JP2009019858A - Heat exchanger and water heater - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of providing high heat exchange efficiency by advancing heating gas at a much rate toward an area for arranging a plurality of heat recovery pipe body parts, while eliminating or reducing complicatedness of using a member for regulating a flow of the heating gas. <P>SOLUTION: This heat exchanger HE has a plurality of heat exchange pipe body parts 30a mutually juxtaposed and extended in the substantially same direction in a plurality of rows and a plurality of stages, and a case 1 for storing the plurality of these pipe body parts 30a inside and oppositely arranging an air supply port 11 for introducing the heating gas inside in an end row L1 of the plurality of pipe body parts 30a. The plurality of pipe body parts 30a of the end row L1 are offset in arrangement more distant from the air supply port 11 than the other pipe body part in a partial pipe body part among these pipe body parts, and are arranged in arrangement for forming a recessed part 38 opposed to the air supply port 11 by recessing in the direction distant from the air supply port 11. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a heat exchanger used for heat recovery from a heating gas such as combustion gas using a heat transfer tube to heat a desired fluid to be heated, and a hot water apparatus including the heat exchanger.

  As an example of a heat exchanger, the applicant of the present invention is a case in which a plurality of thin heat transfer tubes are accommodated in a case in which an air supply port and an exhaust port for allowing combustion gas to flow in and out are formed. Previously proposed (see, for example, Patent Documents 1 and 2). The plurality of heat transfer tubes extend in substantially the same direction and are arranged in a plurality of rows and stages. According to such a configuration, heat exchange is performed when the combustion gas flowing into the case passes through the gap between the heat transfer tubes. About the said several heat exchanger tube, the heat transfer area can be enlarged by increasing the number etc. and heat recovery amount can be increased. Therefore, it is suitable for an application for recovering latent heat from combustion gas.

  However, the prior art still has room for improvement as described below.

  That is, with reference to FIG. 13, in the prior art, when the combustion gas is introduced into the case 9 from the air supply port 91 and proceeds to the plurality of heat transfer tubes 8, the combustion gas is first divided into a plurality of It collides with the front row (end row) L1 of the heat transfer tube 8. For this reason, most of the combustion gas bounced off by the front row L1 travels toward the upper and lower wall portions 92a, 92b of the case 9 through the region in front of the heat transfer tube 8 as indicated by the arrow N10, or the arrow N11. As shown in FIG. 5, a phenomenon of proceeding toward both side walls 92c and 92d of the case 9 occurs. Such a phenomenon becomes more prominent as the gap dimension s1 of the heat transfer tube 8 is reduced. However, when such a phenomenon occurs, the degree of action of the combustion gas on the plurality of heat transfer tubes 8 is lowered, and the heat exchange efficiency is lowered. Moreover, the trouble that the part which combustion gas advances among the wall parts of the various places of case 9 is heated to high temperature also arises.

  For example, the above-described problem may be caused by, for example, a means that a restriction plate for restricting the flow of combustion gas is provided in the case, and the gap between the case and the plurality of heat transfer tubes is strictly defined to a predetermined size. This can be solved. However, when such a means is employed, the heat exchanger manufacturing work becomes complicated, which is not preferable in terms of increasing the productivity of the heat exchanger.

Japanese Patent Laid-Open No. 2005-274043 JP 2005-337543 A

  The present invention has been conceived under the circumstances as described above, and eliminates or reduces the complexity of using a member for regulating the flow of the heating gas, but for heat recovery. To provide a heat exchanger capable of obtaining a high heat exchange efficiency by advancing a heating gas at a high rate toward a region where a plurality of tube parts are provided, and a hot water device including the heat exchanger Is the issue.

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

  The heat exchanger provided by the first aspect of the present invention includes a plurality of tube portions for heat exchange that are arranged in a plurality of rows and stages and extend in substantially the same direction, and the plurality of tube portions are disposed inside. And a case in which an air supply port for containing and introducing a heating gas is provided facing one of the end rows of the plurality of tube parts. The plurality of tube portions of the end row are offset to an arrangement in which some of the tube portions are further away from the air supply port than the other tube portions, and move away from the air supply port. It is provided in the arrangement | sequence which forms the recessed part which became depressed in the direction and faced the said air supply opening.

  According to such a configuration, when the heating gas is advanced from the air supply port into the case, the heating gas enters the recesses formed in the end rows of the plurality of tube portions. Since this recess is recessed in a direction away from the air supply port, when the heating gas enters the recess, the heating gas advances from the inside of the recess toward the arrangement region of the plurality of tube portions. Is promoted. Even if the heating gas collides with a plurality of tube sections in the end row and bounces back, if such a phenomenon occurs in the recess, most of the heating gas is disposed in the tube section. Proceeding directly toward a non-existing region is preferably suppressed. As described above, in the present invention, many heating gases are appropriately advanced toward the arrangement region of the heat exchanging tube portion without using a member for regulating the flow of the heating gas. be able to. As a result, it is possible to obtain high heat exchange efficiency while reducing manufacturing costs. It is possible to appropriately prevent a problem that the wall portion of the case is heated to a high temperature by the heating gas.

  In a preferred embodiment of the present invention, the plurality of tube parts of all or a part of the end row are arranged farther from the air supply port as being closer to a predetermined height of the middle portion in the row direction of the end row. In this way, they are sequentially displaced in the direction facing the air supply port, and are provided in an array bent in a substantially V shape when viewed in the axial length direction of the plurality of tube portions.

  According to such a configuration, the width of the concave portion is relatively small in a portion far from the air supply port, but can be increased in a portion close to the air supply port, and a large amount of heating gas is placed in the concave portion. It can be made to progress. Further, the plurality of tube portions forming the recesses are arranged in an approximately V-shape, and the plurality of tube portions are sequentially displaced in the facing direction to the air supply port. A gap between the plurality of tube portions can be increased. For this reason, it becomes easy for the heating gas which entered the recessed part to pass through such a gap, and it is more preferable to advance a large amount of the heating gas toward the arrangement region of the plurality of tube portions.

  The heat exchanger provided by the second aspect of the present invention includes a plurality of tube parts for heat exchange that are arranged in a plurality of rows and stages and extend in substantially the same direction, and the plurality of tube parts are disposed inside. And a case in which an air supply port for containing and introducing a heating gas is provided facing one of the end rows of the plurality of tube parts. And at least one of the plurality of tube portions in the end row is bent in a direction in which the whole or a part of the longitudinal direction is away from the air supply port, and is in a direction away from the air supply port. A concave portion facing the air supply port is formed.

  According to such a configuration, when the heating gas is advanced from the air supply port into the case, the heating gas enters a recess formed in at least one tube portion of the end row. Since this recess is recessed in a direction away from the air supply port, when the heating gas enters the recess, the heating gas advances from the inside of the recess toward the arrangement region of the plurality of tube portions. Is promoted. Thus, according to the said structure, the effect | action similar to the heat exchanger provided by the 1st side surface of this invention is acquired, many members are used, without using the member for regulating the flow of the gas for a heating. The gas for heating can be appropriately advanced toward the arrangement region of the tube part for heat exchange. As a result, it is possible to obtain high heat exchange efficiency while reducing manufacturing costs. Of course, it is possible to prevent the heating gas from directly traveling to the wall portion of the case, and it is possible to appropriately prevent a problem that the wall portion of the case is heated to a high temperature.

  In a preferred embodiment of the present invention, in the heat exchanger provided by the second aspect of the present invention, the plurality of tube portions of the end row are part of the other tube portions. It is offset in a position farther from the air supply port than the tube body part, and is provided in an array that further forms an additional recess that faces the air supply port and is recessed in a direction away from the air supply port.

  According to such a configuration, in addition to the concave portion formed by bending the tube portion of the end row, an additional concave portion formed by offsetting the tube portion of the end row is further formed. For this reason, these recesses can be made large and deeply recessed in the direction away from the air supply port. As a result, after the heating gas has been advanced to the recess, it can be made to proceed at a higher rate from the recess toward the arrangement region of the plurality of tube portions, which is more advantageous for improving the heat exchange efficiency. .

  In a preferred embodiment of the present invention, a recessed portion that is recessed in a direction away from the air supply port is provided in one or more other rows adjacent to the end row among the plurality of rows of the tubular body portions. It has been.

  According to such a configuration, the offset portion or the bent portion of the tube portion of the end row is prevented from interfering with the tube portion of the other row adjacent to the end row, and the tubes of these rows are arranged. The parts can be brought close to each other. Moreover, according to the said structure, the other row | line | column adjacent to the end row | line also has the recessed part similar to an end row | line | column, and it is set as the structure which is easy to let the gas for heating which has advanced pass. For this reason, when the heating gas passes through the arrangement region of the plurality of tubular body portions in the end row and reaches another row adjacent to the end row, the heating gas progresses by the tubular body portion in this row. It can be prevented from being greatly disturbed. Therefore, it becomes possible to advance the gas for heating more efficiently toward the arrangement region of the plurality of tube portions.

  In a preferred embodiment of the present invention, a plurality of spiral tubular bodies are provided in a substantially concentric lap winding shape and are provided with a tubular lap winding structure portion accommodated in the case. Among the structural portions, a plurality of tube portions arranged in a plurality of rows and stages are a plurality of tube portions for heat exchange.

  According to such a configuration, since the plurality of tube portions for heat exchange are configured using a plurality of spiral tubes, for example, a large number of tubes that extend in a straight line are used. As compared with the case of providing a plurality of tubes in a plurality of rows and a plurality of rows, the total number of tubes can be greatly reduced. Therefore, it is preferable for facilitating the manufacture of the heat exchanger and reducing the manufacturing cost.

  In a preferred embodiment of the present invention, the tubular body winding structure includes first and second tubular body winding structures that are formed separately from each other and stacked in the axial direction thereof. The first tubular wrapping structure portion is configured by laminating a plurality of loop portions of each helical tubular body in a predetermined direction, and the second tubular wrapping structure portion is formed in each helical shape. A plurality of loop portions of the tubular body are laminated in a direction inclined to the direction opposite to the predetermined direction.

  According to such a configuration, a plurality of loop portions of the first tubular wrapping structure portion and a plurality of loop portions of the second tubular wrapping structure portion are arranged in a bent shape. it can. For this reason, it can be easily realized to form a recess in the tube portion facing the air supply port. In addition, it is possible to easily and appropriately realize an increase in the bending width of the plurality of loop portions and formation of the concave portion in a deep shape. That is, unlike the above-described configuration, when using only one tubular body winding structure portion to achieve an arrangement in which a plurality of tubular body portions are arranged in a bent shape, this bent portion is a spiral. Since this is a projecting portion of the tubular tube, it may be an obstacle when fitting the multiple helical tubes together, and it may be difficult to provide the multiple helical tubes in a substantially concentric lap winding structure. However, according to the said structure, such a malfunction is also eliminated.

  The hot water device provided by the third aspect of the present invention includes the heat exchanger provided by the first or second aspect of the present invention, and the heating gas at the air supply port of the case of the heat exchanger. And a combustor for supplying the combustion gas.

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

  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 specifically described with reference to the drawings.

  1 to 5 show an example of a heat exchanger HE to which the present invention is applied. 1 and 2, the heat exchanger HE of the present embodiment includes a case 1 into which combustion gas is introduced, and a plurality of heat transfer tubes accommodated in the case 1. Helical tubular bodies 3A and 3B are provided.

  The case 1 has a hollow, substantially rectangular parallelepiped shape, and an air supply port 11 and an exhaust port 12 for combustion gas are formed in the rear wall portion 10a and the front wall portion 10b. The exhaust port 12 has a rectangular shape as shown in FIG. 5, for example, and the air supply port 11 is the same as this. The bottom wall 10c of the case 1 is provided with a drain outlet 13 for drain. When latent heat recovery is performed from the combustion gas using the heat exchanger HE, a drain (condensed water) is generated, and the drain flows down from the spiral tubular bodies 3A and 3B onto the bottom wall portion 10c. The discharge port 13 serves to discharge such a drain to the outside of the case 1. The drain is generally strongly acidic including nitrogen oxides in the combustion gas. For this reason, Preferably, each part of case 1, spiral tube 3A, 3B, etc. parts which may contact with a drain are made from stainless steel or other materials excellent in acid resistance.

  The plurality of spiral tubular bodies 3A and 3B are stacked one above the other and constitute first and second tubular body wrapping structure portions Sa and Sb. More specifically, each of the spiral tubular bodies 3A and 3B has a configuration in which a plurality of loop portions 30 that are substantially oval in plan view are stacked via a plurality of gaps 39 in the vertical height direction of the case 1. Yes. Each loop portion 30 has a pair of straight tubular tube portions 30a extending in the left-right width direction of the case 1, and a pair of tube portions 30b, 30b ′ connected to these ends and curved in a semicircular arc shape. ing. However, the sizes of the respective loop portions 30 of the plurality of spiral tubular bodies 3A are different from each other, and these are fitted to each other and arranged in a substantially concentric wrapping shape. This portion is the first tubular body winding structure portion Sa. Similarly, the loop portions 30 of the plurality of spiral tubular bodies 3B are also arranged in a substantially concentric lap winding shape with different sizes, and this portion is the second tubular lap winding structure portion Sb. In the present embodiment, the tube portions 30a and 30b do not have a so-called winding gradient. For example, the entire tube portions 30a and 30b are horizontal, and only the tube portion 30b ′ has a winding gradient. . However, the spiral tubular bodies 3A and 3B can be configured so that the entire loop portion 30 has a winding gradient instead of such a configuration.

  As shown in FIG. 4, the plurality of spiral tubular bodies 3 </ b> A and 3 </ b> B are arranged such that the plurality of tubular body portions 30 a are positioned between the air supply port 11 and the exhaust port 12. The plurality of tube sections 30a are arranged in a plurality of rows and a plurality of stages in the front-rear horizontal direction and the vertical height direction of the case 1 (in the drawing, a total of 10 rows L1 to L10 in the front-rear horizontal direction and six stages in the vertical height direction) Are lined up. However, each of the rows L1 to L10 is not in a configuration in which a plurality of tubular body portions 30a are arranged in a straight line, and a part of the plurality of tubular body portions 30a is offset forward of the case 1, They are provided in an array bent in a substantially V shape (however, in FIG. 4, a substantially V shape in the horizontal direction).

  More specifically, the plurality of loop portions 30 of the first tubular body winding structure portion Sa are vertically tilted and stacked so that the lower one is disposed away from the air supply port 11. . On the other hand, the plurality of loop portions 30 of the second tubular body winding structure portion Sb are vertically inclined and stacked vertically so as to approach the air supply port 11 as the lower one is opposite to the above. . Accordingly, in each of the plurality of rows L1 to L10, the front and rear horizontal direction of the case 1 is such that the closer to the intermediate height of each row, the farther from the air inlet 11 the closer to the middle height of each row. The positions are sequentially shifted and arranged in a substantially V shape in the horizontal direction. As a result, the plurality of tubular body portions 30 a in the end row L 1 closest to the air supply port 11 form a recess 38 that faces the air supply port 11. Although not indicated by the reference numerals, the tube portions 30a of the other rows L2 to L10 also form recesses similar to the recesses 38.

  As shown in FIG. 2, extended pipes 37a and 37b penetrating through the side wall 10e of the case 1 are integrally or separately provided at the lower end and the upper end of the plurality of spiral pipes 3A and 3B. Has been. These are connected to a plurality of headers 7a to 7d for incoming and outgoing hot water. When circulating hot water in the plurality of spiral tubes 3A, 3B, for example, in a state where the headers 7b, 7c are connected to each other and the spiral tubes 3A, 3B are connected, the header 7a is allowed to enter water, And the hot water can be discharged from the header 7d.

  6 and 7 show an example of a hot water device provided with the heat exchanger HE described above.

  The hot water device WH of the present embodiment includes a heat exchanger 5 and a combustor 6 other than the heat exchanger HE. The combustor 6 is disposed in the can body 60 and can burn predetermined fuel such as fuel gas or fuel oil supplied from the outside of the can body 60 through the fuel supply pipe 62. Combustion air is supplied upward from the fan 61 into the can body 60, and the combustion gas generated by the combustor 6 is configured to rise toward the heat exchanger 5.

  The heat exchanger 5 is for recovering sensible heat from the combustion gas, for example, a structure in which a heat transfer tube 51 having a plurality of fins 52 is arranged in a can body 50 mounted on the can body 60. have. The heat exchanger HE is arranged above the heat exchanger 5 and connected via an auxiliary can body 59. As shown in FIG. 7, the combustion gas whose sensible heat has been recovered by the heat exchanger 5 passes through the auxiliary can body 59 from the inside of the can body 50 and is supplied to the air supply port 11 of the heat exchanger HE. It is configured. The heat exchanger HE will recover latent heat from the combustion gas after the sensible heat has been recovered by the heat exchanger 5.

  As shown in FIG. 6, the header 7 d for the hot water of the heat exchanger HE is connected to the water inlet 51 a of the heat transfer pipe 51 by piping. In this hot water device WH, when water is introduced into the header 7a of the heat exchanger HE, the water flows through the plurality of spiral tubes 3A, 3B from the lower side to the upper side, When heated. The hot water heated in this way is then sent to the heat transfer tube 51 of the heat exchanger 5 and further heated, and then discharged from the hot water outlet 51b and supplied to a desired hot water supply destination.

  Next, the operation of the heat exchanger HE and the hot water device WH provided with the heat exchanger HE will be described.

  In FIG. 4, first, when combustion gas enters the case 1 of the heat exchanger HE from the air supply port 11, the combustion gas enters the recess 38 of the end row L <b> 1. As a result, a part of the combustion gas that passes through the gap 39 of the end row L1 as it is, except for a part of the combustion gas, collides with the surface of the tube portion 30a of the end row L1. However, since such a collision is performed in the recess 38, the combustion gas bounced off by the tube body portion 30a of the end row L1 does not travel as it is to the region where the tube body portion 30a is not provided, or Less. Therefore, combustion gas can be efficiently advanced with respect to the arrangement region of the plurality of tube portions 30a, and high heat exchange efficiency can be obtained.

  Since the concave portion 38 is recessed in the form where the tubular body portion 30a exists on the upper side and the lower side thereof, the combustion gas directed upward and downward from the concave portion 38 causes the upper wall portion 10d and the bottom wall of the case 1 to move. Proceeding directly toward the portion 10c is also effectively prevented. Therefore, the case where the bottom wall portion 10c and the top wall portion 10d of the case 1 are unduly heated to a high temperature is also eliminated. Unlike the present embodiment, when the drain falls from the spiral tubular bodies 3A, 3B onto the bottom wall portion 10c in a state where the bottom wall portion 10c is heated to a high temperature, the drain is rapidly heated and evaporated. Although noise (evaporation temperature) is generated, according to the heat exchanger HE, it is possible to prevent such abnormal noise from being generated. Although the concave portion 38 is open to the opposite side wall portions 10e and 10f of the case 1, as described above, in the heat exchanger HE, the concave portion 38 is directed toward the arrangement region of the plurality of tubular body portions 30a. Therefore, the amount of the combustion gas that travels directly toward the both side wall portions 10e and 10f of the case 1 can be reduced accordingly. Therefore, it is also suitably suppressed that the side wall portions 10e and 10f are heated to a high temperature.

  In the end row L1, except for a portion thereof, the plurality of tube portions 30a are sequentially displaced in the front-rear horizontal direction of the case 1, and the gap 39 positioned in such a portion has a large width. For this reason, the quantity of the combustion gas which progresses toward the arrangement | positioning area | region of the pipe | tube part 30a of the other row | line | columns L2-L10 after passing through the clearance gap 39 between the pipe | tube part 30a of the end row L1 can be increased. .

  The tube portions 30a of the other rows L2 to L10 are arranged in the same manner as the tube portions 30a of the end row L1 and form recesses similar to the recesses 38. However, the combustion gas can be properly passed. That is, unlike the present embodiment, for example, when the plurality of tube portions 30a of the second row L2 are arranged in a straight line in the vertical direction and the gaps 39 are arranged in a small array, the tube portions 30a pass through the end row L1. It is difficult for the burned combustion gas to pass through the region of the second row L2, and the combustion gas bounced back by the tube portion 30a of the second row L2 is directed toward the bottom wall portion 10c and the upper wall portion 10d of the case 1. There is a risk of proceeding directly. On the other hand, in this embodiment, such a possibility can be eliminated appropriately and combustion gas can be advanced smoothly also to the area | region of other row | line | columns L2-L10. For this reason, in this heat exchanger HE, the combustion gas can be efficiently applied to each of the plurality of tube sections 30, and the heat exchange efficiency can be further increased. Further, if the second row L2 has the same tube arrangement as the end row L1, it is possible to bring them closer without interfering with the tube portions 30a of these two rows L1 and L2. Become.

  In this heat exchanger HE, a plurality of helical tubes 3A, 3B are used as heat transfer tubes, and this has a tubular body winding structure. Therefore, while reducing the number of the helical tubes 3A, 3B, The total number of tube parts 30a can be increased. Therefore, as compared with the case where a simple straight tube is used as the heat transfer tubes and these are provided in a plurality of rows and stages, there is an advantage that the number of heat transfer tubes is reduced and the manufacturing cost of the heat exchanger HE is reduced. It is done. In the heat exchanger HE, the first and second tubular body winding structures Sa and Sb are stacked one above the other as means for providing the row of tubular body portions 30a in a bent arrangement. In addition, the bending width of the tube portions 30a in each row can be increased. That is, unlike the present embodiment, rather than stacking a plurality of spiral tubes vertically, a plurality of spiral tubes having a plurality of loop portions arranged in a bent shape are fitted to each other so as to be substantially concentric. If it is intended to be provided in the lap winding structure, when the bent portion is large, the bent portions interfere with each other, making it difficult to properly fit the spiral tubes. . On the other hand, in the heat exchanger HE of the present embodiment, the first and second tubular body winding structures Sa and Sb are both spirals formed so that the loop portion 30 is inclined only in one direction. Since the tubular bodies 3A or 3B only need to be fitted together, the above-described problems are preferably solved.

  8 to 12 show another embodiment of the present invention. In these drawings, elements that are the same as or similar to those in the above embodiment are given the same reference numerals as in the above embodiment.

  In the embodiment shown in FIG. 8 and FIG. 9, a tube lap winding structure Sc of a plurality of spiral tubes 3C is provided. Each tubular body portion 30c near the air supply port 11 of each helical tubular body portion 3C is a tubular body portion that is bent in a substantially V shape in whole or in the longitudinal direction. The bending direction is a direction away from the air supply port 11. As a result, the end row L1 closest to the air supply port 11 among the multiple rows of tube body portions 30c of the tubular body winding structure portion Sc faces the air supply port 11 and moves away from the air supply port 11. A recess 38a that is recessed in the direction is formed. Concave portions similar to the concave portions 38a are also formed in the other rows L2 to L5. As shown in FIG. 9, the plurality of recesses 38 a are formed so as to communicate in series in the vertical direction of the case 1. Since the plurality of tube portions 30a near the exhaust port 12 are straight tubular, no recess corresponding to the recess 38a is formed in these portions. In the present embodiment, each of the plurality of spiral tubular body portions 3C is bent in the tubular body portion 30c, but can be fitted to each other. For this reason, unlike the above-described embodiment, the tube lap winding structure portion Sc does not need to be formed by stacking two tube lap winding structure portions vertically, and the tube lap winding structure portion having a single-layer structure. It is said that.

  According to the present embodiment, when the combustion gas advances from the air supply port 11 into the case 1, the combustion gas enters the plurality of concave portions 38a of the end row L1. For this reason, most of the combustion gas that has collided with the tube portion 30c of the end row L1 is rebounded toward the air supply port 11 and flows out of the recess 38a as it is, and a lot of the combustion gas communicates with the recess 38a. It progresses toward the arrangement | positioning area | region of the other pipe parts 30c and 30a through the clearance gap 39 currently performed. Therefore, also in the present embodiment, high heat exchange efficiency can be obtained as in the above embodiment. Since the concave portion 38a has a form in which a part of the tubular body portion 30c exists on both sides in the width direction of the case 1, the combustion gas that has entered the concave portion 38a enters the both side wall portions 10e and 10f in the width direction of the case 1. Proceeding directly toward is properly suppressed. Therefore, it is also possible to prevent the side wall portions 10e and 10f from being heated to a high temperature. Although the upper part and the lower part of the concave part 30a are open, as described above, the amount of the combustion gas that advances from the concave part 38a toward the arrangement region of the plurality of tube parts 30c, 30a is large. The amount of combustion gas that passes through the upper part and the lower part and proceeds directly toward the upper wall part 10d and the bottom wall part 10c of the case 1 is reduced. Therefore, it is suppressed that the upper wall part 10d and the bottom wall part 10c are heated to high temperature.

  When the tube part 30c of the end row L1 is bent, the dimension becomes longer than that when the tube part 30c is not bent, and the heat transfer area of the tube part 30c is increased. Therefore, it becomes more preferable to increase the heat recovery amount. Further, since the size of the gap 39 formed between the tube portions 30c also becomes longer and the opening area thereof becomes larger, the combustion gas that has entered the recess 38a passes through the gap 39 and has another size. The effect which becomes easy to advance toward the arrangement | positioning area | region of the tube parts 30c and 30a is also acquired.

  In the embodiment shown in FIGS. 10 and 11, the embodiment shown in FIGS. 1 to 5 and the embodiment shown in FIGS. 8 and 9 are combined. More specifically, the present embodiment has the first and second tubular body winding structures Sd and Se stacked in the vertical height direction of the case 1, but the first tubular body weight The spirally wound structure portion Sd is configured to be displaced so that the plurality of loop portions 30 of the spiral tube body 3D are located on the lower side so as to move away from the air supply port 11. On the other hand, the second tubular body winding structure portion Sd is configured to be displaced so as to move away from the air supply port 11 as the plurality of loop portions 30 of the spiral tubular body 3E are located on the upper side. Yes. For this reason, the end row L1 is formed with a concave portion 38 that faces the air supply port 11 based on the positional deviation of the tube portion 30c. Further, the tube portions 30c near the air inlet 11 of each of the spiral tubes 3D and 3E are formed as bent tube portions whose entire length region or part thereof is bent in a substantially V shape, and the end row L1. The plurality of tube portions 30c are formed with recesses 38a based on the bending. Therefore, the end row L1 is formed with a series of recesses 38, 38a.

  In the present embodiment, the recesses 38 and 38 a are connected in series, and this region is deeply recessed toward the front of the case 1. Therefore, of the combustion gas that has entered the recesses 38 and 38a, the ratio of the combustion gas that advances from these recesses 38 and 38a directly toward the arrangement region of the plurality of tube portions 30c and 30a is increased. It is possible to further increase the exchange efficiency. In addition, the concave portions 38 and 38 a have a part of the plurality of tube parts 30 c above and below them, and a part of the plurality of tube parts 30 c on both sides in the width direction of the case 1. Due to the form, the combustion gas that has entered the recesses 38 and 38a is more appropriately prevented from proceeding directly in the vertical direction and the lateral width direction of the case 1, and the case 1 is unnecessarily heated. Is more thoroughly prevented.

  In the embodiment shown in FIG. 12, a plurality of tube portions 30d extending in the width direction of the case 1 are provided in a plurality of rows and stages in the case 1 into which combustion gas is introduced. However, the plurality of tube portions 30d are bent in a direction in which all or part of the longitudinal direction is away from the air supply port 11. Accordingly, a recess 38 b that faces the air supply port 11 is formed in the end row L <b> 1 that is closest to the air supply port 11. Concave portions similar to the concave portions 38b are also formed in rows other than the end row L1. At both ends of the plurality of pipe portions 30d, there are provided header portions 70a, 70b for incoming water and hot water, and auxiliary header portions 71, and the hot water supplied to the header portion 70a for incoming water is a plurality of A configuration in which after passing through a part of the pipe body part 30d and flowing into the auxiliary header part 71, it passes through the other part of the plurality of pipe body parts 30d and flows into the header part 70b for hot water, and can be discharged outside. It is said that.

  In the present embodiment, the end rows L1 of the plurality of tube portions 30d are formed with recesses 38b facing the air supply port 11, and the other rows are also formed with recesses similar to the recesses 38b. Therefore, for example, the same operation as that of the embodiment shown in FIGS. 8 and 9 can be obtained, and the combustion gas can be efficiently advanced with respect to the arrangement region of the plurality of tube portions 30d. As can be understood from the present embodiment, the plurality of tube portions referred to in the present invention can be configured using a tube other than the helical tube. Although not shown in the drawings, the pipes of the embodiment shown in FIGS. 1 to 5 are formed by sequentially shifting the positions of a plurality of straight tubular pipes or bending them as shown in FIG. It can also be set as the structure which provided the recessed part which faced the air supply opening | mouth by providing in the arrangement | sequence similar to the body part 30a.

  The present invention is not limited to the embodiment described above. 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.

  When a part of the plurality of tubular body parts in the end row is offset to a position farther from the air supply port than the other tubular body parts, the plurality of tubular body parts are connected to each other as in the above embodiment. However, the present invention is not limited to this, although it is preferable to use a substantially V-shaped array that is displaced in the direction facing the air supply port. Moreover, when forming a recessed part by bending the tube part of an end row, it is preferable to form a recessed part largely by bending all the some pipe body parts of an end row, but it is not limited to this, too. In the present invention, it is sufficient that at least one tube portion of the end row is bent to form a recess, and a straight tubular tube portion having no bent portion may exist in the end row.

  Of the plurality of rows of tube portions, it is desirable to form a recess in the other row adjacent to the end row, but this is not a limitation. Even when the recesses are formed only in the end rows and the recesses are not formed in the other rows, heat is generated by advancing more heating gas toward the arrangement region of the plurality of tube portions than in the prior art. An effect of increasing the exchange efficiency can be obtained.

  The case is not limited as long as it accommodates a plurality of tube parts for heat exchange and into which a heating gas such as combustion gas flows. The direction in which the heating gas advances from the air supply port toward the plurality of tube parts is not limited to the horizontal direction. For example, it can also be set as the structure which advances the gas for a heating from the upper direction or the downward direction with respect to a some tube part. In this case, the uppermost row or the lowermost row of the plurality of tube portions is an end row facing the air supply port.

  In the embodiment described above, the heat exchanger according to the present invention is used for latent heat recovery, but is not limited to this. For example, the combustion gas generated by the combustor is directly guided to the intake port of the case. Thus, sensible heat can be recovered, or both sensible heat and latent heat can be recovered. The hot water device as used in 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. It is a concept that broadly includes a device that generates hot water (including one in which antifreeze is heated).

It is a plane sectional view showing an example of a heat exchanger to which the present invention is applied. It is front sectional drawing of the heat exchanger shown in FIG. FIG. 3 is a sectional view taken along line III-III in FIG. 1. It is IV-IV sectional drawing of FIG. It is a front view of the heat exchanger shown in FIG. It is front sectional drawing which shows an example of the hot water apparatus provided with the heat exchanger shown in FIG. It is VII-VII sectional drawing of FIG. It is a plane sectional view showing other examples of a heat exchanger to which the present invention is applied. It is IX-IX sectional drawing of FIG. It is a plane sectional view showing other examples of a heat exchanger to which the present invention is applied. It is XI-XI sectional drawing of FIG. It is a plane sectional view showing other examples of a heat exchanger to which the present invention is applied. (A) is side sectional drawing which shows an example of a prior art, (b) is plane sectional drawing of (a).

Explanation of symbols

WH Hot water device HE Heat exchanger L1 End row (for multiple tube parts)
Sa-Se tubular body winding structure 1 case 3A-3E helical tube 6 combustor 11 air supply port 12 exhaust port 30 loop unit (of helical tube)
30a, 30c Tube part 38, 38a Concave part

Claims (8)

A plurality of tube portions for heat exchange extending in substantially the same direction in a plurality of rows and stages, and
A case in which the plurality of tube parts are accommodated inside, and an air supply port for introducing a heating gas into the inside is provided facing one of the end rows of the plurality of tube parts,
A heat exchanger comprising:
The plurality of tube portions in the end row are offset in a position in which some of the tube portions are further away from the air supply port than other tube portions, and are recessed in a direction away from the air supply port. The heat exchanger is provided in an array that forms a recess facing the air supply port.   The plurality of tube parts of all or part of the end row are arranged farther from the air inlet so that the closer to the predetermined height of the middle portion in the row direction of the end row, the farther from the air inlet. 2. The heat exchanger according to claim 1, wherein the heat exchanger is provided in an array that is sequentially displaced in a facing direction and bent in a substantially V shape when viewed in the axial length direction of the plurality of tube portions. A plurality of tube portions for heat exchange extending in substantially the same direction in a plurality of rows and stages, and
A case in which the plurality of tube parts are accommodated inside, and an air supply port for introducing a heating gas into the inside is provided facing one of the end rows of the plurality of tube parts,
A heat exchanger comprising:
Of the plurality of tube portions of the end row, at least one tube portion is bent in a direction in which the whole or a part of the longitudinal direction is away from the air supply port, and is recessed in a direction away from the air supply port. A heat exchanger characterized by forming a recess facing the air supply port.   The plurality of tube portions of the end row are offset to a position where some of the tube portions are further away from the air supply port than other tube portions, and are recessed in a direction away from the air supply port. 4. The heat exchanger according to claim 3, wherein the heat exchanger is provided in an array further forming an additional recess facing the air supply port.   5. The recessed portion that is recessed in a direction away from the air supply port is also provided in one or a plurality of other rows adjacent to the end row among the plurality of rows of the tubular body portions. The heat exchanger in any one. A plurality of spiral tubular bodies are provided in a substantially concentric lap winding shape, and include a tubular body wrapping structure portion accommodated in the case,
6. The tubular body winding structure section according to claim 1, wherein a plurality of tubular body sections arranged in a plurality of rows and a plurality of stages are the plurality of tubular body sections for heat exchange. Heat exchanger. As the tubular body winding structure portion, there are first and second tubular body winding structure portions that are formed separately from each other and stacked in the axial direction thereof,
The first tubular body winding structure portion is configured such that a plurality of loop portions of each spiral tubular body are inclined and laminated in a certain direction,
7. The heat exchanger according to claim 6, wherein the second tubular body winding structure portion is configured such that a plurality of loop portions of each spiral tubular body are stacked while being inclined in a direction opposite to the predetermined direction. . A heat exchanger according to any one of claims 1 to 7,
A combustor for supplying combustion gas as the heating gas to an air supply port of the case of the heat exchanger;
A hot water apparatus comprising:

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