover body 21 </ b> A is fitted into the upper opening of the peripheral wall portion 20 and is welded to the peripheral wall portion 20. A plurality of convex portions 25a projecting toward the inside of the can body 2 are formed on the inner peripheral surface in the vicinity of the upper end of the peripheral wall portion 20, and the cover body 21A is positioned by contacting these convex portions 25a. Is planned. The plurality of convex portions 25 a are formed by pressing the peripheral wall portion 20, and are positioned at an appropriate interval in the circumferential direction of the peripheral wall portion 20.

  The cover body 21B has an opening 22B formed at the center thereof, and has a substantially disk shape similar to the cover body 21A. However, the opening 22 </ b> B is used as a combustion gas discharge port for discharging the combustion gas after heat recovery to the outside of the can body 2. A plurality of convex portions 25b similar to the convex portion 25a described above are formed on the inner peripheral surface in the vicinity of the lower end of the peripheral wall portion 20, and the cover body 21A is inserted into the lower opening of the peripheral wall portion 20 to be plural. It is welded to the peripheral wall part 20 in the state which contact | abutted to the convex part 25b. The opening 22B is formed as a burring hole similar to the opening 22A, and an annular wall 221 protruding upward is formed on the periphery thereof. A drain receiving portion 26 capable of receiving a drain dripping from the water pipe 4 with latent heat recovery is formed at the bottom of the can body 2. The drain receiving portion 26 includes an annular wall 221, a lower portion of the peripheral wall portion 20, an annular space portion 26a formed therebetween, and a bottom portion thereof. The cover body 21 </ b> B is formed with a drain discharge port 26 b for discharging the drain received by the drain receiving portion 26 to the outside of the can body 2.

  The plurality of water tubes 4 include a plurality of coiled tube portions 40 disposed in the can body 2 and a plurality of curved tubes 41 connected to both end portions 400 thereof. The heat exchanger A1 of the present embodiment includes a total of three water tubes 4, and each of the coiled tube portions 40 is formed using a spiral tube and is a hollow circular spiral loop portion 40a. Has a configuration in which a plurality of layers are stacked in the vertical direction. However, the plurality of coiled tube portions 40 have different winding diameters, and the tube-wrapped structure portion SC has the plurality of coiled tube portions 40 arranged concentrically or substantially concentrically. It is constituted by having. In this tubular body winding structure portion SC, the plurality of loop portions 40a are arranged in the horizontal direction in addition to the vertical direction.

  As shown well in FIGS. 4 and 5, the plurality of curved pipes 41 of the water pipe 4 serve as joint pipes that connect the plurality of coiled tube portions 40 and the header 5. Step portions 410a and 410b having tapered surfaces are formed at both end portions 41a and 41b of each curved pipe 41, and the outer diameter of the portion closer to the tip than the step portions 410a and 410b is larger than the intermediate portion in the longitudinal direction. The small diameter part. Each bent tube 41 is connected to the coiled tube portion 40 by fitting a small diameter portion of one end portion 41 a thereof to the end portion 400. The fitting direction of the small diameter portion and the end portion 400 is a tangential direction of the loop portion 40 a of the coiled tubular body portion 40. The tapered surface of the stepped portion 410a is in contact with the end surface of the end portion 400, and the contact portion is welded or brazed. However, as means for connecting the water pipe 4 and the curved pipe 41, for example, means shown in FIG. 8 can be used. In the means shown in the figure, a pipe expansion process is applied to the most distal end portion of the one end portion 41 a of the bent tube 41, and this portion is externally fitted to the end portion 400 of the water tube 4. Also by such means, appropriate connection by fitting the water pipe 4 and the curved pipe 41 is possible.

  The plurality of bent pipes 41 are inserted through a plurality of openings 200 provided in the vicinity of both upper and lower ends of the peripheral wall portion 20, and the portions near the other end portions 41 b of the bent pipes 41 protrude to the outside of the can body 2. ing. The plurality of bent pipes 41 have different bending radii and overall lengths, and the arrangement pitch P3 of the portion penetrating the peripheral wall portion 20 and the other end portion 41b is more than the arrangement pitch P2 of the one end portions 41a. Has been increased. With this configuration, the connection work of the header 5 is facilitated, and the interval between the plurality of openings 200 can be increased to increase the strength of this portion. The portions near the other end 41b of the plurality of bent pipes 41 extend linearly in a direction orthogonal to the peripheral wall portion 20, and are parallel to each other. Further, each curved pipe 41 is configured such that a portion having a larger diameter than the penetrating portion does not exist in a portion from the penetrating portion to the peripheral wall portion 20 to the other end portion 41b. With such a configuration, the operation of inserting the plurality of bent pipes 41 through the plurality of openings 200 of the peripheral wall portion 20 can be easily and appropriately performed.

  Preferably, each opening 200 is formed as a burring hole in which the peripheral edge stands and the strength of the peripheral edge is increased. Further, a part of the peripheral wall portion 20 including a portion where the plurality of openings 200 are formed is formed as a non-arc-shaped flat plate portion 201. The flat plate portion 201 extends in the vertical direction with a constant width and projects outward in the radial direction of the can body 2 from other regions. According to such a configuration, it is easy to dimension each opening 200, and the strength of the peripheral wall 20 can be increased. Furthermore, since the space | interval of the coil-shaped pipe part 40 and the flat plate part 201 becomes large, it becomes possible to use the thing with a comparatively big curvature radius as the curved pipe 41. FIG.

  Each of the pair of headers 5 is connected to the other end portions 41 b of the plurality of bent tubes 41. Each header 5 is configured by using, for example, a circular pipe 52, and at one end thereof, a connection port 50 to which a water inlet pipe 99a or a hot water outlet pipe 99b shown in FIG. 1 is connected is formed. The header 5 is provided with a plurality of openings 51, the small-diameter portion of the other end 41 b of each curved pipe 41 is fitted into each opening 51, and the tapered surface of the stepped portion 410 b is the opening 51. It is in contact with the peripheral edge. This contact portion is welded or brazed. Thereby, the connection between each curved pipe 41 and the header 5 is ensured, and a waterproof seal is achieved.

  As clearly shown in FIG. 2, the partition member 6 partitions the space 3 surrounded by the tubular body winding structure SC into first and second regions 30a and 30b in the vertical direction. belongs to. Each coiled tubular part 40 of the tubular body winding structure SC is divided into first and second heat exchange parts HT1 and HT2 surrounding the first and second regions 30a and 30b by the partition member 6, respectively. Has been. The partition member 6 includes a main body portion 60 that is located in the space portion 3 and has a concave portion that is recessed downward on the upper surface portion, and a flange piece 61 that is formed on the outer peripheral surface of the main body portion 60. Have. The main body 60 has a configuration in which, for example, a heat insulating material 60b rich in fire resistance and heat resistance is laminated on the upper surface of a stainless steel plate 60a. The heat insulating material 60b is, for example, ceramic. As shown in FIG. 6, the collar piece 61 is provided so as to make the outer peripheral surface of the main body 60 substantially one round or more than one round, and has a spiral shape in which a step H <b> 1 is generated at both ends. The partition member 6 is attached to the coiled tube parts 40 by screwing the spiral flange 61 into the plurality of coiled tube parts 40. Note that the flange 61 partitions the first and second heat exchange portions HT1 and HT2, and the combustion gas passes from the first heat exchange portion HT1 to the second heat exchange portion HT1 in the tubular body winding structure portion SC. The heat exchange part HT2 is prevented from proceeding in a short circuit.

  A combustion gas passage 32 is formed between the outermost coiled tube portion 40 and the peripheral wall portion 20. As shown in FIG. 2, a gap 31 is formed between the loop portions 40 a adjacent to each other in the vertical direction of the plurality of coiled tube portions 40. The first and second regions 30 a and 30 b and the combustion gas passage 32 communicate with each other through the gap 31. As a result, as will be described later, the combustion gas travels from the first region 30a to the combustion gas passage 32 via the gap 31 of the first heat exchange section HT1, and then from the combustion gas passage 32 to the second gas passage 32. It passes through the gap 31 of the heat exchange part HT2 and goes toward the second region 30b.

  The annular wall 220 of the cover body 21A is in contact with the upper part of the innermost coiled tube portion 40 as indicated by reference numeral n1, and the combustion gas passes between them from the first region 30a. Direct flow into the combustion gas passage 32 is prevented. Further, as indicated by reference numeral n2, the annular wall 221 of the cover body 21A is in contact with the lower part of the innermost coiled tubular portion 40, and the combustion gas passes between them through the combustion gas passage 32. Thus, direct flow into the second region 30b is prevented.

  As shown in FIG. 3, the gaps 31 between the coiled tube portions 40 are formed by using a plurality of spacers 7. More specifically, as shown in FIG. 7, the spacer 7 is formed by cutting and raising a plurality of locations on a base portion 70 made of, for example, a long rectangular flat plate made of stainless steel. It has the structure arranged in line. The plurality of projecting portions 71 are inserted between the loop portions 40a of the respective coiled tube portions 40, whereby the gap 31 is formed and the height dimension of the gap 31 is defined. As shown in FIG. 4, in this heat exchanger A1, for example, three spacers 7 are provided at substantially equal intervals. A portion other than the insertion portion of the protruding portion 71 of the spacer 7 is a gap 31 between the loop portions 40a adjacent in the vertical direction.

  As shown well in FIGS. 4 and 5, the plurality of curved pipes 41 of the water pipe 4 serve as joint pipes that connect the plurality of coiled tube portions 40 and the header 5. Step portions 410a and 410b having tapered surfaces are formed at both end portions 41a and 41b of each curved pipe 41, and the outer diameter of the portion closer to the tip than the step portions 410a and 410b is larger than the intermediate portion in the longitudinal direction. The small diameter part. One end portion 41 a of each curved tube 41 is connected to the end portion 400 by the small diameter portion being fitted into the end portion 400 of the coiled tubular body portion 40. The fitting direction of the small diameter portion and the end portion 400 is a tangential direction of the loop portion 40 a of the coiled tubular body portion 40. The tapered surface of the stepped portion 410a is in contact with the end surface of the end portion 400, and the contact portion is welded or brazed.

  The plurality of bent pipes 41 are inserted through a plurality of openings 200 provided in the vicinity of both upper and lower ends of the peripheral wall portion 20, and portions of the bent pipes 41 near the other end 41 b protrude to the outside of the can body 2. ing. The plurality of bent pipes 41 have different bending radii and overall lengths, and the arrangement pitch P3 of the portion penetrating the peripheral wall portion 20 and the other end portion 41b is more than the arrangement pitch P2 of the one end portions 41a. Has been increased. With this configuration, the connection work of the header 5 is facilitated, and the interval between the plurality of openings 200 can be increased to increase the strength of this portion. The portions near the other end 41b of the plurality of bent pipes 41 extend linearly in a direction orthogonal to the peripheral wall portion 20, and are parallel to each other. Further, each curved pipe 41 is configured such that a portion having a larger diameter than the penetrating portion does not exist in a portion from the penetrating portion to the peripheral wall portion 20 to the other end portion 41b. With such a configuration, the operation of inserting the plurality of bent pipes 41 through the plurality of openings 200 of the peripheral wall portion 20 can be easily and appropriately performed.

  Preferably, each opening 200 is formed as a burring hole in which the peripheral edge stands and the strength of the peripheral edge is increased. Further, a part of the peripheral wall portion 20 including a portion where the plurality of openings 200 are formed is formed as a non-arc-shaped flat plate portion 201. The flat plate portion 201 extends in the vertical direction with a constant width and projects outward in the radial direction of the can body 2 from other regions. According to such a configuration, it is easy to dimension each opening 200, and the strength of the peripheral wall 20 can be increased. Furthermore, since the space | interval of the coil-shaped pipe part 40 and the flat plate part 201 becomes large, it becomes possible to use the thing with a comparatively big curvature radius as the curved pipe 41. FIG.

  Each of the pair of headers 5 is connected to the other end portions 41 b of the plurality of bent tubes 41. Each header 5 is configured using, for example, a circular pipe 52, and a connection port 50 to which a water inlet pipe or a hot water outlet pipe (not shown) is connected is formed at one end thereof. The header 5 is provided with a plurality of openings 51, the small diameter portion of the other end 41 b of each curved pipe 41 is fitted into each opening 51, and the tapered surface of the stepped portion 410 b is the peripheral edge of the opening 51. Abut. This contact portion is welded or brazed. Thereby, the connection between each curved pipe 41 and the header 5 is ensured, and a waterproof seal is achieved.

  The aforementioned heat exchanger A1 is manufactured, for example, by the following method.

  First, as shown in FIG. 9, a plurality of coiled tube portions 40 having a lap winding shape are produced. These are produced by bending a straight tube body into a spiral shape to produce a plurality of coiled tube portions 40 having different diameters and then fitting them together. Next, as shown in FIG. 10, the bent pipe 41 is connected to both end portions 400 of each coiled tube body 40 to complete a plurality of water tubes 4. As described with reference to FIG. 4 and FIG. 5, the curved pipe 41 is connected to each coiled tube body 40 by connecting the distal end portion 41 a of the bent tube 41 with a reduced diameter to each coiled tube body. Since it is carried out by being fitted into the end portion 400 of the portion 40, even if the arrangement pitch P2 of the plurality of end portions 400 is small, the operation can be easily performed. Since the taper surface of the stepped portion 410a is brought into contact with the end portion 400 for welding or brazing, the water sealing performance is also improved.

  As shown in FIG. 11, the partition member 6 is attached to the plurality of coiled tube portions 40. In this attachment, the main body portion 60 of the partition member 6 is rotated in the spiral direction of each coil-shaped tube portion 40 while entering the inside of the plurality of coil-shaped tube portions 40 from one end thereof. Is carried out by screwing into each coil-shaped tube part 40. When the partition member 6 is rotated in the predetermined direction, the partition member 6 advances inward in each coiled tube body portion 40 in a predetermined direction, and when it is reversed, the partition member 6 is moved to a predetermined height. The work to set to is easy. Thereafter, the plurality of spacers 7 are attached to the plurality of coiled tube portions 40. In this attachment, the plurality of projecting portions 71 of each spacer 7 are inserted between the loop portions 40a from the outside of the outermost coiled tube portion 40. Thereby, the clearance gap 31 can be formed between the loop parts 40a, and the dimension can be prescribed | regulated to the same dimension as the thickness of each protrusion part 71. FIG. In the configuration shown in FIG. 11, the protrusions 71 of the spacers 7 are not inserted into the portions corresponding to the flange pieces 61 of the partition member 6. Can be configured so that they are inserted into a common gap portion. Each spacer 7 may be divided into a plurality of portions in the vertical direction.

  On the other hand, as shown in FIG. 12, a non-cylindrical plate-like member 20 'is manufactured. The plate-like member 20 ′ is a portion formed as the peripheral wall portion 20 of the can body 2, and is formed using a rectangular stainless steel plate having flexibility. A pair of projecting pieces 20a 'is formed by bending the pair of edge portions 20a of the plate-like member 20'. In addition, a plurality of openings 200 through which the bent pipe 41 of each water pipe 4 is inserted are also formed. The plate-like member 20 ′ is preliminarily subjected to a bending process so as to be easily formed into a cylindrical shape, and a flat plate portion 201 is also formed.

  After the plate-like member 20 ′ is manufactured, the space between the pair of end edges 20 a is widened to surround the plurality of coiled tube portions 40 by the plate-like member 20 ′. At that time, the plurality of bent pipes 41 are inserted through the openings 200 from the other end 41b side. Since the regions near the other end portions 41b of the plurality of bent pipes 41 are straight pipes parallel to each other as described above, the operation of inserting these portions into the plurality of openings 200 is easily and appropriately performed. be able to.

  Thereafter, as shown in FIG. 13, the plate-like member 20 'is formed into a cylindrical shape by bringing the pair of edge portions 20a of the plate-like member 20' into contact with each other. By sandwiching the pair of protruding pieces 20a ′ using an appropriate jig (not shown), the plate-like member 20 ′ can be maintained in a cylindrical shape. Weld. By this operation, the peripheral wall portion 20 formed into a cylindrical shape is formed. The protruding piece 20a ′ is formed over the entire length of the end edge portion 20a, and the protruding piece 20a ′ is formed at one or a plurality of positions (for example, the upper end and the lower end of the end edge portion 20a). Etc.) may be partially provided.

  Next, the pair of headers 5 are connected to the plurality of bent pipes 41. As described above, the connection structure of the header 5 does not use a special member. The other end 41b of each bent pipe 41 is fitted into the opening 51 of the header 5 and is welded or brazed. It is possible to reduce the cost because it is sufficient. Further, since the arrangement pitch P3 of the other end 41b and the opening 51 of the curved pipe 41 is increased, the connection work between each curved pipe 41 and the header 5 becomes easier.

  Although not shown in FIG. 13, a pair of cover bodies 21 </ b> A and 21 </ b> B are fitted into the upper opening and the lower opening of the peripheral wall portion 20, and these are welded to the peripheral wall portion 20. As described above, the cover bodies 21A and 21B can be positioned by using the plurality of convex portions 25a and 25b formed on the peripheral wall portion 20, so that their attaching work is also easy. It is. Further, the plurality of brackets 23 are also welded to the peripheral wall portion 20. However, the welding time of these brackets 23 may be either before or after the plate-like member 20 'is formed in a cylindrical shape.

  Although the heat exchanger A1 is appropriately manufactured by the manufacturing method described above, as understood from the above description, in this heat exchanger A1, the arrangement pitch of the end portions 400 of the plurality of coiled tube portions 40 is set. Even if P2 is small, the header 5 can be easily and appropriately connected to the plurality of coiled tube portions 40 by using the plurality of bent tubes 41. In particular, in this embodiment, since the coiled tube part 40 is surrounded by the peripheral wall part 20 of the tubular body 2 after the curved pipe 41 is connected to the coiled tubular body part 40, the coiled tubular body part 40. The operation of connecting the bent pipe 41 to the pipe is even easier. Furthermore, even when the plurality of curved pipes 41 are greatly protruded from the coiled tubular body portion 40, the plurality of curved pipes 41 are connected to the plurality of openings 200 of the peripheral wall portion 20 (plate-like member 20 ′). The plurality of coiled tube portions 40 can be appropriately surrounded by the plate-like member 20 ′. When the dimension in which each curved pipe 41 protrudes to the outside of the can body 2 is small, the header 5 is considerably close to the can body 2, and welding work for attaching the header 5 to each curved pipe 41 is performed. Although it may become difficult, according to this embodiment, since a part of each curved pipe 41 can be protruded largely, such a fear is also eliminated appropriately.

  Next, the configuration of the hot water supply device B1 shown in FIG. 1 will be described. This hot water supply apparatus B1 includes a combustor 1, a bottom casing 80, and an exhaust duct 81 in addition to the heat exchanger A1.

  The combustor 1 is of a reverse combustion type in which, for example, kerosene is used as fuel, and this fuel is sprayed downward using a spray nozzle (not shown) and burned, and a part thereof is formed in the opening 22A of the heat exchanger A1. Is provided to enter. Therefore, in the hot water supply apparatus B1, the fuel is injected toward the first region 30a of the heat exchanger A1, and the first region 30a is a combustion chamber. The combustor 1 is covered and supported by a can body 10 connected on the heat exchanger A <b> 1, and fuel is supplied from the outside of the can body 10 through a pipe 12. A blower fan 13 for feeding combustion air downward into the can body 10 and a motor M for driving the fan body 10 are provided on the upper portion of the can body 10. The downward blowing action by the blower fan 13 is useful for advancing the combustion gas in a certain path to be described later.

  The bottom casing 80 has a substantially rectangular parallelepiped box shape with a hollow inside, and the heat exchanger A1 and the exhaust duct 81 are placed on the bottom casing 80 so as to be aligned. Openings 80 a and 80 b communicating with the opening 22 B of the heat exchanger A 1 and the bottom opening of the exhaust duct 81 are formed in the upper wall portion of the bottom casing 80. Thus, the combustion gas that has traveled from the opening 22B of the heat exchanger A1 into the bottom casing 80 passes through the bottom casing 80 and travels upward from below the exhaust duct 81. The combustion gas flowing into the exhaust duct 81 is then discharged to the outside as exhaust gas from the exhaust port 81a. The exhaust duct 81 includes, for example, a sound absorbing material (not shown) such as glass wool, and serves as a silencer for reducing exhaust sound.

  A pipe 82 penetrating the bottom casing 80 is connected to the drain outlet 26b of the heat exchanger A1. With this structure, the drain received by the drain receiving portion 26 does not flow into the bottom casing 80. The drain discharged through the pipe 82 is sent to, for example, a neutralizer (not shown). This neutralizer contains a neutralizing agent such as calcium carbonate for neutralizing an acidic drain in a suitable container.

  A water inlet pipe 99a and a hot water outlet pipe 99b are connected to the pair of headers 5. In this connection, it is preferable that the lower header 5 is connected to water and the upper header 5 is connected to hot water. If it does in this way, since the water flow direction with respect to the several water pipe 4 becomes upward and becomes a direction opposite to the advancing direction (downward) of a combustion gas, it becomes advantageous to improving heat exchange efficiency. In particular, since the non-heated relatively low temperature water is supplied to the second heat exchanging unit HT2, the amount of heat recovered by the second heat exchanging unit HT2 is increased, and latent heat recovery is performed in this portion. It is suitable for making it perform.

  In this hot water supply apparatus B1, when the combustor 1 is driven, the fuel burns in the first region 30a, and combustion gas is generated. Although this combustion gas tends to travel downward, the lower portion of the first region 30a is blocked by the partition member 6, and therefore does not travel directly to the second region 30b. The combustion gas passes through the gap 31 of the first heat exchange part HT1 of the tubular body winding structure part SC and flows into the combustion gas passage 32. The first heat exchange unit HT1 recovers sensible heat from the combustion gas in such a process. The first heat exchanging part HT1 can increase the amount of heat recovery because the plurality of loop parts 40a are arranged in an overlapping manner. Since the upper surface portion of the partition member 6 is formed in a concave shape, the combustion gas that has progressed downward near the center of the first region 30a is reflected upward so as to avoid the vicinity of the center, A circulation flow of the combustion gas as shown by an arrow N1 in FIG. 1 can be generated. As a result, the temperature of the combustion gas in the first region 30a is made uniform, and the amount of combustion gas flowing into each of the plurality of gaps 31 is made uniform, so that the heat exchange efficiency can be further increased. It becomes.

  The combustion gas that has traveled to the combustion gas passage 32 then travels downward through the combustion gas passage 32, passes through the gap 31 of the second heat exchange section HT2, and flows into the second region 30b. In such a process, the second heat exchange unit HT2 performs latent heat recovery from the combustion gas. Similarly to the first heat exchanging unit HT1, the second heat exchanging unit HT2 can increase the amount of heat recovered because the plurality of loop portions 40a are arranged in an overlapping manner.

  When the latent heat recovery is performed in the second heat exchange part HT2, a drain is generated in that part and adheres to the surface of each loop part 40a. This drain flows down downward by the action of gravity and the downward flow of the combustion gas, and is suitably received by the drain receiving portion 26. Since each coil-shaped tube part 40 is spiral and is inclined, it can be expected that the drain easily flows downward along the surface of the coil-shaped tube part 40. If the drain remains attached to the surface of the coiled tube body 40, the direct contact between the coiled tube body 40 and the combustion gas may be hindered by the drain, which may reduce the amount of heat transfer. By making it easier to flow downward, such a fear can be eliminated. The drain received by the drain receiving portion 26 is then appropriately discharged to the outside through the drain discharge port 26b and the pipe 82. Therefore, the inside of the bottom casing 80 is not contaminated by the acidic drain, and the bottom casing 80 can be made of a material cheaper than stainless steel, such as copper or iron, which is inferior in acid resistance.

14 to 35 show another embodiment. In the drawings after FIG. 14, the same or similar elements as those of the above embodiment are denoted by the same reference numerals as those of the above embodiment.

  FIG. 14 shows an example in which the peripheral wall portion 20 of the can body 2 is configured using a pair of first plate-like members 20A and a second plate-like member 20B that are divided vertically. The pair of first plate-like members 20 </ b> A have a plurality of bent pipes 41 penetrating therethrough, and projecting pieces 21 d for joining are formed at both end edges thereof. A header 5 is attached to the plurality of curved pipes 41. On the other hand, projecting pieces 21e are formed on the upper and lower ends of both end edges of the second plate-like member 20B so as to sandwich the pair of first plate-like members 20A. The part is provided with an extending part 203 protruding in the circumferential direction from the upper and lower parts. The extending portion 203 is a portion that is formed into a cylindrical shape by being directly joined without sandwiching the first plate-like member 20A.

  In the present embodiment, the peripheral wall portion 20 of the can body 2 can be appropriately formed by joining a pair of the first plate-like member 20A and the second plate-like member 20B together to form a cylinder. It is. In order to connect the header 5 to the plurality of coiled tube parts 40 before the plurality of coiled tube parts 40 are surrounded by the second plate-like member 20B, the header 5 is attached. The can body 2 does not get in the way when performing a water flow inspection in a state or a visual inspection of whether or not their connection is appropriate, and an advantage of facilitating the inspection can be obtained. In addition, since the pair of first plate-like members 20A are individually attached to the upper curved pipe 41 and the lower curved pipe 41, for example, the upper curved pipe 41 and the lower curved pipe 41 are attached. Even in the case where there is a deviation in arrangement with the tube 41, the first plate member 20A can be easily attached to them.

  The hot water supply device B2 shown in FIG. 15 has a configuration in which a heat insulating material 84 and a spacer 85 are arranged in the can body 2 of the heat exchanger A2. Further, in the bottom casing 3, a drain receiving member 83A is disposed. The heat insulating material 84 has a ring shape, and is interposed between the upper end of the tubular body winding structure SC and the gap 39a between the cover body 21A. The heat insulating material 84 is, for example, ceramic having elasticity. As described above, since the tubular body winding structure SC is formed using a spiral tubular body, the upper end surface of the tubular body winding structure SC is inclined. Correspondingly, the thickness of the heat insulating material 84 is not made constant, and the lower end surface thereof is inclined, thereby appropriately closing the gap 39a. According to such a configuration, the heat insulating material 84 appropriately prevents the combustion gas from passing through the gap 39a from the first region 30a and proceeding to the upper end of the combustion gas passage 32 in a short-circuit manner. Therefore, it is not necessary to bring the annular wall 220 of the cover body 21 </ b> A into contact with the inner peripheral surface of the innermost coiled tubular portion 40. As a result, the combustor opening 22 </ b> A can be made smaller than the inner diameter of the coiled tube body 40.

  The spacer 85 has a ring shape like the heat insulating material 84 and is disposed on the bottom of the can body 2 to support the tubular body winding structure portion SC. Since the lower end surface of the tubular body winding structure SC is inclined in the same manner as the upper end surface, the thickness of the spacer 85 is not constant and the upper surface is inclined as in the heat insulating material 84 described above. . Further, the support member 85 closes the end portion of the combustion gas passage 32. Therefore, the combustion gas that has reached the end portion is also appropriately prevented from proceeding directly to the second region 30b without passing through the gap 31 of the tubular body winding structure SC. For this reason, it is not necessary to bring the annular wall 221 of the cover body 21B into contact with the inner peripheral surface of the innermost coiled tubular portion 40. In the present embodiment, the annular wall 221 protrudes downward.

  The bottom portion of the can body 2 serves as a drain guide portion that guides the drain flowing down from the tubular body winding structure portion SC to the combustion gas outlet 22B. As described above, since the upper surface of the spacer 85 is inclined, it is possible to make the drain flow easily toward the combustion gas outlet 22B using this inclination. The receiving member 83A has, for example, a dish shape, and is disposed immediately below the combustion gas outlet 22B so as to receive a drain dripping from the combustion gas outlet 22B. The drain received by the receiving member 83 </ b> A is discharged to the outside of the bottom casing 80 through the pipe 82.

  Also in this embodiment, as in the previous embodiment, the inside of the bottom casing 80 can be prevented from being contaminated by the drain. The combustion gas outlet 22B is also used as a drain outlet, and it is not necessary to separately provide a drain outlet for the heat exchanger A2. Therefore, the combustion gas outlet 22B is suitable when it is desired to simplify the configuration of the heat exchanger A2. .

  In the embodiment shown in FIG. 16, a downward convex portion 210 is press-molded on the cover body 21A, and this convex portion 210 is in contact with the upper end of the tubular body winding structure portion SC. The downward surface of the convex portion 210 is an inclined surface corresponding to the upper end of the tubular body winding structure portion SC. According to this embodiment, it is possible to prevent a gap through which the combustion gas passes above the tubular body winding structure SC. A separate member such as the heat insulating material 84 shown in FIG. 15 is not necessary, and it is possible to eliminate the need to bring the annular wall 220 into contact with the coiled tubular body 40.

  In the embodiment shown in FIG. 17, the drain dripping downward from the combustion gas outlet 22 </ b> B of the heat exchanger A <b> 2 is received by the bottom wall of the bottom casing 80. A drain discharge port 80a is formed in the bottom wall. Preferably, the bottom wall is inclined so that the drain easily flows toward the drain outlet 80a. In the present embodiment, the bottom casing 80 is used as a drain receiving member, and it is not necessary to use a dedicated drain receiving member, so that the total number of parts can be reduced. However, in order to avoid the bottom casing 80 from being easily corroded due to an acidic drain, it is preferable to make the material excellent in stainless steel or other acid resistance.

  In the embodiment shown in FIG. 18, the dimensions L1 and L2 of the gaps 31 of the first and second heat exchange parts HT1 and HT2 are different. Specifically, the dimension L1 is smaller than the dimension L2. According to such a configuration, it is possible to increase the relative heat recovery amount of the second heat exchange part HT2 with respect to the first heat exchange part HT1 as compared with the case where the dimensions L1 and L2 are equal. It becomes suitable for latent heat recovery. Of course, in the present invention, contrary to the present embodiment, the dimension L1 may be larger than the dimension L2.

  The heat exchanger A3 shown in FIG. 19 includes two auxiliary partition members 63A and 63B. These materials are all made of stainless steel, for example. The auxiliary partition member 63A has a ring shape and divides the second heat exchange part HT2 of the tubular body winding structure part SC into two divided parts HT21 and HT22, and the combustion gas passage 32 is divided into two divided parts 32a and 32b. It is provided to divide into Preferably, the width of the second heat exchange part HT2 is larger in the vertical direction than the first heat exchange part HT1, and the width of each of the first heat exchange part HT1 and the two divided parts HT21 and HT22 is made larger. There is no big difference. The auxiliary partition member 63B has a disk shape and is provided in contact with the lower end of the tubular body winding structure portion SC, thereby closing the lower opening of the second region 30b.

  In the present embodiment, the combustion gas that has passed through the first heat exchange part HT1 and has traveled to the split part 32a of the combustion gas passage 32 then passes through the gap 31 of the split part HT21 of the second heat exchange part HT2. To enter the second region 30b. Next, the combustion gas passes from the second region 30b through the gap of the dividing portion HT22, proceeds to the dividing portion 32b of the combustion gas passage 32, and then proceeds to the combustion gas outlet 22B. As understood from the flow of such combustion gas, in the present embodiment, the tubular body winding structure portion SC has three regions of the first heat exchange portion HT1 and the two divided portions HT21 and HT22. The combustion gas passes through these three areas in a meandering manner. Further, the three regions are made uniform in width so that there is no great difference in their width. Therefore, it is possible to reduce the variation in the amount of progress of the combustion gas with respect to each part of the tubular body winding structure SC, and to further improve the heat exchange efficiency. Further, when the tubular body winding structure SC is subdivided, the combustion gas passage area is reduced, and the flow velocity of the combustion gas can be increased. This also increases the heat exchange efficiency.

  The heat exchanger A4 shown in FIG. 20 has a configuration in which an extending portion HT23 extending further downward than the auxiliary partition member 63B is provided in the lower portion of the tubular body winding structure portion SC. Preferably, the vertical width of the extending portion HT23 is also substantially the same as that of the first heat exchange portion HT1 and the two divided portions HT21 and HT22. In this heat exchanger A4, the combustion gas that has traveled to the dividing portion 32b of the combustion gas passage 32 passes through the gap 31 of the extending portion HT23 from this portion.

  According to this embodiment, the tubular body winding structure SC is further subdivided into four regions, and the combustion gas sequentially acts on all of the subdivided portions. Therefore, it is possible to further increase the heat exchange efficiency as compared with the heat exchanger A3 shown in FIG.

  In the embodiment shown in FIG. 21, a total of five coiled tube portions 40 are provided in an overlapping manner. According to the present embodiment, since the number of the coiled tube portions 40 is large, the heat recovery amount can be increased. As will be understood from the present embodiment, the present invention can easily achieve high heat exchange efficiency by increasing the number of coiled tube portions.

  In the embodiment shown in FIG. 22, a plurality of coiled tube portions 40 are provided in a staggered arrangement, and the other side of the gap 31 between the loop portions 40a of one coiled tube portion 40 is another The loop part 40a of one coiled tubular part 40 exists. According to the present embodiment, as shown by an arrow N2, when the combustion gas passes through the gap 31 of one coiled tubular body portion 40, the combustion gas collides with the side loop portion 40a. Therefore, the contact degree of the combustion gas with respect to each loop part 40a is raised, and heat recovery amount can be increased. As understood from the present embodiment, in the present invention, it is possible to improve the heat exchange efficiency by devising the arrangement of the plurality of coiled tube portions 40, and the plurality of coiled tube portions. 40 can be provided in various arrangements.

  In the heat exchanger A5 shown in FIG. 23, the tube diameters of the plurality of coiled tube portions 40 are not uniform, and the innermost coiled tube portion 40 (40A) is a plurality of other coils. The tube diameter is larger than that of the tubular body portion 40 (40B). Since the helical pitch of the coiled tubular body part 40A is different from the helical pitch of the coiled tubular body part 40B, as means for forming the gap 31 between the loop parts 40a of the coiled tubular body part 40A, the spacer 7 and Another spacer 7A having a different arrangement pitch of the protrusions 71 is used.

  In the present embodiment, the tube diameter of the coiled tube portion 40A is increased, and the amount of water passing through this portion is large. On the other hand, the coiled tubular portion 40A directly surrounds the first region 30a as a combustion chamber and is the portion heated to the highest temperature. Therefore, the amount of heat recovered by the coiled tubular portion 40A is increased, which makes it possible to further increase the heat exchange efficiency. In addition, the coiled tube portions 40A and 40B have different spiral pitches due to the difference in tube diameter, and the gap 31 between the coiled tube portion 40A and the coiled tube body. The gap 31 of the part 40B has a step in the vertical height direction. Accordingly, the combustion gas collides with the coiled tube part 40B after passing through the gap 31 between the coiled tube part 40A from the space 3. As a result, the degree of contact between the coiled tubular portion 40 and the combustion gas is increased, and an effect of further improving the heat exchange efficiency can be expected.

  In the heat exchanger A5 shown in FIG. 23, since the spiral pitches of the coiled tube parts 40A and 40B are different, the flange 61 of the partition member 6 is screwed into both the coiled tube parts 40A and 40B. It is difficult to make it. For this reason, in this heat exchanger A5, the flange piece 61 is screwed into only the innermost coiled tubular part 40A, and the other coiled tubular part 40B is provided with a plurality of additional partition members 63. It is partitioned using. Each partition member 63 has, for example, a semicircular thin plate shape, and is inserted into the gap 31 of the coiled tubular body portion 40B from the side of the tubular body winding structure portion SC as shown in FIG. By providing the partition member 63, the combustion gas that has progressed from the first region 30a into the lower region of the first heat exchange unit HT1 travels downward and flows directly into the second region 30b. That is blocked.

  FIG. 25 shows another example of the partition member attaching means. In the present embodiment, a plurality of additional partition members 62A are inserted into the gaps 31 of the plurality of spiral tubular body portions 40 from the outside. The partition member 62 </ b> A is similar to the partition member 62 described above, but an inner edge portion thereof is a protruding portion 620 that protrudes into the space portion 3. On the other hand, although the partition member 6A has a flange 61A, the flange 61A is not for screwing into the spiral tubular body portion 40, but rather than the inner diameter of the innermost spiral tubular portion 40. The outer diameter is slightly smaller. The partition member 6 is inserted into the space portion 3 from the upper opening of the space portion 3, so that the flange piece 61 </ b> A is locked and supported by the protruding portion 620. Also according to this embodiment, the partition member 6 can be appropriately attached to a predetermined location in the space portion 3.

  26 to 33 show another example of means for forming a gap between the loop portions of the coiled tube portion. In the embodiment shown in FIGS. 26 and 27, a protrusion 49 a is formed on each loop portion 40 a of the coiled tube body 40. The loop portions 40a adjacent to each other in the vertical direction are in contact with each other through the protrusions 49a, whereby the gap 31 is formed.

  In the embodiment shown in FIGS. 28 and 29, a part of each of the upper surface and the lower surface of the loop portion 40a is a convex portion 49b, and the loop portions 40a are in contact with each other through these convex portions 49b. As a result, a gap 31 is formed. For example, as shown in FIG. 29, a part of the loop portion 40a has a non-circular flat cross section, thereby forming a convex portion 49b. . As shown in FIG. 30, this can be formed by pressing a part of the coiled tube portion 40 from both sides.

  In the embodiment shown in FIG. 31, concave portions 49b 'are formed at a plurality of locations of the loop portion 40a. The concave portion 49b 'can be formed by pressing a part of the coiled tube portion 40 from above and below to deform it into a flat shape. The loop portions 40a adjacent to each other in the vertical direction are stacked so as to be in contact with each other, but the portion where the recess 40b 'is formed is a gap 31. Even with such a configuration, the gap 31 can be appropriately formed.

  In the embodiment shown in FIG. 32, a spiral groove 49 c is formed on the outer surface of the loop portion 40 a, and a part of the groove 49 c is a gap 31. In the embodiment shown in FIG. 33, two grooves 49c having different spiral directions are formed. As the number of grooves 49c increases, the total size of the gaps 31 can be increased, and a large number of grooves 49c may be formed. Further, the gap 31 can be formed even when a non-spiral annular groove is formed.

  According to the embodiment as shown in FIGS. 26 to 33, it is not necessary to use the spacer 7 as means for forming the gap 31, and the mounting work is omitted. Therefore, it is suitable for facilitating the assembly work of the heat exchanger.

  FIG. 34 and FIG. 35 show an example when the combustor of the hot water supply apparatus is of the normal combustion type. A hot water supply device B3 shown in these drawings includes a combustor 1A and a heat exchanger A6. The combustor 1A is a gas combustor that burns fuel gas such as natural gas supplied through the gas supply pipe 12 upward, and is surrounded by a can 10 connected to the lower part of the heat exchanger A6. ing. Combustion air is sent upward into the can 10 by a blower fan 13.

  The heat exchanger A6 is configured such that the combustor opening 22A is formed at the bottom of the can body 2 and is located immediately above the combustor 1A. The combustion gas outlet 22 </ b> B is formed in the upper part of the can body 2. This heat exchanger A6 is substantially the same as the heat exchanger A1 shown in FIGS. However, the positional relationship of the drain receiving portion 26 is not reversed and is formed at the bottom of the can body 2. Moreover, as shown in FIG. 35, the loop part 40a of each coil-shaped tube part 40 is a hollow rectangular shape connected in a spiral shape, and the peripheral wall part 20 of the can body 2 has a rectangular rectangular tube shape corresponding thereto. It is. Although not shown in the drawing, the fuel combustion portion of the combustor 1A has a rectangular shape in plan view, and the shapes of the loop portion 40a and the peripheral wall portion 20 correspond to this. When the fuel combustion portion of the combustor 1A has a circular shape in plan view, the loop portion 40a and the peripheral wall portion 20 may have a hollow circular shape. The header 5B is connected to both end portions of the plurality of coiled tube portions 40. The header 5B is directly connected to both ends of the coiled tube portion 40.

  In the hot water supply apparatus B3 of the present embodiment, the combustion gas generated in the combustor 1A passes upward through the combustor opening 22A and enters the first region 30a of the space 3. Next, the combustion gas passes through the gap 31 of the first heat exchange section HT1 and travels upward in the combustion gas passage 32, and then passes through the gap 31 of the second heat exchange section HT2 and enters the second heat exchange section HT2. It progresses to the area | region 30b, and is discharged | emitted from the combustion gas outlet 22B to the exterior of the can body 2. Such a heat recovery process is basically the same as that of the reverse combustion type, and the sensible heat recovery and the latent heat recovery can be assigned to the first and second heat exchanging units HT1 and HT2, respectively. When the combustion gas passes through the gap 31 between the first and second heat exchange portions HT1 and HT2, the combustion gas comes into contact with many loop portions 40a. This also increases the heat exchange efficiency. The drain generated along with the latent heat recovery flows downward along the spiral gradient of each coiled tubular body portion 40 and is received by the drain receiving portion 26. And it discharges | emits appropriately from the discharge port 26b to the exterior of the can body 2. FIG.

  As will be understood from the present embodiment, the heat exchanger according to the present invention is not limited to being used in combination with a reverse combustion type combustor, but also when used in combination with a forward combustion type combustor. The effect intended by the invention can be obtained. In the heat exchanger according to the present invention, the traveling direction of the combustion gas does not matter.

  The present invention is not limited to the contents of the above-described embodiment. The specific configuration of each part of the heat exchanger and the hot water apparatus according to the present invention can be varied in design in various ways.

  The combustor may be any combustor that generates combustion gas, such as an oil combustor or a gas combustor, and various combustors can be used. The hot water device according to the present invention means a device having a function of generating hot water, and is used for various types of hot water supply devices for general hot water supply, bath hot water supply, heating, snow melting, and the like, and hot water supply. Includes a device for producing hot water.

It is a schematic sectional drawing which shows an example of a heat exchanger and a hot water supply apparatus provided with the same. It is sectional drawing of the heat exchanger shown in FIG. It is sectional drawing of the heat exchanger shown in FIG. It is a plane sectional view of the heat exchanger shown in FIG. It is a principal part expanded sectional view of FIG. It is a perspective view of the partition member used for the heat exchanger shown in FIG. It is a principal part perspective view of the spacer used for the heat exchanger shown in FIG. It is principal part cross-section explanatory drawing which shows the other example of the connection structure of the coiled tube part which comprises a water pipe, and a curved pipe. It is a schematic perspective view which shows an example of the coiled tube part of a water pipe. It is a schematic perspective view which shows the process of assembling an accessory to the coiled tube part shown in FIG. It is sectional drawing which shows the process of assembling an accessory to the coiled-tube part shown in FIG. It is a schematic perspective view which shows the process of enclosing the coil-shaped tube part shown in FIG. 10 and its accessory parts with a plate-shaped member. It is a perspective view which shows the state which enclosed the coil-shaped tube part shown in FIG. 10 and its accessory by the plate-shaped member. It is a disassembled perspective view which shows the other example of a heat exchanger . It is a principal part schematic sectional drawing which shows the other example of a heat exchanger and the hot-water supply apparatus provided with the same. It is principal part sectional drawing which shows the other example of a heat exchanger . It is a principal part schematic sectional drawing which shows the other example of a heat exchanger and the hot-water supply apparatus provided with the same. It is a schematic sectional drawing which shows the other example of a heat exchanger . It is sectional drawing which shows the other example of a heat exchanger . It is sectional drawing which shows the other example of a heat exchanger . It is principal part sectional drawing which shows the other example of a heat exchanger . It is principal part sectional drawing which shows the other example of a heat exchanger . It is sectional drawing which shows the other example of the heat exchanger to which this invention was applied. It is explanatory drawing of the attachment means of the partition member applied to the heat exchanger shown in FIG. It is explanatory drawing which shows the other example of the attachment means of a partition member. It is a principal part side view which shows the other example of the means to form a clearance gap in a coiled tube part. It is XXVII-XXVII sectional drawing of FIG. It is a principal part side view which shows the other example of the means to form a clearance gap between coiled tube parts. It is XXIX-XXIX sectional drawing of FIG. FIG. 30 is a perspective view of the coiled tube portion shown in FIGS. 28 and 29. (A) is a principal part side view which shows the other example of the means which forms a clearance gap in a coil-shaped tubular-body part, (b) is XXXI-XXXI sectional drawing of (a). It is a principal part side view which shows the other example of the means to form a clearance gap between coiled tube parts. It is a principal part side view which shows the other example of the means to form a clearance gap between coiled tube parts. It is sectional drawing which shows the other example of a heat exchanger and a hot-water supply apparatus provided with the same. FIG. 35 is a plan sectional view of FIG. 34. It is explanatory drawing which shows an example of a prior art. It is explanatory drawing which shows the other example of a prior art.

Explanation of symbols

A1 to A6 heat exchanger SC tubular body winding structure portion HT1 first heat exchange portion HT2 second heat exchange portion 1 combustor 2 can body 3 space portion 4 water pipe 5 header 6 partition member 20 peripheral wall portion (can body )
21A, 21B Cover body 22A Combustor opening 22B Combustion gas outlet 30a First region 30b Second region 31 Gap 32 Combustion gas passage 40 Coiled tube portion 40a Loop portion

Claims (16)

A can body having a cylindrical peripheral wall portion and having a combustor opening and a combustion gas outlet formed at both ends in the axial length direction;
A coiled tube portion for heat exchange having a plurality of loop portions arranged in the can so as to be arranged in the axial length direction through a gap;
A space part surrounded by the coiled tubular part and having one end communicating with the combustor opening;
A combustion gas passage formed between the coiled tubular body portion and the peripheral wall portion of the can body and guiding the combustion gas that has progressed to the combustion gas outlet;
A heat exchanger comprising:
The coiled tube portion includes at least one additional coiled tube portion having a different diameter or width of each loop portion, and the plurality of loop portions are in the axial length direction and in a direction intersecting with the axial length direction. A plurality of coiled tubular body portions, and a tubular body winding structure portion in which the plurality of coiled tubular body portions are overlapped;
The space portion is divided into first and second regions in the axial length direction by closing an axial length direction intermediate portion of the space portion, and the tubular body winding structure portion is divided into the first and second regions. A partition member that is divided into first and second heat exchanging portions that surround the region,
The combustion gas introduced to or generated in the first region passes through the gap in the first heat exchange section from the first region and proceeds to the combustion gas passage, and then the second heat. It is configured to pass through the gap of the replacement part ,
The tube diameters of the plurality of coiled tube parts are not uniform, and among the plurality of coiled tube parts, the tube diameter of the innermost coiled tube part is maximized, The amount of water flow in the innermost coiled tube part is increased, and a step is generated in each gap between the innermost coiled tube part and the outer coiled tube part. The heat exchanger is configured to collide with the outer coiled tube part after passing through the gap between the innermost coiled tube parts .   2. The heat exchanger according to claim 1, wherein each of the coiled tube portions is configured by using a spiral tube body in which the plurality of loop portions are spirally connected. The heat exchanger according to claim 1 or 2, wherein the first and second heat exchange units are partitioned by the partition member or a member separate from the partition member.   The gap between the end portion of the tubular body winding structure portion and the can body is closed, and the combustion gas travels directly from the first region to the start end portion of the combustion gas passage near the combustor opening. The heat exchanger according to any one of claims 1 to 3, further comprising a combustion gas stopper portion to be suppressed. The combustion gas passage is formed in a series across the outer periphery of each of the first and second heat exchange parts,
A combustion gas stopper portion is provided that blocks a terminal portion near the combustion gas outlet in the combustion gas passage and suppresses the combustion gas that has reached the terminal portion from proceeding directly to the second region. The heat exchanger according to any one of claims 1 to 4. Each of the second heat exchange part and the combustion gas passage is divided into two divided parts in the axial direction, and the combustion gas that has passed around the first heat exchange part in the combustion gas passage A first auxiliary partition member that leads to the second region by proceeding to the gap of one divided portion of the second heat exchange portion,
The combustion gas guided to the second region is prevented from proceeding as it is to the combustion gas outlet, and the combustion gas is advanced to the gap of the other one divided portion of the second heat exchange portion. The heat exchanger according to any one of claims 1 to 4, further comprising a second auxiliary partition member.   The tubular body winding structure portion is further extended closer to the combustion gas outlet than the second auxiliary partition member, and has progressed to a portion surrounding the extension portion in the combustion gas passage. The heat exchanger according to claim 6, wherein the combustion gas is configured to further pass through a gap between the extended portions.   The water entering the plurality of coiled tube sections is made in the second heat exchanging section, and the water that has passed through the second heat exchanging section then flows into the first heat exchanging section. The heat exchanger according to any one of claims 1 to 7.   The heat exchanger according to any one of claims 1 to 8, wherein the first and second heat exchanging portions are configured to have different gap sizes. A hot water device comprising a combustor and a heat exchanger for recovering heat from the combustion gas generated by the combustor,
A hot water device, wherein the heat exchanger according to any one of claims 1 to 9 is used as the heat exchanger. The heat exchanger is provided in a posture where the combustor opening is higher than the combustion gas outlet.
The combustor is connected to the top of the heat exchanger and is configured to burn fuel downward;
The hot water apparatus according to claim 10, wherein a bottom casing that guides combustion gas that has passed downward through the combustion gas outlet to an exhaust outlet is connected to a lower portion of the heat exchanger . A drain receiving portion provided in the can of the heat exchanger and receiving a drain flowing down from the tubular body winding structure portion;
The hot water apparatus according to claim 11 , further comprising: a drain discharge unit that discharges the drain received by the drain receiver to the outside of the heat exchanger so as not to flow into the bottom casing . The heat exchanger is configured to guide a drain flowing down from the tubular body winding structure portion to the combustion gas outlet,
The hot water apparatus according to claim 11 , wherein a drain receiving member is provided in the bottom casing so as to receive a drain flowing down from the combustion gas outlet and discharge the drain to the outside of the bottom casing . The heat exchanger is configured to guide a drain flowing down from the tubular body winding structure portion to the combustion gas outlet,
The hot water apparatus according to claim 11 , wherein the bottom casing includes a bottom wall that receives a drain that flows down from the combustion gas outlet, and a discharge port that discharges the drain received on the bottom wall to the outside. . The heat exchanger is provided in a posture in which the combustor opening is lower than the combustion gas outlet,
The combustor is connected to a lower portion of the combustor and configured to burn fuel upward;
The heat exchanger includes a drain receiving portion that receives a drain that flows down from the tubular body winding structure portion, and the drain received by the drain receiving portion does not flow down on the combustor. The hot-water apparatus of Claim 10 provided with the drain discharge means discharged | emitted outside . Each loop part of the said tubular body winding structure part is a hollow rectangular shape, and the surrounding wall part of the can body of the said heat exchanger is a rectangular cylinder shape surrounding each said loop part . Hot water device.

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