JP2007017112A - Heat source device and heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat source device capable of recovering efficiently heats from combustion gases generated from two combustors, while simplifying structure or the like, and capable of restraining an exhaust port peripheral part for the combustion gases from being contaminated with drain. <P>SOLUTION: This heat source device is provided with an upper heat exchange part UH and a lower heat exchange part UL layered along a vertical height direction, as the two heat exchange parts for recovering the heats individually from the combustion gases generated from the first and second combustors, the heat exchange parts UH, LH are arranged inside a casing 5 having air supply ports 51a, 51b for guiding the combustion gases toward the heat exchange parts UH, LH, and an exhaust port 52 formed in a wall part 50b erected along the vertical height direction, and are partitioned vertically by a partitioning plate 6, and an erected part 61 erected upwards is provided in an end edge sided to the exhaust port 52 or in the vicinity portion thereof out of the partitioning plate 6, to restrain the drain dropped from the upper heat exchange part UH onto the partitioning plate 6 from being splashed toward the exhaust port 52. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention includes at least two combustors, and performs heat recovery from combustion gases generated by the two combustors, for example, to generate hot water for general hot water supply and to heat hot water for floor heating. The present invention relates to a heat source device capable of individually heating two kinds of fluids to be heated, and a heat exchanger that can be suitably used as a component of the heat source device.

  As a heat source device, there is a so-called two-can two-circuit type device such as that described in Patent Document 1, for example. This heat source device is provided with two combustors such as gas burners in two cans, and these two cans have two heat recovery units individually from the combustion gas generated by the two combustors. A heat exchanger is provided. According to such a configuration, the operation control of the two combustors and the heat recovery by the two heat exchangers are performed separately, for example, generation of hot water for general hot water supply and heating of hot water for floor heating. Can be performed independently.

  However, in the heat source device as described above, there is still room for improvement as described below.

  In other words, when recovering heat from combustion gas, from the viewpoint of improving its efficiency, in addition to sensible heat of combustion gas, it is also necessary to recover latent heat in combustion gas (more precisely, latent heat of water vapor in combustion gas) There is. As means for meeting such a demand, for example, as shown in FIG. 14, latent heat is applied to cans 92a and 92b including two combustors 90a and 90b and sensible heat recovery heat exchangers 91a and 91b. It is conceivable to additionally provide heat exchangers 93a and 93b for recovery. However, according to such a configuration, since the heat exchangers 93a and 93b for recovering latent heat are arranged in the horizontal direction, it is possible to prevent the overall lateral width from being increased while avoiding interference between them. Therefore, it is difficult to increase the lengths La and Lb. For this reason, as each heat exchanger tube 930 which comprises heat exchanger 93a, 93b, it is necessary to use a comparatively short thing. However, with such a configuration, it is necessary to considerably increase the total number of the heat transfer tubes 930 as means for increasing the heat exchange efficiency of the heat exchangers 93a and 93b. This complicates the structure of the heat exchangers 93a and 93b and causes a problem that the manufacturing cost is expensive.

  In addition, when latent heat recovery is performed from combustion gas, water vapor in the combustion gas is condensed and many drains (condensed water) are generated. In general, this drain is the sulfur oxide in the combustion gas. It becomes strongly acidic to about PH3 that absorbs nitrogen oxides and the like. Therefore, such a strong acid drain is prevented from being scattered, for example, toward the exhaust port of the heat exchanger due to the flow of the combustion gas and contaminating or corroding the peripheral portion thereof. It is also requested.

  The present applicant has previously proposed, for example, the means described in Patent Document 2 as a means for preventing drain scattering. In this means, a wall portion projecting downward is provided on the upper wall portion of the casing surrounding the heat transfer tube of the heat exchanger, and the drain portion extends from the heat transfer tube of the heat exchanger toward the exhaust port in front of the wall portion. I try not to scatter. However, this means cannot prevent the drain accumulated on the drain receiver located below the heat transfer tube from being scattered. In order to prevent the drain on the drain receiver from being scattered toward the exhaust port and contaminating the periphery thereof, the exhaust port must be provided at a considerably high position of the casing. Restricted and exhaust resistance increases. Further, there is a restriction that a drain recovery unit must be connected to a portion of the drain receiver near the combustion gas downstream.

Japanese Patent Laying-Open No. 2003-4227 (see FIG. 3) Japanese Patent Laid-Open No. 11-23067

  The present invention has been conceived under the circumstances described above, and it is possible to efficiently use the combustion gas generated from each of the two combustors while simplifying the structure and reducing the manufacturing cost. To provide a heat source device and a heat exchanger capable of recovering heat and appropriately suppressing problems such as contamination of the periphery of the exhaust port of the combustion gas by a drain generated by heat recovery Is the issue.

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

  The heat source device provided by the first aspect of the present invention includes first and second combustors that can be driven to burn independently of each other, a plurality of heat transfer tubes, and the first and second heat exchangers. A heat source device comprising at least two heat exchange parts for individually recovering heat from the combustion gas generated by each of the combustors, wherein the two heat exchange parts have a vertical height Provided with an upper heat exchanging portion and a lower heat exchanging portion provided in an overlapping arrangement in the direction, and the upper heat exchanging portion and the lower heat exchanging portion are provided with an air inlet and a vertical height for guiding combustion gas toward them. It is arranged in a casing having an exhaust port formed on a wall portion standing in the direction, and is partitioned up and down by a partition plate arranged in the casing, and among the partition plates, near the exhaust port Edge of or Is provided with an upstanding portion that stands upward so that the drain that has fallen onto the partition plate from the upper heat exchange portion can be prevented from scattering toward the exhaust port. It is said.

  According to such a configuration, the following effects can be obtained.

  That is, two heat exchanging parts capable of individually recovering heat from the combustion gases generated by the first and second combustors overlap in the vertical direction as an upper heat exchanging part and a lower heat exchanging part. Therefore, even when the lengths of the plurality of heat transfer tubes constituting these heat exchange portions are increased, they do not interfere with each other, and each heat transfer tube can be lengthened. Therefore, high heat exchange is achieved while reducing the number of heat transfer tubes in each of the upper and lower heat exchange sections, simplifying the structure of each heat exchange section, suppressing the increase in size, and reducing the manufacturing cost. Efficiency can be obtained. Moreover, since the upper heat exchange part and the lower heat exchange part can be made into the structure accommodated in one casing, simplification of a structure and suppression of an enlargement are promoted more.

  As a further important effect, according to the present invention, when latent heat is recovered from combustion gas using the upper heat exchange section, even if the drain generated in the upper heat exchange section falls on the partition plate. The scattering of the drain toward the exhaust port due to the flow of the combustion gas is appropriately suppressed by the standing portion of the partition plate. Therefore, the trouble that the exhaust port periphery is contaminated by the drain is also avoided. In particular, since the standing portion stands upward from the partition plate, it will properly block the drain present on the partition plate, and the effect of preventing the drain from scattering will be very excellent, Furthermore, there is no restriction that a portion for treating the drain has to be provided on the downstream side of the partition plate in the combustion gas flow direction. In addition, according to the present invention, even if the exhaust port is provided at the same height as the partition plate, the exhaust port is set to such a height in order to prevent contamination around the exhaust port. By providing, it becomes possible to rationally discharge the two types of combustion gases that have passed through each of the upper heat exchange section and the lower heat exchange section to the outside of the casing through one exhaust port. As described above, according to the present invention, the flexibility in selecting the position when the exhaust port is provided in the casing is excellent.

  The heat exchanger provided by the second aspect of the present invention has a plurality of heat transfer tubes for recovering heat from the combustion gas, and is arranged so as to overlap each other in the vertical height direction. The upper and lower heat exchanging portions, the upper heat exchanging portion and the lower heat exchanging portion therein, and the intake port for guiding the combustion gas toward the upper heat exchanging portion and the lower heat exchanging portion; A casing having an exhaust port formed in a wall portion standing in the height direction, a partition plate disposed in the casing and partitioning the upper heat exchange portion and the lower heat exchange portion, and the partition Of the plate, it is provided at the edge near the exhaust port or in the vicinity thereof, and the drain that has fallen on the partition plate from the upper heat exchanging portion can be prevented from scattering toward the exhaust port. Standing upright and It is characterized in that it comprises a.

  The heat exchanger having such a configuration can be suitably used as a component of the heat source device provided by the first aspect of the present invention, and the same effect as described for the heat source device can be obtained.

  In a preferred embodiment of the present invention, the exhaust port is formed in a shape extending in a substantially horizontal direction, and the upright portion of the partition plate is in a direction intersecting the traveling direction of the combustion gas with respect to the upright portion. It extends in a series and is formed to have a longer dimension than the exhaust port so as to face the entire length region in the longitudinal direction of the exhaust port.

  According to such a configuration, the drain that has fallen onto the partition plate from the upper heat exchanging portion is more reliably prevented from scattering toward the exhaust port.

  In a preferred embodiment of the present invention, the upright portion of the partition plate is in contact with or close to any one of the upper heat exchange portions near the exhaust port, and the heat transfer tube It has at least one of a hydrophilic treatment part which promotes that a drain falls on a partition plate, a rough surface treatment part, and a plurality of grooves.

  According to such a configuration, when the drain is generated and attached to the surface of the heat transfer tube with which the upright portion of the partition plate is in contact with or approaching, the drain easily flows down through the upright portion. That is, drain elimination from the heat transfer tube is promoted. Therefore, it is possible to prevent the drain attached to the heat transfer tube near the exhaust port from being scattered toward the exhaust port due to the flow of the combustion gas.

  In a preferred embodiment of the present invention, the partition plate has an upper plate body and a lower plate body that are overlapped in the vertical thickness direction, and the upper plate body constitutes the upper heat exchange section. The lower plate body has a convex stepped portion swelled downward so as to approach the heat transfer tube of the lower heat exchange portion. ing.

  According to such a structure, the clearance gap between each heat exchanger tube and partition plate of an upper heat exchange part and a lower heat exchange part can be made small. Therefore, it is preferable to increase the amount of heat recovered by the heat transfer tube by preventing a large amount of combustion gas from flowing through these gaps. On the other hand, the upper plate body and the lower plate body each having a convex step portion can be easily manufactured by, for example, pressing a thin metal plate, so that the partition plate is inexpensive and lightweight. Can be manufactured.

  In a preferred embodiment of the present invention, the partition plate includes a plurality of upward and downward stepped portions that bulge upward and downward so as to approach the respective heat transfer tubes of the upper heat exchange portion and the lower heat exchange portion. These upward and downward stepped portions extend in a direction intersecting the combustion gas flow direction in the casing and are arranged in a staggered manner in the combustion gas flow direction.

  According to such a configuration, since the gaps between the heat transfer tubes of the upper heat exchanging portion and the lower heat exchanging portion and the upward and downward stepped portions of the partition plate are reduced, there is still a lot of combustion in this portion. The heat exchange efficiency can be improved by preventing the gas from flowing. On the other hand, the partition plate can be formed, for example, by pressing a single metal plate, and is more suitable for reducing the manufacturing cost and weight of the partition plate.

  In a preferred embodiment of the present invention, at the end portions of the plurality of heat transfer tubes constituting the upper heat exchange portion and the lower heat exchange portion, the upper and lower ends protrude above and below the plurality of heat transfer tubes, respectively. The header of the upper heat exchange part and the header of the lower heat exchange part are displaced in the horizontal direction so as not to overlap in the vertical height direction, and the header of the lower heat exchange part The upper end of is set to the same height as the lower end of the upper heat exchanging part or higher.

  According to such a configuration, the heat transfer tubes can be brought close to each other so that the headers of the upper heat exchange unit and the lower heat exchange unit do not interfere with each other. Thus, the gap between the partition plate that partitions them and each heat transfer tube can be reduced, and a large amount of combustion gas can be prevented from flowing through the gap. It is also effective to reduce the total height of the upper heat exchange part and the lower heat exchange part, and to reduce the size of the casing, and thus the overall height of the heat source device.

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

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

  1 to 6 show an example of a heat source device to which the present invention is applied. As clearly shown in FIG. 1, the heat source apparatus A of the present embodiment includes cans 1A and 1B, combustors 2A and 2B, primary heat exchangers 3A and 3B, and a secondary heat exchanger B. ing. Although the detailed configuration of the secondary heat exchanger B will be described later, the secondary heat exchanger B includes an upper heat exchange unit UH and a lower heat exchange unit LH configured by a plurality of heat transfer tubes 40. This heat source device A has two hot water heaters P1 and P2 that perform hot water heating independent of each other. The hot water heating unit P1 includes the upper heat exchange unit UH and the primary heat exchanger 3A, and is a part that generates so-called hot water for general hot water supplied to, for example, a kitchen or a washroom. On the other hand, the hot water heating part P2 includes the lower heat exchange part LH and the primary heat exchanger 3B, and is a part for heating hot water used for floor heating, for example, as a heating terminal.

  The combustors 2A and 2B are, for example, a gas combustor that burns city gas or the like, or an oil combustor that burns kerosene or the like, and is disposed inside the can bodies 1A and 1B. These combustors 2A and 2B can burn fuel by using combustion air supplied upward from blower fans 29A and 29B attached to the lower portions of the cans 1A and 1B. Performed independently of each other. The primary heat exchangers 3A and 3B are disposed above the combustors 2A and 2B, and recover sensible heat from the combustion gas that has traveled upward from the combustors 2A and 2B. These primary heat exchangers 3A and 3B are configured by using, for example, a plurality of finned pipes that penetrate the can bodies 1A and 1B in a substantially horizontal direction.

  The secondary heat exchanger B is for further recovering latent heat from the combustion gas that has passed through each of the primary heat exchangers 3A and 3B and from which sensible heat has been recovered, and between the upper portions of the can bodies 1A and 1B. It is provided so as to be bridged over. The secondary heat exchanger B is a so-called multi-tube type, and in addition to the plurality of heat transfer tubes 40 described above, a plurality of headers 41 provided at both ends of the heat transfer tubes 40, the headers 41 and the heat transfer tubes 40. And a partition plate 6 that vertically divides the upper heat exchange unit UH and the lower heat exchange unit LH (see FIGS. 4 to 6).

  The upper heat exchange unit UH and the lower heat exchange unit LH of the secondary heat exchanger B are configured such that supply and discharge of hot water are performed independently of each other. More specifically, as shown to Fig.3 (a), the both ends of the some heat exchanger tube 40 which comprises the upper heat exchange part UH are used for the entrance and exit for the hot water which has the water inlet 410 and the hot water outlet 411. Headers 41A and 41B and a hot water return header 41C are provided. For example, a water supply pipe 48 for supplying tap water or the like is connected to the water inlet 410, and water supplied from the water supply pipe 48 to the water inlet 410 is supplied to one of the plurality of heat transfer pipes 40 from the header 41A. After passing through the section and flowing into the header 41C, it passes through the remaining portions of the plurality of heat transfer tubes 40 and flows into the header 41B. In such a distribution process, the water is heated by the combustion gas and discharged from the hot water outlet 411. As shown in FIGS. 1 and 2, the hot water outlet 411 is connected to the primary heat exchanger 3A via a pipe 47. From the hot water pipe 46 connected to the primary heat exchanger 3A, a kitchen and other parts are provided. Hot water is sent to the hot water supply destination.

  The lower heat exchange part LH of the secondary heat exchanger B overlaps the lower part of the upper heat exchange part UH, and its basic configuration is the same as that of the upper heat exchange part UH described above. Specifically, as shown in FIG. 3B, at both ends of the plurality of heat transfer tubes 40 constituting the lower heat exchanging portion LH, there are headers 41D and 41E for incoming and outgoing hot water, and for turning back hot water. Header 41F. When hot water sent from the floor heating main body (not shown) through the hot water return pipe 45 is supplied into the header 41D from the water inlet 412, the hot water passes through a part of the plurality of heat transfer pipes 40 thereafter. Then, after flowing into the header 41F, it passes through the remaining portions of the plurality of heat transfer tubes 40, flows into the header 41E, and discharges from the hot water outlet 413. The hot water outlet 413 is connected to the primary heat exchanger 3B via a pipe 44 as shown in FIGS. 1 and 2, and the heated hot water is a hot water pipe connected to the primary heat exchanger 3B. 43 is returned toward the floor heating main body.

  As clearly shown in FIG. 4, the rear wall 50 a and the front wall 50 b erected in the vertical height direction of the casing 5 are provided with two upper and lower air supply ports 51 a and 51 b and one exhaust port 52. ing. The cans 1A, 1B and the casing 5 are connected via the auxiliary cans 11A, 11B, and the combustion gas that has passed through the primary heat exchanger 3A in the can 1A passes through the auxiliary can 11A. Then, the combustion gas that has passed through the primary heat exchanger 3B in the can 1B passes through the auxiliary can 11B and is guided to the air supply 51b. . The air supply port 51 a is provided at a position higher than the partition plate 6, and the combustion gas that has flowed into the casing 5 from the air supply port 51 a travels from the exhaust port 52 after traveling toward the upper heat exchange unit UH. It proceeds to the outside of the casing 5. On the other hand, the air supply port 51b is provided at a position lower than the partition plate 6, and the combustion gas flowing into the casing 5 from the air supply port 51b travels toward the lower heat exchange portion LH. It proceeds from the exhaust port 52 to the outside of the casing 5.

  The secondary heat exchanger B is provided in a posture in which the casing 5 and the plurality of heat transfer tubes 40 are inclined by an appropriate angle θ with respect to the horizontal direction, as well shown in FIGS. 1 and 2. The partition plate 6 is similarly inclined. As will be described later, such an inclination is useful for allowing the drain generated along with the recovery of latent heat from the combustion gas to flow toward the drain outlet 59 and smoothly discharging it to the outside. As shown in FIG. 2, the exhaust port 52 has a long rectangular shape extending in a substantially horizontal direction. The exhaust port 52 is substantially horizontal by being inclined relative to the bottom wall portion 50c and the upper wall portion 50d of the inclined casing 5 by an angle θ. If the exhaust port 52 is inclined, when attaching a member called an exhaust top or other members to the exhaust port 52, it becomes necessary to make the members oblique, so that the installation becomes complicated. Although the appearance appearance is also bad, such an inconvenience can be appropriately avoided by making the exhaust port 52 substantially horizontal. Further, for example, the connection part for the exhaust port of the heat source device (for hot water supply device) provided in the pipe space of the apartment house is usually provided so as to correspond to the horizontally extended exhaust port. Yes, it will be suitable for such applications.

  As described above, the partition plate 6 is a member that vertically partitions the upper heat exchange unit UH and the lower heat exchange unit LH. As illustrated in FIGS. 4 to 6, for example, the upper plate body 60 a and the lower plate body 60 b. And the three thin metal plates of the intermediate plate 60c are overlapped and joined. Since an acidic drain falls on the partition plate 6, preferably, the material of the partition plate 6 is acid resistant such as stainless steel. Since the acidic drain contacts the heat transfer tube 40 and the bottom wall portion 50c of the casing 5, these portions are preferably made of a material having acid resistance such as stainless steel.

  The intermediate plate 60c of the partition plate 6 has a substantially flat plate shape sandwiched between the upper plate 60a and the lower plate 60b. For example, as shown well in FIG. It is supported so that it may contact | abut to both the side wall parts 50e. The intermediate plate 60c serves as a base member for the partition plate 6 and also serves to increase the overall strength of the partition plate 6. Therefore, the thickness of the upper plate 60a and the lower plate 60b is reduced. To help. Both the upper plate body 60a and the lower plate body 60b are formed by pressing a flat metal plate, and the central portion excluding these outer peripheral edge portions is more upward than the outer peripheral edge portion. It is formed as a bulging convex step 601 or a convex step 602 bulging downward. By forming these convex step portions 601 and 602, the entire thickness of the partition plate 6 is increased, and the heat transfer tubes 40 and the partition plate 6 of the upper heat exchange portion UH and the lower heat exchange portion LH, respectively. The gaps s1 and s2 are both reduced. Unlike this embodiment, for example, as shown in FIG. 13, the gaps s1 ′ and s2 between the partition plate 6 and the plurality of heat transfer tubes 40 are formed only by forming the partition plate 6 by a single flat plate. 'Will grow. In this case, a large amount of combustion gas passes through the gap portions, and the amount of heat recovered by the plurality of heat transfer tubes 40 is reduced. However, according to the present embodiment, such a problem can be solved. it can.

  As clearly shown in FIG. 4, an upright portion 61 erected upward is provided at one edge of the partition plate 6 near the exhaust port 52. The standing portion 61 is formed, for example, by bending one end edge of any of the upper plate 60a, the lower plate 60b, and the intermediate plate 60c upward. The upper end of the upright portion 61 is in contact with or close to the heat transfer tube 40a having the lowest height in the last row closest to the exhaust port 52 of the upper heat exchange portion UH. Further, the standing portion 61 extends in a series in substantially the same direction as the direction in which the exhaust port 52 extends while facing the exhaust port 52. As shown in FIG. 5, the horizontal length L <b> 1 of the upright portion 61 is longer than the horizontal length L <b> 2 of the exhaust port 52, and the upright portion of the secondary heat exchanger B is viewed from the front. 61 is provided so as to overlap the full length region of the exhaust port 52 in the horizontal direction. In addition, the partition plate 6 is substantially parallel to the plurality of heat transfer tubes 40, the bottom wall portion 50c of the casing 5, and the like, and is inclined with respect to the horizontal direction similarly to them. This inclination helps the drain that has fallen on the partition plate 6 to flow on the partition plate 6 to be quickly eliminated. In one side edge portion where the height of the partition plate 6 is lowered, one or a plurality of hole portions (not shown) for dropping the drain flowing toward the one side edge portion onto the bottom wall portion 50c. ) Is provided. Further, instead of such a configuration, for example, the drain that flows toward the one side edge of the partition plate 6 is allowed to flow down from the longitudinal end of the one side edge onto the bottom wall 50c. You can also

  The bottom wall portion 50c of the casing 5 plays a role of receiving a drain falling from the partition plate 6 and a drain generated in the lower heat exchange portion LH. A discharge port 59 for discharging the drain on the bottom wall 50c to the outside of the casing 5 is provided at one end of the bottom wall 50c on the lower side. The drain discharged from the discharge port 59 is sent to, for example, a neutralizer (not shown), and is discarded after the neutralization process is completed by the neutralizer. The neutralizer has a configuration in which a neutralizing agent such as calcium carbonate is accommodated in a container.

  Next, the operation of the heat source device A will be described.

  First, when water flows through the upper heat exchanger UH and the primary heat exchanger 3A of the secondary heat exchanger B, the combustor 2A is driven to burn at this point. Then, the combustion gas generated by the combustor 2A rises in the can 1A and reaches the primary heat exchanger 3A, and sensible heat is recovered in this portion. Thereafter, the combustion gas flows into the region above the partition plate 6 in the casing 5 from the air supply port 51a of the secondary heat exchanger B, and after the latent heat recovery is performed by the heat transfer tube 40 of the upper heat exchanger B. The air is discharged from the exhaust port 52 to the outside. By such a thing, the water supplied to the upper heat exchange part B and the primary heat exchanger 3A is heated efficiently, and the hot water for general hot water supply is produced | generated appropriately. On the other hand, when there is circulation of hot water in the lower heat exchange part LH and the primary heat exchanger 3B, the combustor 2B is driven to burn. As a result, the combustion gas generated thereby reaches the primary heat exchanger 3B and is subjected to sensible heat recovery, and then from the supply port 51b of the secondary heat exchanger B to the partition plate 6 in the casing 5. Flows into the lower region. Then, the combustion gas is subjected to latent heat recovery and discharged to the outside from the exhaust port 52. The hot water that has passed through the lower heat exchange section LH and the primary heat exchanger 3B is appropriately heated and returned to the floor heating main body.

  In the secondary heat exchanger B, as described above, the upper heat exchanging unit UH and the lower heat exchanging unit LH for individually collecting latent heat from the combustion gas generated by the two combustors 2A and 2B overlap each other. And is provided so as to straddle the top of the two cans 1A and 1B. For this reason, in this secondary heat exchanger B, each heat transfer tube 40 can be lengthened, and high heat exchange efficiency can be obtained while reducing the number of heat transfer tubes 40. Further, the secondary heat exchanger B collectively accommodates the upper heat exchanging unit UH and the lower heat exchanging unit LH in one casing 5, and substantially two heat exchangers for recovering latent heat. Are integrated as a single heat exchanger. For this reason, the heat source device A has a very rational structure compared to, for example, a configuration in which two heat exchangers for recovering latent heat are separately arranged and provided side by side. The manufacturing cost can be reduced while suppressing the production.

  When latent heat is recovered from the combustion gas by the plurality of heat transfer tubes 40 of the upper heat exchanging unit UH, acidic drains are generated and attached to the surfaces of the plurality of heat transfer tubes 40, and this drops on the partition plate 6. To do. On the other hand, in this heat source device A, an upright portion 61 is provided at one edge of the partition plate 6 near the exhaust port 52. For this reason, even if the combustion gas flows at a high speed along the upper surface of the partition plate 6, the drain on the partition plate 6 is appropriately prevented from scattering toward the exhaust port 52. The upper end of the upright portion 61 is in contact with or close to the heat transfer tube 40a, and a large gap is not formed between the upright portion 61 and the heat transfer tube 40a so that the drain passes. The scattering prevention effect is higher. As a result, the problem that the peripheral portion of the exhaust port 52 and the members provided in front of the exhaust port 52 are contaminated by the acidic drain is appropriately avoided.

  In particular, the upright portion 61 is formed to have a length in the horizontal direction longer than that of the exhaust port 52, and the upright portion 61 faces the entire length of the exhaust port 52 in the horizontal direction. The drain is more reliably prevented from scattering toward the exhaust port 52. In addition, the partition plate 6 is inclined, and the drain dropped on the partition plate 6 flows along the inclination and then flows down onto the bottom wall portion 50c, so that a large amount of drain is accumulated on the partition plate 6. This also prevents the drain from being scattered toward the exhaust port 52.

  As described above, the upper end of the upright portion 61 is in contact with or close to the heat transfer tube 40a, but according to such a structure, the drain on the surface of the heat transfer tube 40a passes through the upright portion 61 and the heat transfer tube 40a. It becomes easy to flow down below. In some cases, a drain dripping from another heat transfer tube 40 positioned above the surface of the heat transfer tube 40a may adhere, and a larger amount of drain adheres than the heat transfer tube 40 positioned above. On the other hand, the heat transfer tube 40a is located in the rearmost row closest to the exhaust port 52, and when the flow of the combustion gas hits the heat transfer tube 40a, the drain attached to the heat transfer tube 40a. May be scattered toward the exhaust port 40a. On the other hand, as described above, if the drain easily flows down from the surface of the heat transfer tube 40a, such a possibility is reduced.

  In this heat source device A, since the partition plate 6 is provided with the rising portion 61 for preventing the scattering of drain, the intermediate height of the front wall 50b of the casing 5 where the exhaust port 52 has substantially the same height as the partition plate 6. It can be formed in a part. Thus, it is suitably realized that the combustion gas that has passed through the upper heat exchange unit UH and the combustion gas that has passed through the lower heat exchange unit LH are exhausted to the outside through one exhaust port 52. For example, when two exhaust ports are provided, a separate means for collecting the combustion gases separately discharged from the two exhaust ports is required, or a plurality of parts such as an exhaust top are used. However, according to the present embodiment, such a disadvantage can be appropriately eliminated.

  Drain is also generated by the recovery of latent heat in the lower heat exchanging portion LH, but this drain drops on the bottom wall portion 50c of the casing 5, and then the drain discharge port 59 along the inclination of the bottom wall portion 50c. And then discharged to the outside. As described above, since the exhaust port 52 is provided at the upper and lower intermediate heights of the front wall 50b of the casing 5, the drain dropped on the bottom wall 50c rises to the exhaust port 52 by the flow of the combustion gas. There is almost no fear of scattering.

  7 to 12 show other embodiments of the present invention. In these drawings, the same or similar elements as those of the above embodiment are denoted by the same reference numerals as those of the above embodiment.

  In the embodiment shown in FIG. 7A, the standing portion 61 of the partition plate 6 stands up diagonally. Even with such a configuration, it is possible to prevent the drain dripped onto the partition plate 6 from being scattered toward the exhaust port 52. The standing part 61 referred to in the present invention is basically required only to stand upward, and its specific standing angle is not limited.

  In the embodiment shown in FIG. 7B, a part of the upper plate 60a of the partition plate 6 is formed as a convex step portion 61A. Preferably, the upper surface of the convex step portion 61A is in contact with or close to the lowest heat transfer tube 40 of the upper heat exchange portion UH. As will be understood from the present embodiment, the upright portion in the present invention can be formed in a step shape having an appropriate height and width.

  In the embodiment shown in FIG. 7C, the upper end of the standing portion 61 of the partition plate 6 is in contact with or close to the heat transfer tube 40a of the upper heat exchange unit UH, and at least one side surface of the partition plate 6 is A hydrophilic processing portion 65 to which a hydrophilic paint is applied is provided. Preferably, the hydrophilic treatment portion 65 is also provided on the upper end surface of the standing portion 61, and more preferably on the side surface opposite to the one side surface of the standing portion 61 (this point will be described later). The same applies to the roughened surface processing portion and the groove). According to such a configuration, since the standing portion 61 has hydrophilicity, the drain on the surface of the heat transfer tube 40 a can flow more easily along the standing portion 61, and the drain on the surface of the heat transfer tube 40 a reaches the exhaust port 52. It becomes more suitable for preventing scattering toward.

  In the embodiment shown in FIG. 8A, a rough surface processing portion 65 </ b> A is provided on one side surface of the standing portion 61. The rough surface processing portion 65A is a portion where a large number of minute irregularities are formed by, for example, blasting or machining. In the embodiment shown in FIG. 5B, a plurality of concave grooves 65B extending in the vertical direction are formed on one side surface of the standing portion 61. In the embodiment shown in FIG. 5C, the standing portion 61 is formed in a corrugated plate shape, and a plurality of concave grooves 65 </ b> C extending in the vertical direction are also formed on one side surface of the standing portion 61. In any of the embodiments shown in FIGS. 8A to 8C, the drain on the surface of the heat transfer tube 40a easily flows downward along the upright portion 61, similarly to the embodiment shown in FIG. Thus, it is possible to prevent many drains from remaining on the surface of the heat transfer tube 40a.

  In the embodiment shown in FIG. 9, the partition plate 6 is formed by directly superposing the upper plate body 60a and the lower plate body 60b, and does not include the intermediate plate body 60c of the previous embodiment. Yes. Although the upper plate body 60a and the lower plate body 60b have upward and downward convex steps 601 and 602, the same as in the previous embodiment, but at least one of the upper plate body 60a and the lower plate body 60b. Both side edges are in contact with and supported by the casing 5. According to the present embodiment, since the number of plate bodies constituting the partition plate 6 is small, it is suitable for reducing the manufacturing cost. Of course, the gaps s1 and s2 between the partition plate 6 and the heat transfer tube 40 can be made minute so that the heat exchange efficiency does not decrease.

  In the embodiment shown in FIG. 10, the partition plate 6 is configured by using only one plate body, and has a plurality of step portions 69a that swell upward and a plurality of step portions 69b that swell downward. is doing. Each of these step portions 69a and 69b has a shape extending in a direction intersecting with the flow direction of the combustion gas (the left-right direction in FIG. 6A), and alternately one by one in the flow direction of the combustion gas. Are lined up. The plurality of step portions 69a and 69b are formed by press molding, for example.

  According to the present embodiment, the gaps between the heat transfer tubes 40 and the partition plates 6 of the upper heat exchange unit UH and the lower heat exchange unit LH can be partially but reduced, and thus heat can be reduced. A decrease in exchange efficiency can be suppressed. Since the partition plate 6 can be easily manufactured by pressing one metal plate, the manufacturing cost can be further reduced. Of the plurality of upward stepped portions 69a, the stepped portion 69a located at the left end of FIG. 10A plays the same role as the convex stepped portion 61A shown in FIG. It corresponds to an example of an upright portion in the present invention. However, in addition to the left end step portion 69a, for example, an upright portion (not shown) in which one end edge of the partition plate 6 is bent upward may be separately provided.

  In the embodiment shown in FIG. 11, the heat transfer tube 40 of the lower heat exchange unit LH is shorter than the heat transfer tube 40 of the upper heat exchange unit UH, and the headers 41D to 41F of the lower heat exchange unit LH The position is shifted closer to the center in the longitudinal direction of the heat transfer tube 40 than the headers 41A to 41C of the exchange unit UH. Thus, the headers 41A and 1B and the header 41F, and the header 41C and the headers 41D and 41F are offset so as not to overlap in the vertical direction, and gaps 89a and 89b are formed therebetween. The headers 41D to 41F of the lower heat exchange unit LH are located immediately below the plurality of heat transfer tubes 40 of the upper heat exchange unit UH, and the heights h1 of their upper ends are the headers 41A to 41C of the upper heat exchange unit UH. The height h2 is equal to or higher than the lower end height h2. The partition plate 6 is appropriately bent so that a part of the partition plate 6 passes through the gaps 89a and 89b, and is arranged in the casing 5 so as to partition between the upper heat exchange unit UH and the lower heat exchange unit LH. Both side edges are supported on both side walls of the casing 5.

  According to the present embodiment, the headers 41A to 41C of the upper heat exchange unit UH and the headers 41D to 41F of the lower heat exchange unit LH do not unduly interfere with each other, so that the upper heat exchange unit UH and the lower heat exchange unit The space | interval s3 of each heat exchanger tube 40 with the part LH can be made small. The headers 41A to 41F are formed so as to protrude upward and downward from the plurality of heat transfer tubes 40 connected to the headers 41A to 41F. For example, as shown in FIG. 13, the headers 41D to 41F are directly below the headers 41A to 41C. When 41E is arranged in an overlapping manner, the interval s3 ′ of the heat transfer tube 40 between the upper heat exchange unit UH and the lower heat exchange unit LH is increased. On the other hand, in the present embodiment shown in FIG. 11, since the above-described interval s3 can be reduced, the partition plate 6 is formed of, for example, one substantially flat plate. Even if it is a case, the clearance gap between this partition plate 6 and the heat exchanger tube 40 can be made small, and it can prevent the malfunction that heat exchange efficiency falls significantly. Note that the present invention does not exclude the configuration as shown in FIG. 13, and is included in the embodiment of the present invention as long as the standing portion referred to in the present invention is provided on the partition plate.

  In the embodiment shown in FIG. 12, the entire upper heat exchange unit UH and the entire lower heat exchange unit LH are displaced in the horizontal direction. As a result, the headers 41A and 41B and the header 41F and the headers 41C and 41D and 41E do not overlap in the vertical direction, and are offset in the horizontal direction so that gaps 88a and 88b are formed between them. ing. The height h1 of the upper ends of the headers 41D to 41F of the lower heat exchange unit LH is the same as or higher than the height h2 of the lower ends of the headers 41A to 41C of the upper heat exchange unit UH. The partition plate 6 partitions the upper heat exchange unit UH and the lower heat exchange unit LH so as to pass through the gaps 88a and 88b.

  Also in this embodiment, as in the embodiment shown in FIG. 11, the interval s3 between the heat transfer tubes 40 between the upper heat exchange portion UH and the lower heat exchange portion LH is reduced, and the partition plate 6 is, for example, substantially flat. Advantages such as the ability to use a single plate body can be obtained. Moreover, in this embodiment, there is also an advantage that the lengths of the heat transfer tubes 40 of the upper heat exchange part UH and the lower heat exchange part LH can be made substantially the same. There is no need to prepare heat tubes.

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

  The partition plate referred to in the present invention is only required to be provided so as to partition the upper heat exchange part and the lower heat exchange part vertically, and its specific material, shape, size, mounting method, etc. are arbitrary. You can choose. The specific height and width (length) of the upright portion provided on the partition plate are not limited.

  In the present invention, instead of a configuration in which an exhaust port is provided in the front wall of the casing and combustion gas is introduced into the inside from the rear portion of the casing, for example, an exhaust port is provided in the rear wall of the casing, and the combustion gas is supplied to the casing. It is also possible to adopt a configuration in which it is introduced into the interior from the front portion of the. The exhaust port may be provided in any of the wall portions standing in the vertical direction of the casing. Further, in the present invention, for example, two exhaust ports are provided in the casing, and two kinds of combustion gases respectively passing through the upper heat exchange unit and the lower heat exchange unit pass through the two exhaust ports separately. It does not matter even if it is configured. In the present invention, there is an advantage that the exhaust port can be formed at the same height as the partition plate. However, the exhaust port and the partition plate are not necessarily different in height. It can also be made.

  The plurality of heat transfer tubes constituting the upper heat exchanging section and the lower heat exchanging section do not necessarily have to be configured by using a straight tube body, for example, by using a bellows-shaped tube body or a U-shaped tube. You can also The heat source device according to the present invention is not limited to the one having both a general hot water supply function and a heating function for warm water for floor heating. For example, a specific function such as a general hot water supply function and a hot water supply function for a bathtub or a use application of heated hot water is not limited. As the fluid to be heated that circulates in the heat transfer tube, an antifreeze liquid or other fluids can be used. In addition, in the present invention, instead of the so-called normal combustion method in which the combustion gas is advanced above the combustor, for example, a so-called reverse combustion method in which heat exchange is performed while the combustion gas is traveling downward may be employed. Is possible.

It is a schematic sectional drawing which shows an example of the heat source apparatus which concerns on this invention. It is a schematic front view of the heat source device shown in FIG. (A) is the IIIa-IIIa schematic sectional drawing of FIG. 1, (b) is the IIIb-IIIb schematic sectional drawing of FIG. It is IV-IV sectional drawing of FIG. It is VV sectional drawing of FIG. It is VI-VI sectional drawing of FIG. (A)-(c) is principal part sectional drawing which shows the other example of the standing part provided in a partition plate in this invention. (A)-(c) is principal part sectional drawing which shows the other example of the standing part provided in a partition plate in this invention. It is principal part front sectional drawing which shows the other example of this invention. (A) is principal part side surface sectional drawing which shows the other example of this invention, (b) is XX sectional drawing of (a). It is front sectional drawing which shows the other example of this invention. It is front sectional drawing which shows the other example of this invention. It is front sectional drawing which shows the other example of this invention. It is a schematic front view which shows an example of the related technique of this invention.

Explanation of symbols

A Heat source device B Secondary heat exchanger (heat exchanger)
UH Upper heat exchange part LH Lower heat exchange part 2A, 2B Combustor 5 Casing 6 Partition plate 40 Heat transfer pipe 41 Header 51a, 51b Air supply port 52 Exhaust port 60a Upper plate body 60b Lower plate body 61 Standing part

Claims (7)

First and second combustors that can be driven to burn independently of each other;
Each having a plurality of heat transfer tubes and at least two heat exchangers for individually recovering heat from the combustion gas generated by each of the first and second combustors;
A heat source device comprising:
As the two heat exchange parts, provided with an upper heat exchange part and a lower heat exchange part provided in an arrangement overlapping in the vertical height direction,
These upper heat exchanging part and lower heat exchanging part are arranged in a casing having an air supply port for guiding combustion gas toward them and an exhaust port formed in a wall portion standing up and down in the vertical direction. In addition, it is divided up and down by a partition plate arranged in this casing,
Among the partition plates, at the edge near the exhaust port or in the vicinity thereof, it is possible to suppress the drain that has fallen on the partition plate from the upper heat exchange part from being scattered toward the exhaust port, A heat source device, characterized in that an upright portion that stands upward is provided. An upper heat exchanging section and a lower heat exchanging section each having a plurality of heat transfer tubes for recovering heat from the combustion gas, and arranged to overlap each other in the vertical height direction;
The upper heat exchange part and the lower heat exchange part are housed inside, and an air supply port for guiding combustion gas toward the upper heat exchange part and the lower heat exchange part, and a wall part standing up and down in the vertical direction A casing having an exhaust port formed in
A partition plate arranged in the casing and partitioning the upper heat exchange unit and the lower heat exchange unit;
Among the partition plates, it is possible to prevent the drain that is provided on the edge near the exhaust port or in the vicinity thereof and that has fallen on the partition plate from the upper heat exchange part from being scattered toward the exhaust port. A standing part that stands up upwards,
A heat exchanger characterized by comprising: The exhaust port is formed in a shape extending in a substantially horizontal direction,
The upright portion of the partition plate extends in a series in a direction intersecting with the traveling direction of the combustion gas with respect to the upright portion, and is more than the exhaust port so as to face the full length region in the longitudinal direction of the exhaust port. The heat exchanger according to claim 2, wherein the heat exchanger is formed in a long dimension.   The upright portion of the partition plate is in contact with or close to any one of the upper heat exchange portions near the exhaust port, and the drain falls from the heat transfer tube onto the partition plate. The heat exchanger according to claim 2, wherein the heat exchanger has at least one of a hydrophilic treatment portion to be promoted, a rough surface treatment portion, and a plurality of grooves.   The partition plate has an upper plate body and a lower plate body stacked in the vertical thickness direction, and the upper plate body is a convex that swells upward so as to approach the heat transfer tube constituting the upper heat exchange section. 5. The method according to claim 2, wherein the lower plate body has a convex step portion that swells downward so as to approach the heat transfer tube of the lower heat exchange portion. The heat exchanger according to crab.   The partition plate has a plurality of upward and downward stepped portions that bulge upward and downward so as to approach the respective heat transfer tubes of the upper heat exchange portion and the lower heat exchange portion, and 5. The downward stepped portion extends in a direction intersecting with a combustion gas flow direction in the casing and is arranged in a staggered manner in the combustion gas flow direction. Heat exchanger. At the end portions of the plurality of heat transfer tubes that respectively constitute the upper heat exchange portion and the lower heat exchange portion, a header is provided with upper and lower ends protruding above and below the plurality of heat transfer tubes,
The header of the upper heat exchange part and the header of the lower heat exchange part are displaced in the horizontal direction so as not to overlap in the vertical height direction, and the upper end of the header of the lower heat exchange part is the upper heat exchange The heat exchanger according to any one of claims 2 to 6, wherein the heat exchanger is set to a height equal to or higher than a lower end of the portion.

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