JP4264825B2 - Heat source equipment - Google Patents

Description

  The present invention relates to a heat source device, and more particularly to a heat source device capable of recovering latent heat of combustion gas and air that has passed through a primary heat exchange means.

  Conventionally, as in the heat source device disclosed in Patent Document 1 below, a primary heat exchanger that mainly recovers sensible heat is provided in the middle of the gas flow path, and the combustion gas that has passed through the primary heat exchanger downstream thereof There is a so-called latent heat recovery type heat source device provided with a secondary heat exchanger that mainly recovers latent heat.

  Further, some of the heat source devices of the prior art have a function of replenishing hot water in a bathtub in addition to a hot water supply function. As such a heat source device having a plurality of functions, there is one provided with a heating system referred to as a single-can two-water channel type. A heat source device that employs a heating system called a single-can two-water channel type includes, for example, a heat exchanger for hot water supply and a heat exchanger for reheating, and these heat exchangers are a single unit. It has the structure arranged in the gas flow path.

Japanese Patent Laid-Open No. 11-148642

  The latent heat recovery type heat source device disclosed in Patent Document 1 has the advantage of being able to recover up to latent heat in addition to the sensible heat of combustion gas, and having high thermal efficiency. On the other hand, the heat source device provided with the single-can two-channel heating system disclosed in Patent Document 2 has an advantage that the overall shape is compact and the manufacturing cost is low.

  In order to provide a heat source device that combines the advantages of a latent heat recovery type heat source device and a single-can two-channel heat source device, the present inventors have provided a primary for hot water supply and bath reheating of a single-can two-channel heat source device. A heat source device in which a secondary heat exchanger is arranged downstream of the heat exchanger in the flow direction of the combustion gas was prototyped. The heat source device configured as described above has a compact device configuration, a low manufacturing cost, and high thermal efficiency.

  However, when the inventors repeated further operation experiments on the heat source device described above, the combustion gas that passes through the overlapping portion of the heat exchanger for hot water supply and the heat exchanger for bathing in the primary heat exchanger Was found to be hotter than the combustion gas that passed through the part where the heat exchangers did not overlap. Based on this result, when the present inventors configured the heat source device as described above, the combustion gas introduced into the secondary heat exchanger generates temperature unevenness depending on the site, and the secondary heat exchanger It has been found that there is a risk that the recovery efficiency of heat energy in will be reduced.

  Therefore, in the present invention, in order to solve the above-mentioned new problem, it is possible to suppress the temperature unevenness of the combustion gas flowing into the secondary heat exchange means, and to provide a heat source device with high heat energy recovery efficiency in the secondary heat exchanger With the goal.

The invention according to claim 1, which is provided to solve the above problems, includes a combustion burner, a blowing means for introducing outside air, and a gas flow path through which combustion gas or air generated in the combustion burner flows. In the middle of the gas flow path, a primary heat exchange means for exchanging heat with the combustion gas or air flowing through the gas flow path, and a downstream side of the primary heat exchange means in the flow direction of the combustion gas or air are arranged. Secondary heat exchanging means, and the primary heat exchanging means includes a first region where the exhaust temperature of the combustion gas or air discharged downstream of the gas flow path is low, and the combustion gas or air. And a second region having a higher temperature than the combustion gas or air discharged from the first region, and the secondary heat exchange means communicates with the gas flow path, and the combustion gas or air Circulate A gas circulation space, the gas circulation space with respect to the first region of the primary heat exchange means, a low-temperature gas circulation space corresponding to the downstream side in the flow direction of combustion gas or air, and the second region. And a high-temperature gas circulation space corresponding to the downstream side of the flow direction of the combustion gas or air, and a guiding means for guiding the combustion gas or air flowing into the high-temperature gas circulation space to the low-temperature gas circulation space side is arranged , The heat source device is characterized in that a gap through which the drain generated in the secondary heat exchange means can flow is formed between the guide means and the bottom surface of the gas circulation space .

  As described above, when the heat exchange is performed when the combustion gas or air discharged after the heat exchange in the primary heat exchange means flows into the secondary heat exchange means while maintaining the temperature unevenness, the secondary heat exchange is performed. There is a possibility that sufficient heat exchange efficiency cannot be obtained in the means.

  Based on such knowledge, in the heat source device of the present invention, the combustion gas and air flowing into the high-temperature gas circulation space that is assumed to reach the high-temperature combustion gas and air in the gas circulation space of the secondary heat exchange means, Guiding means for guiding to the low temperature gas circulation space side where the combustion gas or air is assumed to reach is provided. Therefore, in the heat source device of the present invention, it is possible to minimize the occurrence of temperature unevenness in the combustion gas and air in the secondary heat exchange means.

The heat source device of the present invention can effectively use the heat transfer area of the secondary heat exchange means because there is little temperature variation in the combustion gas and air in the gas circulation space of the secondary heat exchange means. Therefore, the heat source device of the present invention has high heat energy recovery efficiency in the secondary heat exchange means.
In the heat source device of the present invention, the secondary heat exchange means is provided to further collect thermal energy from the combustion gas or air from which the thermal energy has been collected by the primary heat exchange means. Therefore, the secondary heat exchange means can recover the sensible heat that cannot be recovered by the primary heat exchange means, and can also recover the latent heat of the combustion gas and air. When the latent heat of the combustion gas or air is recovered in the secondary heat exchange means, drainage is generated. Since the drain generated in the secondary heat exchange means is exposed to the combustion gas, it is highly corrosive and needs to be discharged to the outside as smoothly as possible.

As described above, in the heat source device of the present invention, the gap through which the drain can flow is provided between the guide means provided in the secondary heat exchange means and the bottom surface of the gas circulation space. Therefore, in the heat source device of the present invention, the drain generated in the secondary heat exchange means is smoothly discharged without being blocked by the guiding means.

According to a second aspect of the present invention, the primary heat exchanging means includes a plurality of heat exchanging circuits each including a heat receiving pipe through which hot water or a heat medium circulates and fins attached to the heat receiving pipe. The fins are shared between the plurality of heat exchange circuits, and the second region includes a cross-sectional region of the gas flow path occupied by one of the heat exchange circuits constituting the plurality of heat exchange circuits, and another heat a region where the cross-sectional area of the gas channel exchange circuit occupies overlap, the first region, the cross-sectional area between the gas flow path heat exchange circuit is occupied, characterized in that a region that does not overlap claims Item 2. The heat source device according to Item 1 .

  In the heat source apparatus of the present invention, the primary heat exchange means includes a plurality of heat exchange circuits and shares fins. Therefore, the height of the fin attached to the heat receiving pipe arranged in the second region, which is the region where the cross-sectional regions of the gas flow path occupied by the heat exchange circuit overlap, is the height of the gas flow path occupied by the heat exchange circuit. It becomes shorter than the height of the fin distribute | arranged to the 1st area | region where cross-sectional area | regions do not overlap. Furthermore, when it is set as the above-mentioned structure, even if the height of the fin is the same in the second region and the first region, hot water or a heat medium flows in a part of the heat exchange circuit existing in the second region. Otherwise, heat exchange in this heat exchange circuit is not performed. Therefore, in the heat source device of the present invention, the combustion gas and air discharged from the second region of the primary heat exchange means tend to be higher in temperature than the combustion gas or air discharged from the first region.

  As described above, when the primary heat exchanging means is provided with a plurality of heat exchanging circuits, there is a possibility that temperature unevenness of the combustion gas flowing out from the primary heat exchanging means may occur. In this way, if heat exchange is performed in the secondary heat exchanging means with the combustion gas and air maintaining temperature unevenness, unevenness occurs in the heat exchange in the secondary heat exchanging means, and sufficient heat exchange efficiency is achieved. May not be obtained. However, the heat source device of the present invention is configured such that the guiding means is arranged in the gas circulation space of the secondary heat exchange means and the combustion gas and air flowing into the high temperature gas circulation space are guided to the low temperature gas circulation space side. . Therefore, in the heat source device of the present invention, it is possible to minimize the occurrence of uneven temperature of the combustion gas and air in the secondary heat exchange means, and to effectively use the heat transfer area of the secondary heat exchange means.

According to a third aspect of the present invention, the primary heat exchanging means includes a heat exchange circuit configured to include a heat receiving pipe through which hot water or a heat medium flows and fins attached to the heat receiving pipe. , the second region, the arrangement density of the heat receiving tube is a high region, the first region, to claim 1, wherein the arrangement density of the heat receiving tube than the second region is a region of low It is a heat-source apparatus of description .

  In the heat source device of the present invention, the primary heat exchange means includes a first region where the arrangement density of the heat receiving tubes is low and a second region where the arrangement density of the heat receiving tubes is high. In the second region of the primary heat exchange means, since the heat receiving tubes are arranged at a high density, the fins attached to the heat receiving tubes are shorter than the fins attached to the heat receiving tubes in the first region. The heat exchange efficiency tends to be lower than the heat exchange efficiency in the first region. For this reason, in the heat source device of the present invention, the temperature of the combustion gas or air discharged to the downstream side with the heat exchange in the primary heat exchange means is higher than the first region where the heat receiving tube is disposed at a lower density. The higher second region tends to be higher. As described above, if the combustion gas or air discharged from the primary heat exchange means flows into the secondary heat exchange means in a state where the temperature is uneven, the heat exchange efficiency is sufficient in the secondary heat exchange means. Is likely not to be obtained.

  Based on such knowledge, the heat source device of the present invention guides the combustion gas and air flowing into the high-temperature gas circulation space to the low-temperature gas circulation space side by arranging the guidance means in the gas circulation space of the secondary heat exchange means, Eliminates temperature variations in combustion gases and air. Therefore, the heat source device of the present invention can obtain sufficient heat exchange efficiency in the secondary heat exchange means without being affected by the temperature unevenness of the combustion gas or air discharged from the primary heat exchange means.

  The heat source device according to claim 2 or 3, wherein the primary heat exchange means includes a fin mounted on the heat receiving tube disposed on the heat receiving tube disposed in the second region and having a fin height mounted on the heat receiving tube disposed on the second region. It may be higher than the height.

  Even in such a configuration, it is possible to minimize the occurrence of uneven temperature of the combustion gas and air in the secondary heat exchange means and efficiently recover the thermal energy of the combustion gas and air.

The heat source device according to any one of claims 1 to 3 , wherein the guiding means increases the ventilation resistance of the combustion gas or air in the high temperature gas circulation space more than the ventilation resistance of the combustion gas or air in the low temperature gas circulation space. It is desirable that it is characterized by this. (Claim 4 )

  The heat source device of the present invention is such that, for example, the guiding means is disposed only in the high-temperature gas circulation space, so that the high-temperature gas circulation space has a larger flow resistance of combustion gas and air than the low-temperature gas circulation space. is there. Therefore, in the heat source device of the present invention, the high-temperature combustion gas that tends to flow in the high-temperature gas circulation space is smoothly guided toward the low-temperature gas circulation space, and the temperature unevenness of the combustion gas and air existing in the gas circulation space Is resolved. Therefore, the heat source device of the present invention has high heat exchange efficiency in the secondary heat exchange means.

In the heat source apparatus according to any one of claims 1 to 4, the guiding means is a plate, greater than the surface area of the portion the surface area of the portion that is disposed to the hot gas flow space is arranged in the cold gas flow space It may be a thing. (Claim 5 )

  According to such a configuration, it is possible to smoothly guide the high-temperature combustion gas or air that is assumed to flow into the high-temperature gas circulation space to the low-temperature gas circulation space, and the temperature unevenness of the combustion gas or air in the secondary heat exchange means Moreover, generation | occurrence | production of the heating nonuniformity of hot water or a heat medium can be suppressed.

  Here, in general, a high-temperature gas tends to exist above a low-temperature gas. Therefore, when the combustion gas or air discharged from the primary heat exchange means has a temperature difference as described above, the higher the temperature of the combustion gas or air, the higher the temperature, which may promote temperature unevenness.

Accordingly, in the invention according to claim 6 provided based on such knowledge, the heat source according to any one of claims 1 to 5 , wherein the guiding means is suspended from the top surface side of the gas circulation space. Device.

  According to such a configuration, high-temperature combustion gas and air that tend to be unevenly distributed upward can be smoothly guided to the low-temperature gas circulation space, and temperature unevenness of the combustion gas and air that performs heat exchange in the secondary heat exchange means. Can be solved more reliably.

In the invention according to claim 7 , the guiding means is suspended from the top surface side of the gas circulation space, and the lower end portion of the guiding means is downstream of the upper end portion in the flow direction of the combustion gas or air in the gas circulation space. The heat source device according to any one of claims 1 to 6 , wherein

  In the heat source device of the present invention, the lower end portion of the guiding means is lower than the upper end portion in the gas circulation space because the guiding means is attached in an inclined state in the gas circulation space or the guiding means has a curved shape. It is located downstream of the combustion gas and air in the flow direction. Therefore, in the heat source device of the present invention, high-temperature combustion gas and air are guided from the high-temperature gas circulation space side to the low-temperature gas circulation space side, and the temperature balance of the combustion gas and air in the gas circulation space is optimized and combustion is performed. Ventilation resistance of gas and air can be minimized.

  As described above, the heat source device of the present invention has low ventilation resistance in the gas circulation space. Therefore, the heat source device of the present invention can reduce the load of the blowing means that operates during combustion in the combustion burner, and can suppress the operating noise of the blowing means to a minimum.

According to an eighth aspect of the present invention, the guide means provides a large resistance portion that imparts a large flow resistance to the combustion gas or air that passes through the gas circulation space, and the combustion gas or air than the large resistance portion. A small resistance portion having a small flow resistance to be applied, wherein the large resistance portion is disposed in the high temperature gas circulation space, and the small resistance portion is disposed in the low temperature gas circulation space. The heat source device according to any one of 7 .

  According to such a configuration, high-temperature combustion gas and air flowing into the high-temperature gas circulation space can be smoothly guided to the low-temperature gas circulation space. Therefore, according to the present invention, temperature unevenness of the combustion gas and air introduced into the secondary heat exchange means can be eliminated, and the heat exchange efficiency in the secondary heat exchange means can be further improved.

  As described above, if the guiding means is arranged, the occurrence of uneven temperature of the combustion gas or air in the secondary heat exchange means can be suppressed, but the guiding means becomes a flow resistance of the combustion gas or air depending on the arrangement position, There is a problem that a large load is applied to the air blowing means, and noise accompanying the operation of the air blowing means is increased.

Accordingly, the invention according to claim 9 provided on the basis of such knowledge is that the secondary heat exchange means has an inlet for introducing combustion gas or air into the gas circulation space, and combustion flowing in the gas circulation space. and a discharge port for discharging the gas or air, induction means, a heat source of any of claims 1 to 8, characterized in that it is arranged in an intermediate position of the inlet and outlet Device.

  With such a configuration, it is possible to suppress the occurrence of uneven temperature of the combustion gas and air in the secondary heat exchange means, and to reduce the load on the air blowing means for supplying combustion air to the combustion burner. Moreover, since the load concerning a ventilation means is small, the heat source apparatus of this invention can suppress the operation | movement sound of the ventilation means at the time of combustion operation to the minimum.

The invention according to claim 10, the secondary heat exchanger means, according to claim 1 to 9, characterized in that it is constituted by a multi-tube heat exchanger arranged a large number of heat receiving tubes in the gas flow space The heat source device according to any one of the above.

  Since the heat source device of the present invention employs a multi-tube heat exchanger as the secondary heat exchange means, the device configuration is simple and the manufacturing cost is low.

The invention according to claim 11 is characterized in that the secondary heat exchanging means has an inlet for introducing combustion gas or air into the gas circulation space, and an outlet for discharging combustion gas or air flowing in the gas circulation space. And a multi-tube heat exchanger in which a large number of heat receiving pipes are arranged in the gas distribution space, and the heat receiving pipe extends in a direction that blocks an imaginary line connecting the inlet and the outlet. 11. The heat source device according to claim 10 , wherein the guiding means is arranged along the extending direction of the heat receiving pipe arranged in the gas circulation space.

  In the heat source device of the present invention, since the guiding means is arranged along the heat receiving pipe, the combustion gas or air that has flowed into the gas circulation space spreads throughout the gas circulation space. Therefore, according to the present invention, it is possible to eliminate the uneven temperature of the combustion gas in the gas circulation space and to effectively use the heat transfer area of each heat receiving tube.

  ADVANTAGE OF THE INVENTION According to this invention, the heat source apparatus which can make uniform the temperature distribution of the combustion gas and air which flow in in the gas distribution space of a secondary heat exchange means, and can collect | recover the thermal energy which combustion gas and air have to the maximum can be provided. .

  Next, a heat source device according to an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is an operation principle diagram showing a heat source apparatus according to an embodiment of the present invention. FIG. 2 is a perspective view showing a first heat exchange unit employed in the heat source apparatus shown in FIG. 3A is a cross-sectional view taken along the line AA in FIG. 2, and FIG. 3B is a cross-sectional view taken along the line BB in FIG. FIG. 4 is an enlarged view of a main part of the operation principle diagram shown in FIG. FIG. 5 is an exploded perspective view of a secondary heat exchanger employed in the heat source apparatus shown in FIG. 6A is an enlarged front view of the main part of the heat source device shown in FIG. 1, and FIG. 6B is a side view of FIG. Fig.7 (a) is a front view which shows the gas induction plate employ | adopted in the secondary heat exchanger shown in FIG. 5, (b) is typical about the positional relationship of the gas induction plate in a secondary heat exchanger. It is the perspective view shown in. FIG. 8 is a cross-sectional view of the secondary heat exchanger shown in FIG. 9A and 9B are front views showing modifications of the gas guide plate shown in FIG. FIG. 10A is a perspective view showing still another modified example of the gas guide plate shown in FIG. 7, and FIG. 10B is a side view of the heat source device provided with the gas guide plate shown in FIG. 11, 12 and 13 are front views showing modifications of the heat source device shown in FIG.

  In FIG. 1, reference numeral 1 denotes a heat source apparatus according to this embodiment. The heat source device 1 is a canned and two-waterway latent heat recovery combustion device, and includes a combustion section 2 that combusts fuel and a gas passage 3 through which combustion gas generated by combustion flows. In the middle of the gas flow path 3, a primary heat exchange part 4 a is disposed, and a secondary heat exchange part 4 b is disposed on the downstream side of the gas flow path 3 with respect to the primary heat exchange part 4 a.

  The combustion unit 2 includes a burner 10 configured by arranging a plurality of combustion tubes 8, an ignition device 9, and a blower 11 for supplying air necessary for combustion to the burner 10, and a combustion region A and B are classified. The burner 10 can be switched between a combustion operation in which fuel is burned only by the combustion pipe 8 constituting the combustion region A and a combustion operation in which fuel is burned by all the combustion pipes 8 constituting the combustion regions A and B.

  As shown in FIG. 2, the primary heat exchange part 4a is comprised from the primary heat exchanger 5 for bath reheating, and the primary heat exchanger 6 for hot-water supply. The primary heat exchangers 5 and 6 mainly recover sensible heat of the combustion gas by heat exchange between the hot water flowing in the heat receiving pipes 13 and 15 and the combustion gas passing through the gas flow path 3. The primary heat exchangers 5 and 6 are integrated by sharing the fin plate 12. The primary heat exchangers 5 and 6 are arranged so that the width direction of the fin plate 12 faces the arrangement direction of the combustion tubes 8. The primary heat exchanger 5 has a plurality of heat receiving tubes 13 penetrating through a large number of fin plates 12 arranged in parallel, and ends of adjacent heat receiving tubes 13 are connected by a “U” -shaped bend tube 16. It is. Similarly, the primary heat exchanger 6 allows a plurality of heat receiving pipes 15 to penetrate a large number of fin plates 12, and ends of adjacent heat receiving pipes 15 are connected by a “U” -shaped bend pipe 16. Is. The primary heat exchangers 5 and 6 are provided with bent flow paths constituted by the heat receiving pipes 13 and 15 and the bend pipe 16, respectively.

  The primary heat exchanger 5 is configured such that the four heat receiving tubes 13 are arranged at positions offset toward one end side in the width direction of the fin plate 12 (left side in FIG. 1). As shown in FIG. 1 and FIG. 2, the primary heat exchanger 6 has eight heat receiving tubes 15 arranged at substantially equal intervals over the entire width of the fin plate 12 and two stages in the height direction of the fin plate 12. It is arranged.

  The heat receiving pipe 13 of the primary heat exchanger 5 is arranged between the heat receiving pipes 15 and 15 of the primary heat exchanger 6 arranged in two stages in the height direction of the fin plate 12. Therefore, the primary heat exchanging portion 4a has an overlapping region in which the heat receiving tubes 15 are arranged in two stages in the height direction of the fin plate 12, that is, in the flow direction of the combustion gas, and the heat receiving tubes 13 are arranged between the heat receiving tubes 15. The heat receiving pipe 13 is not arranged in the height direction of the fin plate 12 and the single area S (first area) in which the heat receiving pipe 15 is arranged in two stages. In other words, the primary heat exchange unit 4a is configured by an overlapping region T in which the occupied regions of the primary heat exchangers 5 and 6 in the gas flow path 3 are overlapped and a single region S that is occupied only by the primary heat exchanger 6. ing. In the overlapping region T, the arrangement density of the heat receiving tubes 13 and 15 per unit area of the fin plate 12 is higher than that of the single region S.

  As shown in FIG. 1, the overlapping region T occupies a region corresponding to the combustion region A of the combustion unit 2 described above in the gas flow path 3. On the other hand, the single region S occupies substantially the entire gas flow path 3, that is, the region corresponding to both the fuel regions A and B. In the primary heat exchange part 4a, the so-called fin height differs between the overlapping region T and the single region S. More specifically, as shown in FIG. 4, the primary heat exchanging portion 4 a is configured such that the length L1 of the fin plate 12 between the heat receiving tubes 13 and 15 arranged vertically in the overlapping region T has a single region S. Is extremely shorter than the length L2 of the fin plate 12 between the heat receiving tubes 15 and 15 arranged vertically. Further, the length from the top of the heat receiving pipe 15 arranged at the lowermost stage of the primary heat exchange part 4a to the lower end of the fin plate 12 is longer on the single region S side (L4) than on the overlapping region T side (L3). Is longer. Therefore, the heat exchange efficiency of the primary heat exchanger 6 of the primary heat exchanger 4a is lower on the overlapping region T side than on the single region S side.

  The secondary heat exchange means 4 b is configured by the secondary heat exchanger 20 and the connection member 35. As shown in FIG. 5, the secondary heat exchanger 20 is connected by brazing a number of heat receiving tubes 25 to headers 22 and 23 arranged in parallel to both ends of a hollow box-shaped case member 21. This is a so-called multi-tube heat exchanger. The case member 21 includes a case body 26 and a top plate 27 formed by bending a metal plate as shown in FIG. The case member 21 is substantially box-shaped by brazing the top plate 27 to the case body 26 and brazing the tube plate 28 to the flanges provided at both ends of the case body 26. Thereby, the heat receiving pipe 25 is accommodated inside the case body 26, and a gas circulation space 24 through which combustion gas flows is formed. The case member 21 has a configuration in which an exhaust port 30 is provided on the front surface of the case body 26 and an introduction port 31 is provided on the back surface. In addition, a drain port 32 is provided on the bottom surface of the case body 26.

  The exhaust port 30 is an opening for discharging combustion gas from the secondary heat exchanger 20. An exhaust member 33 having four exhaust openings is mounted on the front side of the exhaust port 30 as shown in FIG. The inlet 31 is for introducing the combustion gas from which most of the sensible heat has been recovered in the primary heat exchange section 4 a into the secondary heat exchanger 20.

  The secondary heat exchanger 20 is connected to the gas flow path 3 via the connecting member 35 as shown in FIG. In the connection member 35, a collecting portion 36 connected to the opening portion of the gas flow path 3 and a connection portion 37 are arranged in a substantially “L” shape, and form a flow path communicating with the inside. As shown in FIG. 6C, the collecting portion 36 has an opening 34 that communicates with the opening portion of the gas flow path 3, and the combustion gas that has passed through the primary heat exchange portion 4 a flows through the opening 34. Part. In addition, as shown in FIGS. 6A and 6B, the collecting portion 36 is also a portion on which the secondary heat exchanger 20 is placed, and has a shape that is inclined downward as it is separated from the connecting portion 37 side. Yes.

  The connection portion 37 is a portion that is in surface contact with the back surface of the case member 21 of the secondary heat exchanger 20, and is an opening 38 for discharging the combustion gas that has flowed in from the collecting portion 36 to the secondary heat exchanger 20 side. Is provided. The secondary heat exchanger 20 is mounted above the gathering portion 36 and is in a state in which the back side (the inlet 31 side) is in close contact with the connection portion 37. When the secondary heat exchanger 20 is arranged in this manner, the inlet 31 of the secondary heat exchanger 20 and the opening 38 of the connecting portion 37 communicate with each other, and the secondary heat exchanger 20 is on the front side (drain port 32 side). Is connected to the gas flow path 3 in a posture inclined downward. As a result, the secondary heat exchanger 20 is in a state of having a flow gradient toward the drain port 32, and the drain generated in the secondary heat exchanger 20 flows smoothly toward the drain port 32. It has a configuration.

  The heat receiving pipes 25 are metal cylinders, and are arranged in parallel with a gap that allows the combustion gas to pass therethrough. As shown in FIG. 5, the heat receiving tubes 25 are arranged such that four heat receiving tubes 25 are arranged in the vertical direction of the main body case 21, and twelve rows of heat receiving tubes 25 are arranged in the width direction of the main body case 21. It is brazed against. The secondary heat exchanger 20 has a configuration in which the heat receiving tubes 25 are arranged in a row (staggered pattern).

  Of the heat receiving pipes 25 arranged in the case member 21, those arranged in the first to sixth rows from the inlet 31 side constitute the upstream heat receiving pipe group 40, and are adjacent to 7 to 12. The one in the row is classified as the downstream heat receiving tube group 41.

  As shown in FIG. 5, the header 22 is configured by brazing a cup-shaped cup member 43 (end chamber member) to the tube plate 28. The header 23 is formed by brazing two cup-shaped cup members 45 and 46 (end chamber members) to the tube plate 28 side by side. The cup members 45 and 46 are provided with a water inlet 48a and a water outlet 48b, respectively. As shown in FIG. 1, the water inlet 48 a is connected to a water supply pipe 63 that supplies hot water from the outside. Further, the water outlet 48b is connected to the primary heat exchanger 5 for heating hot water for hot water supply.

  The tube plate 28 is formed by forming a large number of tube insertion holes 47 in accordance with the arrangement of the heat receiving tubes 25 with respect to a rectangular metal plate. The cup member 43 brazed to the tube plate 28 on the header 22 side is brazed so as to cover all the tube insertion holes 47 to form a water chamber 49a. The cup members 45 and 46 brazed to the tube plate 28 on the header 23 side are mounted so as to cover the connection regions of the upstream heat receiving tube group 40 and the downstream heat receiving tube group 41, respectively, thereby forming a water chamber 49b and a water chamber 49c. is doing.

  As shown in FIG. 1 and FIG. 4, the gas circulation space 24 surrounded by the case member 21 and the headers 22 and 23 is composed of a high-temperature gas circulation space H that is substantially vertically above the combustion region A and a combustion It is classified into a low-temperature gas circulation space L that is substantially vertically upward with respect to the region B. More specifically, the high-temperature gas circulation space H is a space formed on the downstream side of the gas flow path 3 with respect to the combustion region A of the burner 10 and the overlapping region T of the primary heat exchange unit 4a. On the other hand, the low temperature gas circulation space L is a space formed on the downstream side of the gas flow path 3 with respect to the combustion region B of the burner 10 and the single region S of the primary heat exchange unit 4a. In other words, the high-temperature gas circulation space H is a series of high-temperature gas flow paths 3a following the combustion region A of the burner 10 to the overlapping region T of the primary heat exchange unit 4a and the high-temperature gas circulation space H of the secondary heat exchange unit 4b. It is a region located at the end. The low temperature gas circulation space L is a region located at the end of a series of low temperature gas flow paths 3b following the single region S and the low temperature gas circulation space L from the combustion region B.

  A metal gas guide plate 50 is disposed in the gas circulation space 24 along the heat receiving pipe 25. The gas guide plate 50 is brazed and fixed in a posture substantially orthogonal to the top plate 27 of the case member 21. Assuming that the top plate 27 is attached to the case body 26, the gas guide plate 50 is inserted between the heat receiving pipes 25, 25 disposed in the intermediate portion of the case body 26 in the depth direction, and the introduction port 31 and the exhaust gas are exhausted. A part of the gas flow path 3 connecting the mouth 30 is blocked. As shown in FIG. 8, the gas guide plate 50 is fixed in a state where it is inserted from the top plate 27 side between the heat receiving pipe 25 constituting the upstream heat receiving pipe group 40 and the heat receiving pipe 25 constituting the downstream heat receiving pipe group 41. Has been. As a result, the gas flow path 3 constituted by the gas flow space 24 is divided into an upstream area (upstream area U) and a downstream area (downstream area D) as shown in FIG. 7B. And is classified as

  As shown in FIG. 7A, the gas guide plate 50 is a plate body formed into a distorted shape in which a part of a rectangular metal plate is missing. More specifically, the gas guide plate 50 includes a large resistance portion 51 having a height h1 and a small resistance portion 52 having a height h2 (h1> h2) with the virtual boundary line X as a boundary. being classified. The gas guide plate 50 acts as a flow resistance against the fuel gas and air discharged from the exhaust port 30, and the flow resistance is larger in the small resistance portion 52 than in the large resistance portion 51. Therefore, the gas guide plate 50 functions as a guide unit that guides the combustion gas or air introduced from the inlet 31 to the low temperature gas circulation space L side.

  The height h <b> 1 of the large resistance portion 51 is such that it reaches the position of the heat receiving pipe 25 arranged in the lowermost portion of the heat receiving pipe 25 arranged in the case member 21 from the top plate 27 side of the case member 21. The height h1 of the large resistance portion 51 is lower than the height of the internal space (gas circulation space 24) of the case member 21. For this reason, a gap is formed below the gas guide plate 50 as shown in FIGS. 6B and 7B.

  On the other hand, the height h2 of the small resistance portion 52 is about 1/3 to 1/2 of the height h1, and is within the heat receiving pipe 25 arranged in the case member 21 in a state of being fixed to the top plate 27. The position reaches the position of the one arranged in the heat receiving pipe 25 fixed to the second stage from above. The gas guide plate 50 is fixed so that the boundary line X between the large resistance portion 51 and the small resistance portion 52 arrives almost on the boundary between the high temperature gas circulation space H and the low temperature gas circulation space L described above.

  Next, the flowing water system 60 formed in the heat source device 1 of the present embodiment will be described. The running water system 60 of the present embodiment is roughly classified into two systems: a bath running water system 61 for bathing a bath and a hot water running water system 62 for hot water supply. The bath running water system 61 is a circulation channel that supplies hot water in the bath 65 to the primary heat exchanger 5 and heats it back to the bath 65 side. More specifically, the bath running water system 61 is configured by connecting a bath outlet pipe 70 and a bath return pipe 68 to a water inlet 66 and a water outlet 67 of the primary heat exchanger 5. In the middle of the bath return pipe 68, a circulation pump 71 for circulating hot water in the bath running water system 61 is provided.

  On the other hand, the hot water flow system 62 supplies hot water from an external water supply source via the water supply pipe 63 and supplies hot water heated in the primary heat exchanger 6 and the secondary heat exchanger 20 to the hot water tap 74. It is a system. More specifically, as shown in FIG. 1, the hot water supply running water system 62 is roughly configured by a water supply pipe 63, a hot water supply pipe 77, and a bypass pipe 78. The water supply pipe 63 is a pipe for supplying hot water from a water supply source (not shown), and is connected to the inlet 72 of the secondary heat exchanger 20. A water outlet 73 of the secondary heat exchanger 20 is connected to a water inlet 75 of the primary heat exchanger 6 via a connection pipe 79. The hot water supply pipe 77 is a pipe for supplying hot water to the hot water tap 74 and is connected to the water outlet 76 of the primary heat exchanger 6. A bypass pipe 78 branched from the water supply pipe 63 is connected in the middle of the hot water supply pipe 77. A flow control valve 80 is disposed in the middle of the bypass pipe 78. The flow rate control valve 80 is for adjusting the mixing ratio of the low temperature hot water introduced through the bypass pipe 78 and the high temperature hot water flowing in the hot water supply pipe 77.

  Next, functions of the heat source device 1 will be described. The heat source device 1 has three operation modes, a hot water supply single mode, a bath single mode, and a hot water supply / bath combined mode, as in the conventional one-can two-water heat source device.

  The operation when the heat source device 1 operates in the hot water supply single mode will be described focusing on the flow of hot water and combustion gas. The hot water supply single mode is an operation mode in which hot water for hot water supply is heated while the heating operation of hot water stored in the bath 65 is stopped. The control means 85 of the heat source device 1 is supplied with hot water from an external water supply source when the hot water tap 74 is opened. The hot water supplied from the water supply source is heated by passing through the secondary heat exchanger 20 and the primary heat exchanger 6 in this order, and is discharged from the hot water tap 74.

  More specifically, the low-temperature hot water supplied by the water supply pipe 63 is, as shown in FIGS. 1 and 8, first, the upstream heat receiving pipe group from the water inlet 48a of the secondary heat exchanger 20 through the water chamber 49b. It flows into each heat receiving pipe 25 constituting 40. The hot water flowing through the upstream heat receiving pipe group 40 flows into the water chamber 49a formed on the header 22 side, and then flows into each heat receiving pipe 25 constituting the downstream heat receiving pipe group 41 by changing the flow direction. Hot water flowing through the downstream heat receiving pipe group 41 flows into the water chamber 49c formed on the header 23 side, and is discharged from the water outlet 48b.

  The hot water discharged from the water outlet 48 b of the secondary heat exchanger 20 flows into the water inlet 75 of the primary heat exchanger 6 through the connection pipe 79. Hot water flowing from the water inlet 75 flows through a bent flow path constituted by the heat receiving pipes 15 and the bend pipes 16 penetrating through the fin plates 12. The hot water supplied to the secondary heat exchanger 6 is heated by heat exchange with the combustion gas passing through the gaps between the fin plates 12 and then discharged from the water outlet 76. The hot water flowing into the secondary heat exchanger 20 is heated by exchanging heat with the combustion gas while reciprocating in the heat receiving pipes 25 arranged in the gas circulation space 24 in this way.

  The hot hot water flowing through the hot water supply pipe 77 joins the low temperature hot water flowing through the bypass pipe 78 branched from the water supply pipe 63. The control means 85 adjusts the amount of hot water flowing through the bypass pipe 78 by adjusting the opening degree of the flow rate control valve 80 in accordance with the hot water temperature set via a remote controller (not shown). Thereby, the hot hot water heated in the primary heat exchanger 6 and the secondary heat exchanger 20 and the low-temperature hot water supplied from the external water supply source are mixed in a predetermined ratio, and the hot water temperature in the hot water tap 74 is changed. It is adjusted to a predetermined temperature.

  On the other hand, when the heat source device 1 operates in the hot water supply single mode, the control device 85 performs all combustion composing both the combustion regions A and B of the burner 10 on the condition that water flow in the hot water supply water flow system 62 is started. An ignition operation is performed by supplying fuel gas to the pipe 8. Further, the control means 85 starts the blower 11 in parallel with the ignition operation, and starts supplying air required for the combustion operation in the burner 10.

  The high-temperature combustion gas generated in the combustion regions A and B of the burner 10 flows downstream of the gas flow path 3 and flows into the gaps of a large number of fin plates 12 constituting the primary heat exchange unit 4a. The combustion gas generated in the combustion regions A and B exchanges heat with hot water flowing in the heat receiving pipes 25 arranged in the overlapping region T and the single region S, respectively, and most of the sensible heat is recovered.

  Here, as described above, in the fin plate 12, the fin heights L1 and L3 on the combustion region A side are extremely shorter than the fin heights L2 and L4 on the combustion region B side. Therefore, the primary heat exchange unit 4a has a lower sensible heat recovery efficiency in the overlapping region T than in the single region S. Therefore, the combustion gas discharged from the primary heat exchange unit 4a has a temperature distribution depending on the part. That is, when the heat source device 1 operates in the hot water supply single mode, the combustion gas discharged downstream from the overlap region T (hereinafter referred to as high-temperature combustion gas as necessary) is the combustion gas discharged from the single region S. The amount of sensible heat remaining without being recovered is higher than that (hereinafter referred to as low-temperature combustion gas if necessary), and the temperature is high.

  The combustion gas that has passed through the primary heat exchange section 4a flows in the gas flow path 3 further toward the downstream side (upper side) while maintaining the above-described temperature distribution, and reaches the secondary heat exchange section 4b. The combustion gas that has reached the secondary heat exchange unit 4 b flows into the gas circulation space 24 from the inlet 31 of the secondary heat exchanger 20 through the connection member 35.

  Of the combustion gas flowing into the gas circulation space 24, the high-temperature combustion gas discharged from the overlapping region T preferentially flows into the high-temperature gas circulation space H side of the gas circulation space 24 and is discharged from the single region S. The low temperature combustion gas preferentially flows into the low temperature gas circulation space L side. As described above, the high-temperature combustion gas has a higher residual amount of sensible heat than the low-temperature combustion gas and has a high temperature. Furthermore, the high temperature combustion gas tends to stay above the high temperature gas circulation space H as in the case of the bath single mode.

  However, part of the combustion gas that has flowed into the upstream region U of the high temperature gas circulation space H circulates along the gas guide plate 50 toward the low temperature gas circulation space L, together with the low temperature combustion gas that has flowed into the low temperature gas circulation space L. It flows into the downstream region D of the low temperature gas circulation space L. Therefore, the atmosphere temperature in the gas circulation space 24 becomes substantially uniform, and heat exchange is performed on the entire heat transfer surface of the heat receiving pipe 25.

  Next, the flow of hot water and combustion gas when the heat source device 1 operates in the bath single mode will be described. The bath single mode is an operation mode in which hot water stored in the bath 65 is heated in the first heat exchange unit 4a while hot water supply is stopped. When operating in the bath single mode, the control means 85 of the heat source device 1 activates the circulation pump 71 to circulate hot water in the bath 65 into the bath running water system 61. When the water flow in the bath running water system 61 is confirmed, the control means 85 supplies the fuel gas only to the combustion pipes 8 arranged in the combustion region A among the combustion pipes 8 constituting the burner 10 and operates the ignition device 9. Ignition operation. The control device 85 activates the blower 11 almost simultaneously with the ignition operation, and starts supplying air necessary for combustion to the burner 10. Thereby, when the heat source device 1 operates in the bath single mode, a high-temperature combustion gas is generated only in the combustion region A of the burner 10, and a normal-temperature air flow is generated in the combustion region B.

  The high-temperature combustion gas generated in the combustion region A of the burner 10 flows downstream of the gas flow path 3 and flows into the gaps between the fin plates 12 provided in the overlapping region T of the primary heat exchange part 4a. The high-temperature combustion gas that has flowed into the overlapping region T exchanges heat on the surfaces of the fin plate 12 and the heat receiving pipe 13, and most of the sensible heat of the combustion gas is recovered. Thereby, the hot water flowing through the heat receiving pipe 13 of the primary heat exchanger 5 is heated. The combustion gas from which most of the sensible heat has been collected flows further downstream (upper side in FIG. 1) through the gas flow path 3, and reaches the secondary heat exchange section 4b. The combustion gas passes through the connection member 35 and flows into the high-temperature gas circulation space H of the gas circulation space 24 corresponding to the downstream of the combustion region A from the inlet 31 provided on the back surface of the secondary heat exchanger 20.

  On the other hand, the substantially normal temperature air flow that has passed through the combustion region B passes through the gaps between the numerous fin plates 12 provided in the single region S of the primary heat exchange unit 4b, and reaches the secondary heat exchange unit 4b. The air flow flows from the inlet 31 of the secondary heat exchanger 20 into the low temperature gas circulation space L corresponding to the downstream of the combustion region B.

  As described above, when the heat source device 1 operates in the bath single mode, the combustion gas and air flowing into the secondary heat exchanger 20 have a predetermined temperature distribution. In other words, the combustion gas flowing into the high-temperature gas circulation space H of the secondary heat exchanger 20 has been recovered in the primary heat exchange part 4a, although most of the sensible heat has been recovered in the primary heat exchange part 4a. Thermal energy remains as much as there was no sensible heat or latent heat. On the other hand, the air flow that flows into the low temperature gas circulation space L of the secondary heat exchanger 20 is substantially at normal temperature, and the thermal energy is lower than the combustion gas that flows into the high temperature gas circulation space H. Therefore, the combustion gas that has flowed into the secondary heat exchanger 20 tends to be unevenly distributed above the high-temperature gas circulation space H as shown by hatching in FIG.

  Here, as described above, the gas induction plate 50 is disposed in the gas circulation space 24 of the secondary heat exchanger 20. The gas guide plate 50 has a large resistance portion 51 on the high temperature gas circulation space H side larger than the small resistance portion 52 on the low temperature gas circulation space L side, and is opposed to the inlet 31 provided in the case member 21. It is arranged. In addition, the gas guide plate 50 is fixed in a state of hanging from the top plate 27 side of the case member 21. Therefore, a part of the combustion gas that has flowed into the upstream region U of the high temperature gas circulation space H flows into the downstream region D of the high temperature gas circulation space H through the gap formed below the gas guide plate 50. The remaining part of the combustion gas flows along the gas guide plate 50 toward the low temperature gas circulation space L, and flows into the downstream region D of the low temperature gas circulation space L together with the air present in the low temperature gas circulation space L. Thereby, the atmospheric temperature of the gas distribution space 24 becomes substantially uniform, and the heat transfer area of the heat receiving pipe 25 can be used effectively.

  Next, an operation when the heat source device 1 operates in the hot water supply / bath combined mode will be described. In the hot water supply / bath combined mode, the hot water flows in a state where the flow of hot water in the single hot water supply mode and the flow of hot water in the single bath mode are combined. That is, in the hot water supply / bath combined mode, hot water in the bath 65 circulates in the bath running water system 61 and the primary heat exchanger 5, and hot water supplied through the water supply pipe 63 passes through the secondary heat exchanger 20 and the primary heat. Heated by the exchanger 6 and discharged to the outside through the hot water supply pipe 77.

  On the other hand, the flow of combustion gas in the hot water supply / bath combined mode is the same as that in the above-described hot water supply single mode. More specifically, in the hot water supply / bath combined mode, a flame is formed in all the combustion pipes 8 constituting the burner 10, and combustion gas is generated. The combustion gas generated in the burner 10 flows in the gas flow path 3 downstream, that is, upward, and reaches the primary heat exchange unit 4a. The combustion gas passes through the gaps between the numerous fin plates 12 constituting the primary heat exchange section 4a, and flows in the heat receiving tubes 13 and 15 of the primary heat exchanger 5 for bath heating and the primary heat exchanger 6 for hot water supply. Exchange heat with hot water.

  The combustion gas from which most of the sensible heat has been recovered by heat exchange in the primary heat exchange unit 4 a further flows downstream of the gas flow path 3. Here, the heat receiving tubes 15 of the primary heat exchanger 6 are arranged at substantially equal intervals over the entire width direction of the fin plate 12, but the heat receiving tubes 13 of the primary heat exchanger 5 overlap the primary heat exchanging portion 4a. It is unevenly distributed in the region T. That is, in the primary heat exchange section 4a, the arrangement density of the heat receiving tubes 13 and 15 on the overlapping region T side is higher than the arrangement density of the heat receiving tubes 15 arranged on the single region S side. Therefore, the fin heights L1 and L3 of the overlapping region T are lower than the fin heights L2 and L4 of the single region S, and the heat recovery efficiency is low. Therefore, the combustion gas (high temperature combustion gas) discharged from the overlapping region T of the primary heat exchange unit 4a has a relatively large residual amount of sensible heat than the combustion gas (low temperature combustion gas) discharged from the single region S, It is hot.

  The combustion gas that has passed through the primary heat exchange section 4a flows into the gas circulation space 24 of the secondary heat exchanger 20 with the above-described temperature distribution being substantially maintained. That is, the high temperature combustion gas preferentially flows into the high temperature gas circulation space H of the gas circulation space 24, and the low temperature combustion gas preferentially flows into the low temperature gas circulation space L.

  The high temperature gas flowing into the high temperature gas circulation space H is guided to the low temperature gas circulation space L side by the gas guide plate 50 arranged in parallel to the inlet 31 of the secondary heat exchanger 20. Thereby, the temperature distribution of the combustion gas flowing into the gas circulation space 24 becomes substantially uniform.

  As described above, the heat source device 1 is provided with the gas induction plate 50 in the gas circulation space 24 of the secondary heat exchanger 20, is generated in the overlapping region T of the primary heat exchange unit 4 a, and flows into the high-temperature gas circulation space H. The high-temperature combustion gas is guided to the low-temperature gas circulation space L side. Further, the gas induction plate 50 is fixed so as to hang down from the top plate 27 side of the secondary heat exchanger 20. The gas guide plate 50 has a large resistance portion 51 disposed on the high temperature gas circulation space H side, a small resistance portion 52 disposed on the low temperature gas circulation space L side, and disposed along each heat receiving pipe 25. Yes. Therefore, the high-temperature combustion gas and air that tend to be unevenly distributed above the gas circulation space 24 can be smoothly guided to the low-temperature gas circulation space L, and the temperature unevenness of the combustion gas and air in the gas circulation space 24 can be further increased. It can be solved more reliably. Therefore, in the heat source device 1, even if the combustion gas or air discharged from the primary heat exchange unit 4a has temperature unevenness, the temperature distribution in the gas circulation space 24 is substantially uniform, and the secondary heat exchanger 20 is The heat transfer area of each heat receiving pipe 25 to be configured can be effectively used. Therefore, the heat source device 1 has high heat exchange efficiency in the secondary heat exchanger 20, and can sufficiently recover the heat energy of the combustion gas generated by the combustion.

  Further, as described above, the gas induction plate 50 is fixed in a state where a predetermined gap is formed between the bottom surface of the case body 26 constituting the secondary heat exchanger 20. Further, the secondary heat exchanger 20 is arranged so that the drain port 32 side faces downward, and a flow gradient is formed toward the drain port 32 side. Therefore, in the heat source device 1, the drain generated in the secondary heat exchanger 20 is smoothly discharged from the drain port 32.

  As described above, the secondary heat exchanger 20 is a multi-tube heat exchanger configured by arranging a large number of heat receiving tubes 25 in parallel, and has a simple device configuration. Is cheap.

  In the heat source device 1, the combustion gas and air discharged from the primary heat exchange unit 4 a are dispersed throughout the gas circulation space 24. Therefore, even if combustion gas or air flows into the gas circulation space 24 with hot water remaining in each heat receiving pipe 25 of the secondary heat exchanger 20 as if operating in the bath single mode, the heat receiving pipe. There are no problems such as hot water boiling or boiling in 25 areas. In addition, since the hot water in the heat receiving pipe 25 does not locally become hot in the heat source device 1, there is almost no problem that unexpectedly hot water is discharged immediately after the start of the hot water supply operation after the bath single mode. .

  The gas guide plate 50 described above has a large resistance portion 51 and a small resistance portion 52 having different surface areas from the boundary line X as shown in FIG. 7, and flows into the upstream region U of the high-temperature gas circulation space H. The burned combustion gas can be efficiently guided to the low temperature gas circulation space L side. However, since the gas guide plate 50 is plate-shaped, there is a possibility that the heat transfer area of the heat receiving pipe 25 arranged at a position adjacent to the downstream side of the gas guide plate 50 cannot be effectively used. For this reason, when such a situation is assumed, for example, a gas guide plate 90 having some openings 91 as shown in FIG. 9A, or a gas in which the whole or a part thereof is meshed as shown in FIG. 9B. It is desirable to employ a guide plate 92 or the like. According to such a configuration, the heat transfer area of the heat receiving pipe 25 arranged in the gas circulation space 24 can be effectively utilized to the maximum extent.

  The gas guide plate 50 described above has a flat plate shape, but the present invention is not limited to this. For example, as shown in FIGS. 10 (a) and 10 (b), the gas guide plate 50 has a curved shape. The gas guide plate 93 may be arranged. Further, as shown in FIG. 11, the gas guide plate 50 may have a configuration in which the lower end side is inclined to the downstream side in the flow direction of the combustion gas and air flowing in the gas circulation space 24 from the upper end side (top plate 21 side). Even in such a configuration, the combustion gas that has flowed into the upstream region U of the high-temperature gas circulation space H is efficiently guided to the low-temperature gas circulation space L side, and the temperature unevenness of the combustion gas in the gas circulation space 24 is reduced. While being able to eliminate, the ventilation resistance of the combustion gas and air in the gas distribution space 24 can be suppressed. Therefore, when it is set as a structure as shown in FIG.10 and FIG.11, in addition to the improvement of the heat exchange efficiency in the secondary heat exchanger 20, the load which acts on the air blower 11 accompanying the fall of the ventilation resistance in the gas distribution space 24 And the operation sound of the blower 11 can be suppressed to the minimum.

  Further, the heat source device 1 described above has a configuration in which only one gas guide plate 50 or the like is disposed in the gas circulation space 24 of the secondary heat exchanger 20, but the present invention is not limited to this. For example, as shown in FIG. 12, a gas guide plate 50 is arranged in the central portion of the gas circulation space 24 and a gas guide plate 95 smaller than the gas guide plate 50 on the downstream side in the gas flow direction of the combustion gas in the gas circulation space 24. It is good also as a structure which arranged. If the gas circulation space 24 is provided with a large number of gas guide plates 50 and the like in this way, the combustion gas and air can be more reliably distributed to every corner of the gas circulation space 24, and the secondary heat The heat exchange efficiency in the exchanger 20 can be improved.

  In addition, the gas guide plate 50 and the like described above are both arranged in both the high temperature gas circulation space H and the low temperature gas circulation space L. However, the present invention is not limited to this, for example, FIG. As shown in FIG. 13, the gas guide plate 96 may be disposed only on the high temperature gas circulation space H side. Even in such a configuration, the ventilation resistance on the high temperature gas circulation space H side is higher than that on the low temperature gas circulation space L side, and the combustion gas and air flowing into the high temperature gas circulation space H can be smoothly transferred to the low temperature gas circulation space. It can be guided to the L side.

It is an operation principle figure showing a heat source device which is one embodiment of the present invention. It is a perspective view which shows the 1st heat exchange part employ | adopted in the heat-source apparatus shown in FIG. (A) is AA sectional drawing of FIG. 2, (b) is BB sectional drawing of FIG. It is a principal part enlarged view of the action | operation principle figure shown in FIG. It is a disassembled perspective view of the secondary heat exchanger employ | adopted in the heat-source apparatus shown in FIG. (A) is the front view which expanded the principal part of the heat-source apparatus shown in FIG. 1, (b) is a side view of (a). (A) is a front view which shows the gas induction plate employ | adopted in the secondary heat exchanger shown in FIG. 5, (b) shows typically the positional relationship of the gas induction plate in a secondary heat exchanger. FIG. It is sectional drawing of the secondary heat exchanger shown in FIG. (A), (b) is a front view which shows the modification of the gas guide plate shown in FIG. 7, respectively. (A) is a perspective view which shows another modification of the gas induction | guidance | derivation board shown in FIG. 7, (b) is a side view of the heat-source apparatus which has arrange | positioned the gas induction | guidance | derivation board shown to (a). It is a front view which shows the modification of the heat-source apparatus shown in FIG. It is a front view which shows another modification of the heat-source apparatus shown in FIG. It is a front view which shows another modification of the heat-source apparatus shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat source apparatus 2 Combustion part 3 Gas flow path 4a Primary heat exchange means 4b Secondary heat exchange means 5,6 Primary heat exchanger 7 Secondary heat exchanger 10 Burner 11 Blower 12 Fin plate 13, 14, 25 Heat receiving pipe 20 2 Next heat exchanger 21 Case member 24 Gas distribution space 26 Case body 27 Top plate 30 Exhaust port 31 Inlet port 32 Drain port 50, 90, 92, 93, 95, 96 Gas induction plate 51 Large resistance portion 52 Small resistance portion A Combustion Region B Combustion region H High-temperature gas circulation space L Low-temperature gas circulation space X Borderline T Overlapping region (second region)
S Single area (first area)

Claims (11)

A combustion burner, air blowing means for introducing outside air, and a gas flow path through which combustion gas or air generated in the combustion burner flows,
In the middle of the gas flow path, there are primary heat exchange means for exchanging heat with the combustion gas or air flowing through the gas flow path, and two of the primary heat exchange means disposed downstream of the primary heat exchange means in the flow direction of the combustion gas or air A secondary heat exchange means,
The primary heat exchanging means includes a first region in which a discharge temperature of the combustion gas or air discharged to the downstream side of the gas flow path is low, and a combustion in which the discharge temperature of the combustion gas or air is discharged from the first region. And a second region that is hotter than gas or air,
The secondary heat exchange means communicates with the gas flow path, and has a gas circulation space through which combustion gas or air circulates,
The gas circulation space includes a low-temperature gas circulation space corresponding to the downstream side in the flow direction of the combustion gas or air with respect to the first region of the primary heat exchange means, and the flow direction of the combustion gas or air with respect to the second region. A hot gas distribution space corresponding to the downstream side,
Guiding means for guiding the combustion gas or air flowing into the hot gas circulation space to the cold gas circulation space side is arranged ,
A heat source device characterized in that a gap through which drain generated in the secondary heat exchange means can flow is formed between the guiding means and the bottom surface of the gas circulation space . The primary heat exchange means includes a plurality of heat exchange circuits each including a heat receiving pipe through which hot water or a heat medium circulates and fins attached to the heat receiving pipe. Sharing fins,
The second area is an area where a cross-sectional area of a gas flow path occupied by one of the heat exchange circuits constituting the plurality of heat exchange circuits overlaps with a cross-sectional area of a gas flow path occupied by another heat exchange circuit And
Wherein the first region is a heat source apparatus according to claim 1, the cross-sectional area between the gas flow path heat exchange circuit is occupied, characterized in that a region that does not overlap. The primary heat exchanging means includes a heat exchange circuit configured to include a heat receiving pipe through which hot water or a heat medium circulates and fins attached to the heat receiving pipe,
The second region is a region having a high arrangement density of the heat receiving tubes ,
2. The heat source device according to claim 1, wherein the first region is a region in which an arrangement density of the heat receiving tubes is lower than that of the second region. Induction means, the ventilation resistance of the combustion gas or air in the hot gas flow space, according to any one of claims 1 to 3, characterized in that to increase than flow resistance of the combustion gas or air at low temperature gas flow space Heat source device. Induction means is a plate-like, the surface area of the portion that is disposed to the hot gas flow space, according to any one of claims 1 to 4, wherein the greater than the surface area of the portion that is disposed cold gas flow space Heat source device. The heat source device according to any one of claims 1 to 5 , wherein the guiding means is suspended from the top surface side of the gas circulation space. The guiding means is suspended from the top surface side of the gas circulation space, and the lower end portion of the guiding means is located downstream of the upper end portion in the flow direction of combustion gas or air in the gas circulation space. The heat source device according to any one of claims 1 to 6 . The guiding means includes a large resistance portion that provides a large flow resistance to the combustion gas or air that passes through the gas circulation space, and a small resistance portion that provides a smaller flow resistance to the combustion gas or air than the large resistance portion. has the door, the large resistor portion is arranged in the hot gas flow space, a heat source apparatus according to any one of claims 1 to 7 wherein the small resistance portion is characterized in that it is arranged in the low-temperature gas flow space . The secondary heat exchange means has an inlet for introducing combustion gas or air into the gas circulation space, and an outlet for discharging combustion gas or air flowing in the gas circulation space,
The heat source apparatus according to any one of claims 1 to 8 , wherein the guiding means is disposed at an intermediate position between the introduction port and the discharge port.   The heat source device according to any one of claims 1 to 9, wherein the secondary heat exchange means is configured by a multi-tube heat exchanger in which a large number of heat receiving tubes are arranged in a gas circulation space. The secondary heat exchange means has an inlet for introducing combustion gas or air into the gas circulation space, and an outlet for discharging combustion gas or air flowing in the gas circulation space. It is composed of a multi-tube heat exchanger with a large number of heat receiving tubes arranged in
The heat receiving pipe extends in a direction blocking an imaginary line connecting the inlet and the outlet,
The heat source device according to claim 10 , wherein the guiding means is arranged along an extending direction of the heat receiving pipe arranged in the gas circulation space.

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