JP2010032200A - Water heater - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a water heater capable of properly recovering drain generated in a secondary heat exchanger and introducing it to a neutralizer. <P>SOLUTION: The water heater 1 includes the secondary heat exchanger 30 in an exhaust part 6, and a receiving part 40 in a position above an inlet 6e for introducing combustion gas into the exhaust part 6 from an exhaust collecting part 5 below the secondary heat exchanger 30. The water heater 1 can prevent infiltration of the drain generated by the secondary heat exchanger 30 into a side of the exhaust collecting part 5 by the receiving part 40. A scattering preventing part 60 is provided in a position below an exhaust port 6d above the secondary heat exchanger 30. The water heater 1 can prevent scattering of the drain to the outside via the exhaust port 6d by the scattering preventing part 60. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a hot water supply device, and more particularly to a device provided with a secondary heat exchanger in addition to a primary heat exchanger.

  Conventionally, a so-called latent heat recovery type hot water supply apparatus as disclosed in Patent Documents 1 and 2 below has been provided. This type of hot water supply apparatus includes a combustion means for burning fuel, a primary heat exchanger for mainly recovering sensible heat contained in the combustion gas generated therein, and a second for recovering mainly latent heat. And a secondary heat exchanger.

JP 2006-207902 A JP 2006-275367 A

  In the above-described latent heat recovery type hot water supply apparatus, the heat efficiency is improved by recovering the latent heat in the secondary heat exchanger, but further improvement in the heat efficiency has been demanded. Further, in the above-described latent heat recovery type hot water supply apparatus, drain is generated along with heat exchange in the secondary heat exchanger. When this drain is exposed to the combustion gas, the acidity becomes high and the liquid becomes corrosive. After the drain having increased acidity in this way falls from the secondary heat exchanger, if it unexpectedly flows into the region where the high-temperature combustion gas flows, it is further condensed to improve the acidity, There was a problem that the corrosivity increased. Accordingly, there has been a demand for preventing the drain generated in the secondary heat exchanger from flowing into an unexpected region provided upstream in the flow direction of the combustion gas. Moreover, when drainage with high acidity leaks to the outside from the exhaust port, there is a possibility that it corrodes not only inside the hot water supply apparatus but also outside. Therefore, in the conventional hot water supply apparatus, there has been a problem of how to prevent the leakage of the drain generated in the secondary heat exchanger and introduce it into the neutralizer provided for neutralizing the drain.

  Then, in order to solve such a problem, the present invention has an object of providing a hot water supply apparatus that can appropriately recover the drain generated in the secondary heat exchanger and introduce it into the neutralizer.

  The hot water supply apparatus of the present invention provided to solve the above-described problems includes a combustion means for burning fuel, a combustion gas passage through which combustion gas generated in accordance with a combustion operation in the combustion means flows downward, An exhaust collecting portion that exists downstream in the flow direction of the combustion gas with respect to the combustion gas passage, accepts and passes the combustion gas that has passed through the combustion gas passage, and changes the flow direction upward; and the exhaust collecting portion Heat exchange between an exhaust part that receives and passes the combustion gas sent from the exhaust gas, flows upward and exhausts, an inlet that allows the combustion gas to flow into the exhaust part, and the combustion gas that flows through the combustion gas passage A primary heat exchanger capable of heating hot and cold water, a secondary heat exchanger disposed downstream of the primary heat exchanger in the flow direction of the combustion gas, and heat exchange in the secondary heat exchanger Occur A neutralizer that can neutralize the drain, and a receiving portion that is provided above the inlet and below the secondary heat exchanger and that receives the drain falling from the secondary heat exchanger And a drain discharge system that bypasses the drain that has fallen to the receiving part and bypasses the exhaust collecting part provided at the lower part of the exhaust part and leads directly to the neutralizer. (Claim 1).

  In the hot water supply apparatus of the present invention, a secondary heat exchanger is provided in the exhaust part, and a receiving part is provided at a position below this and above the inlet of the combustion gas with respect to the exhaust part. Moreover, in the hot water supply device of the present invention, the drain that has fallen to the receiving portion can be bypassed the introduction port and guided to the neutralizer through the drain discharge system. Therefore, in the hot water supply apparatus of the present invention, it is possible to prevent drain generated due to heat exchange in the secondary heat exchanger from entering the high temperature region upstream of the exhaust part through the inlet, Can be reliably neutralized.

  The hot water supply device of the present invention is a ridge line portion formed between a plurality of wind receiving surfaces intersecting the flow direction of the combustion gas introduced into the exhaust portion from the inlet and the adjacent wind receiving surfaces. It is desirable that the ridge portion protrudes toward the upstream side in the flow direction of the combustion gas.

  According to such a configuration, even when the receiving part is provided in the exhaust part, it is possible to prevent the ventilation resistance of the combustion gas flowing into the exhaust part from becoming excessively large.

  In the hot water supply apparatus of the present invention, the receiving part has a planar wind receiving surface that intersects with the flow direction of the combustion gas introduced from the inlet to the exhaust part, and a notch, and the wind receiving surface Is located on the wall surface side of the exhaust part, and it is desirable that the wind receiving surface be inclined downward toward the notch part (Claim 3).

  In the case of such a configuration, the receiving portion is arranged to be inclined toward the notch portion, so that drain can be discharged efficiently. Furthermore, this inclination can prevent the ventilation resistance of the combustion gas flowing into the exhaust part from becoming excessively large. In addition, since the receiving portion is planar, almost no processing is required and the production efficiency does not decrease.

  In the hot water supply apparatus of the present invention, the exhaust part has an exhaust port through which combustion gas can be discharged, and is located below the exhaust port and in a region above the secondary heat exchanger. It is possible to provide scattering prevention means capable of preventing the scattering of drain from the side to the exhaust port side.

  According to such a configuration, it is possible to prevent the drain generated in the secondary heat exchanger from leaking outside through the exhaust port on the flow of the combustion gas passing through the exhaust section.

  In the hot water supply apparatus of the present invention, the scattering prevention means includes a plurality of intersecting surfaces intersecting the flow direction of the combustion gas introduced from the introduction port to the exhaust portion, and a ridge line portion formed between the adjacent intersecting surfaces. It is desirable that the ridge portion protrudes toward the upstream side in the flow direction of the combustion gas.

  According to such a configuration, it is possible to prevent excessive increase in the ventilation resistance (exhaust resistance) of the combustion gas discharged from the exhaust part while preventing the drain from leaking from the exhaust part.

  In the hot water supply apparatus of the present invention, the scattering prevention means has a planar intersection surface that intersects the flow direction of the combustion gas introduced from the inlet to the exhaust portion, and the intersection surface is the flow direction of the combustion gas. It is desirable that it be inclined with respect to a plane orthogonal to the above (claim 6).

  According to such a configuration, it is possible to prevent the drain from leaking to the outside from the exhaust part by the scattering prevention means. Further, since the intersecting plane is inclined with respect to a plane perpendicular to the flow direction of the combustion gas, the ventilation resistance (exhaust resistance) of the combustion gas discharged from the exhaust part is reduced, and the exhaust resistance is excessively increased. It can be prevented from becoming large.

  In the hot water supply apparatus of the present invention, a drain discharge port capable of discharging drain is provided in the exhaust part, a neutralizer is provided below the exhaust part, and a drain discharge system is connected to the drain discharge port. It is desirable that the neutralizer is formed by pipe connection.

  In such a configuration, since the drain flows downward through the drain discharge system, the drain can smoothly flow toward the neutralizer.

  In the hot water supply apparatus of the present invention, a tray portion for receiving drain to be discharged is provided inside the exhaust portion, the introduction port is provided in the tray portion, and an opening edge of the introduction port faces the receiving portion. It is desirable that an upright weir is provided (claim 8).

  In such a configuration, the drain to be discharged generated in the exhaust part flows and is discharged to the tray part, and thus can be discharged smoothly. In addition, since the weir part is erected toward the receiving part at the opening edge of the inlet port provided in the saucer part, the drain received by the saucer part is exhausted through the inlet port because the weir part becomes an obstacle. It does not flow into the exhaust collecting part or the like located at the lower part of the part.

  In the hot water supply apparatus of the present invention, the secondary heat exchanger has a plurality of heat receiving pipes arranged in the exhaust part, a water inlet header, and a water outlet header, and the water inlet header and the water outlet header On the other hand, a plurality of heat receiving tubes may be connected to each other (claim 9).

  Further, in the hot water supply apparatus of the present invention, the heat receiving pipe is turned up so as to connect between the plurality of crossing parts traversing the inside of the exhaust part and the crossing parts located on the upstream side and the downstream side in the hot water flow direction. And a flow of hot water that has been supplied from the upstream crossing portion at the folding portion and can be supplied to the downstream crossing portion (claim 10).

  According to this configuration, it is possible to secure a sufficiently large heat transfer area for heat exchange while downsizing the secondary heat exchanger.

  In the hot water supply apparatus of the present invention, a planar partition plate is provided below one or more of the plurality of crossing portions arranged vertically in the exhaust portion, and the partition plate is provided with a notch. The notch portion may be disposed on the wall surface side of the exhaust portion, and the partition plate may be disposed with a downward slope toward the notch portion side (claim 11).

  According to such a configuration, the partition plate increases the airflow resistance in the exhaust part, and the residence time of the combustion gas flowing into the exhaust part can be extended. Therefore, the heat exchange efficiency between the combustion gas and hot water flowing through the heat receiving pipe is improved. improves. Further, since the partition plate is provided with a notch portion, the drain that has fallen along the heat receiving pipe can be discharged through the notch portion. In addition, since the partition plate is arranged with a downward slope toward the notch portion side, the drain can flow downward through the notch portion.

  In the hot water supply apparatus of the present invention, a plurality of heat receiving tubes are arranged in the horizontal direction in the exhaust part, and one heat receiving tube of the plurality of heat receiving tubes and another receiving tube adjacent to the one heat receiving tube. The space | interval with a heat pipe may spread on the lower side rather than the upper side of the exhaust part (Claim 12).

  In such a configuration, it is possible to prevent the drain that has fallen through the heat receiving pipe from staying on the lower side of the exhaust part. Further, with the above-described configuration, it is possible to prevent the flow velocity of the combustion gas flowing into the exhaust part from being extremely lowered on the upstream side in the flow direction of the combustion gas in the exhaust part, that is, on the lower side of the exhaust part. Therefore, with the above-described configuration, the combustion gas can flow from the lower side to the upper side while maintaining a flow rate suitable for heat exchange.

  In the hot water supply apparatus of the present invention, the heat receiving pipe may be constituted by a spiral pipe, and may be arranged so that water can be passed in the vertical direction in the exhaust part (claim 13).

  According to this configuration, it is possible to secure a sufficiently large heat transfer area for heat exchange while downsizing the secondary heat exchanger.

  Further, when the heat receiving pipe is configured by a spiral pipe, the heat receiving pipe has a spiral baffle plate having a spiral shape, and the spiral baffle plate is arranged along the lower side of the spiral pipe constituting the heat receiving pipe. It is desirable that it is made (Claim 14).

  According to such a configuration, the combustion gas can flow along the spiral baffle plate disposed below the spiral pipe, and the heat exchange efficiency in the heat receiving pipe can be further improved.

  When the heat receiving pipe is constituted by a spiral pipe in the hot water supply apparatus of the present invention, the combustion gas is prevented from passing through the central space provided at the turning center position of the spiral pipe portion constituting the heat receiving pipe. It is desirable to provide a possible baffle (claim 15).

  According to this configuration, it is possible to prevent the combustion gas from passing through the central space provided at the turning center position of the heat receiving pipe constituted by the spiral pipe, and the hot water flowing through the heat receiving pipe and the combustion gas can be prevented. Heat exchange can be further promoted.

  In the hot water supply apparatus of the present invention, it is desirable that the heat receiving pipe can pass water from a position downstream in the flow direction of the combustion gas flowing through the exhaust portion to a position upstream in the flow direction of the combustion gas. Item 16).

  In such a configuration, the hot water flowing through the heat receiving pipe and the combustion gas flowing through the exhaust section are opposed to each other at some or all positions. Therefore, if it is set as the above-mentioned structure, the heat exchange efficiency in a secondary heat exchanger can be improved further.

  In the hot water supply apparatus of the present invention, the direction of the hot water flowing in the heat receiving pipe and the direction of the combustion gas flowing in the exhaust part may be opposite directions at all positions (claim 17).

  In such a configuration, the hot water flowing through the heat receiving pipe and the combustion gas flowing through the exhaust section become counterflows at all positions. Thereby, heat exchange efficiency improves reliably.

  In the hot water supply apparatus of the present invention, the combustion means may combust fuel gas obtained by vaporizing liquid fuel (claim 18).

  When so-called vaporization type combustion means that vaporizes and burns liquid fuel as the combustion means as in the present invention, combustion noise can be minimized. Therefore, if the configuration of the present invention is adopted, for example, a soundproof material or the like that is conventionally disposed in the exhaust portion can be omitted or simplified.

  ADVANTAGE OF THE INVENTION According to this invention, the hot water supply apparatus which can collect | recover the drain generate | occur | produced with the secondary heat exchanger appropriately, and can introduce | transduce into a neutralizer can be provided.

It is the front view which looked at a part of hot-water supply apparatus concerning one embodiment of the present invention. It is a perspective view which shows a secondary heat exchanger. It is AA sectional drawing of FIG. (A), (b) is a perspective view which shows a receiving part and a scattering prevention part, respectively. It is sectional drawing which shows the modification of an exhaust part. (A) is a receiving part, (b) is a top view which shows a scattering prevention part. (A) is an expanded sectional view which shows the structure of the heat receiving pipe employ | adopted as the secondary heat exchanger, (b) is an expanded cross section which shows the structure of the heat receiving pipe in the state which has arrange | positioned the transverse part in the up-down direction. FIG. (A) is a front view which shows the structure in the exhaust part of the hot water supply apparatus which employ | adopted the secondary heat exchanger which concerns on a modification, (b) is AA sectional drawing of (a). (A) is a front view which shows the structure in the exhaust part of the hot water supply apparatus which employ | adopted the secondary heat exchanger which concerns on a modification, (b) is a perspective view which shows the secondary heat exchanger shown to (a). . It is a front view which shows the modification of the secondary heat exchanger shown in FIG. (A) is a front view which shows the structure in the exhaust part of the hot water supply apparatus which employ | adopted the secondary heat exchanger which concerns on a modification, (b) is the 1st arrangement | sequence method in the secondary heat exchanger shown to (a) AA sectional view showing a state in which the heat receiving pipe is arranged in Fig. 6A is a sectional view taken on line AA showing a state in which the heat receiving pipe is arranged by the second arrangement method in the secondary heat exchanger shown in (a). is there. (A) is a front view which shows the structure of the secondary heat exchanger employ | adopted with the hot water supply apparatus shown in FIG. 1, (b) shows the structure of the secondary heat exchanger concerning the modification of (a). It is a front view. It is sectional drawing which shows the modification of an exhaust part. (A) is a front view showing a state where a baffle plate is provided in the exhaust part shown in FIG. 7 (a), and (b) is a front view showing a state where a baffle plate is provided in the exhaust part shown in FIG. 11 (a). is there. It is a perspective view which shows the modification of the heat receiving pipe employ | adopted as a secondary heat exchanger. It is a front view which shows the modification of an exhaust part. (A)-(c) is sectional drawing which shows the modification of an exhaust_gas | exhaustion assembly part.

  Then, the hot water supply apparatus 1 which concerns on one Embodiment of this invention is demonstrated in detail, referring drawings. In the following description, the vertical / left / right positional relationship will be described based on a normal installation state unless otherwise specified.

  The hot water supply device 1 is a so-called latent heat recovery type hot water supply device including a combustion section 2 (combustion means), a primary heat exchanger 20, and a secondary heat exchanger 30. The hot water supply device 1 includes a combustion case 3 and an exhaust collecting unit 5 below the combustion unit 2. Further, an exhaust part 6 is provided on the side of the combustion part 2. Further, a neutralizer 7 is provided below the exhaust collecting portion 5. The combustion case 3 and the exhaust part 6 communicate with an exhaust collecting part 5 provided on the bottom side of the hot water supply device 1. As a result, the hot water supply apparatus 1 is formed with a space communicating from the combustion case 3 through the exhaust collecting portion 5 to the exhaust portion 6 so as to have a substantially “U” cross-sectional shape.

  The combustion unit 2 may employ any conventionally known combustion device. However, in the present embodiment, a so-called vaporization type combustion device that vaporizes liquid fuel to generate combustion gas and burns it is employed. ing. Therefore, the combustion part 2 has a low combustion noise compared with what employ | adopted the combustion form which sprays and burns liquid fuel from a spray nozzle like the conventionally well-known spray type combustion apparatus. The combustion unit 2 can perform a combustion operation so as to form a flame toward the combustion case 3 provided below.

  The combustion case 3 is located on the lower side with respect to the combustion unit 2 and is a portion (combustion gas passage) through which high-temperature combustion gas generated in accordance with the combustion operation in the combustion unit 2 flows. A water pipe 15 is wound around the combustion case 3 in order to prevent an excessively high temperature due to the high-temperature combustion gas flowing inside. A connection port 16 is provided on one end side of the water pipe 15, and a pipe 38 described later is connected thereto. Further, the other end of the water pipe 15 is connected to a primary water inlet 25 of the primary heat exchanger 20 which will be described in detail later.

  A primary heat exchanger 20 is provided at a lower end side portion of the combustion case 3. The primary heat exchanger 20 is mainly for recovering sensible heat contained in the combustion gas flowing through the combustion case 3. The primary heat exchanger 20 is configured by a so-called fin-and-tube heat exchanger. That is, the primary heat exchanger 20 has a series of water pipes 21 bent into a substantially “U” shape, and the water pipes 21 are inserted so as to cross the combustion case 3. A large number of fins 22 are attached to the water pipe 21. The primary heat exchanger 20 can heat-heat the hot water flowing in the water pipe 21 by heat exchange with the high-temperature combustion gas flowing in the combustion case 3.

  The water pipe 21 has a primary water outlet 23 on one end side and a primary water inlet 25 on the other end side. The primary water outlet 23 is connected to a hot water supply destination such as a curan through a pipe or the like (not shown). On the other hand, a water pipe 15 wound around the combustion case 3 is connected to the primary water inlet 25.

  The exhaust collecting portion 5 is a portion that is disposed below the combustion case 3 and communicates directly with the combustion case 3. Exhaust collecting portion 5 has an internal space that extends in the width direction (right and left direction in FIG. 1) of hot water supply device 1 on the bottom side of hot water supply device 1. Further, the exhaust collecting portion 5 communicates with an exhaust portion 6 disposed on the side of the combustion case 3. Therefore, the exhaust collecting part 5 functions as a part that allows the combustion gas flowing downward in the combustion case 3 to flow in and flows out the combustion gas toward the exhaust part 6. In other words, the exhaust collecting portion 5 functions as a portion for turning upward the flow direction of the combustion gas flowing downward.

  As shown in FIG. 1, the exhaust part 6 has a space 6b that is surrounded on all sides by an outer wall member 6a and communicates in the vertical direction. In the exhaust part 6, an exhaust cylinder 6c is connected to an exhaust port 6d provided on the upper end side, and the space 6b communicates with the external atmosphere via this. The space 6b in the exhaust part 6 communicates with the exhaust collecting part 5 through an inlet 6e provided on the lower end side. As shown in FIG. 3, the introduction port 6e is provided in the tray part 10, and the dam part 11 is formed in the opening edge so that it may protrude toward the space 6b side by burring process. As a result, the drain received by the tray 10 is prevented from falling from the exhaust section 6 side to the exhaust collection section 5 side due to the dam section 11 becoming an obstacle. In addition, the inlet 6e of this embodiment is located in the approximate center of the saucer part 10. FIG.

  As shown in FIGS. 1 to 3, a secondary heat exchanger 30 is disposed in the space 6 b of the exhaust unit 6. The secondary heat exchanger 30 includes a plurality of heat receiving pipes 31, a water inlet header 32 and a water outlet header 33. The heat receiving pipe 31 is excellent in heat conductivity and is formed by a pipe having a smooth surface. For this reason, even if the drain generated by heat exchange adheres to the surface of each heat receiving pipe 31, the drain falls smoothly without stagnation on the surface of the heat receiving pipe 31. Each heat receiving pipe 31 is arranged side by side so as to extend in the vertical direction in the exhaust part 6.

  Each heat receiving pipe 31 has one end connected to a water inlet header 32 provided on the upper end side of the exhaust section 6 and the other end connected to a water outlet header 33 provided on the lower end side of the exhaust section 6. Yes. Therefore, the hot water supplied to the secondary heat exchanger 30 first flows into the water inlet side header 32, then flows divided into each heat receiving pipe 31 connected thereto, and then gathers at the water outlet side header 33 and flows out to the outside. Will be.

  As shown in FIG. 2 and FIG. 3, the heat receiving tube 31 has a shape that is folded back into a substantially “<” shape in the middle. Thereby, the heat receiving pipe 31 has a plurality of crossing portions 31a that cross the inside of the exhaust portion 6 in the middle, and has a folded portion 31b between the crossing portions 31a and 31a. The transverse part 31a is arranged with a downward slope. Moreover, the crossing part 31a differs in the direction of the downward slope from the crossing part 31a distribute | arranged to the position adjacent to an up-down direction. Specifically, as shown in FIG. 2, the crossing portion 31 a that is located on the uppermost side (upstream side) of the heat receiving pipe 31 is lowered toward the back side (right side in FIG. 3) of the hot water supply device 1. It is arranged with a downward slope so as to incline. On the other hand, the crossing part 31a in the position adjacent to the lower side (downstream side) of the crossing part 31a is connected to the crossing part 31a via the turn-up part 31b, and is on the front side (left side in FIG. 3) of the hot water supply device 1. It is arranged with a downward slope so as to incline downward as it goes. As described above, the heat receiving pipe 31 is provided with the transverse portion 31a and the folded portion 31b one after another to form a series of flow paths. Therefore, when hot water is supplied to the heat receiving pipe 31, the hot water flows in a zigzag manner between the front side and the back side of the hot water supply device 1 while gradually flowing out to the water discharge side header 33. Will head to.

  As shown in FIG. 2, the heat receiving pipe 31 includes a forward crossing portion 31 a (crossing portion A) that flows hot water from the front side to the back side of the hot water supply device 1 among the plurality of crossing portions 31 a. When the flow of hot water from the back side to the front side is the reverse direction crossing portion 31a (crossing portion B), and the turn portion T is formed by connecting the forward and reverse direction crossing portions 31a, 31a with the folded portion 31b, A large number of turn portions T are arranged in the vertical direction. In this case, when the turn part located on the upper side is the turn part T1, and the turn part located on the lower side is the turn part T2, the reverse transverse part 31a (transverse part B) of the turn part T1 and the turn part T2 The forward crossing portion 31a (crossing portion A) is constituted by the same crossing portion 31a. When the turn portions T1 and T2 are assumed in this way, the forward and reverse crossing portions 31a and 31a are separated in the vertical direction and shifted in the horizontal direction, more specifically in the direction intersecting the hot water flow direction. It is in a positional relationship. Therefore, as shown in FIG. 5A, it is assumed that the turn portions T1 and T2 are formed in the order, the reverse transverse portions 31a and 31a, and the folded portion 31b connecting them are arranged along the virtual planes I1 and I2. In this case, the virtual planes I1 and I2 are inclined with respect to the vertical planes V1 and V2.

  Further, as shown in FIG. 5 (a), the forward crossing portions 31a of the turn portions T are arranged in the vertical direction along the vertical plane V1, and the reverse crossing portions 31a of the turn portions T are They are arranged side by side in the vertical direction so as to be along a vertical plane V2 parallel to the vertical plane V1 with a predetermined interval. A virtual plane I1 along which a turn part T1 including a forward crossing part 31a and a forward crossing part 31a below the front crossing part 31a, and a virtual part along which a turn part T2 including a reverse crossing part 31a and a forward crossing part 31a below the virtual crossing are provided. The plane I2 is inclined in directions opposite to each other with respect to the vertical plane. Therefore, as shown in FIG. 1 and FIG. 5A, when the heat receiving pipe 31 constituting the secondary heat exchanger 30 is viewed from the front side of the hot water supply device 1, the portion bent in a substantially “<” shape is vertically It looks as if it continues to the direction.

  The forward crossing portion 31a and the reverse crossing portion 31a are provided at predetermined pitches in the vertical direction along the vertical planes V1 and V2, respectively. The angle θ1 formed by the virtual plane I1 and the vertical planes V1 and V2 and the angle θ2 formed by the virtual plane I2 and the vertical planes V1 and V2 are the same in any part. In the present embodiment, the angles θ1 and θ2 are the same.

  As shown in FIGS. 1 and 2, the secondary heat exchanger 30 has a structure in which a plurality of (four in the present embodiment) heat receiving tubes 31 having a bent shape are arranged side by side as described above. Each of the heat receiving tubes 31 is placed in the exhaust portion 6 in a posture in which the heat receiving tubes 31 face in the vertical direction. Each heat receiving pipe 31 is arranged in the exhaust portion 6 in the width direction of the hot water supply device 1 (left and right direction in the state shown in FIG. 1). Moreover, each heat receiving pipe 31 is arrange | positioned so that the crossing part 31a may extend in the depth direction (direction which cross | intersects a paper surface in the state shown in FIG. 1) of the hot water supply apparatus 1. FIG.

  In the secondary heat exchanger 30, a slight gap is provided between adjacent heat receiving tubes 31, but the turn portions T of the heat receiving tubes 31 are arranged to be folded. Therefore, the secondary heat exchanger 30 has a relatively large ventilation resistance of the combustion gas flowing between the heat receiving pipes 31. Therefore, the combustion gas that has flowed into the secondary heat exchanger 30 slowly flows between the heat receiving pipes 31 and is discharged after the latent heat is sufficiently recovered.

  The upper end side of each heat receiving pipe 31 is connected to the water inlet side header 32. The water inlet header 32 is provided with a secondary water inlet 35. Further, the secondary water inlet 35 is connected to a water supply source (not shown) through a pipe (not shown). On the other hand, the lower end side of each heat receiving pipe 31 is connected to the water discharge side header 33. The water outlet header 33 is provided with a secondary water outlet 37. The secondary water outlet 37 is connected to the connection port 16 of the primary heat exchanger 20 described above via a pipe 38.

  As shown in FIG. 1, the exhaust section 6 has a flow passage cross-sectional area of the heat exchange arrangement region 6x in which the secondary heat exchanger 30 is arranged so that the secondary heat exchanger 30 can be accommodated with almost no gap. It is said. Therefore, almost all of the combustion gas that has flowed into the upstream region 6y of the exhaust part 6 is directed from the lower side to the upper side between the heat receiving tubes 31 of the secondary heat exchanger 30 arranged in the heat exchange arrangement region 6x. And pass through to the downstream region 6z side.

  The exhaust part 6 has a receiving part 40 at the lower side of the secondary heat exchanger 30, more specifically at the boundary between the heat exchange area 6 x and the upstream area 6 y. The receiving unit 40 has a function of receiving drain generated by heat exchange in the secondary heat exchanger 30 and preventing the drain from dropping from the exhaust unit 6 to the exhaust collecting unit 5 via the inlet 6e. . The receiving part 40 is formed by bending a rectangular metal plate at a substantially central part in the width direction as shown in FIGS. 4 (a) and 4 (b).

  The receiving portion 40 includes wind receiving surfaces 41 and 42 and a ridge line portion 43 that is formed in the bent portion and forms the boundary between the wind receiving surfaces 41 and 42. As shown in FIG. 1, the receiving portion 40 is attached in such a posture that the ridge line portion 43 is convex toward the introduction port 6 e side. In other words, the receiving portion 40 is attached so as to be substantially “V” -shaped in a state viewed in a cross section on a plane intersecting the ridge line portion 43. Thus, since the receiving part 40 is set so as to protrude toward the upstream side in the flow direction of the combustion gas flowing in from the introduction port 6e, the flow path resistance of the combustion gas is not limited even if the receiving part 40 is arranged. It doesn't grow up. In the present embodiment, a fixing piece (not shown) is provided at the edge of the receiving portion 40, and the fixing piece is attached to the inside of the outer wall member 6a by welding. The same applies to the scattering prevention means 60 described below.

  As shown in FIG. 3, the receiving part 40 has a ridge line part 43 facing in the depth direction of the exhaust part 6, and the ridge line part 43 is substantially in the center of the width direction of the secondary heat exchanger 30 (direction in which the heat receiving pipes 31 are arranged). It is installed in alignment so that it arrives at. Moreover, the receiving part 40 is located above the opening area | region of the inlet 6e, and substantially the whole opening area | region of the inlet 6e is hidden by the receiving part 40 in the state seen from upper direction. That is, the opening area of the inlet 6e is included in the projection area formed by projecting the receiving part 40 toward the bottom surface side of the exhaust part 6 provided with the inlet 6e. Therefore, even if the drain generated in the secondary heat exchanger 30 falls into the receiving part 40 or the drain further falls down along the receiving part 40, the drain does not flow into the introduction port 6e.

  As shown in FIG. 1, a drain discharge port 47 is provided in the upstream region 6y. As shown by a two-dot chain line in FIG. 1, the drain discharge port 47 is connected to a neutralizer 7 provided below the exhaust collecting portion 5 via a pipe 48. Thus, a series of drain discharge systems 50 is formed that guides the drain that has fallen from the secondary heat exchanger 30 to the receiving unit 40 to the neutralizer 7 by bypassing the inlet 6e. That is, the hot water supply device 1 has a series of drain discharge systems 50 connected to the neutralizer 7 via a pipe 48 connected to the drain discharge port 47 from the receiving unit 40, and the drain is neutralized via this. 7, the drain can be prevented from dropping into the lower exhaust collecting portion 5 through the inlet 6e.

  Further, scattering is formed above the secondary heat exchanger 30, specifically, at a boundary portion between the heat exchange area 6 x where the secondary heat exchanger 30 is arranged and the downstream area 6 z where the exhaust port 6 d is provided. The prevention part 60 (scattering prevention means) is provided. As shown in FIG. 4, the scattering prevention unit 60 has a structure similar to that of the receiving unit 40 described above. The anti-scattering part 60 is obtained by bending a rectangular plate body, and has intersecting surfaces 61 and 62 and a ridge line part 63 that forms a boundary between them. As shown in FIG. 1, the scattering prevention unit 60 is set so as to protrude the ridge line portion 63 toward the upstream side in the flow direction of the combustion gas, similarly to the receiving unit 40. In other words, the anti-scattering part 60 is attached so that the cross-sectional shape is substantially “V” -shaped when viewed in a cross-section on a plane intersecting the ridge line part 63. Therefore, the flow path resistance of the combustion gas does not increase so much even if the scattering prevention unit 60 is provided. Further, the scattering prevention unit 60 is installed in such a posture that the ridge line portion 63 faces the depth direction of the exhaust portion 6 and arrives at the substantially central portion in the width direction of the secondary heat exchanger 30 (the direction in which the heat receiving pipes 31 are arranged). Yes.

  The anti-scattering unit 60 is located below the opening area of the exhaust port 6 d provided on the top surface of the exhaust unit 6. An opening region of the exhaust port 6d is included in a projection region formed by projecting the scattering prevention unit 60 toward the top surface side of the exhaust unit 6. Therefore, even if the drain generated in the secondary heat exchanger 30 is scattered on the combustion gas flow, the scattered drain flow is blocked by the scattering prevention unit 60 and does not leak to the outside from the exhaust unit 6.

  Then, operation | movement of the hot water supply apparatus 1 is demonstrated in detail focusing on the flow of combustion gas or hot water. When the hot water supply device 1 detects that hot water has been supplied from an external water supply source to the secondary heat exchanger 30 by a flow sensor or the like (not shown), the combustion unit 2 starts a combustion operation. Combustion gas generated by the combustion operation in the combustion section 2 flows downward in the combustion case 3. Thereafter, the combustion gas passes through the exhaust collecting portion 5 provided on the bottom side of the hot water supply device 1 and escapes to the exhaust portion 6 side through the introduction port 6 e provided on the bottom surface of the exhaust portion 6. The combustion gas that has flowed into the exhaust part 6 in this way passes through the gap between the receiving part 40 disposed at the boundary between the upstream area 6y of the exhaust part 6 and the heat exchange area 6x, and the heat exchange area. It flows into approximately the center of 6x. The combustion gas that has flowed into the heat exchange arrangement region 6x flows so as to sew between the heat receiving pipes 31 constituting the secondary heat exchanger 30, and then reaches the downstream region 6z and is connected to the exhaust port 6d. It is exhausted to the outside through the exhaust cylinder 6c.

  On the other hand, the hot water supplied from the outside flows into each of a plurality of (four in the illustrated state) heat receiving pipes 31 connected thereto via the water inlet side header 32 of the secondary heat exchanger 30. The hot water flowing into each heat receiving pipe 31 passes through the zigzag channel formed so as to go back and forth between the front side and the back side of the hot water supply device 1 by repeating the crossing part 31a and the turning part 31b. It flows toward. Since the flow of hot water in the heat receiving pipe 31 as a whole flows from the upper side to the lower side, it is in a counterflow relationship with the flow of the combustion gas flowing upward in the space 6b. Therefore, the hot water flowing through each heat receiving pipe 31 flows toward the water discharge side header 33 provided on the lower side of the exhaust part 6 while exchanging heat efficiently with the combustion gas.

  Here, when heat exchange is performed in the secondary heat exchanger 30 as described above, latent heat contained in the combustion gas flowing in the exhaust section 6 is recovered into hot water flowing in each heat receiving pipe 31. . Along with this, moisture contained in the combustion gas is condensed, and drain adheres to the surface of the heat receiving pipe 31 of the secondary heat exchanger 30. As described above, the crossing portions 31a (forward crossing portion 31a, reverse crossing portion 31a) arranged vertically in each heat receiving pipe 31 are along virtual surfaces I1 and I2 inclined with respect to the vertical surfaces V1 and V2. Has been placed. Therefore, the drain adhering to each heat receiving pipe 31 falls smoothly toward the receiving part 40 provided below.

  Here, as described above, the size and arrangement of the receiving portion 40 are adjusted so that the entire opening region of the introduction port 6e provided on the bottom surface of the exhaust portion 6 is hidden when viewed from above. . The hot water supply apparatus 1 has a series of drain discharge systems 50 connected to the neutralizer 7 via a pipe 48 connected to the drain discharge port 47 from the receiving unit 40, and the drain is neutralized via this. 7 can be led. Furthermore, the opening edge of the inlet 6e is formed so as to protrude toward the space 6b by burring. Therefore, even if the drain falls from the secondary heat exchanger 30 to the receiving portion 40, the drain does not flow into the exhaust collecting portion 5 positioned upstream in the flow direction of the combustion gas via the inlet 6e. Then, it is discharged toward the neutralizer 7 through the drain discharge system 50 and neutralized. Further, since the receiving part 40 is arranged with the ridge line part 43 facing downward, the ventilation resistance acting on the combustion gas introduced into the exhaust part 6 from the introduction port 6e is not so large. For this reason, the combustion gas introduced into the exhaust part 6 is introduced into the secondary heat exchanger 30 without decreasing the flow velocity so much even if it passes through the receiving part 40.

  Further, as described above, the scattering prevention unit 60 is provided above the secondary heat exchanger 30. Therefore, even if the drain is blown up on the flow of the combustion gas that has passed through the secondary heat exchanger 30, the drain is captured by the scattering prevention unit 60 and does not leak to the outside. Moreover, since the scattering prevention part 60 is arrange | positioned so that the ridgeline part 63 may protrude toward the downward direction, the combustion gas which finished heat exchange flows toward the exhaust port 6d smoothly, and is discharged | emitted outside.

  As described above, the hot water heated in the secondary heat exchanger 30 flows out from the secondary outlet 37 provided in the outlet header 33 by heat exchange with the combustion gas flowing through the exhaust section 6. Hot water flowing out from the secondary outlet 37 flows into the primary heat exchanger 20 from the primary inlet 25 through a pipe 38 connected thereto. The hot water flowing into the primary heat exchanger 20 is heated by heat exchange with the high-temperature combustion gas flowing downward in the combustion case 3 and then flows out from the primary outlet 23. The hot hot water flowing out from the primary outlet 23 is supplied to a hot water supply destination such as a currant or a bathtub connected to the hot water through a pipe (not shown).

  As described above, the hot water supply device 1 of the present embodiment has the receiving portion 40 provided at a position below the secondary heat exchanger 30 provided in the exhaust portion 6 and above the inlet 6e. In addition, the drain can be discharged through the drain discharge system 50 extending from the receiving portion 40 to the neutralizer 7 through the pipe 48 connected to the drain discharge port 47, and the drain collects the exhaust through the inlet 6e. It can prevent falling to the part 5 side. Therefore, in the hot water supply device 1, when the drain falls into the exhaust collecting portion 5, the drain is exposed to a high temperature atmosphere and the acidity of the drain is increased, or the exhaust collecting portion 5 is corroded by the drain having high acidity. Can be prevented.

  The above-described hot water supply device 1 is provided with the scattering prevention unit 60 in a region below the exhaust port 6d provided in the exhaust unit 6 and above the secondary heat exchanger 30, and the secondary heat It is possible to prevent the scattering of drain from the exchanger 30 side to the exhaust port 6d side. Therefore, in the hot water supply device 1, the drain generated in the secondary heat exchanger 30 rides on the flow of the combustion gas passing through the exhaust part 6 and leaks to the outside from the exhaust port 6 d, or the leaked drain causes the drain of the hot water supply device 1. Corrosion of the main body case can be prevented.

  Moreover, the receiving part 40 and the scattering prevention part 60 which were mentioned above are the wind-receiving surfaces 41 and 42 which cross | intersect the flow direction of the combustion gas introduce | transduced into exhaust gas from the inlet 6e, and the crossing surfaces 61 and 62, and these. The ridge line portions 43 and 63 are formed between the ridge line portions 43 and 63 so as to protrude toward the upstream side in the flow direction of the combustion gas. Therefore, in the hot water supply device 1, even if the receiving part 40 and the scattering prevention part 60 are provided, the ventilation resistance in the exhaust part 6 does not become excessively large.

  In the above embodiment, considering that the ventilation resistance in the exhaust part 6 is increased by arranging the receiving part 40 and the scattering prevention part 60, the shape of the receiving part 40 and the scattering prevention part 60 is substantially “V”. Although the configuration is illustrated in which it is shaped like a letter and is convex toward the upstream side (downward) in the flow direction of the combustion gas, the present invention is not limited to this. For example, like the receiving part 64 shown in FIG. 5 and the scattering prevention part 65, it can comprise by the board etc. which were provided so that the exhaust part 6 might be crossed. The receiving part 64 and the scattering prevention part 65 described below are also attached in the same manner as the receiving part 40 and the scattering prevention part 60 described above.

  Specifically, as shown in FIG. 6A, the receiving portion 64 is rectangular and has a flat air receiving surface 67 and a notch portion 66. The receiving portion 64 is provided with a notch 66 on the end side 64 a of the wind receiving surface 67, and the end 64 a side of the wind receiving surface 67 provided with the notched portion 66 is formed on the outer wall member 6 a of the exhaust portion 6. It is attached to abut. And the end side 64c facing the end side 64a is arranged and attached in the middle of the exhaust part 6. In other words, the receiving part 64 is attached so as to protrude toward the inside of the exhaust part 6 from the end side 64a side where the notch part 66 is provided. At this time, the end sides 64 b and 64 d of the receiving part 64 positioned so as to sandwich the notch part 66 are in contact with the outer wall member 6 a of the exhaust part 6. That is, the receiving portion 64 is fixed by a total of three end sides 64a, 64b, and 64d, that is, an end side 64a provided with the notch 66 and end sides 64b and 64d adjacent to the end side 64a. Moreover, since the receiving part 64 is attached so as to be inclined downward toward the notch part 66, the flow path resistance can be reduced. Furthermore, in this embodiment, since the drain which fell from the heat receiving pipe 31 is received by the receiving part 64, it can be dropped to the saucer part 51 located under the receiving part 64 via the notch part 66. The drain can be efficiently discharged without being retained in the period exhaust unit 6.

  In addition, the inlet 6e is provided with a dam portion 52 at the opening edge, and is arranged at a position shifted from the center of the tray portion 51. The receiving part 64 is arranged above the opening area of the introduction port 6e as in the embodiment shown in FIG. That is, almost the entire opening area of the introduction port 6 e is hidden by the receiving portion 64 when viewed from above. Therefore, the opening area of the inlet 6e is included in the projection area formed by projecting the receiving part 64 toward the bottom surface side of the exhaust part 6 provided with the inlet 6e. Therefore, even if the drain generated in the secondary heat exchanger 30 falls on the receiving part 64 or the drain further falls down along the receiving part 64, the drain does not flow into the introduction port 6e.

  Further, as shown in FIG. 6B, the scattering prevention unit 65 is square and has a planar intersection surface 68, similar to the receiving unit 64. The scattering prevention part 65 is attached so that three end sides 65 a, 65 b, 65 d among the end sides 65 a, 65 b, 65 c, 65 d of the intersecting surface 68 come into contact with the outer wall member 6 a of the exhaust part 6. That is, the remaining end side 65c is disposed so as to be disposed approximately in the middle of the exhaust part 6. Therefore, the scattering prevention part 65 is also attached so as to protrude from the end side 65 a of the intersecting surface 68 toward the inside of the exhaust part 6, similarly to the receiving part 64. Further, the scattering prevention portion 65 is also inclined downwardly from the end side 65c of the intersecting surface 68 located in the middle of the exhaust portion 6 toward the outer wall member 6a. Specifically, since the intersecting surface 68 is inclined with respect to a plane orthogonal to the flow direction of the combustion gas, the flow path resistance (exhaust resistance) can be reduced. The exhaust port 6d is disposed at a position shifted from the center of the exhaust unit 6, and the scattering prevention unit 65 is disposed below the opening region of the exhaust port 6d as in the embodiment shown in FIG. That is, when viewed from below, almost the entire opening area of the exhaust port 6d is hidden by the scattering prevention unit 65. Therefore, the opening area of the exhaust port 6d is included in the projection area formed by projecting the scattering prevention part 65 toward the top surface side of the exhaust part 6 provided with the exhaust port 6d. Therefore, it is possible to prevent the drain generated in the secondary heat exchanger 30 from being scattered and leaked together with the combustion gas.

  Further, in the above embodiment, the scattering prevention portion 60 or 65 is provided to prevent the drain from scattering from the exhaust port 6d. However, the flow rate of the exhausted combustion gas is not so fast. When the scattering of drain does not become a problem or when it is not necessary to consider the scattering of drain, the configuration may be such that the scattering preventing units 60 and 65 are not provided.

  As described above, the neutralizer 7 is provided below the exhaust unit 6. For this reason, when the above-described configuration is adopted, the drain collected by the exhaust unit 6 flows downward through the drain discharge system 50 and is smoothly collected by the neutralizer 7. In the above embodiment, the configuration in which the neutralizer 7 is provided below the exhaust portion 6 in consideration of discharging the drain smoothly is illustrated, but the present invention is not limited to this, and the neutralizer 7 may be provided at any position.

  A plurality of the secondary heat exchangers 30 described above are connected so as to connect between a water inlet header 32 disposed on the upper side of the exhaust section 6 and a water outlet header 33 disposed on the lower side of the exhaust section 6 ( In this embodiment, four heat receiving pipes 31 are connected, and hot water is allowed to flow downward from above. Therefore, in the hot water supply apparatus 1, the hot water flow in the secondary heat exchanger 30 is in a counter flow with the combustion gas flow passing through the secondary heat exchanger 30, and the heat exchange efficiency is high.

  As described above, the secondary heat exchanger 30 has a configuration in which the water inlet side header 32 is disposed on the upper side and the water outlet side header 33 is disposed on the lower side, and hot water can be circulated from the upper side to the lower side. However, the present invention is not limited to this, and for example, as shown in FIG. 8, both the water inlet side header 32 and the water outlet side header 33 are provided in the lower region of the exhaust part 6, and between them May be configured to be connected by a heat receiving tube 70 bent so that the external shape becomes a “U” shape. Also in the case of such a configuration, by arranging the receiving unit 40 and the scattering prevention unit 60 described above below and above the secondary heat exchanger 30, the drain flows into the exhaust collecting unit 5 through the inlet 6e. It is possible to prevent the drain from being scattered outside through the exhaust port 6d.

  The secondary heat exchanger 30 described above employs a heat receiving pipe 31 in which the crossing portions 31a crossing the opening region of the exhaust portion 6 are connected by a folded portion 31b, and the inside of the exhaust portion 6 reciprocates in a zigzag manner. Therefore, the heat transfer area is sufficiently large while being compact in the vertical direction. Moreover, as above-mentioned, the heat receiving pipe 31 has the virtual surfaces I1 and I2 along which the turn parts T1 and T2 including the crossing parts 31a and 31a adjacent to the upper and lower sides and the folded-back part 31b connecting these have vertical surfaces V1 and V2. It is bent so as to be inclined.

  More specifically, in the present embodiment, the heat receiving pipe 31 of the secondary heat exchanger 30 includes a forward crossing portion 31a which is one of the plurality of crossing portions 31a and a position adjacent to the lower side with respect to the forward crossing portion 31a. The reverse crossing portion 31a is located in a horizontal positional relationship with each other, and the two are connected by a folded portion 31b (see FIG. 7A). Therefore, the virtual planes I1 and I2 along which the turn portions T (T1 and T2) including the forward and reverse crossing portions 31a and 31a are set have the same interval D between the forward and reverse crossing portions 31a and 31a. When the angle between the vertical planes V1 and V2 is θ, the forward and reverse crossing portions 31a and 31a are not displaced in the horizontal direction and are lined up and down as shown in FIG. 7B. It is possible to make the secondary heat exchanger 30 compact in the height direction by D · (1-cos θ) for each turn portion T while securing a heat transfer area equivalent to that in the case of the state. In the present embodiment, since the plurality of turn portions T (n turns) are provided, the height of the secondary heat exchanger 30 as a whole can be suppressed by n · D (1-cos θ). Therefore, the hot water supply device 1 has a compact device configuration and high thermal efficiency.

  In addition, as described in the present embodiment, the configuration in which the forward and reverse crossing portions 31a and 31a constituting each turn portion T are provided along the virtual surfaces I1 and I2 inclined with respect to the vertical surfaces V1 and V2. Then, the drain adhering to the heat receiving pipe 31 due to heat exchange tends to fall downward. Therefore, by adopting the secondary heat exchanger 30 described above, it is possible to prevent the heat exchange efficiency from being reduced due to the adhesion of the drain and the heat receiving pipe 31 from being corroded.

  The heat receiving pipe 31 employed in the secondary heat exchanger 30 in the present embodiment is provided with a forward crossing portion 31a along one vertical surface V1 of the two vertical surfaces V1 and V2 facing each other. A reverse crossing portion 31a is provided along the vertical plane V2. Therefore, the spread in the width direction of each heat receiving pipe 31, that is, the spread in the direction intersecting the flow direction of the hot water in the forward and reverse direction crossing portions 31a and 31a is an area partitioned by the vertical planes V1 and V2. It wo n’t come off. Therefore, according to the configuration described above, the size of the heat receiving pipe 31 and the secondary heat exchanger 30 can be reduced not only in the height direction but also in the horizontal direction. Moreover, since it can arrange | position the heat receiving pipe | tube 31 with high density by setting it as such a structure, the thermal efficiency in the secondary heat exchanger 30 can be improved.

  In the said embodiment, about all the turn parts T which comprise the heat receiving pipe 31, the structure by which the forward and reverse direction crossing parts 31a and 31a were distribute | arranged along the virtual surfaces I1 and I2 inclined by the fixed angle (theta) is illustrated. However, the present invention is not limited to this, and the forward and reverse transverse portions 31a and 31a are arranged side by side in the vertical direction as shown in FIG. There may be. In other words, as shown in FIG. 7A, in the heat receiving pipe 31 described above, the crossing portions 31a are arranged in a staggered manner, and the virtual surfaces I1 and I2 along which the turn portions T1 and T2 extend are inclined with respect to the vertical surfaces V1 and V2. However, the present invention is not limited to this, and as shown in FIG. 7B, the crossing portions 31a are arranged in a line in the vertical direction, and the crossing portions 31a are folded back. What was connected by the part 31b may be used. Further, the angle θ of the imaginary planes I1 and I2 may be different for a part or all of the turn portions T constituting the heat receiving pipe 31. That is, the vertical and horizontal displacements of the forward and reverse crossing portions 31a and 31a and the width displacement may be different for each turn portion T. Also in the case of such a configuration, the heat receiving pipe 31 reciprocates in the exhaust section 6 in a zigzag manner, and the heat transfer area is sufficiently increased by that amount, so that the secondary heat exchanger 30 and the hot water supply device 1 are made compact. be able to.

  As described above, the heat receiving pipe 31 has a shape that is bent into a substantially “<” shape at a plurality of folded portions 31 b provided in the middle. Therefore, even if the heat receiving pipe 31 is exposed to the combustion gas and becomes high temperature, the secondary heat exchanger 30 can be relaxed so that the distortion generated with the expansion of the heat receiving pipe 31 is minimized.

  Further, the secondary heat exchanger 30 may employ the heat receiving pipe 31 bent so as to reciprocate in the exhaust section 6 as described above, but as shown in FIG. A heat receiving pipe 72 that linearly connects the side header 32 and the water discharge side header 33 in the vertical direction may be used. According to this configuration, the drain adhering to the heat receiving pipe 72 falls more smoothly downward, and the reduction in thermal efficiency due to the drain adhering to the surface of the heat receiving pipe 72 can be further reduced.

  In the heat receiving pipe 31 shown in the above embodiment and the heat receiving pipes 70 and 71 shown in FIGS. 8 and 9 as modifications, the intervals between the adjacent heat receiving pipes 31, 70, 71 are above the exhaust section 6. However, the present invention is not limited to this. For example, as shown in FIG. 10, the heat receiving pipe 31 on the lower side (upstream side in the flow direction of the combustion gas). , 70, 71 (in the example shown in FIG. 10, the interval between the heat receiving tubes 71) may be wider than the interval on the upper side (downstream in the combustion gas flow direction). In such a configuration, it is possible to prevent the drain that has fallen through the heat receiving pipes 31, 70, 71 from staying on the lower side of the exhaust unit 6. Further, with the configuration as shown in FIG. 10, the flow velocity of the combustion gas flowing into the exhaust part 6 extremely decreases on the upstream side in the flow direction of the combustion gas in the exhaust part 6, that is, on the lower side of the exhaust part 6. Can be prevented. Therefore, as described above, if the interval between the heat receiving tubes 31 is increased below the secondary heat exchanger 30 from above, the combustion gas is discharged from the exhaust section while maintaining a flow rate suitable for heat exchange. The heat exchange efficiency can be further improved.

  The heat receiving pipe 31 shown in the above embodiment and the heat receiving pipes 70 and 71 shown in FIGS. 8 and 9 as modifications are not branched between the water inlet side header 32 and the water outlet side header 33 in the middle. Although it was connected linearly in the up-down direction, the present invention is not limited to this, and may be branched into a plurality of systems between the water inlet side header 32 and the water outlet side header 33. . Specifically, for example, as in a heat receiving pipe 72 shown in FIG. 11A, a substantially annular heat receiving portion 72a and connection portions 72b and 72c connected to the water inlet side header 32 and the water outlet side header 33 are provided. It may be. When the heat receiving pipe 72 is employed in the secondary heat exchanger 30, the hot water entering from the connection portion 72b connected to the water inlet side header 32 has two systems (hereinafter also referred to as branch paths 72d and 72e) in the heat receiving portion 72a. After being divided, they merge at the connection portion 72 c and flow into the water discharge side header 33. In the case of such a configuration, a sufficient heat transfer area can be secured for each heat receiving pipe 72, and thermal efficiency can be further improved. Moreover, when the main part (branch path 72d, 72e) of the heat receiving part 72a is configured by a pipe extending in the vertical direction like the heat receiving pipe 72, the drain adhering to the surface of the heat receiving pipe 72 easily falls down, It is possible to reduce the decrease in thermal efficiency and the possibility of corrosion due to adhesion of the partial drain.

  When a plurality of heat receiving pipes 72 as shown in FIG. 11A are arranged side by side with respect to the water inlet side header 32 and the water outlet side header 33, the heat receiving part 72 a is configured with respect to the water inlet side header 32 and the water outlet side header 33. By arranging the virtual planes I3 along the branch paths 72d and 72e to be substantially orthogonal, the branch paths 72d and 72e can be arranged in a grid pattern as shown in FIG. 11B. It is. By adjusting the angle of the imaginary plane I3 with respect to the inflow side header 32 and the outflow side header 33, as shown in FIG. 11 (c), the branch paths 72d and 72e can be in a staggered state. . When the heat receiving pipe 72 is adopted, the magnitude of the pressure loss (venting resistance) of the combustion gas in the exhaust part 6 and the thermal efficiency in the secondary heat exchanger 6 can be adjusted by appropriately adjusting the angle of the imaginary plane I3. The size can be adjusted as appropriate.

  As shown in FIG. 1 and the like, the secondary heat exchanger 30 described above includes a secondary water inlet 35 provided in the water inlet side header 32 and a secondary water outlet 37 provided in the water outlet side header 33 on the same side. Is provided. That is, as shown to Fig.12 (a), each heat receiving pipe 31 connected to the inflow side header 32 and the outflow side header 33 is made into the 1st-mth heat receiving pipe 31 (m = natural number: m = 4 in this embodiment). ), Both the secondary water inlet 35 and the secondary water outlet 37 are provided on the first heat receiving pipe 31 side. In such a configuration, the hot water flow concentrates on the first heat receiving pipe 31 and the like close to both the secondary water inlet 35 and the secondary water outlet 37 among the first to m-th heat receiving pipes 31, and the water inlet side header 32. In addition, there is a possibility that the flow of hot water is distributed between the m-th heat receiving pipe 31 side and the first heat receiving pipe 31 side connected to the end portion of the water discharge side header 33. When the occurrence of such distribution is assumed, as shown in FIG. 12B, a secondary water inlet 35 is provided on the first heat receiving pipe 31 side, and a secondary water outlet 37 is provided on the m-th heat receiving pipe 31 side. With this configuration, the above-described distribution of the hot water flow can be eliminated or suppressed, and the occurrence of uneven heating in the secondary heat exchanger 30 can be more reliably prevented.

  In the above embodiment, the heat receiving pipe 31 is exemplified by a so-called bare pipe having no irregularities on the surface. However, the present invention is not limited to this, for example, a so-called flexible pipe or corrugated pipe. The surface may have unevenness. Further, even when a heat receiving tube 31 having an uneven surface is employed, it is desirable that the size of the unevenness be as small as possible in order to smoothly drop and collect the drain.

  In the above embodiment, the heat receiving pipes 31 are arranged at a high density in the secondary heat exchanger 30, and the heat exchange arrangement region 6x of the exhaust part 6 is made large enough to fit the secondary heat exchanger 30 without any gaps. Therefore, although the ventilation resistance in the secondary heat exchanger 30 is sufficiently large and heat exchange with the combustion gas can be sufficiently performed, the present invention is not limited to the above configuration. For example, as shown in FIG. 13, by further providing a partition plate 69 below one or a plurality of bent portions of the heat receiving pipe 31 of the secondary heat exchanger 30, that is, a plurality of crossing portions 31a arranged vertically. Further, the residence time of the combustion gas can be extended. Specifically, in the present embodiment, the eleven partition plates 69 are staggered from the introduction port 6e toward the exhaust port 6d so that the flow of the combustion gas zigzags along the heat receiving pipe 31. It is arranged. Therefore, in the secondary heat exchanger 30 shown in FIG. 13, since it becomes counterflow with combustion gas in all the positions of the heat receiving pipe 31, heat exchange efficiency becomes still higher. The partition plate 69 has the same configuration as the planar receiving portion 64 shown in FIG. That is, it has a wind receiving surface 67, and a notch 66 is provided on one end side of the wind receiving surface 67, and is arranged with an inclination that is a downward slope toward the notch 66. Therefore, in this embodiment, when the drain generated in the heat receiving pipe 31 falls, most of the drain is received by the partition plate 69. Thereby, the drain which fell from the heat receiving pipe 31 adheres to the lower heat receiving pipe 31 again, the heat of the hot water heated by the combustion gas is taken, and the malfunction which reduces heat exchange efficiency as a result can be prevented. .

Further, as described above, instead of setting the flow path cross-sectional area of the heat exchange arrangement region 6x of the exhaust section 6 to a size that allows the secondary heat exchanger 30 to be accommodated with almost no gap, the above-described partition plate 69 is provided. Also good. According to such a configuration, the residence time of the combustion gas in the heat exchange arrangement region 6x can be extended to a level sufficient to recover latent heat, and the heat exchange efficiency can be further improved.
The exhaust unit 6 shown in FIG. 13 has a configuration including the planar receiving unit 64 and the scattering preventing unit 65. However, in the present invention, the “V” -shaped receiving unit 40 shown in FIG. The secondary heat exchanger 30 including the scattering prevention unit 60 may be used.

  Further, in the case where the straight pipe type heat receiving pipe 71 and the branch passages 72d and 72e of the heat receiving pipe 72 are constituted by pipes having a shape extending in the vertical direction, as shown in FIGS. 14 (a) and 14 (b). As shown in the figure, the baffle plate 55 is provided so as to cross the heat receiving pipe 71 and the branch paths 72d and 72e in the middle part in the longitudinal direction (height direction), thereby flowing straight in the exhaust part 6 from below to above. It is possible to adopt a configuration that prevents this. When the baffle plate 55 is arranged as shown in FIGS. 14 (a) and 14 (b), the combustion gas flows in a zigzag manner in the exhaust part 6, and the residence time of the combustion gas is sufficient to recover the latent heat. Can be extended to the extent.

  When the baffle plate 55 is arranged as shown in FIGS. 14A and 14B, the magnitude of the pressure loss (venting resistance) of the combustion gas, the magnitude of the thermal efficiency in the secondary heat exchanger 30, and the like are taken into consideration. The interval between the baffle plates 55 can be adjusted appropriately in the vertical direction. Specifically, for example, in the case where five baffle plates 55 are alternately provided in the vertical direction as shown in FIGS. 14A and 14B, the interval between the baffle plates 55 and 55 arranged in the vertical direction is set from below. When a, b, c, and d are set, a> b> c> d can be set. Thus, when the space | interval of each baffle plate 55 is adjusted, the pressure loss of the combustion gas which flows through the exhaust part 6 can be reduced.

  More specifically, in the case where heat exchange can be performed by a pipe portion extending in the vertical direction like the heat receiving pipe 72, the drain generated along with the heat exchange gathers downward along the surface of the heat receiving pipe 72. Therefore, the drain tends to collect on the lower side of the heat receiving pipe 72. When the above-described intervals a, b, c, and d are uniform, the passage area of the combustion gas becomes constant, so that the combustion gas can pass through the region below the heat receiving pipe 72 as much as the drain is collected. Becomes narrower, and the pressure loss increases accordingly.

  Further, from the viewpoint of heat transfer, the drain adhering to the surface of the heat receiving pipe 72 becomes a heat transfer resistance. Therefore, in order to improve the heat transfer efficiency, it is desirable to remove the drain adhering to the surface of the heat receiving pipe 72 as early as possible. When the baffle plate 55 is provided as shown in FIGS. 14A and 14B, the baffle plate 55 is provided so that the heat receiving pipe 72 penetrates the baffle plate 55 for the purpose of surely deflecting the flow direction of the combustion gas. It will be. Therefore, when the baffle plate 55 is present at the portion where the drain collects, the flow of the drain passing through the surface of the heat receiving pipe 72 is once blocked by the baffle plate 55, and the film thickness of the drain adhering to the surface of the heat receiving pipe 72 at that portion. May become thicker and heat transfer efficiency may decrease. Therefore, assuming such a situation, it is desirable to reduce the arrangement density of the baffle plates 55 in the lower region of the heat receiving pipe 72 where the drain is likely to gather.

  In consideration of the change in the size of the region through which the combustion gas can pass due to the adhesion of the drain and the viewpoint of the heat transfer efficiency due to the adhesion of the drain, the interval between the baffle plates 55 arranged vertically is lower on the lower side. It is desirable to make it wider than the upper side (in the example shown in FIGS. 14A and 14B, a> b> c> d). By adjusting the distance between the baffle plates 55 in this way, the pressure loss of the combustion gas flowing through the exhaust section 6 can be reduced, and the heat transfer efficiency can be increased.

  When the baffle plate 55 is provided as described above, the drain generated in the heat receiving pipes 71 and 72 falls on the baffle plate 55. Therefore, it is also possible to use the baffle plate 55 to collect the drain as in the case of the receiving unit 40 described above.

  The above-described heat receiving pipe 31 has a zigzag appearance, and is capable of flowing hot water so as to reciprocate in the exhaust section 6, and the heat receiving pipes 71 and 72 flow hot water straight up and down. However, the present invention is not limited to this, and instead of the heat receiving pipe 31 and the heat receiving pipes 71 and 72, for example, a heat receiving pipe wound in a spiral shape as shown in FIG. 75 can also be employed. Even in such a configuration, it is possible to secure a sufficiently large heat transfer area for heat exchange while making the secondary heat exchanger 30 compact.

  Further, when a spiral pipe is employed as in the heat receiving pipe 75 described above, a spiral baffle plate 76 formed along the pipe is prepared, and this is placed below the spiral pipe portion. It is desirable to have a distributed configuration. According to such a configuration, the combustion gas introduced into the exhaust part 6 flows along the spiral baffle plate 76 disposed below the spiral pipe, and the entire surface of the heat receiving pipe 75 is effective for heat transfer. Can be used.

  In addition, although the heat receiving pipe 75 shown in FIG. 15 is wound with substantially the same pitch in the vertical direction, that is, the interval between the upper and lower pipes is substantially the same, the present invention is not limited to this, It is good also as making a pitch differ vertically. More specifically, in the case where the heat receiving pipe 75 is employed, as in the case where the heat receiving pipe 72 described above is adopted, the drain collects downward, and the size of the region through which the combustion gas can pass due to the adhesion of the drain is small. There is a possibility of becoming smaller in the lower region. When such a situation is a concern, it is desirable to make the pitch of the pipe on the lower side larger than the pitch of the pipe on the upper side of the heat receiving pipe 75.

  When the heat receiving pipe 75 described above is employed, a space (a central space 77) through which combustion gas can pass is formed at the turning center position of the spiral pipe portion. When the combustion gas passes through such a space, there is a concern that the heat exchange efficiency is lowered. Therefore, in order to solve such a problem, when the heat receiving pipe 75 is employed, it is desirable to provide a baffle member 78 that can prevent the combustion gas from passing through the central space. As the baffle member 78, for example, a cylindrical body or a columnar body having a size that can be accommodated in the central space 77 can be employed. As described above, if the baffle member 78 is provided, it is possible to prevent the combustion gas from passing through the central space 77 and further promote the heat exchange between the hot water flowing in the heat receiving pipe 75 and the combustion gas. can do.

  As described above, the hot water supply apparatus 1 employs a so-called vaporization type combustion mode in which liquid fuel is vaporized and burned as the combustion unit 2, and sprays liquid fuel as in the so-called reverse combustion system. Combustion noise is small compared to those employing a combustion mode that burns. Therefore, in the hot water supply apparatus 1 described above, it is not necessary to provide a soundproof material in the exhaust part 6 or the like, and the soundproof material gets wet with the drain and causes corrosion or deterioration, or the soundproof material cannot exhibit sufficient soundproof performance. Does not occur.

  The above-described hot water supply apparatus 1 is configured to include the combustion section 2 that adopts a vaporization type combustion form from the viewpoint of generating combustion noise and omitting a soundproof material, but the present invention is limited to this. Instead, any combustion mode such as a conventionally known reverse combustion method may be used as the combustion unit 2. If a problem such as the generation of combustion noise or deterioration of the soundproofing material due to the adhesion of drain is concerned by adopting a reverse combustion type as the combustioning part 2, the soundproofing material is used as the outer wall surface of the exhausting part 6. It is desirable to adopt a configuration that can prevent adhesion of drain to the soundproofing material by attaching to the soundproofing material.

  The exhaust part 6 shown in the above embodiment has a cylindrical shape whose cross-sectional area does not change in the vertical direction. However, the present invention is not limited to this, and for example, as shown in FIG. The heat exchange arrangement area 6x where the heat exchanger 30 is arranged may be narrower than other areas. According to such a configuration, the flow of the combustion gas passing through the secondary heat exchanger 30 is reduced to a speed suitable for heat exchange, and the ventilation resistance of the combustion gas is increased on the upstream side and the downstream side of the secondary heat exchanger 30. It can be prevented from becoming excessively high.

  As shown in FIG. 16, when the upstream region 6y and the downstream region 6z are shaped so as to bulge out from the heat exchange region 6x, the exhaust port 6d and the introduction port 6e are directly above or just below the secondary heat exchanger 30. Can be placed at a position outside of. In order to prevent the drain from leaking from the exhaust port 6d to the outside in the case of such a configuration, as shown in the above embodiment, the scattering prevention unit 60 is disposed directly above the secondary heat exchanger 30. Alternatively, the anti-scattering part 60 may be disposed below the exhaust port 6d as shown in FIG. On the other hand, with respect to the receiving part 40, even if the inlet 6e is provided at a position off the direct side of the secondary heat exchanger 30 as shown in FIG. 16, the drain falling from the secondary heat exchanger 30 It is desirable that the heat exchanger be disposed directly under the secondary heat exchanger 30 so that the heat can be reliably received.

  The hot water supply device 1 shown in the above embodiment can receive the drain generated in the secondary heat exchanger 30 installed in the exhaust unit 6 by the receiving unit 40. For this reason, the hot water supply device 1 employs a material with excellent rust prevention characteristics such as stainless steel for the exhaust collecting portion 5 or is configured so that it does not flow to an unexpected place when drain flows. Therefore, there is no need to take measures for drain inflow. The hot water supply device 1 is not limited to such a configuration, and in addition to providing the receiving portion 40, the exhaust collecting portion 5 is made of stainless steel in case drainage flows into the exhaust collecting portion 5. It may be made of a material excellent in rust prevention characteristics such as.

  In addition, as shown in FIG. 17A, the hot water supply device 1 has a drain discharge right under the exhaust portion 6 or in the vicinity thereof so that even if the drain has entered the exhaust collecting portion 5, it can be immediately discharged. It is also possible to provide the outlet 90 separately. When the drain discharge port 90 is provided, as shown in FIG. 17 (b), the drain collecting portion 5 enters the exhaust collecting portion 5 so that the drain does not flow to an unexpected place and collects at the drain discharging port 90 side. The bottom surface of 5 has a downward slope toward the drain outlet 90 side, or a weir 91 that divides the bottom surface of the exhaust collecting portion 5 into a region below the exhaust portion 6 and another region as shown in FIG. It is good also as a provided structure. Moreover, also when providing the weir 91, it is good also as a structure which inclined the bottom face in the area | region divided by the weir 91 toward the drain discharge port 90 side. By taking these measures, it is possible to minimize inconvenience due to the drain entering the exhaust collecting portion 5.

  In the exhaust part 6 shown in the above embodiment, the configuration in which the “V” -shaped receiving part 40 and the scattering prevention part 60 or the planar receiving part 64 and the scattering prevention part 65 are provided is shown. However, the present invention is not limited to this, and a configuration may be adopted in which one is provided with a “V” -shaped receiving part 40 or scattering prevention part 60 and the other is provided with a planar receiving part 64 or scattering prevention part 65.

  In the above embodiment, the receiving portions 40 and 64 and the scattering preventing portions 60 and 65 are configured to attach a fixing piece (not shown) to the outer wall member 6a by welding. However, the present invention is not limited to this, and screws A configuration using fixing means such as the above may be used.

1 Hot-water supply device 2 Combustion part (combustion means)
3 Combustion case (combustion gas passage)
6 Exhaust part 6d Exhaust port 6e Inlet 7 Neutralizer 10 Receptacle part 11 Weir part 20 Primary heat exchanger 30 Secondary heat exchangers 31, 70, 71, 72, 75 Heat receiving pipe 31a Transverse part 31b Folding part 32 Inlet side Header 33 Water discharge side header 40, 64 Receiving part 41, 42, 67 Wind receiving surface 43, 63 Ridge line part 50 Drain discharge system 60, 65 Scatter prevention part (scattering prevention means)
66 Notch 61, 62, 68 Crossing surface 69 Partition plate 76 Spiral baffle plate 77 Central space 80 Neutralizer

Claims (18)

Combustion means for burning fuel;
A combustion gas passage through which the combustion gas generated along with the combustion operation in the combustion means flows downward;
An exhaust collecting portion that exists downstream in the flow direction of the combustion gas with respect to the combustion gas passage, receives and passes the combustion gas that has passed through the combustion gas passage, and changes the flow direction upward;
An exhaust part that receives and passes the combustion gas sent from the exhaust collection part, and flows and exhausts upward;
An inlet that allows combustion gas to flow into the exhaust,
A primary heat exchanger capable of heating hot water by heat exchange with the combustion gas flowing through the combustion gas passage;
A secondary heat exchanger disposed downstream of the primary heat exchanger in the flow direction of the combustion gas;
A neutralizer capable of neutralizing drain generated in association with heat exchange in the secondary heat exchanger;
A receiving portion that is provided above the inlet and below the secondary heat exchanger, and that receives drain falling from the secondary heat exchanger;
A drain discharge system that bypasses the drain that has fallen to the receiving part and bypasses the exhaust collecting part provided at the lower part of the exhaust part, and directly leads to the neutralizer. A water heater. The receiving portion has a plurality of wind receiving surfaces intersecting with the flow direction of the combustion gas introduced from the inlet to the exhaust portion, and a ridge portion formed between adjacent wind receiving surfaces,
The hot water supply apparatus according to claim 1, wherein the ridge line portion protrudes toward the upstream side in the flow direction of the combustion gas. The receiving part has a flat wind receiving surface that intersects with the flow direction of the combustion gas introduced from the inlet to the exhaust part, and a notch part,
The wind receiving surface is located on the wall surface side of the exhaust part,
The hot water supply device according to claim 1, wherein the wind receiving surface is inclined downward toward the notch portion. The exhaust part has an exhaust port through which combustion gas can be discharged,
Splash prevention means capable of preventing the scattering of drain from the secondary heat exchanger side to the exhaust port side is provided in a region below the exhaust port and above the secondary heat exchanger. The hot water supply device according to any one of claims 1 to 3. The scattering prevention means has a plurality of intersecting surfaces intersecting with the flow direction of the combustion gas introduced from the introduction port into the exhaust portion, and a ridge portion formed between adjacent intersecting surfaces,
The hot water supply apparatus according to claim 4, wherein the ridge line portion protrudes toward the upstream side in the flow direction of the combustion gas. The scattering prevention means has a planar crossing surface that intersects the flow direction of the combustion gas introduced from the inlet to the exhaust part,
The hot water supply apparatus according to claim 4, wherein the intersecting surface is inclined with respect to a plane perpendicular to the flow direction of the combustion gas. A drain outlet that can discharge drain is provided in the exhaust part.
A neutralizer is provided below the exhaust part,
The hot water supply device according to any one of claims 1 to 6, wherein the drain discharge system is formed by connecting the drain discharge port and the neutralizer. A tray portion for receiving drainage to be discharged is provided inside the exhaust portion,
The inlet is provided in the saucer,
The hot water supply device according to any one of claims 1 to 7, wherein a weir portion standing toward the receiving portion is provided at an opening edge of the introduction port. The secondary heat exchanger has a plurality of heat receiving pipes arranged in the exhaust part, a water inlet header, and a water outlet header,
The hot water supply apparatus according to any one of claims 1 to 8, wherein a plurality of heat receiving pipes are respectively connected to the water inlet side header and the water outlet side header.   The heat receiving pipe has a plurality of crossing parts traversing the inside of the exhaust part, and a folding part that connects between the transverse part located on the upstream side in the flow direction of the hot water and the transverse part located on the downstream side. The hot water supply device according to claim 9, wherein the flow of hot water supplied from the upstream crossing portion can be folded back and supplied to the downstream crossing portion. A planar partition plate is provided below one or more of the plurality of transverse parts arranged vertically in the exhaust part,
The partition plate is provided with a notch,
The notch is arranged on the wall surface side of the exhaust part,
The hot water supply apparatus according to claim 10, wherein the partition plate is arranged with a downward slope toward the notch portion. A plurality of heat receiving tubes are arranged in the horizontal direction in the exhaust part,
The space between one heat receiving pipe of the plurality of heat receiving pipes and another heat receiving pipe adjacent to the one heat receiving pipe is wider on the lower side than the upper side of the exhaust part. Item 12. A hot water supply apparatus according to any one of Items 9 to 11.   The hot water supply apparatus according to claim 9, wherein the heat receiving pipe is configured by a spiral pipe and is arranged so as to allow water to flow vertically in the exhaust part. A spiral baffle plate having a spiral shape;
The hot water supply apparatus according to claim 13, wherein the spiral baffle plate is disposed along a lower part of a spiral pipe constituting the heat receiving pipe.   15. A baffle member capable of preventing combustion gas from passing through a central space provided at a turning center position of a spiral pipe portion constituting a heat receiving pipe is provided. The hot water supply device described in 1.   The heat receiving pipe is configured to allow water to flow from a position downstream in the flow direction of the combustion gas flowing through the exhaust portion to a position upstream in the flow direction of the combustion gas. The hot water supply device according to crab.   The hot water supply apparatus according to claim 16, wherein the direction of the hot water flowing in the heat receiving pipe and the direction of the combustion gas flowing in the exhaust section are opposed to each other at all positions.   The hot water supply apparatus according to any one of claims 1 to 17, wherein the combustion means burns fuel gas obtained by vaporizing liquid fuel.

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