JP2018141598A - Heat exchanger and heat source machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger that can restrain a first shell plate from being heated to a temperature higher than that of a second shell plate, and a heat source machine that comprises the same.SOLUTION: A primary heat exchanger 5 comprises a case 51 and a heat exchange part 52. The case 51 comprises a first shell plate 51a1 and a second shell plate 52a2. The heat exchange part 52 includes a plurality of heat transfer pipe parts 52a. The plurality of heat transfer pipe parts 52a include a first heat transfer pipe 52a1 and a second heat transfer pipe 52a2. The case 51 includes an inflow port 5a and an outflow port 5b. The inflow port 5a is provided between the first shell plate 51a1 and the second shell plate 51a2 in an opposing direction D1. The outflow port 5b is biasedly arranged on the side of the first shell plate 51a1 in the opposing direction D1. A gap X1 between the first shell plate 51a1 and the first heat transfer pipe 52a1 is smaller than a gap X2 between the second shell plate 51a2 and the second heat transfer pipe 52a2 in the opposing direction D1.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a heat exchanger and a heat source device, and more particularly to a heat exchanger and a heat source device including the heat exchanger.

  2. Description of the Related Art Conventionally, there is a heat source apparatus including a heat exchanger that exchanges heat between combustion gas as a heating fluid supplied by a burner and hot water flowing through a heat exchange unit. Such a heat source machine is described in, for example, Japanese Utility Model Laid-Open No. 6-15868 (Patent Document 1). In the heat source apparatus described in this publication, an inflow port for combustion gas is provided at the lower end of the case of the heat exchanger, and an outflow port for combustion gas is provided at the upper end of the case of the heat exchanger.

Japanese Utility Model Publication No. 6-15868

  In the heat source apparatus described in the above publication, for example, when the outlet of the combustion gas is arranged to be biased toward the first body plate, the combustion gas flows more on the first body plate side than the first body plate side, and combustion Gas drift occurs. In this case, the first body plate is heated to a higher temperature than the second body plate. For this reason, a crack may arise in the 1st body plate by the higher thermal stress acting on the 1st body plate than the 2nd body plate.

  The present invention has been made in view of the above problems, and an object thereof is a heat exchanger capable of suppressing the first body plate from being heated to a higher temperature than the second body plate, and a heat source apparatus including the heat exchanger. Is to provide.

  The heat exchanger of the present invention includes a heat exchange part and a case. The heat exchanging section is for exchanging heat between a heating gas flowing outside and hot water flowing inside. The case has a first body plate and a second body plate facing the first body plate, and accommodates the heat exchange unit. The heat exchange part includes a plurality of heat transfer tube parts arranged to run in parallel with each other in the case. The plurality of heat transfer tube portions include a first heat transfer tube portion and a second heat transfer tube portion. The first heat transfer tube portion is disposed closest to the first body plate among the plurality of heat transfer tube portions. The second heat transfer tube portion is disposed closest to the second body plate among the plurality of heat transfer tube portions. The case includes an inflow port through which the heating gas flows into the case and an outflow port through which the heating gas flows out of the case. The heat exchange part is disposed between the inlet and the outlet. The inflow port is provided between the first trunk plate and the second trunk plate in the facing direction in which the first trunk plate and the second trunk plate face each other. The outflow port is arranged so as to be biased toward the first body plate in the facing direction. In the facing direction, the distance between the first body plate and the first heat transfer tube portion is smaller than the distance between the second body plate and the second heat transfer tube portion.

  According to the heat exchanger of the present invention, the outflow port is arranged to be biased toward the first body plate in the facing direction, and the distance between the first body plate and the first heat transfer tube portion in the facing direction is the second body plate. And the interval between the second heat transfer tube portion. For this reason, it can suppress that the gas for a heating flows between the 1st trunk | drum and a 1st heat exchanger tube part rather than between the 2nd trunk | drum and a 2nd heat exchanger tube part. Therefore, it can suppress that a 1st trunk plate is heated to high temperature rather than a 2nd trunk plate. For this reason, it can suppress that a crack arises in a 1st trunk plate by suppressing that a higher thermal stress acts on a 1st trunk plate than a 2nd trunk plate.

  In said heat exchanger, the heat exchange part contains the 3rd heat exchanger tube part arrange | positioned between the 1st heat exchanger tube part and the 2nd heat exchanger tube part in the opposing direction. The pitch between the first heat transfer tube portion and the third heat transfer tube portion is larger than the pitch between the second heat transfer tube portion and the third heat transfer tube portion. For this reason, by making the pitch between the first heat transfer tube portion and the third heat transfer tube portion larger than the pitch between the second heat transfer tube portion and the third heat transfer tube portion, the first body plate and the first heat transfer tube portion Can be made smaller than the distance between the second body plate and the second heat transfer tube portion.

  In said heat exchanger, the heat exchange part contains the 4th heat exchanger tube part and the 5th heat exchanger tube part. Each of the fourth heat transfer tube portion and the fifth heat transfer tube portion is disposed on the outlet side so as to face each of the first heat transfer tube portion and the second heat transfer tube portion in the intersecting direction intersecting the opposing direction. In the crossing direction, the first heat transfer tube portion is arranged so as to be shifted from the fourth heat transfer tube portion. The 2nd heat exchanger tube part is arranged so that it may overlap with the 5th heat exchanger tube part. For this reason, the heat absorption efficiency of the 4th heat exchanger tube part can be improved because the gas for heating becomes easy to flow into the 4th heat exchanger tube part. Thereby, the heat exchange efficiency of a heat exchanger can be improved.

  In the heat exchanger described above, the heat exchange unit includes a plurality of fins. Each of the plurality of fins includes a main surface, and a first through hole and a second through hole that are provided in the main surface at an interval in an opposing direction. The plurality of fins are stacked and spaced from each other in the extending direction in which the first heat transfer tube portion and the second heat transfer tube portion extend. The 1st heat exchanger tube part is inserted in the 1st penetration hole. The 2nd heat exchanger tube part is inserted in the 2nd penetration hole. For this reason, the heat absorption efficiency of the heat exchange part can be improved by the plurality of fins. Thereby, the heat exchange efficiency of a heat exchanger can be improved.

  In the above heat exchanger, at least one of the plurality of fins includes a first protrusion and a second protrusion protruding from the main surface. The 1st convex part is arranged between the 1st penetration hole and the 1st body board. The 2nd convex part is arranged between the 2nd penetration hole and the 2nd body board. When the main surface is viewed from the extending direction, the area of the first protrusion is smaller than the area of the second protrusion. For this reason, it can prevent suppressing the quantity of the gas for a heating which flows between a 1st trunk | drum and a 1st heat exchanger tube part too much. Thereby, the heat exchange efficiency of a heat exchanger is securable.

  The heat source apparatus of the present invention includes the above heat exchanger and a burner for generating a heating gas supplied to the heat exchanger. According to the heat source apparatus of the present invention, the first body plate of the heat exchanger can be suppressed from being heated to a higher temperature than the second body plate.

  As described above, according to the present invention, it is possible to provide a heat exchanger capable of suppressing the first body plate from being heated to a higher temperature than the second body plate, and a heat source device including the heat exchanger. it can.

It is the schematic which shows the structure of the heat-source equipment in one embodiment of this invention. It is a schematic sectional drawing which shows the structure by which the primary heat exchanger in one embodiment of this invention, the burner, and the secondary heat exchanger were connected. It is a schematic perspective view which shows the structure of the primary heat exchanger in one embodiment of this invention. It is a schematic top view which shows the structure of the primary heat exchanger in one embodiment of this invention. It is a general | schematic disassembled perspective view which shows the structure of the primary heat exchanger in one embodiment of this invention. It is a schematic top view which shows the structure by which the top plate part of the primary heat exchanger in one embodiment of this invention was removed. It is a schematic bottom view which shows the structure by which the top plate part of the primary heat exchanger in one embodiment of this invention was removed. It is a schematic perspective view which shows the structure of the fin of the primary heat exchanger in one embodiment of this invention. It is a schematic sectional drawing which shows the structure of the primary heat exchanger in a comparative example. It is a schematic sectional drawing which shows the structure of the primary heat exchanger in one embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
First, the structure of the heat source machine in one embodiment of the present invention will be described. A heating-only heat source device will be described as an example of the heat source device of the present embodiment. A latent heat recovery type heat source device capable of recovering the latent heat of the combustion gas will be described as an example of the heat source device of the present embodiment.

  Referring to FIG. 1, a heat source device 1 according to the present embodiment includes a housing 2, a burner 3, a blower (fan) 4, a primary heat exchanger 5, a secondary heat exchanger 6, The sump 7, the drain pipe 8, the drain pipe 9, the heat medium circulation circuit 10, the valve 11, the circulation pump 12, the heat medium tank 13, and the water supply pipe 14 are mainly provided. All the parts except the case 2 are arranged in the case 2.

  The burner 3 is for generating combustion gas supplied to the primary heat exchanger 5 and the secondary heat exchanger 6. This combustion gas is for exchanging heat between the primary heat exchanger 5 and the secondary heat exchanger 6. The blower (fan) 4 is for supplying combustion air to the burner 3. The blower (fan) 4 is disposed below the burner 3 and is configured to flow the combustion gas from below to above.

  The primary heat exchanger 5 and the secondary heat exchanger 6 are for exchanging heat between the heat medium and the combustion gas. The primary heat exchanger 5 is configured to be able to recover the sensible heat of the combustion gas supplied by the burner 3. The secondary heat exchanger 6 is configured to be able to recover the latent heat of the combustion gas supplied by the burner 3. The primary heat exchanger 5 and the secondary heat exchanger 6 are connected to each other. The primary heat exchanger 5 is located above the burner 3, and the secondary heat exchanger 6 is located above the primary heat exchanger 5. The secondary heat exchanger 6 is provided with an exhaust port EP. The exhaust port EP is configured to be able to exhaust the combustion gas from which sensible heat has been recovered by the primary heat exchanger 5 and latent heat has been recovered by the secondary heat exchanger 6 to the outside of the housing 2.

  The combustion gas after heat exchange in the primary heat exchanger 5 is passed through the secondary heat exchanger 6 so that water (heated fluid) in the secondary heat exchanger 6 is preheated in the combustion gas. Condensed water is condensed and drainage is generated. This drain is acidic because nitrogen oxides in the exhaust gas are dissolved therein. The lower surface of the case 61 of the secondary heat exchanger 6 and the neutralizer 7 are connected via a drain pipe 8, and acidic drainage passes from the secondary heat exchanger 6 to the neutralizer 7 through the drain pipe 8. Sent. The neutralizer 7 is filled with a neutralizing agent, and acidic drainage can be neutralized by this neutralizing agent. A drain pipe 9 is connected to the neutralizer 7, and the drain neutralized by the neutralizer 7 is discharged out of the housing 2 through the drain pipe 9.

  The primary heat exchanger 5 and the secondary heat exchanger 6 are connected to a heat medium circulation circuit 10. The heat medium circulation circuit 10 is for circulating the heat medium in the heat source unit 1. The heating medium circulation circuit 10 is configured to supply the heating medium returned from the heating terminal to the heating terminal again. In the present embodiment, the heating terminal includes a high temperature terminal and a low temperature terminal. This high temperature terminal is, for example, a bathroom heater. This low temperature terminal is, for example, a floor heating device.

  The heat medium circulation circuit 10 includes a high-temperature forward circuit 10a, a low-temperature forward circuit 10b, and a bypass circuit 10c. The high-temperature going circuit 10 a is configured to supply the heat medium returned from the heating terminal (high-temperature terminal and low-temperature terminal) to the high-temperature terminal via the secondary heat exchanger 6 and the primary heat exchanger 5. The low temperature going circuit 10 b is configured to supply the heat medium returned from the heating terminal (high temperature terminal and low temperature terminal) to the low temperature terminal via the secondary heat exchanger 6. The bypass circuit 10c is configured to branch the high-temperature forward circuit 10a and join a part of the heat medium supplied to the high-temperature terminal to the low-temperature forward circuit 10b.

  The valve 11 is configured to allow a heat medium to flow from the high-temperature forward circuit 10a to the low-temperature forward circuit 10b via the bypass circuit 10c. Specifically, the valve 11 is closed when the heat medium flows from the high temperature forward circuit 10a to the heating high temperature forward terminal, and when the heat medium flows from the high temperature forward circuit 10a to the low temperature forward circuit 10b via the bypass circuit 10c. It is configured to be opened.

  The circulation pump 12 is for circulating the heat medium in the heat medium circulation circuit 10. The circulation pump 12 is connected between the primary heat exchanger 5 and the heat medium tank 13. The heat medium tank 13 is for suppressing a pressure increase accompanying the expansion or contraction of the volume caused by the temperature change of the heat medium, or a pressure drop accompanying the contraction. Further, the heat medium tank 13 is configured to be able to supplement the heat medium from the water supply pipe 14.

  Next, with reference to FIG. 2, the structure in which the primary heat exchanger 5, the burner 3, and the secondary heat exchanger 6 of the present embodiment are connected will be described in more detail. The primary heat exchanger 5 of the present embodiment is a so-called 1 can 1 water type heat exchanger.

  A case 61 of the secondary heat exchanger 6 is placed on the case 51 of the primary heat exchanger 5. In this state, the case 51 of the primary heat exchanger 5 and the case 61 of the secondary heat exchanger 6 are connected by the screw 21 so that the primary heat exchanger 5 and the secondary heat exchanger 6 are connected to each other. ing. The heat exchange part 62 of the secondary heat exchanger 6 is arranged on the exhaust outlet EP side with respect to the outlet 5 b of the primary heat exchanger 5. Combustion gas flows into the case 61 of the secondary heat exchanger 6 from the outlet 5b of the primary heat exchanger 5, flows outside the heat exchange section 62 of the secondary heat exchanger 6, and flows out of the exhaust port EP. To do. The exhaust member 22 is connected to the case 61 of the secondary heat exchanger 6 with a screw 21 so as to communicate with the exhaust port EP.

  On the case 31 of the burner 3, the case 51 of the primary heat exchanger 5 is placed. In this state, the case 31 of the burner 3 and the case 51 of the primary heat exchanger 5 are connected by the screw 21, whereby the burner 3 and the primary heat exchanger 5 are connected to each other.

  Next, with reference to FIGS. 2-8, the structure of the primary heat exchanger 5 of this Embodiment is demonstrated in more detail. In the present embodiment, the primary heat exchanger 5 corresponds to the heat exchanger in the claims.

  As shown in FIGS. 2 and 3, the primary heat exchanger 5 mainly includes a case 51, a heat exchange unit 52, a plurality of bend pipes 53, and a plurality of fin pipes 54. The case 51 includes a body plate portion 51a and a top plate portion 51b. The body plate portion 51a of the case 51 includes a first body plate 51a1 and a second body plate 51a2. The second trunk plate 51a2 faces the first trunk plate 51a1.

  The case 51 includes an inlet 5a through which the heating gas flows into the case 51 and an outlet 5b through which the heating gas flows out of the case. The inflow port 5a is provided at the lower end of the body plate portion 51a. The inflow port 5a is an opening defined by the lower end of the body plate portion 51a. The inflow port 5a is provided from the first body plate 51a1 to the second body plate 51a2. The outlet 5b is provided in the top plate portion 51b. The outflow port 5b is configured in an oval shape in plan view. A heat exchange unit 52 is accommodated in the case 51.

  As shown in FIG. 3 and FIG. 4, the heat exchanging section 52 is for exchanging heat between the heating gas flowing outside and hot water flowing inside. The heat exchange part 52 includes a plurality of heat transfer tube parts 52a and a plurality of fins 52b. In addition, the heat exchange part 52 should just contain the some heat exchanger tube part 52a, and does not need to contain the some fin 52b. 3 and 4, only the plurality of fins 52b located at the center and both ends in the stacking direction are shown as the plurality of fins 52b for the sake of simplicity and convenience of explanation.

  As shown in FIGS. 4 and 5, the body plate portion 51 a is provided so as to surround the heat exchange portion 52. The top plate portion 51 b is provided so as to cover the trunk plate portion 51 a and the heat exchange unit 52. The top plate portion 51b is connected to the body plate portion 51a with screws 21. The plurality of bend pipes 53 and the plurality of fin pipes 54 are disposed outside the case 51.

  A plurality of bend pipes 53 and a pipe of a high-temperature forward circuit 10a (not shown) are connected to one end of the plurality of heat transfer tube portions 52a. A plurality of fin pipes 54 are connected to the other ends of the plurality of heat transfer tube portions 52a. The plurality of heat transfer tube portions 52a are linearly configured. The plurality of bend pipes 53 and the plurality of fin pipes 54 are each curved in a U shape. One bend pipe 53 connects one ends of two heat transfer tube portions 52a among the plurality of heat transfer tube portions 52a. One fin pipe 54 connects the other ends of the two heat transfer tube portions 52a among the plurality of heat transfer tube portions 52a. The plurality of heat transfer tube portions 52a, the plurality of bend pipes 53, and the plurality of fin pipes 54 are configured to meander while being connected to one. The plurality of heat transfer tube portions 52a, the plurality of bend pipes 53, and the plurality of fin pipes 54 connected to one are configured to reciprocate in the direction in which the plurality of fins 52b are stacked.

  As shown in FIGS. 2 and 4, the plurality of heat transfer tube portions 52 a are arranged so as to run parallel to each other in the case 51. The outlet 5b extends along the direction in which the plurality of heat transfer tube portions 52a extend. The plurality of heat transfer tube portions 52a are a first heat transfer tube portion 52a1 disposed closest to the first body plate 51a1 among the plurality of heat transfer tube portions 52a, and a second body plate 51a2 among the plurality of heat transfer tube portions 52a. 2nd heat exchanger tube part 52a2 arranged near. The first heat transfer tube portion 52a1 is disposed along the first body plate 51a1. The second heat transfer tube portion 52a2 is disposed along the second body plate 51a2. The first heat transfer tube portion 52a1 and the second heat transfer tube portion 52a2 are arranged in parallel to each other in the facing direction D1 in which the first body plate 51a1 and the second body plate 51a2 face each other.

  The heat exchange part 52 is arranged between the inflow port 5a and the outflow port 5b. The inflow port 5a is provided between the first trunk plate 51a1 and the second trunk plate 51a2 in the facing direction D1 in which the first trunk plate 51a1 and the second trunk plate 51a2 face each other. The outflow port 5b is biased to the first body plate 51a1 side in the facing direction D1. That is, the outflow port 5b is disposed between the center and the first body plate 51a1 in the facing direction D1.

  In the facing direction D1, an interval X1 between the first body plate 51a1 and the first heat transfer tube portion 52a1 is smaller than an interval X2 between the second body plate 51a2 and the second heat transfer tube portion 52a2. This interval X1 is the shortest distance between the first body plate 51a1 and the first heat transfer tube portion 52a1 in the facing direction D1. This interval X2 is the shortest distance between the second body plate 51a2 and the second heat transfer tube portion 52a2 in the facing direction D1. Moreover, this space | interval X1 is smaller than the radius of the 1st heat exchanger tube part 52a1. This interval X1 is, for example, 6 mm. The interval X2 is larger than the radius of the second heat transfer tube portion 52a2. This interval X2 is, for example, 11 mm. The diameter of the first heat transfer tube portion 52a1 is equal to the diameter of the second heat transfer tube portion 52a2.

  The heat exchange part 52 includes a third heat transfer pipe part 52a3, a fourth heat transfer pipe part 52a4, a fifth heat transfer pipe part 52a5, and a sixth heat transfer pipe part 52a6. The first heat transfer tube portion 52a1, the second heat transfer tube portion 52a2, and the third heat transfer tube portion 52a3 are arranged in the lower stage, and the fourth heat transfer tube portion 52a4, the fifth heat transfer tube portion 52a5, and the sixth heat transfer tube portion 52a6 are in the upper stage. Is arranged.

  The third heat transfer tube portion 52a3 is disposed between the first heat transfer tube portion 52a1 and the second heat transfer tube portion 52a2 in the facing direction D1. Each of the fourth heat transfer tube portion 52a4, the fifth heat transfer tube portion 52a5, and the sixth heat transfer tube portion 52a6 is opposed to each of the first heat transfer tube portion 52a1, the second heat transfer tube portion 52a2, and the third heat transfer tube portion 52a3. It is arranged on the outlet 5b side so as to face the intersecting direction D2 that intersects with.

  In the intersecting direction D2, the first heat transfer tube portion 52a1 is displaced from the fourth heat transfer tube portion 52a4. Specifically, the first heat transfer tube portion 52a1 is arranged to be shifted to the first body plate 51a1 side with respect to the fourth heat transfer tube portion 52a4 in the facing direction D1. In the intersecting direction D2, the second heat transfer tube portion 52a2 is disposed so as to overlap the fifth heat transfer tube portion 52a5. In the cross direction D2, the third heat transfer tube portion 52a3 is disposed so as to overlap the sixth heat transfer tube portion 52a6. The diameters of the third heat transfer tube portion 52a3, the fourth heat transfer tube portion 52a4, the fifth heat transfer tube portion 52a5, and the sixth heat transfer tube portion 52a6 are the same as those of the first heat transfer tube portion 52a1 and the second heat transfer tube portion 52a2. Equal to the diameter of

  Each of the plurality of fins 52b is sandwiched between the first body plate 51a1 and the second body plate 51a2. One end of each of the plurality of fins 52b is brazed to the first body plate 51a1, and the other end of each of the plurality of fins 52b is brazed to the second body plate 51a2.

  Each of the plurality of fins 52b includes a main surface 52b1 and a plurality of through holes H. The plurality of through holes H are arranged in two upper and lower stages in the intersecting direction D2 intersecting the facing direction D1. The plurality of through-holes H are all formed in a perfect circle, and the diameters thereof are equal to each other. The plurality of through holes H is a concept including not only “open holes” but also “burring holes”.

  The plurality of through holes H include a first through hole H1 and a second through hole H2 that are provided on the main surface 52b1 at an interval in the facing direction D1. In the facing direction D1, a third through hole H3 is provided between the first through hole H1 and the second through hole H2. Furthermore, a fourth through hole H4, a fifth through hole H5, and a sixth through hole H6 are provided on the main surface 52b1 at intervals in the facing direction D1. Each of the first through hole H1, the second through hole H2, and the third through hole H3 is disposed to face the intersecting direction D2 with each of the fourth through hole H4, the fifth through hole H5, and the sixth through hole H6. ing.

  Each of the plurality of heat transfer tube portions 52a is inserted into each of the plurality of through holes H of the plurality of fins 52b. Specifically, the first heat transfer tube portion 52a1 is inserted into the first through hole H1. The second heat transfer tube portion 52a2 is inserted in the second through hole H2. The third heat transfer tube portion 52a3 is inserted into the third through hole H3. Further, the fourth heat transfer tube portion 52a4, the fifth heat transfer tube portion 52a5, and the sixth heat transfer tube portion 52a6 are inserted into the fourth through hole H4, the fifth through hole H5, and the sixth through hole H6, respectively.

  The pitch of the heat transfer tube portions 52a is the distance between the center points C of the heat transfer tube portions 52a adjacent to each other with an interval in the facing direction D1. The pitch P1 between the first heat transfer tube portion 52a1 and the third heat transfer tube portion 52a3 is larger than the pitch P2 between the second heat transfer tube portion 52a2 and the third heat transfer tube portion 52a3. The pitch P2 between the second heat transfer tube portion 52a2 and the third heat transfer tube portion 52a3 is the pitch between the fourth heat transfer tube portion 52a4 and the sixth heat transfer tube portion 52a6, and the fifth heat transfer tube portion 52a5 and the sixth heat transfer tube portion 52a6. Equal to the pitch of That is, the pitch between the fourth heat transfer tube portion 52a4 and the sixth heat transfer tube portion 52a6 and the pitch between the fifth heat transfer tube portion 52a5 and the sixth heat transfer tube portion 52a6 are the pitch P2.

  The first heat transfer tube portion 52a1 and the second heat transfer tube portion 52a2 are disposed asymmetrically with respect to the symmetry axis A passing through the center of the fin 52b in the facing direction D1 in the intersecting direction D2. On the other hand, the fourth heat transfer tube portion 52a4 and the fifth heat transfer tube portion 52a5 are arranged in line symmetry with respect to the symmetry axis A passing through the center of the fin 52b in the facing direction D1 in the intersecting direction D2. The symmetry axis A passes through each of the center points C of the third heat transfer tube portion 52a3 and the fifth heat transfer tube portion 52a5.

  As shown in FIG. 6 and FIG. 7, the plurality of fins 52 b are stacked and spaced from each other in the extending direction in which the first heat transfer tube portion 52 a 1 and the second heat transfer tube portion 52 a 2 extend. The first through-hole H1 to the sixth through-hole H6 (FIG. 2) of each of the plurality of fins 52b are arranged so as to overlap each other in the direction in which the plurality of fins 52b are stacked. The combustion gas as the heating gas flows in the gaps between the plurality of fins 52b.

  As shown in FIG. 8, at least one of the plurality of fins 52b includes a plurality of convex portions PP protruding from the main surface 52b1. The plurality of convex portions PP are configured in a truncated cone shape. The plurality of protrusions PP are arranged on the upstream side of the combustion gas with respect to the first through hole H1, the second through hole H2, and the third through hole H3. The plurality of convex portions PP include a first convex portion PP1 and a second convex portion PP2. The first protrusion PP1 is disposed between the first through hole H1 and the first body plate 51a1. The 2nd convex part PP2 is arrange | positioned between the 2nd through-hole H2 and the 2nd trunk | drum 51a2. When the main surface 52b1 is viewed from the extending direction in which the first heat transfer tube portion 52a1 and the second heat transfer tube portion 52a2 extend, the area of the first protrusion PP1 is smaller than the area of the second protrusion PP2.

  The plurality of fins 52b include a plurality of cut and raised slits SL and a plurality of cut and raised wall portions WP. The plurality of cut and raised slits SL protrude from the main surface 52b1. The plurality of cut and raised slits SL extend in the facing direction. The plurality of cut-and-raised wall portions WP are configured by cutting and raising a part of the fins 52b toward the main surface 52b1. The cut and raised wall portion WP protrudes from the main surface 52b1. The cut and raised wall portion WP is configured by cutting and raising a part of the fin 52b toward the main surface 52b1.

  Next, with reference to FIG. 1 again, the operation of the heat source apparatus of the present embodiment will be described. First, the operation of the heat source unit during high-temperature heating will be described. The heat medium (hot water) returned from the heating terminal (high temperature terminal and low temperature terminal) flows into the secondary heat exchanger 6 through the heat medium circulation circuit 10 and is heated by the combustion gas in the secondary heat exchanger 6. . The heat medium heated by the secondary heat exchanger 6 flows into the heat medium tank 13 and then flows into the circulation pump 12 from the heat medium tank 13. Then, the circulation pump 12 sends out the heat medium, so that the heat medium flows into the primary heat exchanger 5. The heat medium heated by the combustion gas in the primary heat exchanger 5 is supplied to the high temperature terminal through the high temperature forward circuit 10a.

  Then, the operation | movement at the time of the low temperature heating of a heat source machine is demonstrated. As in the case of the high temperature heating described above, the heat medium returned from the heating terminal (low temperature terminal and high temperature terminal) flows into the secondary heat exchanger 6 through the heat medium circulation circuit 10, and in the secondary heat exchanger 6. It is heated by the combustion gas. The heat medium heated by the secondary heat exchanger 6 flows into the heat medium tank 13 and then flows into the circulation pump 12 from the heat medium tank 13. Further, the heat medium flowing from the bypass circuit 10 c also flows into the circulation pump 12. Then, the circulation pump 12 sends out the heat medium, whereby the heat medium is supplied to the low temperature terminal through the low temperature going circuit 10b.

Next, the effects of the present embodiment will be described in comparison with a comparative example.
Unless otherwise specified, the comparative example has the same configuration as that of the present embodiment described above, and therefore, the same elements are denoted by the same reference numerals and description thereof is not repeated.

  Referring to FIG. 9, in the primary heat exchanger 5 of the comparative example, the combustion gas outlet 5b is arranged to be biased toward the first body plate 51a1 as in the case of the primary heat exchanger 5 of the present embodiment. Further, in the primary heat exchanger 5 of the comparative example, the first heat transfer tube portion 52a1 and the second heat transfer tube portion 52a2 are symmetrical with respect to the symmetry axis A passing through the center of the fin 52b in the facing direction D1 in the intersecting direction D2. Has been placed. An interval X1 between the first body plate 51a1 and the first heat transfer tube portion 52a1 is equal to an interval X2 between the second body plate 51a2 and the second heat transfer tube portion 52a2.

  Therefore, as shown by the white arrow in FIG. 9, when the combustion gas flows from the combustion gas inlet 5 a toward the outlet 5 b in the case 51, the combustion gas is more first than the second body plate 51 a 2 side. Many flows on the body plate 51a1 side, and a drift of combustion gas occurs. As a result, as shown by the white arrow in FIG. 9, the combustion gas is more between the first trunk plate 51a1 and the first heat transfer tube portion 52a1 than between the second barrel plate 51a2 and the second heat transfer tube portion 52a2. A lot flows. Accordingly, the first body plate 51a1 is heated to a higher temperature than the second body plate 51a2. For this reason, a crack may occur in the first trunk plate 51a1 due to a higher thermal stress acting on the first trunk plate 51a1 than in the second trunk plate 51a2.

  On the other hand, referring to FIG. 10, according to primary heat exchanger 5 of the present embodiment, outflow port 5b is arranged to be biased toward first body plate 51a1 in opposing direction D1, and the opposing direction In D1, an interval X1 between the first body plate 51a1 and the first heat transfer tube portion 52a1 is smaller than an interval X2 between the second body plate 51a2 and the second heat transfer tube portion 52a2. Therefore, the flow resistance between the first body plate 51a1 and the first heat transfer tube portion 52a1 is larger than the flow resistance between the second body plate 51a2 and the second heat transfer tube portion 52a2. For this reason, it can suppress that combustion gas flows more between the 1st trunk | drum 51a1 and the 1st heat exchanger tube part 52a1 than between the 2nd trunk | drum 51a2 and the 2nd heat exchanger tube part 52a2. Therefore, the first body plate 51a1 can be prevented from being heated to a higher temperature than the second body plate 51a2. For this reason, it can suppress that the 1st trunk | drum 51a1 cracks by suppressing that the thermal stress higher than the 2nd trunk | drum 51a2 acts on the 1st trunk | drum 51a1.

  Further, the difference between the amount of the combustion gas flowing between the first body plate 51a1 and the first heat transfer tube portion 52a1 and the amount of the combustion gas flowing between the second body plate 51a2 and the second heat transfer tube portion 52a2 is reduced. Or can be eliminated. That is, as indicated by the white arrow in FIG. 10, the amount of combustion gas flowing between the first trunk plate 51a1 and the first heat transfer tube portion 52a1 and the second trunk plate 51a2 and the second heat transfer tube portion 52a2. It is possible to balance with the amount of combustion gas flowing into the. For this reason, the difference between the temperature rise of the first body plate 51a1 and the temperature rise of the second body plate 51a2 can be reduced or eliminated. Therefore, the difference between the thermal stress acting on the first trunk plate 51a1 and the thermal stress acting on the second trunk plate 51a2 can be reduced or eliminated. As a result, the temperature rise of the first body plate 51a1 and the second body plate 51a2 and the maximum value of the thermal stress acting on the first body plate 51a1 and the second body plate 51a2 can be reduced.

  In the primary heat exchanger 5 of the present embodiment, the pitch P1 between the first heat transfer tube portion 52a1 and the third heat transfer tube portion 52a3 is greater than the pitch P2 between the second heat transfer tube portion 52a2 and the third heat transfer tube portion 52a3. Is also big. Therefore, the first body plate 51a1 is made by making the pitch P1 between the first heat transfer tube portion 52a1 and the third heat transfer tube portion 52a3 larger than the pitch P2 between the second heat transfer tube portion 52a2 and the third heat transfer tube portion 52a3. And the first heat transfer tube portion 52a1 can be made smaller than the interval X2 between the second body plate 51a2 and the second heat transfer tube portion 52a2. Moreover, since the pipe | tube of the same dimension can be used for the 1st heat exchanger tube part 52a1, the 2nd heat exchanger tube part 52a2, and the 3rd heat exchanger tube part 52a3, the productivity of the primary heat exchanger 5 can be improved.

  In the primary heat exchanger 5 of the present embodiment, the first heat transfer tube portion 52a1 is displaced from the fourth heat transfer tube portion 52a4 in the intersecting direction D2. For this reason, it becomes easy for combustion gas to flow into the 4th heat exchanger tube part 52a4, without being intercepted by the 1st heat exchanger tube part 52a1. Therefore, the heat absorption efficiency of the fourth heat transfer tube portion 52a4 can be improved. Thereby, the heat exchange efficiency of the primary heat exchanger 5 can be improved.

  In the primary heat exchanger 5 of the present embodiment, the first heat transfer tube portion 52a1 is inserted into the first through holes H1 of the plurality of fins 52b, and the second heat transfer tube portion 52a2 is inserted into the second through holes H2. Has been. For this reason, the heat absorption efficiency of the primary heat exchanger 5 can be improved by the plurality of fins 52b. Thereby, the heat exchange efficiency of the primary heat exchanger 5 can be improved.

  In the primary heat exchanger 5 of the present embodiment, the area of the first convex portion PP1 arranged between the first through hole H1 and the first body plate 51a1 is the second through hole H2 and the second body plate. It is smaller than the area of the 2nd convex part PP2 arrange | positioned between 51a2. For this reason, it can suppress that the quantity of the combustion gas which flows between 1st trunk | drum 51a1 and 1st heat exchanger tube part 52a1 decreases too much. Thereby, the heat exchange efficiency of the primary heat exchanger 5 can be ensured.

  As shown in FIG. 1 and FIG. 2, the heat source apparatus 1 of the present embodiment includes the primary heat exchanger 5 and a burner 3 for generating combustion gas supplied to the primary heat exchanger 5. I have. According to the heat source device 1 of the present embodiment, the first body plate 51a1 of the primary heat exchanger 5 can be suppressed from being heated to a higher temperature than the second body plate 51a2.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  1 Heat source machine, 2 housing, 3 burner, 5 primary heat exchanger, 5a inlet, 5b outlet, 6 secondary heat exchanger, 7 neutralizer, 8 drain pipe, 9 drain pipe, 10 heat transfer circuit , 11 Valve, 12 Circulation pump, 13 Heat medium tank, 14 Water supply piping, 21 Screw, 22 Exhaust member, 31, 51, 61 Case, 51a1 First body plate, 51a2 Second body plate, 52, 62 Heat exchange part, 52a Multiple heat transfer tube portions, 52a1 to 52a6 1st to 6th heat transfer tube portions, 52b Multiple fins, 52b1 main surface, 53 Bend pipe, 54 Fin pipe, D1 facing direction, D2 Crossing direction, H1 to H6 1st to 6th Through-hole, P1, P2 pitch, PP1 first protrusion, PP2 second protrusion, X1, X2 spacing.

Claims (6)

A heat exchange section for exchanging heat between a heating gas flowing outside and hot water flowing inside,
A first body plate, a second body plate facing the first body plate, and a case for housing the heat exchange unit;
The heat exchange part includes a plurality of heat transfer tube parts arranged to run in parallel with each other in the case,
The plurality of heat transfer tube portions are a first heat transfer tube portion disposed closest to the first body plate among the plurality of heat transfer tube portions, and a second heat transfer tube portion of the second body plate most of the plurality of heat transfer tube portions. A second heat transfer tube portion disposed nearby,
The case includes an inlet for allowing the heating gas to flow into the case, and an outlet for allowing the heating gas to flow out of the case.
The heat exchanger is disposed between the inlet and the outlet;
The inflow port is provided between the first trunk plate and the second trunk plate in a facing direction in which the first trunk plate and the second trunk plate face each other;
The outlet is disposed in the opposite direction so as to be biased toward the first body plate,
In the facing direction, a heat exchanger in which an interval between the first body plate and the first heat transfer tube portion is smaller than an interval between the second body plate and the second heat transfer tube portion. The heat exchange unit includes a third heat transfer tube unit disposed between the first heat transfer tube unit and the second heat transfer tube unit in the facing direction,
The heat exchanger according to claim 1, wherein a pitch between the first heat transfer tube portion and the third heat transfer tube portion is larger than a pitch between the second heat transfer tube portion and the third heat transfer tube portion. The heat exchange part includes a fourth heat transfer pipe part and a fifth heat transfer pipe part,
Each of the fourth heat transfer tube portion and the fifth heat transfer tube portion faces each of the first heat transfer tube portion and the second heat transfer tube portion in a crossing direction intersecting the opposing direction, and is on the outlet side. Has been placed,
In the crossing direction, the first heat transfer tube portion is arranged to be shifted with respect to the fourth heat transfer tube portion, and the second heat transfer tube portion is arranged to overlap the fifth heat transfer tube portion. The heat exchanger according to claim 1 or 2. The heat exchange unit includes a plurality of fins,
Each of the plurality of fins includes a main surface, and a first through hole and a second through hole provided in the main surface at an interval in the facing direction,
The plurality of fins are stacked and spaced from each other in the extending direction in which the first heat transfer tube portion and the second heat transfer tube portion extend.
The first heat transfer tube portion is inserted into the first through hole,
The heat exchanger according to any one of claims 1 to 3, wherein the second heat transfer tube portion is inserted into the second through hole. At least one of the plurality of fins includes a first convex portion and a second convex portion protruding from the main surface,
The first convex portion is disposed between the first through hole and the first body plate,
The second convex portion is disposed between the second through hole and the second body plate,
The heat exchanger according to claim 4, wherein an area of the first protrusion is smaller than an area of the second protrusion when the main surface is viewed from the extending direction. The heat exchanger according to any one of claims 1 to 5,
A heat source device comprising a burner for generating the heating gas supplied to the heat exchanger.

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