JP5347841B2 - Heat exchanger and hot water device provided with the same - Google Patents

Description

  The present invention relates to a heat exchanger of a type using a helical tube as a heat transfer tube, and a hot water device such as a hot water supply device provided with the heat exchanger.

  The present applicant has previously proposed the one described in Patent Document 1 as an example of a heat exchanger using a helical tube. The heat exchanger described in the document includes a casing into which combustion gas flows, and first and second spiral tubes housed in the casing and arranged in the width direction of the casing. . The first and second spiral pipes are provided with a plurality of extended pipe parts that are partially protruded outside the casing, and the first and second helical pipes are connected to each other by using the plurality of extended pipe parts. In addition, water can be individually passed through the second helical tube. The casing has two air supply ports for individually supplying combustion gas to the first and second spiral tubes, and combustion in which heat recovery is completed by the first and second spiral tubes Two exhaust ports for discharging the gas to the outside of the casing are provided.

  According to such a configuration, it is possible to perform hot water heating using either one of the first and second helical tubes individually or using both at the same time. While using the hot water produced | generated using for a general hot water supply, the hot water produced | generated using the 2nd helical tube can be utilized for a heating use. Moreover, in patent document 1, the part which the 1st and 2nd spiral tube body mutually approached is made to overlap in the up-down height direction of a casing. For this reason, there is also an advantage that the ratio of the heat transfer area of the first and second spiral tubular bodies can be easily changed while suppressing the enlargement of the casing by changing the degree of overlap. can get.

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

  That is, each of the first and second spiral tubular bodies has a configuration in which a plurality of loop portions formed in a substantially oval shape are connected in series, and the first spiral tubular body includes each loop. The longitudinal direction of the portion is provided so as to coincide with the lateral width direction of the casing. Similarly, the second spiral tubular body is also provided so that the longitudinal direction of each loop portion coincides with the lateral width direction of the casing. According to such a configuration, the overall size of the first and second spiral tubular bodies in the lateral width direction of the casing is increased, and accordingly, the lateral width dimension of the casing is also increased. In this type of heat exchanger used in a hot water supply device or the like, it is often required to reduce the overall lateral width as much as possible to reduce the overall size. There may be cases where it is difficult to accurately respond to requests, and there is room for improvement in this regard.

JP 2009-19859 A

  The present invention has been conceived under the circumstances as described above, and when the first and second helical tubes for heat exchange are arranged side by side in the casing, enlargement of the casing is minimized. It is an object of the present invention to provide a heat exchanger that can be suitably reduced in size by avoiding it, and a hot water device including the heat exchanger.

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

  The heat exchanger provided by the first aspect of the present invention includes a casing having a heating gas supply port and an exhaust port, and a heat exchange unit housed in the casing and arranged in the width direction of the casing. Each of the first and second spiral tubes, each of the first and second spiral tubes being connected to the casing by a plurality of loop portions having different vertical and horizontal widths. A heat exchanger in which the width in the longitudinal direction of the first spiral tube is equal to or greater than the width in the longitudinal direction of the second spiral tube. The first spiral tube body is set so that its longitudinal direction is the lateral width direction of the casing, while the second spiral tube body has its longitudinal direction before and after the casing. It is set to be in the depth direction. To have.

  According to such a configuration, the first and second helical tubes are compared with the prior art in which the longitudinal directions of the first and second helical tubes are both set in the lateral width direction of the casing. The total width in the longitudinal direction of the body can be reduced. The longitudinal direction of the second spiral tube is set in the longitudinal direction of the casing. The width of the second spiral tube in the longitudinal direction is the length of the first spiral tube. Since the width is equal to or less than the width in the direction, the second spiral tubular body is also prevented from being bulky in the depth direction of the casing. For this reason, the casing that accommodates the first and second helical tubes, and hence the heat exchanger as a whole is preferably reduced in size.

  In a preferred embodiment of the present invention, the width in the short direction of the first spiral tube and the width in the longitudinal direction of the second spiral tube are substantially equal to each other. At the same time, the vertical heights of the first and second spiral tubular bodies are also substantially equal.

  According to such a configuration, the first and second spiral shapes also in the vertical height direction of the casing while the widths of the first and second spiral tubes do not greatly differ in the longitudinal direction of the casing. It is possible to prevent a large height difference from occurring in the tube body. Therefore, it is preferable to prevent a wasteful space from being largely formed in the casing and to reduce the size of the heat exchanger.

  In a preferred embodiment of the present invention, upper and lower extending tube portions are connected to the loop portions located at the uppermost and lowermost stages of the first and second helical tubes, respectively. The extending tube portion connected to the first spiral tube body extends in the longitudinal direction of the first spiral tube body, thereby penetrating one side wall portion of the casing. Then, a part of the casing is exposed to the outside of the casing, and the extending tube portion connected to the second spiral tube extends in the short direction of the second spiral tube. Accordingly, a part of the casing is exposed outside through the other side wall of the casing.

  According to such a configuration, water can be passed from both sides of the casing to the first and second spiral tubular bodies by using the extended tubular body portion, and piping for passing water is easy. It can be.

  In a preferred embodiment of the present invention, the bottom wall portion of the casing has a drain outlet located near the front portion of the bottom wall portion, and drains from the first and second spiral tubes. The first and second helical tubes are inclined downwardly so that the drain can be led to the drain outlet when the water drops are dropped. Is provided so as to be positioned closer to the front portion of the casing than the upper extending tubular portion, and the spiral winding directions of the first and second helical tubular bodies are different from each other, and One of the second helical tubes located on the left side in the plan view and the front view has a left-handed winding direction when proceeding from below to above, and the other when proceeding from below to above. The winding direction of There.

  According to such a configuration, the lowermost loop portion of each of the first and second spiral tubular bodies is disposed higher in the rear portion than in the front portion. It becomes along the inclination of the bottom wall part of front-falling shape. For this reason, it becomes suitable for making small the clearance gap between the loop part of the lowest step, and the bottom wall part of a casing.

  In a preferred embodiment of the present invention, as the first and second spiral tubes, a pair of straight tube portions in which each loop portion is substantially parallel and the ends of the pair of straight tube portions are connected to each other. A plurality of first and second helical tubes formed in a substantially oval shape having a pair of substantially semicircular arch-shaped bent tube portions, wherein the plurality of first helical tubes are The sizes of these loop portions are different from each other and are substantially concentric, and the plurality of second spiral tubular bodies are also different from each other in size and are substantially concentric. The plurality of second spiral tubular bodies are all or part of the plurality of first spiral tubular bodies, and the curvature radius of the curved pipe portion is all or part of the plurality of first spiral tubular bodies. They are aligned to the same dimensions.

  According to such a configuration, since each of the first and second helical tubes is provided in a plurality, it is possible to increase the heat transfer area of the whole and increase the heat exchange efficiency. In addition, as will be described below, the production of a plurality of first and second helical tubes is also facilitated. That is, the first and second helical tubes can be manufactured by bending a straight pipe, but the radius of curvature of the bent tube portion of the second helical tube is the first. If it is the same as the curvature radius of the curved pipe part of this spiral pipe body, the bending process of the straight pipe at the time of forming these curved pipe parts may be the same process. For this reason, according to the above configuration, the pipes are bent in common when the first and second helical tubes are manufactured, and the manufacturing work is facilitated and the cost is reduced. be able to.

  The hot water apparatus provided by the second aspect of the present invention includes a heating gas supply means, a heat exchanger for performing hot water heating using the heating gas supplied from the heating gas supply means, It is characterized by using the heat exchanger provided by the 1st side surface of the present invention as the heat exchanger.

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

  In a preferred embodiment of the present invention, a fan and first and second combustors that are supplied with combustion air supplied from the fan and generate combustion gas as the heating gas are provided. And the inside of the casing is partitioned into first and second space portions that individually accommodate the first and second spiral tubes, and the air supply port includes the first and second air supply ports. Two air supply ports for individually supplying combustion gas to the two space portions are provided, and the exhaust ports flow into the first and second space portions and flow into the first and second space portions. There is provided only one exhaust port through which the combustion gas whose heat has been recovered by the two helical tubes can be exhausted to the outside of the casing, and the fan is provided through the two air supply ports. Of the first and second spaces Flow rate of the combustion gas flowing into the respectively is configured to correspond to the opening area ratio of the two air inlets.

  According to such a configuration, the flow rate ratio of the combustion gas acting on each of the first and second helical tubes can be set to a desired value by setting the ratio of the opening areas of the two air supply ports to an appropriate ratio. It is possible to set to a desirable ratio. Therefore, it is easy to control the flow rate of the combustion gas even though the one-fan method is adopted.

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

It is a schematic front sectional view showing an example of a hot water device to which the present invention is applied. It is a plane sectional view of the secondary heat exchanger with which the warm water system shown in Drawing 1 was equipped. FIG. 3 is a sectional view taken along line III-III in FIG. 2. It is IV-IV sectional drawing of FIG. (A), (b) is principal part plane sectional drawing which shows the other example of the heat exchanger to which this invention was applied. It is a schematic plan view which shows the other example of the helical tube used for the heat exchanger to which this invention was applied.

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

  1 to 4 show an example of a hot water apparatus to which the present invention is applied. As clearly shown in FIG. 1, the hot water apparatus WH of the present embodiment includes two combustors 3a and 3b, two primary heat exchangers 1a and 1b, and a secondary heat exchanger HE. . The secondary heat exchanger HE corresponds to an example of a heat exchanger to which the present invention is applied.

  The combustors 3a and 3b correspond to an example of the heating gas supply means in the present invention, and are gas burners or oil burners that generate combustion gas as the heating gas. These combustors 3 a and 3 b are separately provided in space portions 30 a and 30 b partitioned by a partition wall 32 in the can 30. In this hot water device WH, a one-fan system is adopted, and a fan 31 is provided at the lower portion of the can 30. A perforated plate 33 is provided at the bottom or below the combustors 3a and 3b, and the combustion air supplied from the fan 31 is supplied to the combustors 3a and 3b by a fuel / air supply port (not shown). From the lower side of the perforated plate 33 and flows into the spaces 30a and 30b. The primary heat exchangers 1a and 1b are for recovering sensible heat from the combustion gas generated by the combustors 3a and 3b. For example, the heat transfer tubes 11a and 11b having a plurality of fins 12 are provided in the space 30a, It is the structure provided in 30b.

  The secondary heat exchanger HE is for recovering latent heat from the combustion gas after sensible heat has been recovered by the primary heat exchangers 1a and 1b, and is disposed above the primary heat exchangers 1a and 1b. Has been. The secondary heat exchanger HE includes a hollow substantially rectangular parallelepiped casing 7, a plurality of first and second spiral tubes 4 and 5 accommodated in the casing 7, and a plurality of upper and lower ends connected to the upper and lower ends. It has the extended pipe parts 6a to 6d and the headers 68a to 68d for water flow.

  The first helical tube 4 corresponds to the primary heat exchanger 1a and the combustor 3a, which are for heating hot water for general hot water supply to a kitchen or a washroom, for example. On the other hand, the second helical tube 5 corresponds to the primary heat exchanger 1b and the combustor 3b, and these are for heating hot water (including antifreeze) for floor heating, for example. is there. The hot water heating means for general hot water supply needs to have higher hot water heating capacity than the hot water heating means for floor heating. For this reason, the combustor 3a has more maximum heat generation than the combustor 3b. The primary heat exchanger 1 a and the first spiral tube 4 have a larger heat transfer area than the primary heat exchanger 1 b and the second spiral tube 5. The header 68a is connected to the inlet 13a of the primary heat exchanger 1a via an appropriate pipe 99a. Similarly, the header 68c is connected to the inlet 13b of the primary heat exchanger 1b via the pipe 99b. It is connected to the. Thus, the water supplied to the header 68b is circulated through the first spiral tubular body 4 and heated, and then sent to the primary heat exchanger 1a to be further heated and discharged from the hot water outlet 14a. To do. The water (antifreeze) supplied to the header 68d flows through the second spiral tubular body 5 and is heated, and then sent to the primary heat exchanger 1b to be further heated and discharged from the hot water outlet 14b. .

  The plurality of first and second helical tubes 4 and 5 are both accommodated in the casing 7 and are arranged in the lateral width direction (the left-right direction in FIG. 1) of the casing 7. The first and second helical tubes 4 and 5 are partitioned by a partition plate 79, and the inside of the casing 7 is partitioned into first and second space portions 77a and 77b by the partition plate 79. Yes. As shown in FIGS. 2 to 4, in the bottom wall portion 70 a of the casing 7, on the rear side (the rear wall portion 70 c side of the casing 7) from the first and second spiral tubular bodies 4 and 5, Two supply ports 71a and 71b for the combustion gas communicating with the first and second space portions 77a and 77b are provided. The front wall portion 70b of the casing 7 is provided with one exhaust port 72 that communicates with both the first and second space portions 77a and 77b. The combustion gas that has passed through the primary heat exchangers 1a and 1b individually flows into the first and second space portions 77a and 77b in the casing 7 from the air supply ports 71a and 71b, whereby the first spiral shape is obtained. A gap 49 between the loop portions 40 described later of the tubular body 4 or a gap 59 between the loop portions 50 of the second spiral tubular body 5 passes from the rear side to the front side of the casing 7 to heat these portions. Thereafter, the gas is discharged from the exhaust port 72 to the outside of the casing 7. In the hot water device WH, the flow rate ratio of the combustion gas acting on the first and second helical tubes 4 and 5 is defined by the ratio of the opening areas Aa and Ab of the two air supply ports 71a and 71b. The details will be described later.

  As shown in FIG. 2, a drain outlet 78 is provided at a position near the front portion of the bottom wall portion 70 a of the casing 7. As shown in FIGS. 3 and 4, the bottom wall portion 70 a has a front downward shape. As a result, when the drain (condensed water) generated along with the recovery of latent heat from the combustion gas drops on the bottom wall 70a, the drain flows closer to the front of the bottom wall 70a and flows into the discharge port 78. And discharged outside the casing 7. Standing walls 73a and 73b that are erected upward are provided at the peripheral portions of the two air supply ports 71a and 71b in the bottom wall portion 70a. These standing walls 73a and 73b serve to prevent the drain on the bottom wall portion 70a from flowing into the air supply ports 71a and 71b.

  The plurality of first and second helical tubes 4 and 5 are manufactured by bending a metal round pipe material such as stainless steel. As clearly shown in FIG. 2, each first spiral tubular body 4 includes a plurality of loop portions 40 having a substantially oval shape in plan view and a gap 49 (see FIGS. 1 and 3). ) In the vertical direction of the casing 7. The plurality of loop portions 40 include a pair of substantially parallel straight tube portions 40a (portions indicated by reference symbol Sa) and a pair of these except for the uppermost step and the lowermost step where the extended tube portions 6a and 6b are connected. It has a pair of semicircular arch-shaped curved pipe parts 40b which connect the end parts of the straight pipe part 40a. However, the plurality of first spiral tubular bodies 4 are different from each other in the size of the loop portion 40 and are arranged in a substantially concentric wrapping shape. Each first spiral tubular body 4 is set such that the longitudinal direction of each loop portion 40 (in the present embodiment, the direction in which each straight tube portion 40a extends) is the lateral width direction of the casing 7. ing.

  The plurality of second spiral tubular bodies 5 have many basic configurations in common with the plurality of first spiral tubular bodies 4 described above, and a plurality of loop portions 50 that are substantially oval in plan view. Are connected in series and stacked in the vertical height direction of the casing 7 with a gap 59 interposed therebetween. Further, the plurality of loop portions 50 are arranged in a substantially concentric lap winding shape. Each loop part 50 is a half connecting a pair of substantially parallel straight pipe parts 50a (parts in a range indicated by reference numeral Sb) and end parts of the pair of straight pipe parts 50a except for the uppermost and lowermost stages. And a pair of circular arch-shaped curved pipe portions 50b. However, the direction of the plurality of second spiral tubes 5 is different from the direction of each first spiral tube 4, and the longitudinal direction of each loop portion 50 (the direction in which each straight tube portion 50 a extends) is different. The casing 7 is set to be in the front-rear depth direction. The longitudinal width L1 of the plurality of first spiral tubular bodies 4 as a whole, the longitudinal width L3 of the plurality of second spiral tubular bodies 5 as a whole, and the lateral width L4 are L1> L3> L4. Are in a relationship. It should be noted that the present invention can also be applied when L1 = L3. Further, the above-described width L3 is aligned with the same dimension as the width L2 in the short direction of the plurality of first spiral tubular bodies 4 as a whole. Furthermore, as shown in FIG. 1, the vertical heights H1 and H2 of the plurality of first and second spiral tubular bodies 4 and 5 as a whole are also made substantially the same size.

  As described above, the plurality of first and second spiral tubes 4 and 5 are different in overall size, but pipe materials having the same outer diameter are used as the raw materials thereof. It has been. In addition, the curvature radius of each of the curved pipe portions 50b of the plurality of second spiral tubular bodies 5 is aligned with the same radius as the curvature radius of any one of the curved pipe portions 40b of the plurality of first spiral tubular bodies 4. It has been. More specifically, FIG. 2 shows a configuration in which a total of six first spiral tubes 4 and a total of four second spiral tubes 5 are provided. The radii of curvature R1 to R4 of the curved pipe portions 50b of the four second spiral tubular bodies 5 are, for example, the curvatures of the four first spiral tubular bodies 4 positioned closer to the inner periphery of the total six. The radius of curvature R1 to R4 of the pipe portion 40b is the same. According to such a configuration, when the pipe material is bent to form the bent tube portion 50b of the second spiral tube body 5, the bent tube portion 40b of the first spiral tube body 4 is formed. It is only necessary to execute the same processing as the bending processing at the time. Therefore, it is possible to easily manufacture the first and second helical tubes 4 and 5 and to obtain an advantage that the cost can be reduced.

  The extending tube portions 6a and 6b connected to the upper end and the lower end of the first spiral tube 4 extend in the longitudinal direction of the first spiral tube 4 and pass through one side wall portion 70d of the casing 7, It protrudes to one side. On the other hand, the extended tube portions 6c and 6d connected to the upper end and the lower end of the second spiral tube 5 extend in the short direction of the second spiral tube 5 and the other side wall portion of the casing 7. It penetrates 70e and protrudes to one side. Accordingly, the headers 68 a to 68 d for water flow attached to the extending tube portions 6 a to 6 d are arranged on both sides of the casing 7. Such a configuration is preferable for facilitating the connection work of water pipes (pipes 99a, 99b, etc.) to the headers 68a to 68d.

  The lower extending tube portions 6b and 6d are located closer to the front portion of the casing 7 than the upper extending tube portions 6a and 6c. The spiral winding directions of the first and second spiral tubular bodies 4 and 5 are opposite to each other. More specifically, each first spiral tube 4 has a right-handed winding direction when viewed from above, whereas each second spiral tube 5 The winding direction when proceeding from below to above is left-handed in plan view. According to such a configuration, as shown in FIG. 3, the rear side (the portion indicated by reference numeral n1) of the lowermost loop portion 40 ′ of the first helical tube 4 is the lower extended tube. The arrangement is higher than the front side (portion indicated by reference numeral n2) of the portion 6b and the loop portion 40 ′, and such a height difference corresponds to the forward downward inclination of the bottom wall portion 70a. Therefore, it is suitable for reducing the gap between the lowermost loop portion 40 ′ and the bottom wall portion 70 a of the first spiral tubular body 4. Such an effect is the same also about the 2nd spiral tube 5, and as shown in Drawing 4, lowermost loop part 50 'of 2nd spiral tube 5 is made from front side n2'. Also, the rear side n1 ′ can be arranged higher, and the gap between the loop portion 50 ′ and the bottom wall portion 70a can be reduced.

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

  First, in the casing 7, the first and second spiral tubes 4, 5 are provided side by side in the width direction of the casing 7, and the first spiral tube 4 has a longitudinal direction in the casing. 7, the second spiral tubular body 5 has a lateral direction of the casing 7 as its short direction. Therefore, when compared with a configuration in which the longitudinal directions of the first and second helical tubes 4 and 5 are both set in the lateral width direction of the casing 7 (configuration corresponding to the prior art), the first and second spirals are compared. It is possible to suppress the overall lateral width of the tubular tubes 4 and 5 from being large and bulky. For this reason, it becomes a preferable thing for reducing the width of the casing 7 and reducing its size.

  Since the width L3 in the longitudinal direction of the second spiral tube 5 is substantially the same as the width L2 in the short direction of the first spiral tube 5, the first and second spiral tubes 4 are arranged. , 5 can be avoided from projecting in the front-rear depth direction of the casing 7 relative to the other. For this reason, it is possible to suppress a large useless space having a large width in the front-rear depth direction in the casing 7. Furthermore, since the vertical heights H1 and H2 of the first and second spiral tubular bodies 4 and 5 are also substantially the same size, there is a large waste space in the vertical height direction in the casing 7. Can be suppressed. For this reason, it is possible to further promote the downsizing of the casing 7 and the downsizing of the entire secondary heat exchanger HE. In the present embodiment, as described above, the first and second spiral tubes 4 and 5 are set in predetermined directions opposite to each other by setting the spiral winding directions of the first and second spiral tubes 4 and 5 to each other. Although it is possible to reduce the gap between the lowermost loop portions 40 ′ and 50 ′ of the spiral tubes 4 and 5 and the bottom wall portion 70 a of the casing 7, such a configuration is also useless in the casing 7. This is useful for eliminating the space and reducing the overall size of the casing 7.

  In the hot water apparatus WH, sensible heat is recovered from the combustion gas generated by the combustor 3a by the primary heat exchanger 1a, and then latent heat is generated by the first spiral tube 4 of the secondary heat exchanger HE. Can be recovered. Similarly, sensible heat and latent heat can be recovered from the combustion gas generated by the combustor 3b by the second helical tube 5 of the primary heat exchanger 1b and the secondary heat exchanger HE. Therefore, by such heat recovery, for example, two types of hot water heating for floor heating and general hot water supply can be efficiently performed individually or simultaneously.

  When hot water is heated as described above, the air blown from the fan 31 is a first path that reaches the exhaust port 72 through the space 30a, the air supply port 71a, and the first space 77a in the can 3. And the second path that reaches the exhaust port 72 through the space 30b, the air supply port 71b, and the second space 77b in the can 3. In such a blowing method, the ratio of the blowing amount to the first and second paths can be defined by the ratio of the opening areas Aa and Ab of the air supply ports 71a and 71b. In this case, by setting the opening areas Aa and Ab to a predetermined ratio, the air flow rate and the combustion gas flow rate in the first and second paths are made preferable. The optimum values of the opening areas Aa and Ab can be easily obtained by conducting an experiment, for example, and the design and production of the hot water device WH can be facilitated.

  The two air supply ports 71a and 71b are preferably dimensioned so that their lateral widths La and Lb are as close as possible to the widths L1 and L4 of the first and second helical tubes 4 and 5, respectively. Combustion gas is configured to act efficiently over substantially the entire area of each of the two helical tubes 4 and 5. Therefore, when changing the ratio of the opening areas Aa and Ab, preferably, the horizontal widths La and Lb of the air supply ports 71a and 71b are not changed, and the vertical widths Lc and Ld are changed. As a specific example, in FIG. 2, the vertical widths Lc and Ld are set to substantially the same dimensions. However, when the flow rate of the combustion gas to the second space 77b is reduced more than this case, As shown in FIG. 5A, the vertical width Ld of the air supply port 71b is made smaller than the vertical width Lc of the air supply port 71a. On the other hand, when increasing the flow rate of the combustion gas to the second space 77b, the vertical width Ld is made larger than the vertical width Lc, for example, as shown in FIG.

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

  The shape of the loop portion of the first and second spiral tubular bodies is not limited to an oval shape. In the plurality of spiral tubular bodies 4A shown in FIG. 6, each loop portion 40 is formed in a substantially long rectangular shape, but the first and second spiral tubular bodies referred to in the present invention have such a form. You can also The loop portions of the first and second spiral tubes need only have shapes with different vertical and horizontal widths, and may be elliptical or oblong, as well as elliptical. Furthermore, the intermediate portion in the longitudinal direction of the loop portion may not be configured as a pair of straight tube portions that are substantially parallel to each other, and instead of the pair of straight tube portions, a bent or curved tube portion. It can also be set as the structure where was used.

  The casing only needs to accommodate the first and second spiral tubular bodies, and a heating gas such as combustion gas flows into the casing, and the specific shape and size thereof are not limited. The air supply port may be configured to be provided in the rear wall portion of the casing, or may be configured to have two exhaust ports corresponding to the air supply ports. The heat exchanger according to the present invention may be of any type for sensible heat recovery and latent heat recovery. The heat exchanger according to the present invention can also be used for sensible heat recovery. The hot water apparatus shown in FIG. 1 is a “single can type” in which a combustor and a primary heat exchanger are accommodated in one can body partitioned by a partition plate, but they are accommodated in separate can bodies. It can also be a “two can type”. Moreover, although the hot water apparatus shown in FIG. 1 is a 1 fan system, it can also be a 2 fan system. The hot water device as used in the present invention means a device having a function of generating hot water, and is used for various types of hot water supply devices for general hot water supply, bath hot water supply, heating, snow melting, and the like, and hot water supply. It is a concept that includes a wide range of equipment for producing hot water. As the heating gas, for example, exhaust gas from a gas engine for cogeneration or a fuel cell can be used other than the combustion gas.

Claims (7)

A casing having an inlet and an outlet for a heating gas;
First and second helical tubes for heat exchange accommodated in the casing and arranged in the width direction of the casing, and
Each of the first and second helical tubes has a configuration in which a plurality of loop portions having different vertical and horizontal widths are connected in series and stacked in the vertical height direction of the casing,
A heat exchanger in which a longitudinal width of the first spiral tubular body is equal to or greater than a longitudinal width of the second spiral tubular body,
The first spiral tubular body is set so that its longitudinal direction is in the lateral width direction of the casing, while the second spiral tubular body is longitudinal in the longitudinal direction of the casing. A heat exchanger characterized by being set to be. The width in the short direction of the first spiral tubular body and the width in the longitudinal direction of the second spiral tubular body are aligned to substantially the same dimension,
2. The heat exchanger according to claim 1, wherein the vertical heights of the first and second spiral tubular bodies are also substantially equal to each other. The upper and lower extending tube portions are connected to the loop portions located at the uppermost and lowermost stages of the first and second helical tubes,
The extending tube portion connected to the first spiral tube body extends in the longitudinal direction of the first spiral tube body, thereby penetrating one side wall portion of the casing. A part of it is exposed outside,
The extending tube portion connected to the second helical tube extends in the short direction of the second helical tube, thereby penetrating the other side wall portion of the casing. The heat exchanger according to claim 1 or 2, wherein a part is exposed to the outside of the casing. The bottom wall of the casing has a drain outlet located near the front of the bottom wall, and when the drain drops from the first and second helical tubes, the drain is drained from the drain. It is inclined in a front-down direction that can be led to the discharge outlet for
The first and second helical tubes are both provided such that the lower extending tube portion is positioned closer to the front of the casing than the upper extending tube portion,
The spiral winding directions of the first and second helical tubes are different from each other, and one of the first and second helical tubes located on the left side in plan view and front view is The heat exchanger according to claim 3, wherein the winding direction when proceeding from below to above is left-handed when viewed from above, and the other winding direction when traveling from below to above is right-handed when viewed from above. As the first and second spiral tubular bodies, a pair of substantially semicircular arch-shaped curved pipes connecting a pair of straight tubular sections in which the loop portions are substantially parallel and ends of the pair of straight tubular sections. A plurality of first and second helical tubes formed in a substantially oval shape having a portion,
The plurality of first helical tubes are substantially concentrically wound with different sizes of the loop portions, and the plurality of second helical tubes are also formed of these loops. The sizes of the parts are different from each other and are substantially concentric overwrapping,
All or a part of the plurality of second spiral tubular bodies has the same or same radius of curvature of the curved pipe portion as the whole or a part of the plurality of first spiral tubular bodies. The heat exchanger according to any one of claims 1 to 4. A hot water apparatus comprising: a heating gas supply means; and a heat exchanger for performing hot water heating using the heating gas supplied from the heating gas supply means,
A hot water apparatus, wherein the heat exchanger according to any one of claims 1 to 5 is used as the heat exchanger. A fan, and combustion air supplied from the fan is distributed and supplied, and first and second combustors for generating combustion gas as the heating gas are provided,
The interior of the casing is partitioned into first and second space portions that individually accommodate the first and second helical tubes,
As the air supply port, there are provided two air supply ports for individually supplying combustion gas to the first and second space portions,
As the exhaust port, it is possible to discharge the combustion gas that has flowed into the first and second space portions and has been heat-recovered by the first and second helical tubes to the outside of the casing. There is only one exhaust port,
The flow rate ratio of the combustion gas flowing from the fan into the first and second space portions via the two air supply ports is configured to correspond to the opening area ratio of the two air supply ports. The hot water device according to claim 6.

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