JP6489436B2 - Heat exchanger and hot water device provided with the same - Google Patents

Description

  The present invention relates to a heat exchanger of a type that recovers heat from a heating gas such as combustion gas using a heat transfer tube, and a hot water device such as a hot water supply device equipped with the heat exchanger.

There exists a thing of patent document 1 as a specific example of the heat exchanger used for a hot-water supply apparatus.
The heat exchanger described in the same document is a case in which a heat transfer tube is accommodated in a case in which combustion gas is supplied to the inside, and a cylindrical projecting portion protrudes from the front wall portion of the case, The inside is an exhaust port.

  When latent heat recovery is performed from the combustion gas using the heat exchanger as described above, water vapor in the combustion gas is condensed and strongly acidic drain water is generated. However, the generation of such drain water is due to the combustion gas being cooled to a temperature below the dew point, and in addition to heat recovery by the heat transfer tube, the combustion gas contacts the part where the temperature of the case is low. By doing so, drain water is also generated. Specifically, for example, when the outside air temperature is low, such as in winter, and the cylindrical projection that forms the exhaust port is cold, the combustion gas comes into contact with the cylindrical projection, thereby forming a cylindrical shape. Drain water may be generated on the inner peripheral surface of the protrusion. If drain water is generated in such a part, the drain water is likely to be scattered outside the exhaust port, and the outer peripheral portion of the exhaust port is contaminated. Therefore, it is desirable to appropriately prevent such a phenomenon.

  The inventors of the present invention perform the drawing process on the front wall portion of the case, and form the substantially cylindrical tubular projecting portion whose inner side is an exhaust port integrally with the front wall portion, whereby the tubular projecting portion is formed. It was conceived that both the case where exhaust is performed with the exhaust duct fitted and connected to the case and the case where exhaust is directly performed to the outside from the exhaust port without using the exhaust duct are conceived. However, when such a means is employed, the length of the cylindrical protrusion cannot be made too long, and the drain water is likely to be scattered outside the exhaust port. In addition, when the cylindrical protruding portion is substantially cylindrical, the diameter of the cylindrical protruding portion cannot be increased so much due to the restriction of the vertical width size of the front wall portion. May have a relatively small opening area. As a result, the flow velocity of the combustion gas when passing through the exhaust port is increased, and the drain water is more easily scattered outside the exhaust port.

Conventionally, as means for suppressing the scattering of drain water from the exhaust port to the outside, for example, there is a means described in Patent Document 2. In this document, a cylindrical projecting portion called an exhaust top is provided on the front wall portion of the case, and two upward and downward inclined plates are provided inside the cylindrical projecting portion. A region between the inclined plates is a substantial exhaust port. According to such a configuration, since the combustion gas is prevented from coming into direct contact with the cylindrical protrusion, the occurrence of drain water on the inner surface of the cylindrical protrusion due to the low outside air temperature is suppressed. Is possible.
However, according to the configuration described above, the mounting structure of the two inclined plates is complicated, and the assembly workability is not so good, so that the manufacturing cost is expensive. In addition, compared to the size of the cylindrical protrusion (exhaust top), the opening size of the exhaust port (opening size between the two inclined plates) is considerably smaller and the exhaust resistance is increased. Also invite.

JP 2013-47575 A JP 2007-232289 A

  The present invention has been conceived under the circumstances as described above, suppresses the generation of drain water in the exhaust port, and has a simple configuration to prevent the drain water from splashing outside the exhaust port. An object of the present invention is to provide a heat exchanger that can be appropriately eliminated, and a hot water apparatus including the heat exchanger.

  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 case in which a heating gas is supplied; and a heat transfer tube that is accommodated in the case and recovers heat from the heating gas. A heat exchanger, wherein the upright front wall of the case is provided with a cylindrical protrusion protruding forward of the case, and the inside of the cylindrical protrusion is an exhaust port An auxiliary member housed in the case, the auxiliary member standing up against or facing the inner surface of the front wall of the case and facing the exhaust port And an upright plate portion provided with an opening to be bent, and an inner peripheral edge portion of the opening portion is bent toward the front side of the case, and is not contacted with the cylindrical projecting portion to the exhaust port. And a burring section that is in It is set to.

According to such a configuration, the following effects can be obtained.
1stly, the burring part of an auxiliary member can bring about the effect | action which becomes difficult for the gas for heating which flows into an exhaust port from the inside of a case to advance directly toward the internal peripheral surface of a cylindrical protrusion part. For this reason, it is possible to prevent a large amount of drain water from being generated in this portion even in the winter season when the outside air temperature is low and the temperature of the cylindrical protrusion is low. As a result, it is possible to appropriately prevent or suppress the problem that the drain water is scattered from the exhaust port to the outside. Since the burring portion is not in contact with the cylindrical projection, even if the temperature of the cylindrical projection is low due to the influence of outside air, the burring portion can be kept at a higher temperature. This is possible, and there is no problem that much drain water is generated on the inner surface of the burring portion.
Secondly, the burring part is formed by bending the inner peripheral edge part of the opening part provided in the upright plate part of the auxiliary member, and its formation is easy. Further, the auxiliary member can be easily attached to the case by using the upright plate portion. Therefore, the assembly workability is good, and it is possible to suitably avoid the trouble that the manufacturing cost of the heat exchanger is significantly increased.
Thirdly, the burring portion does not need to be formed to have the same length as the front and rear lengths of the exhaust port, and even when the burring portion is formed to have a relatively short size, the heating gas is used on the inner peripheral surface of the cylindrical protrusion. It is possible to make it difficult to proceed directly. Further, it is not necessary to form the burring portion with a considerably smaller diameter than the exhaust port. Therefore, the problem that the exhaust resistance is increased by substantially reducing the substantial opening area of the exhaust port due to the provision of the burring portion can be suitably avoided.

In this invention, Preferably, the said cylindrical protrusion part is the substantially cylindrical shape integrally formed in the said front wall part by drawing to the front wall part of the said case.
Here, “substantially cylindrical” includes a stepped cylindrical shape (a cylindrical shape in which cylindrical portions of different diameters are connected with a step), and those with a slight taper on the outer peripheral surface or inner peripheral surface. It is.

According to such a configuration, the projecting length of the cylindrical projecting portion (exhaust port length) cannot be made too long, and the opening area of the exhaust port cannot be formed so large that the heating gas can Based on the fact that the flow velocity at the time of passing becomes faster, originally, there is a problem that drain water is more easily scattered from the exhaust port to the outside. However, according to the present invention, such a problem is preferably solved. Is possible.

  In the present invention, preferably, the burring portion is inclined in a tapered shape so that a gap dimension between the burring portion and the cylindrical protruding portion increases as the distance from the distal end increases.

  According to such a configuration, the burring portion can guide the heating gas in a direction away from the inner peripheral surface of the cylindrical protrusion. Therefore, it becomes possible to prevent more efficiently that much heating gas advances directly to the inner peripheral surface of the cylindrical protrusion and drain water is generated.

  In the present invention, preferably, the burring portion is configured to enter only the base side region of the exhaust port and not enter the tip side region.

  According to such a configuration, it is possible to reduce the size of the burring portion and hence the auxiliary member. In addition, it is more preferable to prevent the burring portion from being provided in a large and bulky state in the exhaust port and to prevent the inside of the exhaust port from being unduly narrowed.

  In the present invention, it is preferable that the burring portion has a non-cylindrical shape and does not enter the lower region of the exhaust port but enters the upper region.

  According to such a configuration, it is also suppressed that the burring portion is large and bulky in the exhaust port, which is more preferable in preventing the substantial opening area of the exhaust port from being unduly narrowed. In addition, according to the said structure, it is difficult to suppress by a burring part that heating gas advances to the lower area | region of an exhaust port, and there exists a possibility that drain water may generate | occur | produce in the lower part of the internal peripheral surface of a cylindrical protrusion part. However, the drain water present in such a site is less likely to be scattered outside the exhaust port as compared with drain water that is generated at the upper part of the inner peripheral surface of the cylindrical protrusion and then drops downward. Therefore, no major problems occur due to the non-cylindrical burring portion.

  In the present invention, preferably, the auxiliary member is provided to be connected to an upper portion of the upright plate portion, and a downward surface of the upper wall portion so as to form a space portion with the upper wall portion of the case. An upper plate portion that is opposed to the upper plate portion, and a heating position is provided at a position of the upper plate portion that is closer to the front in the case and overlaps the exhaust port in the lateral width direction of the case. A hole for allowing the working gas to flow into the space is provided.

According to such a configuration, a portion of the heating gas that passes through the upper portion of the case is almost immediately before it reaches the exhaust port, and between the upper plate portion of the auxiliary member and the upper wall portion of the case. Since it flows into the formed space part, it becomes possible to generate drain water positively in the upper wall part of the case. Therefore, the heating gas that subsequently reaches the exhaust port is less likely to generate drain water in the exhaust port. As a result, it is possible to more effectively suppress the generation of drain water in the exhaust port.
In addition, since there is an upper plate part below the location where the drain water is generated on the upper wall of the case, it is necessary to appropriately prevent this drain water from inadvertently flowing to the exhaust port as it is. Is possible.

  In the present invention, preferably, the lateral width of the hole is set to a size equal to or larger than the proximal end side opening diameter or the lateral width of the exhaust port.

  According to such a configuration, the amount of the heating gas that enters the space between the upper plate portion and the upper wall portion of the case from the hole portion is sufficiently increased, and a drain is formed at the position of the upper wall portion of the case. By actively generating water, the effect of reducing the amount of drain water generated in the exhaust port can be made more remarkable.

  The hot water apparatus provided by the second aspect of the present invention includes the heat exchanger provided by the first aspect of the present invention.

  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 the present invention, preferably, it comprises a burner capable of partial combustion and generating combustion gas as the heating gas, and a fan for supplying combustion air to the burner, and the heat transfer tube The first and second heat transfer tubes arranged in the lateral width direction of the case are provided, and the inside of the case is provided with first and second heat exchange portions that respectively accommodate the first and second heat transfer tubes by a partition member When the hot water apparatus is operated, combustion gas or combustion air is supplied to the first and second heat exchange units, and the first and second exhaust ports are provided to the exhaust port. Combustion gas or combustion air that has passed through each of the heat exchangers is joined and flows in.

  According to such a configuration, as described in detail in the description of the embodiment, for example, the first heat exchange unit is supplied with relatively low-temperature combustion air, and the second heat exchange unit is supplied with the combustion heat. When the combustion gas is supplied, the combustion air and the combustion gas are joined together, so that the temperature of the combustion gas is greatly lowered, and a lot of drain water is easily generated. Under such conditions, the phenomenon of drain water scattering to the outside of the exhaust port becomes conspicuous. However, according to the present invention, such a phenomenon can be suitably prevented or suppressed. is there.

  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.

It is an outline front sectional view showing an example of a hot water device provided with a heat exchanger (secondary heat exchanger) concerning the present invention. It is principal part side surface sectional drawing of FIG. FIG. 2 is a plan sectional view of the secondary heat exchanger shown in FIG. 1. FIG. 4 is a cross-sectional plan view of the structure shown in FIG. 3 with no auxiliary member attached. It is a perspective view of the secondary heat exchanger shown by FIG. (A) is a front perspective view of the auxiliary member shown in FIGS. 2 to 4, (b) is a rear perspective view thereof, (c) is a front view, and (d) is a front view thereof. It is VId-VId sectional drawing of (a). (A), (b) is a perspective view which shows the other example of this invention.

Hereinafter, preferred embodiments of the present invention will be specifically described with reference to the drawings.
In addition, the arrow Fr in drawing shows the front of secondary heat exchanger HE2 mentioned later, and the front-back direction and positional relationship in subsequent description shall follow this.

The hot water device WH shown in FIG. 1 is configured as a hot water supply device, and includes a burner 5, a primary heat exchanger HE1, and a secondary heat exchanger HE2. Although not shown in FIG. 1, an auxiliary member A as shown in FIG. 6 is incorporated in the secondary heat exchanger HE2. The hot water apparatus WH can independently perform two hot water supply operations, ie, general hot water supply and heating hot water supply or bath hot water supply. The primary heat exchanger HE1 and the secondary heat exchanger HE2 are both 1 It is a can two-channel system.
The secondary heat exchanger HE2 corresponds to an example of a heat exchanger according to the present invention. The primary heat exchanger HE1 does not correspond to the heat exchanger according to the present invention.

  The burner 5 is a gas burner, for example, and burns fuel gas by using combustion air sent upward from the fan 51 into the burner case 50. However, the burner 5 can perform so-called partial combustion, and the combustion region is divided into first and second combustion regions a1 and a2 that can be individually controlled for combustion drive.

  The primary heat exchanger HE1 is for recovering sensible heat from the combustion gas traveling upward from the burner 5, and in the can 16 mounted on the burner case 50, a plurality of fins 10a. , 10b, two heat transfer tubes 1A, 1B that are through-joined are accommodated. Partition members 52 and 53 are provided between and below these two heat transfer tubes 1A and 1B, and combustion gases generated by the first and second combustion regions a1 and a2 of the burner 5, respectively. Acts individually on the heat transfer tubes 1A and 1B. Hot water is supplied to the inlets 11a and 11b of the heat transfer tubes 1A and 1B from the hot water headers 23a and 23b of the secondary heat exchanger HE2, and the hot water is a combustion gas in the process of passing through the heat transfer tubes 1A and 1B. It is configured so as to be heated and discharged.

  The secondary heat exchanger HE2 is for recovering latent heat from the combustion gas that has passed through the primary heat exchanger HE1, and is mounted on the primary heat exchanger HE1 via an auxiliary can body 17. Yes. The secondary heat exchanger HE2 includes a plurality of first and second heat transfer tubes 2A and 2B accommodated in the case 3, and a partition member 40 is disposed between them. Is a configuration partitioned into first and second heat exchange sections 21A and 21B. The first and second heat transfer tubes 2A and 2B and the case 3 are made of, for example, stainless steel so as to have corrosion resistance against the strongly acidic drain water generated with the recovery of latent heat.

  As shown in FIG. 3, the plurality of first heat transfer tubes 2 </ b> A are formed as spiral tubes having a substantially rectangular shape or an oval shape in plan view, and are arranged in an overlapping manner. Both the upper and lower ends are drawn out from the side wall 31c of the case 3 and connected to the headers 23a and 24a for hot water and incoming water. The plurality of second heat transfer tubes 2B have the same basic form as the first heat transfer tube 2A, and are formed as spiral tubes arranged in an overlapping manner, and the upper and lower ends thereof are tapped hot water. And headers 23b and 24b for water entry. However, in this embodiment, the non-spiral auxiliary heat transfer tubes 20 are also connected to the headers 23b and 24b. The auxiliary heat transfer tube 20 serves to reduce the flow resistance of the entire heat transfer tube connected to the headers 23b and 24b and to improve the heat exchange efficiency by increasing the heat transfer area. Hot water supply to the first and second heat transfer tubes 2A, 2B (including the auxiliary heat transfer tube 20) is made from the incoming headers 24a, 24b, and passes through the first and second heat transfer tubes 2A, 2B. The heated hot water reaches the headers 23a and 23b for hot water, and thereafter is sent to the heat transfer tubes 1A and 1B of the primary heat exchanger HE1 as described above.

The overall shape of the case 3 is a rectangular parallelepiped, and the rear wall 31b and the front wall 32 are provided with intake ports 34a and 34b for combustion gas and an exhaust port 36. The combustion gas that has passed upward through the primary heat exchanger HE1 is guided to the air supply ports 34a and 34b via the auxiliary can body 17. In FIG. 2, the combustion gas guided to the air supply port 34a has been recovered from the sensible heat by the heat transfer tube 1A of the primary heat exchanger HE1, and is the first heat exchange section of the secondary heat exchanger HE2. Flows into 21A. Although illustration explanation is omitted, a partition member is also provided in the auxiliary can body 17, and the combustion gas after the sensible heat recovery by the heat transfer tube 1B of the primary heat exchanger HE1 is led to the air supply port 34b. And flows into the second heat exchanging portion 21B.

  As shown in FIG. 2, a concave portion 37 extending in the lateral width direction of the case 3 (direction perpendicular to the paper surface of FIG. 2) is formed in the front portion 35a of the bottom wall portion 35 of the case 3 to recover latent heat. The drain water generated and flowing down on the bottom wall portion 35 flows into the concave portion 37. Of the bottom wall portion 35, the portion located below the first and second heat transfer tubes 2A, 2B is a substantially horizontal portion 35b close to the first and second heat transfer tubes 2A, 2B. The position of the concave portion 37 is at the lowest height, for example, by providing a front downward inclined portion 35c in the front region. The concave portion 37 is provided with a drain port 38 for drain water. Instead of this, a drain outlet for drain water may be provided in a laterally open shape at the lower part of at least one of the side walls 31c, 31d. The drain water that has flowed into the concave portion 37 is discharged from the drain port 38 to the outside of the case 3.

  The exhaust port 36 is provided by drawing the front wall portion 32 of the case 3 and integrally forming a cylindrical projecting portion 33 projecting forward on the front wall portion 32. The cylindrical protrusion 33 is substantially cylindrical, and the inside thereof is an exhaust port 36 (see also FIG. 5). In order to reduce the exhaust resistance, it is desirable to make the opening area of the exhaust port 36 relatively large. For this reason, in this embodiment, the opening diameter of the exhaust port 36 is set to a size close to the vertical width of the front wall portion 32, and as shown in FIG. 2, the opening edge lower portion 36 a of the exhaust port 36 and the bottom wall portion 35. The height difference H1 from the front portion 35a is small.

  The auxiliary member A is for preventing drain water from being generated in the exhaust port 36. However, in the present embodiment, as described later, the drain water existing on the front portion 35a of the bottom wall portion 35 is configured to have a function of preventing the drain water from entering the exhaust port 36. The auxiliary member A is formed, for example, by pressing a stainless steel plate.

  As shown in FIG. 6, the auxiliary member A includes an upright plate portion 6 erected in the vertical height direction, an upper plate portion 8 connected to the upper edge portion of the upright plate portion 6, and an opening formed in the upright plate portion 6. It has the burring part 61 provided in a row by the inner periphery of the part 60, and the cover board part 7 connected with the lower edge part of the standing board part 6. FIG.

  The upright plate portion 6 of the auxiliary member A is opposed to the inner surface of the front wall portion 32 of the case 3 and is joined to the front wall portion 32 using means such as spot welding. However, the upright plate portion 6 may be in an opposed approach state in which the upright plate portion 6 is separated from the front wall portion 32. The upright plate portion 6 is provided with an opening 60 facing the exhaust port 36. The opening 60 has a shape in which a circular lower part is partially cut out in a front view.

  The burring portion 61 of the auxiliary member A is a portion where the inner peripheral edge portion of the opening portion 60 of the upright plate portion 6 is bent or curved forward, and as shown in FIG. The gap 68 is formed so as to enter the exhaust port 36 in a non-contact state with the cylindrical protrusion 33. Preferably, the burring portion 61 is formed in a smoothly curved cross-sectional shape. This is preferable for reducing exhaust noise. The burring portion 61 is inclined in a tapered shape, and is formed such that the width Lc of the gap 68 (the radial width of the exhaust port 36) increases toward the tip side. Further, the burring portion 61 is formed as a portion having a comparatively short dimension in the front-rear direction, and only enters the base side region (the right side region in FIG. 2) of the exhaust port 36, and enters the tip side region beyond that. Not entering. Further, the burring portion 61 is non-cylindrical and does not enter the lower region 36b of the exhaust port 36 shown in FIG. 2 (the burring portion 61 corresponding to the lower region 36b is not provided), and the lower region It has entered the region above 36b.

The upper plate portion 8 of the auxiliary member A is provided so as to form a space portion 89 between the upper wall portion 31 a of the case 3. The upper plate portion 8 and the upper wall portion 31a are also joined by means such as spot welding. A hole 80 for allowing the combustion gas to flow into the space 89 is located at a position in the upper plate 8 that is closer to the front in the case 3 and overlaps the exhaust port 36 in the lateral width direction of the case 3. Is provided. Preferably, the lateral width Wd of the hole 80 is set to be equal to or larger than the opening diameter of the proximal end side of the exhaust port 36 (unlike the present embodiment, when the exhaust port 36 is not circular, the lateral width Wd is equal to the exhaust port 36). (This is also the case with the lateral width Wa of the first hole 72a described later). More specifically, the position of the hole 80 is on the front side of the front end of the partition member 40, and as described later, the combustion gas that has passed through the first and second heat exchange portions 21A and 21B, respectively. It is above the location where the (combustion air on the non-combustion side of the burner 5) joins.

  As shown in FIG. 6, the upper plate portion 8 is provided with an additional hole portion 81, which is provided for cutting and processing the downward protruding portion 82. . As shown in FIG. 2, the protrusion 82 is used for positioning and fixing the first heat transfer tube 2A.

  The cover plate portion 7 of the auxiliary member A is a portion for covering the upper portion of the front portion 35 a of the bottom wall portion 35, and the portion near the rear edge portion 7 b is overlapped on the substantially horizontal portion 35 b of the bottom wall portion 35. It is joined. The front edge portion 7 a of the cover plate portion 7 is fixed in contact with or close to the front wall portion 32 of the case 3. This fixing is achieved by welding the upright plate portion 6 to the front wall portion 32. The cover plate portion 7 is provided with a bent portion 70, and a substantially entire area of the cover plate portion 7 or a wide area close thereto is bent into a reverse concave shape in a side sectional view. As a result, a region near the front edge portion 7 a of the cover plate portion 7 is a front rising inclined region 71 a, and a front lowering inclined region 71 b is connected to the rear side via the bent portion 70.

  The cover plate portion 7 is provided with a plurality of holes 72 for allowing drain water flowing on the cover plate portion 7 to flow down on the bottom wall portion 35. The plurality of hole portions 72 are provided so as to be positioned in the bent portion 70, and are arranged at intervals in the lateral width direction of the cover plate portion 7. Each hole 72 is a long hole having a larger width in the lateral width than in the front-rear width, and is open across both the front rising slope area 71a and the front falling slope area 71b. Among the plurality of holes 72, the first hole 72 (72 a) is a hole located behind the exhaust port 36 so as to overlap the exhaust port 36 in the lateral width direction of the case 3. As shown in FIG. 4, the front-rear width La and the lateral width Wa of the first hole 72a are larger than the front-rear width Lb and the lateral width Wb of the other second hole 72 (72b). Preferably, the lateral width Wa of the first hole portion 72a is set to a dimension equal to or larger than the proximal end side opening diameter of the exhaust port 36.

  The front edge portion 7a of the cover plate portion 7 is spaced from the opening edge lower portion 36a of the exhaust port 36 to a position above it, and there is a vertical height between the front edge portion 7a and the opening edge lower portion 36a. A gap 77 having a width in the vertical direction is formed. The gap 77 is a portion that is actively provided to communicate the lower region of the cover plate portion 7 with the exhaust port 36, and the combustion gas that has entered the lower portion of the cover plate portion 7 through the hole 72 is a gap 77. And can flow into the exhaust port 36. Preferably, the width of the gap 77 in the vertical direction is equal to or greater than the pipe gap Le (gap between the pipe sections) in the vertical arrangement direction of the first and second heat transfer tubes 2A and 2B (pipe gap Le. Are the minimum gaps among them, and this is the same for the case inner bottom gap Lf described below), or the lower part of the first and second heat transfer tubes 2A, 2B and the case 3 The width is equal to or larger than the case bottom gap Lf formed between the bottom wall 35 and the bottom wall 35. This means that the vertical width of the gap 77 is equal to or larger than the smaller gap of the tube gap Le and the case bottom gap Lf. Of course, it is also good. Such a configuration is preferable in that the combustion gas can smoothly flow through the gap 77 and the exhaust resistance of the secondary heat exchanger HE2 is prevented from being reduced.

  Next, the operation of the hot water device WH will be described.

  First, as shown in FIG. 2, in the secondary heat exchanger HE2, the combustion gas that has traveled forward in the case 3 flows into the exhaust port 36 by the burring portion 61 of the auxiliary member A. Regulations are added in the direction of travel. Specifically, the combustion gas is regulated such that it does not easily progress directly toward the inner peripheral surface of the cylindrical protrusion 33. In particular, since the burring portion 61 is tapered so that the dimension Lc of the gap 68 between the burring portion 61 and the cylindrical protrusion 33 becomes larger toward the distal end side, the combustion gas flows into the cylindrical protrusion 33. It is possible to reduce the degree to which the combustion gas contacts the inner peripheral surface of the cylindrical protrusion 33 by advancing the combustion gas away from the inner peripheral surface.

  For example, in winter, when the outside air temperature is low and the temperature of the cylindrical protrusion 33 is low, if the combustion gas contacts the cylindrical protrusion 33, there is a possibility that drain water is generated in this portion. If drain water is generated on the inner peripheral surface of the cylindrical protrusion 33, the drain water is likely to be scattered outside the exhaust port 36. The cylindrical protruding portion 33 is formed by drawing, and has a restriction that the protruding dimension cannot be made too long and the opening area of the exhaust port 36 cannot be increased so much. Water is likely to splash outside. On the other hand, in the present embodiment, the degree of contact of the combustion gas with the cylindrical protrusion 33 is reduced, and it is difficult to generate drain water in the exhaust port 36. As a result, drain water from the exhaust port 36 to the outside is reduced. It is possible to suitably prevent scattering.

  The burring portion 61 need not be formed to have a considerably smaller diameter than the exhaust port 36. In addition, as described above, the burring portion 61 enters only the base side region of the exhaust port 36 in the front-rear direction of the case 3. Further, the burring portion 61 is non-cylindrical and does not enter the lower region 36 b of the exhaust port 36. Therefore, the burring portion 61 is not unduly large and bulky inside the exhaust port 36, and the substantial opening area of the exhaust port 36 can be prevented from being greatly reduced.

  A part of the combustion gas that travels in the upper part of the case 3 flows into the space 89 from the hole 80 of the upper plate portion 8, and it is possible to positively generate drain water at the position of the upper wall portion 31a. Is possible. That is, when the first combustion region a1 of the burner 5 is turned off and the second combustion region a2 is turned on, low-temperature combustion air is supplied to the first heat exchange unit 21A, and A high-temperature combustion gas may be supplied to the second heat exchange unit 21B. In such a case, the combustion air and the combustion gas merge at the rear of the exhaust port 36. As a result, the temperature of the combustion gas is lowered, so that the mixed gas is likely to generate drain water. When such a mixed gas flows into the exhaust port 36 as it is, drain water is easily generated in the exhaust port 36, but in the present embodiment, above the region where the combustion air and the combustion gas are mixed, Since the hole portion 80 is provided, it is possible to positively generate drain water in the upper wall portion 31a above the upper plate portion 8, and to allow a mixed gas that does not easily generate drain water to flow into the exhaust port 36. it can. By such a thing, it is prevented more appropriately that drain water is scattered outside the exhaust port 36.

Unlike the above, even when the combustion gas is supplied to each of the first and second heat exchange parts 21A and 21B, for example, when the outside air temperature is low and the temperature of the upper wall part 31a is low, As described above, it is possible to positively generate drain water in the upper wall portion 31a and to allow combustion gas that hardly generates drain water to flow into the exhaust port 36.
About the drain water generated in the upper wall portion 31a, for example, it is possible to guide the upper wall portion 31a and the upper plate portion 8 to the side portion in the case 3 and then guide it onto the bottom wall portion 35. It is possible not to enter the exhaust port 36.

On the other hand, drain water generated by performing latent heat recovery from the combustion gas using the heat transfer tubes 2A and 2B flows into the front portion 35a of the bottom wall portion 35 of the case 3, and the combustion gas directly hits this portion. This is preferably prevented by the cover plate portion 7 of the auxiliary member A. Further, the combustion gas that has entered the lower portion of the cover plate portion 7 from the hole portion 72 passes through the gap 77 between the front edge portion 7a of the cover plate portion 7 and the opening edge lower portion 36a of the exhaust port 36, and enters the exhaust port 36. It flows in smoothly. If the width of the gap 77 is set to a certain size or more (for example, the width of the pipe gap Le or the case inner bottom gap Lf or more), the flow velocity of the combustion gas when passing through the gap 77 is slowed down. It is possible. As a result, in the present embodiment, the drain existing on the front portion 35a of the bottom wall portion 35 is small although the height difference H1 between the opening edge lower portion 36a of the exhaust port 36 and the front portion 35a of the bottom wall portion 35 is small. It is possible to prevent water from being wound up to the exhaust port 36 side by the combustion gas.

  The drain water flows on the cover plate portion 7, and such drain water can flow down below the cover plate portion 7 through the plurality of hole portions 72. Therefore, the drain water present on the cover plate portion 7 is also prevented from being blown off to the exhaust port 36 side by the combustion gas. Since the opening area of the first hole 72 (72a) arranged so as to overlap with the exhaust port 36 in the width direction of the case 3 is large, the rear side of the exhaust port 36 on the cover plate portion 7 (combustion gas flow direction) It is possible to prevent a large amount of drain water from being present in the upstream region, and to more appropriately prevent the drain water from being blown into the exhaust port 36 from the cover plate portion 7.

  Since the cover plate portion 7 is bent in an inverted shape and has a plurality of hole portions 72 arranged side by side in the lateral width direction in the bent portion 70 having the lowest height, Water becomes easy to flow. Moreover, since the area | region close | similar to the exhaust port 36 is made into the front rising inclination area | region 71a among the cover board parts 7, it may arise that drain water climbs up this inclination area | region 71a and enters in the exhaust opening 36. FIG. It becomes difficult. Further, since the hole 72 is opened across both the front rising slope area 71a and the front falling slope area 71b, the drain water flows in the process in which the drain water flows downward through the front falling slope area 71b. It will quickly flow into the hole 72. Even when a phenomenon occurs in which the drain water rises and jumps to the inclined area 71 a, the drain water can be quickly flowed into the hole 72.

  Since the hole 72 is a long hole having a lateral width larger than the front-rear width, drain water flowing on the cover plate part 7 can easily flow into the hole 72 without increasing the opening area of the hole 72 so much. Is possible. The larger the opening area of the hole 72, the more heating gas flows from the hole 72 into the lower region of the cover plate part 7. According to the above configuration, such a situation can be appropriately suppressed. Is possible.

  FIG. 7 shows another embodiment of the present invention. In these drawings, elements that are the same as or similar to those in the above embodiment are denoted by the same reference numerals as those in the above embodiment, and redundant description is omitted.

  The auxiliary member A1 shown in FIG. 7 (a) has an upright plate portion 6 in which a burring portion 61 is continuously provided and an upper plate portion 8, but corresponds to the cover plate portion 7 of the auxiliary member A described above. Is not provided. In the present invention, such a configuration can be used, but a configuration in which the upper plate portion 8 is not provided is also possible.

  The auxiliary member A2 shown in FIG. 7B is provided with a cylindrical burring portion 61 by forming a circular opening 60 in the upright plate portion 6 and bending the entire inner periphery of the opening 60. ing. As understood from the present embodiment, the burring portion referred to in the present invention may be either cylindrical or non-cylindrical.

  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 variously modified within the intended scope of the present invention.

  The front wall portion of the case of the heat exchanger referred to in the present invention means an upright wall portion provided with an exhaust port in the wall portion of the case. The front-rear direction of the heat exchanger does not necessarily match the front-rear direction of the hot water apparatus, and the front wall portion of the heat exchanger may be set to face the rear of the hot water apparatus.

  The present invention is optimal when a substantially cylindrical cylindrical protrusion is formed on the front wall portion of the case by drawing and the inside is used as an exhaust port, but the exhaust port is not necessarily configured as such. May be. The cylindrical protrusion may be formed by a member separate from the case. Moreover, it is good also considering a cylindrical protrusion part as shapes other than cylindrical shape.

  The heat exchanger tube of the heat exchanger is not limited to the spiral tube type, but may be another type of heat transfer tube such as a straight tube body or a serpentine tube body. For supplying the heating gas to the heat exchanger case, instead of providing the air supply port on the rear wall portion of the case, for example, the air supply port is provided in a region near the rear portion of the bottom wall portion or an intermediate region. Can also be performed. The heating gas referred to in the present invention is not limited to the combustion gas, and for example, high-temperature exhaust gas discharged from a power generation unit such as a fuel cell or a gas engine of a cogeneration system can also be used. The heat exchanger is not limited to the one-can two-channel system, but can also be a one-can one-channel system (one type of heat transfer tube is accommodated in one case). 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. Widely includes equipment for producing hot water.

WH Hot water device A, A1, A2 Auxiliary member HE2 Secondary heat exchanger (heat exchanger)
2A, 2B First and second heat transfer tubes (heat transfer tubes)
21A, 21B 1st and 2nd heat exchange part 3 Case (of heat exchanger)
32 Front wall (case)
33 Cylindrical protrusion 36 Exhaust port 36a Opening edge lower part (exhaust port)
5 Burner 51 Fan 6 Standing plate portion 60 Opening portion 61 Burring portion 68 Clearance 8 Upper plate portion 80 Hole portion 89 Space portion

Claims (9)

A case in which heating gas is supplied inside;
A heat transfer tube housed in the case and recovering heat from the heating gas;
With
The upright front wall portion of the case is provided with a cylindrical protruding portion that protrudes forward of the case, and an inner side of the cylindrical protruding portion serves as an exhaust port. ,
An auxiliary member housed in the case;
This auxiliary member is
An upright plate portion that stands up against the inner surface of the front wall portion of the case in an opposing contact or close proximity and has an opening facing the exhaust port; and
A burring portion that is formed by bending the inner peripheral edge of the opening to the front side of the case, and that enters the exhaust port in a non-contact state with the cylindrical protrusion;
A heat exchanger characterized by comprising: The heat exchanger according to claim 1,
The said cylindrical protrusion part is a heat exchanger which is the substantially cylindrical shape integrally formed in the said front wall part by drawing-drawing to the front wall part of the said case. The heat exchanger according to claim 1 or 2,
The said burring part is a heat exchanger which inclines taperingly so that the clearance gap dimension between the said burring part and the said cylindrical protrusion part may become large, so that it progresses to the front end side. The heat exchanger according to any one of claims 1 to 3,
The burring portion is configured to enter only the base side region of the exhaust port and not to enter the tip side region. The heat exchanger according to any one of claims 1 to 4,
The said burring part is a non-cylindrical shape, and is the heat exchanger which is set as the structure which did not approach into a lower area | region among the said exhaust ports, but entered the area | region above it. The heat exchanger according to any one of claims 1 to 5,
The auxiliary member includes an upper plate portion that is connected to the upper portion of the upright plate portion and that faces the downward surface of the upper wall portion so that a space portion is formed between the upper wall portion and the case. And more
A hole for allowing heating gas to flow into the space at a position closer to the front in the case and overlapping with the exhaust port in the lateral width direction of the case. A heat exchanger is provided. The heat exchanger according to claim 6,
The heat exchanger according to claim 1, wherein a width of the hole is equal to or larger than a diameter of the proximal end of the exhaust port or a width of the hole.   A hot water apparatus comprising the heat exchanger according to any one of claims 1 to 7. The hot water device according to claim 8,
A burner capable of partial combustion and generating combustion gas as the heating gas;
A fan for supplying combustion air to the burner;
With
As the heat transfer tube, provided with first and second heat transfer tubes arranged in the width direction of the case,
The inside of the case is partitioned by a partition member into first and second heat exchange units that accommodate the first and second heat transfer tubes, respectively, and the first and second heat exchange units are operated during operation of the hot water apparatus. Is configured to be supplied with combustion gas or combustion air,
A hot water apparatus configured such that combustion gas or combustion air that has passed through each of the first and second heat exchange units merges and flows into the exhaust port.

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