KR20220045914A - Plate type heat exchanger - Google Patents

Abstract

The present invention provides a plate-type heat exchanger with few assembly defects and high thermal efficiency. The plate-type heat exchanger (1) is constructed by stacking a plurality of heat exchange bodies (10). Adjacent heat exchange bodies (10) are stacked such that the internal space (14) of one heat exchange body (10) and the internal space (14) of a different heat exchange body (10) communicate through one opening (12e) and a different opening (11e) installed on each heat exchange body (10). The one heat exchange body (10) has an insertion wall (12j) inserted into the different opposite opening (11e) of the different heat exchange body (10) on the edge of the circumference of the one opening (12e). The front end of the insertion wall (12j) has a discontinuous protruding height in a circumferential direction.

Description

Plate heat exchanger {PLATE TYPE HEAT EXCHANGER}

The present invention relates to a plate heat exchanger configured by laminating a plurality of heat exchangers.

A plate type heat exchanger including a plurality of heat exchangers in which an upper heat exchange plate and a lower heat exchange plate are joined has been proposed (eg, Patent Document 1). Each heat exchanger includes an inner space through which a heat medium flows between the upper heat exchange plate and the lower heat exchange plate, and a plurality of through holes that pass through the inner space in a non-communicable state, and through which combustion exhaust flows in the vertical direction. has

Each heat exchanger has at least one opening communicating with the internal space. Moreover, each opening is arrange|positioned so that it may oppose the opening of the adjacent heat exchanger body. For this reason, the adjacent heat exchangers in the said plate type heat exchanger communicate with each other so that a heat medium may flow toward an upper direction through an opening. Moreover, the inflow pipe which supplies a heat medium to one opening of the most downstream heat exchanger located in the most downstream of the gas flow path of combustion exhaust is inserted. Further, an outlet pipe is inserted from the other opening of the most downstream heat exchanger to one opening of the most upstream heat exchanger. Therefore, in this plate type heat exchanger, the heat medium flowing in from the inlet pipe to the most downstream heat exchanger flows from the most downstream heat exchanger toward the most upstream heat exchanger inside the stacked heat exchanger, and flows out from the opening of the most upstream heat exchanger to the outlet pipe. . Thereby, thermal efficiency can be improved.

Japanese Patent Laid-Open No. 2020-85362

By the way, when manufacturing the plate heat exchanger of patent document 1, it is necessary to laminate|stack many upper and lower heat exchange plates, and to join predetermined parts of an upper and lower heat exchange plate by joining means, such as brazing material. For this reason, it is easy to produce an assembly error, and it is easy to displace the openings of the adjacent heat exchanger bodies. When such an opening shift occurs, there is a problem that the heating medium leaks from the internal space to the outside of the heat exchanger.

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above problems, and an object of the present invention is to provide a plate-type heat exchanger with few assembly defects and high thermal efficiency.

According to the present invention,

A plate type heat exchanger configured by stacking a plurality of heat exchangers,

Each heat exchanger is configured to perform heat exchange between a first fluid flowing through the internal space of the heat exchanger and a second fluid flowing outside the heat exchanger,

The adjacent heat exchangers in the plurality of heat exchangers have an opening provided in the one heat exchanger in which the internal space of one heat exchanger and the internal space of the other heat exchanger are provided in the one heat exchanger and the They are stacked so as to communicate through the other opening installed in the other heat exchanger,

The one heat exchanger has an insertion wall inserted into the other opening when the one heat exchanger and the other heat exchanger are stacked on a periphery of the one opening,

The insertion wall is provided with a plate-type heat exchanger in which a tip end is formed to have a discontinuous protruding height in the circumferential direction.

According to the plate heat exchanger, since an insertion wall inserted into the other opening is provided at the periphery of one opening, when one heat exchanger and the other heat exchanger are stacked, one opening facing each other due to an assembly error When the other opening is displaced from the other opening, the insertion wall sits on the peripheral edge of the other opening. For this reason, the clearance gap between adjacent heat exchangers becomes larger than that in an appropriate lamination|stacking state. Thereby, an assembly defect can be confirmed easily.

In addition, one opening and the other opening communicate with the internal space of each heat exchanger, and since the insertion wall is inserted into the other opening, the insertion wall protrudes into the internal space of the other heat exchanger. For this reason, the flow path resistance of the 1st fluid which flows through the inner space in the vicinity of the other opening by an insertion wall increases, and there exists a possibility that thermal efficiency may fall.

However, according to the plate heat exchanger, since the distal end of the insertion wall has a discontinuous protrusion height in the circumferential direction, a notch of a certain width in the circumferential direction is formed at the distal end of the insertion wall. For this reason, even if the insertion wall protrudes into the inner space of the heat exchanger on the other side, since the first fluid flows through the notch, the decrease in the flow path of the first fluid near the opening on the other side is small. Thereby, an increase in the flow path resistance of the first fluid flowing through the internal space due to the insertion wall can be suppressed, and a decrease in thermal efficiency can be prevented.

Preferably, in the plate heat exchanger,

Each of the heat exchangers is formed by joining a set of heat exchange plates,

One heat exchange plate of the set of heat exchange plates has an outer flange portion on its periphery that is erected and installed on one side in the stacking direction of the heat exchangers,

As for the one heat exchange plate and the adjacent heat exchange plate on the side closer to the one heat exchange plate in the heat exchanger adjacent on the one side, the outer peripheral flange portion and the peripheral edge of the proximity heat exchange plate are laminated of the heat exchanger stacked to overlap each other with a predetermined overlap margin in the direction,

The insertion wall is set such that the maximum protruding height of the tip portion is greater than the overlapping width.

According to the plate heat exchanger, the insertion wall is set so that the maximum protrusion height of the tip portion is greater than the overlap width. A gap of a certain height is created between the perimeter edges of the Thereby, an assembly defect can be confirmed reliably.

Preferably, in the plate heat exchanger,

The said insertion wall is formed so that the said front-end|tip part may be located inside the said one opening rather than a base end.

According to the said plate heat exchanger, it becomes easy to guide the insertion wall into the other opening at the time of assembly. Thereby, 　 assembly defects can be further reduced.

Preferably, in the plate heat exchanger,

The said other heat exchanger has a recessed part concave toward the said one opening side in the peripheral part of the said other opening.

According to the plate heat exchanger, since the other heat exchanger has a concave portion concave toward the one opening side on the peripheral edge of the other opening, when the insertion wall is inserted into the other opening, the tip of the insertion wall is different. It is possible to prevent a large protrusion into the inner space of the heat exchanger on the side. Thereby, an increase in the flow path resistance of the first fluid flowing through the inner space in the vicinity of the other opening can be suppressed.

As described above, according to the present invention, it is possible to manufacture a plate heat exchanger of high thermal efficiency with few assembly defects.

1 is a schematic perspective view showing a heat source device having a heat exchanger according to an embodiment of the present invention, partially cut out.
2 is a schematic perspective view showing a partially disassembled heat exchanger according to an embodiment of the present invention.
Fig. 3 is a schematic schematic diagram for explaining the flow of combustion exhaust and heat medium in the heat exchanger according to the embodiment of the present invention.
4 is a schematic exploded perspective view showing two heat exchangers in an upstream region of a gas flow path of combustion exhaust in a heat exchanger according to an embodiment of the present invention.
Fig. 5 is a schematic plan view showing an example of the upper surface of one heat exchange plate constituting the heat exchanger in the heat exchanger according to the embodiment of the present invention.
6 is a schematic plan view showing an example of the upper surface of the other heat exchange plate constituting the heat exchanger in the heat exchanger according to the embodiment of the present invention.
Fig. 7 is a schematic partial perspective view showing an example of the lower surface of the other heat exchange plate shown in Fig. 6 .
8 is a schematic partial cross-sectional view illustrating a heat exchanger according to an embodiment of the present invention.
9 is a schematic partial cross-sectional view showing a heat exchanger according to another embodiment of the present invention.

Hereinafter, a plate type heat exchanger according to the present embodiment and a heat source device having the same will be described in detail with reference to the accompanying drawings.

As shown in FIG. 1 , the heat source device according to the present embodiment uses water (heat medium) as the first fluid flowing into the heat exchanger 1 from the inlet pipe 20 , and the second fluid generated by the burner 31 . It is a hot water heater which heats by combustion exhaust and supplies it to hot water use places (not shown), such as a faucet and a shower, through the outflow pipe 21. Although not shown, the hot water heater is assembled in the casing. In addition, as the heating medium, another heating medium (eg, antifreeze) may be used.

In this hot water heater, the burner body 3 constituting the outer periphery of the burner 31 , the combustion chamber 2 , the heat exchanger 1 , and the drain tray 40 are provided in order from above. Moreover, on one side (right side in FIG. 1) of the burner body 3, the fan case 4 provided with the combustion fan which sends the mixed gas of fuel gas and air into the burner body 3 is provided. Further, on the other side (left side in Fig. 1) of the burner body 3, an exhaust duct 41 communicating with the drain tray 40 is provided. The exhaust duct 41 discharges the combustion exhaust discharged to the drain pan 40 to the outside of the hot water heater.

In addition, in this specification, when the hot water heater is viewed in a state in which the fan case 4 and the exhaust duct 41 are arranged on the sides of the burner body 3, the depth direction corresponds to the front-back direction, and the width direction is left and right Corresponds to the direction, and the height direction corresponds to the up-down direction.

The burner body 3 has an elliptical shape in a plan view, and is formed of, for example, a stainless-based metal. Although not shown, the burner body 3 is opened downward.

The gas introduction part communicating with the fan case 4 protrudes upward from the center part of the burner body 3 . The burner body 3 has a burner 31 having a flat shape with a combustion surface 30 facing downward. By operating the combustion fan, the mixed gas is supplied into the burner body 3 .

The burner 31 is an all-primary air combustion type, for example, a combustion plate made of ceramics having a number of flame holes (not shown) that open downward, or a combustion mat woven with metal fibers into a net shape. is made of The mixed gas supplied into the burner body 3 is ejected downward from the downward combustion surface 30 by the supply pressure of a combustion fan. By igniting this mixed gas, a flame is formed on the combustion surface 30 of the burner 31, and combustion exhaust is produced|generated. Therefore, the combustion exhaust blown out from the burner 31 is sent to the heat exchanger 1 through the combustion chamber 2 . Next, the combustion exhaust passing through the heat exchanger 1 is discharged to the outside of the hot water heater through the drain 40 and the exhaust duct 41 .

That is, in this heat exchanger 1, the upper side provided with the burner 31 corresponds to the upstream side of the gas flow path of combustion exhaust, and the lower side opposite to the side provided with the burner 31 is combustion exhaust. corresponds to the downstream side of the gas flow path of

The combustion chamber 2 has an elliptical shape in a plan view. The combustion chamber 2 is formed of, for example, a stainless-type metal. The combustion chamber 2 is formed by bending a single rectangular metal plate and joining both ends so that it may open up and down.

As shown in FIG. 2 , the heat exchanger 1 has an elliptical shape in a plan view. The heat exchanger 1 is a plate type heat exchanger in which a plurality (here, 13 layers) of thin plate-shaped heat exchangers 10 are laminated. In addition, the heat exchanger 1 may have a case which covers the periphery.

As shown in Figs. 2 and 3, the heat exchanger 1 is configured by stacking a plurality (here, four stages) of blocks 5 having one or a plurality of heat exchangers 10 in an up-down direction. (Hereinafter, when these blocks 5 are generically called, they are simply called "blocks 5". In addition, along the gas flow path of combustion exhaust, the uppermost block 5 is "upstream block 5a", The middle block 5 is in order from the upstream side, the "first downstream block 5b", "the second downstream block 5c", and the lowest block 5 is the "downstream block 5d" called). The uppermost block 5a and the first downstream block 5b are each constituted by one heat exchanger 10 . Moreover, the 2nd downstream block 5c is comprised by the five heat exchanger bodies 10 laminated|stacking, and the most downstream block 5d is comprised by the six heat exchanger bodies 10 laminated|stacking. In addition, the heat exchanger 1 may be comprised by the block 5 of 3 or less or 5 or more. As will be described later, when one block 5 is composed of a plurality of heat exchangers 10 , water runs parallel to the inside of each heat exchanger 10 constituting the one block 5 in the same direction. flows into Moreover, the heat exchanger 10 adjacent in each block 5 communicates with each other so that water may flow toward upper direction from the downward direction. Further, adjacent blocks 5 communicate with each other so that water flows from below to upward. Moreover, in the adjacent block 5, the flow path direction of the water flowing through the inside of each heat exchanger 10 in one block 5 is each heat exchanger 10 in the other block 5. It is configured to be in the opposite direction to the flow path direction of the water flowing through the inside. Accordingly, the heat exchanger 1 has four flow paths (4 passes) according to the number of stages of the block 5, so that the water flow path of each block 5 is folded back between the adjacent blocks 5 is bent Thereby, a long water flow path is formed in the heat exchanger 1, and thermal efficiency can be improved.

Next, the configuration of the heat exchanger 10 will be described. Each of the heat exchangers 10 has a set of upper heat exchange plates 11 having a common configuration, except that some configurations, such as the position of the upper and lower through-holes and the presence or absence of water passage holes in the corners, are different. It is formed by overlapping the lower heat exchange plate 12 with each other in the vertical direction, and joining a predetermined portion to be described later with a joining means such as brazing material. For this reason, below, the structure of the one heat exchanger 10 is mainly demonstrated. In addition, each figure does not necessarily show an actual size, and does not limit embodiment.

2 and 4 to 6 , the upper and lower heat exchange plates 11 and 12 have an elliptical shape in a plan view. The upper and lower heat exchange plates 11 and 12 are formed of, for example, stainless steel metal plates having a predetermined thickness. The upper and lower heat exchange plates 11 and 12 each have a plurality of upper through holes 11a, lower through holes 12a, and upper and lower through holes 11a and 12a formed on almost the entire surface of the plate except for corners. has an upper through-hole flange portion 11c and a lower through-hole flange portion 12c formed on the peripheral edge of the .

An upper peripheral junction part W1 and a lower peripheral junction part W2 which protrude upward as an outer peripheral flange part are respectively formed in the periphery of the upper and lower heat exchange plates 11 and 12, respectively. Each of the upper and lower peripheral edge junctions W1 and W2 is formed as an inclined wall extending upward at a predetermined angle so that the upper end is located obliquely upward and outward from the base end. For this reason, when the upper and lower heat exchange plates 11 and 12 are stacked, in one heat exchanger 10 , the upper heat exchange plate 11 is fitted inside the lower heat exchange plate 12 . In addition, the lower heat exchange plate 12 of the upper heat exchanger 10 is fitted inside the upper heat exchange plate 11 of the heat exchanger 10 adjacent from the lower side. Therefore, when the plurality of upper and lower heat exchange plates 11 and 12 are stacked, the upper and lower heat exchange plates 11 and 12 have peripheral junctions W1 and W2 of the heat exchanger 10 in the stacking direction. They are arranged to overlap each other with a predetermined overlapping width Hp (refer to FIG. 8).

The upper and lower heat exchange plates 11 and 12 are, in one heat exchanger 10, when the lower peripheral junction portion W2 and the lower peripheral edge of the upper heat exchange plate 11 are joined together, the upper and lower heat exchange plates 11 , 12) are set to be spaced apart with a gap of a predetermined height. In addition, the upper and lower heat exchange plates 11 and 12 are heat exchangers at the lower side when the upper peripheral edge junction portion W1 and the lower peripheral edge of the lower heat exchange plate 12 of the heat exchanger 10 adjacent from above are joined together. The upper heat exchange plate 11 of (10) and the lower heat exchange plate 12 of the heat exchanger 10 adjacent from above are set to be spaced apart from each other with a gap of a predetermined height.

Accordingly, by bonding the upper and lower heat exchange plates 11 and 12, an internal space 14 having a predetermined height is formed (refer to FIG. 3). Further, by joining the plurality of heat exchangers 10 together, an exhaust space 15 having a predetermined height is formed between the heat exchangers 10 adjacent to each other in the vertical direction (refer to FIG. 3 ).

In a region excluding the peripheral edge region of the upper and lower heat exchange plates 11 and 12, upper and lower through-holes 11a and 12a, which are square in plan view, are formed in a zigzag shape at predetermined intervals in the front and rear and left and right directions. has been The upper and lower through-hole flanges 11c and 12c formed at the periphery of the upper and lower through holes 11a and 12a, which are square in plan view, have opening edges of the upper and lower through holes 11a and 12a.緣) is horizontally expanded outward in the circumferential direction, and has a square-shaped outer shape when viewed from a planar point of view. In addition, in the peripheral region of the upper and lower heat exchange plates 11 and 12 , upper and lower through holes 11a and 12a, which are pentagonal in plan view, are formed at predetermined intervals in the front and rear or left and right directions. The upper and lower through-hole flanges 11c and 12c formed at the periphery of the upper and lower through-holes 11a, 12a, which are pentagonal in plan view, are perimeters from the opening edge of the upper and lower through-holes 11a, 12a. It is horizontally enlarged outward in the direction and has a pentagonal shape when viewed from a plan view. The upper and lower through-holes 11a and 12a may have other shapes such as a circular shape or an elliptical shape. In addition, all the upper and lower through-holes 11a, 12a may have the same size and shape, and all the upper and lower through-hole flange parts 11c, 12c may have the same size and shape.

The upper and lower through-holes 11a and 12a and the upper and lower through-hole flanges 11c and 12c are respectively formed at positions corresponding to each other when the upper and lower heat exchange plates 11 and 12 overlap each other. In addition, the upper and lower through holes 11a and 12a and the upper and lower through hole flange portions 11c and 12c are opposite to each other when the upper and lower heat exchange plates 11 and 12 overlap each other by drawing processing. The flange portions 11c and 12c are formed on the bottom surface of the stepped portion protruding inward so that the flange portions 11c and 12c are in surface contact.

Therefore, when the upper and lower heat exchange plates 11 and 12 are superimposed on each other and the upper and lower through hole flanges 11c and 12c are joined by a joining means such as brazing material, the upper and lower through hole flanges 11c and 12c are The flange portion 16 for closing the internal space 14 is formed by the (see Fig. 8). Further, a through hole 13 penetrating the inner space 14 in a non-communicating state is formed by the upper and lower through holes 11a and 12a.

Except for the upper heat exchange plate 11 of the uppermost heat exchanger 10 (hereinafter, referred to as "upstream heat exchanger 10a"), the upper and lower heat exchange plates 11 and 12 are each formed in at least one corner portion. , an upper water passage hole 11e and a lower water passage hole 12e. The upper and lower water passage holes 11e and 12e provided in at least one corner of the upper and lower heat exchange plates 11 and 12 forming one heat exchanger 10 have the upper and lower heat exchange plates 11 and 12 mutually connected to each other. When overlapped, it is opened so as to communicate with the inner space 14 formed between the upper and lower heat exchange plates 11 and 12 .

Upper water passage hole flange portions extending horizontally outward in the circumferential direction from the opening edges 11h and 12h of the upper and lower water passage holes 11e and 12e, respectively, on the peripheral edges of the upper and lower water passage holes 11e and 12e (11f), the lower water passage hole flange part 12f is formed. The upper water passage hole 11e and the upper water passage hole flange portion 11f are, respectively, the lower water passage hole 12e and the lower water passage hole 12e of the adjacent heat exchanger 10 when the adjacent heat exchanger 10 overlaps each other. It is formed in the position corresponding to the through-hole flange part 12f. In addition, the upper water passage hole 11e and the upper water passage hole flange portion 11f are drawn, so that the upper heat exchange plate 11 and the lower heat exchange plate 12 of the heat exchanger 10 adjacent from above are drawn. It is formed on the upper surface of the stepped part protruding outward so that the upper and lower water passage hole flange parts 11f and 12f which face each other when overlapped may come into surface contact. Similarly, the lower water passage hole 12e and the lower water passage hole flange portion 12f are drawn, so that the lower heat exchange plate 12 and the upper heat exchange plate 11 of the heat exchanger 10 adjoining from the bottom are drawn. It is formed on the bottom surface of the stepped part protruding outward so that the upper and lower water passage hole flange parts 11f and 12f which face each other when superimposed on each other may make surface contact.

Accordingly, when the upper and lower heat exchange plates 11 and 12 of the adjacent heat exchanger 10 are overlapped with each other, the upper and lower water passage hole flange portions 11f and 12f are joined by a joining means such as brazing filler metal, the upper and lower sides A water passage hole flange portion 64 for blocking the exhaust space 15 between the adjacent heat exchangers 10 is formed by the water passage hole flange portions 11f and 12f (see Fig. 8). In addition, the water passage holes 63 communicating with the internal space 14 are formed by the upper and lower water passage holes 11e and 12e facing up and down in the adjacent heat exchanger 10 . In addition, the inner space 14 in the peripheral portion of the upper and lower water passage holes 11e and 12e is wider in the vertical direction than the other inner spaces 14 . For this reason, an upper concave portion 65 concave upward is formed on the periphery of the upper water passage hole 11e, and a lower concave portion 66 concave downward at the periphery portion of the lower water passage hole 12e. ) is formed.

The lower water passage hole 12e is formed by burring. For this reason, as shown in FIG. 7 and FIG. 8, the lower water passage hole 12e has the insertion wall 12j which protrudes downward (downstream of the gas flow path of combustion exhaust) from the opening edge 12h. In addition, the lower water passage hole 12e of the lower heat exchange plate 12 of the heat exchanger 10 (hereinafter referred to as "the downstream heat exchanger 10s") located at the most downstream of the gas flow path of the combustion exhaust and the other The insertion wall 12j of the lower water passage hole 12e excluding the lower water passage hole 12e on the right rear side of the lower heat exchange plate 12 of the heat exchanger 10 is the opening edge of the lower water passage hole 12e. A cylindrical portion 12m extending downward from 12h, and a plurality of claw portions protruding downwardly spaced apart by a predetermined angle (eg, 120 degrees) in the circumferential direction from the lower end of the cylindrical portion 12m part; 12n). For this reason, the front-end|tip part of the insertion wall 12j has the protrusion height discontinuous in the circumferential direction, and has the notch 12p of a fixed width between the claw parts 12n.

In addition, the insertion wall 12j has the maximum protrusion height of the tip protruding downward from the upper water passage hole 11e when the upper and lower heat exchange plates 11 and 12 overlap each other (that is, the lower end of the claw portion 12n). of the protrusion height) Hs, the lower peripheral edge junction W2 of the lower heat exchange plate 12 in which the insert wall 12j is installed, and the upper water passage hole 11e into which the insert wall 12j is inserted. It is set so that it may become larger than the overlap width Hp between the upper peripheral edge junction parts W1 of the upper heat exchange plate 11 of the heat exchanger 10 adjacent from the downward direction with which it has. In addition, the insertion wall 12j may have the claw part 12n of 2 or less or 4 or more. In addition, when the some claw part 12n is provided, the height of the claw part 12n may differ. Furthermore, the insertion wall 12j may be comprised only with the claw part 12n without the cylindrical part 12m.

The cylindrical portion 12m of the insertion wall 12j has an outer diameter slightly smaller than the inner diameter of the opposite upper water passage hole 11e, and the tip portion of the claw portion 12n has a cylindrical shape. It has an outer diameter slightly smaller than the part 12m. For this reason, the insertion wall 12j is formed so that a front-end|tip may be located inward rather than a base end.

Therefore, in the state in which the upper and lower heat exchange plates 11 and 12 are properly stacked, the insertion wall 12j formed in the lower water passage hole 12e of the lower heat exchange plate 12 is adjacent to the heat exchanger 10 from below. is inserted into the upper water passage hole 11e of the upper heat exchange plate 11, and the distal end of the insertion wall 12j protrudes below the upper water passage hole flange portion 11f. That is, in this embodiment, the lower water passage hole 12e corresponds to one opening, and the upper water passage hole 11e corresponds to the other opening. Further, the upper water passage hole 11e of the upper heat exchange plate 11 may also be formed by burring.

As shown in FIG. 3 , in all of the through-holes 13 of the heat exchanger 10 , the through-hole 13 of one heat exchanger 10 in the adjacent heat exchanger 10 is the other heat exchanger. The through hole 13 of (10) is arranged so as to be shifted in the left-right direction perpendicular to the direction of the gas flow path of the combustion exhaust. That is, in the heat exchanger 10 adjacent up and down, the projection surface of the through hole 13 of one heat exchanger 10 is arrange|positioned so that the through hole 13 of the other heat exchanger 10 does not overlap. Therefore, after the combustion exhaust flowing from the upstream side passes through the through hole 13 of one heat exchanger 10, the exhaust space between the heat exchanger 10 and the heat exchanger 10 adjacent on the downstream side. (15) flows out. And the combustion exhaust flowing out into the exhaust space 15 collides with the upper heat exchange plate 11 of the heat exchanger 10 adjacent on the downstream side, and the through-hole 13 of the heat exchanger 10 adjacent on the downstream side. ) flows further downstream from That is, when the combustion exhaust flows from the upstream side toward the downstream side in the heat exchanger 1 , a zigzag gas flow path is formed in the heat exchanger 1 . Thereby, the contact time of the combustion exhaust in the heat exchanger 1 and the upper and lower side heat exchange plates 11 and 12 increases.

Next, with reference to FIG. 3, combustion exhaust in the heat exchanger 1 and the flow of water are demonstrated. Each block 5 has an inlet 71 for introducing water into the block 5 , and an outlet 72 for introducing water to the outside of the block 5 . The inlet 71 is each constituted by a predetermined lower water passage hole 12e of the heat exchanger 10 located at the most downstream of the gas flow path of the combustion exhaust of each block 5 . In addition, the outlet 72 is a predetermined upper water passage hole of the heat exchanger 10 located upstream of the gas flow path of combustion exhaust in each block 5b, 5c, 5d other than the upstream block 5a. 11e, and a predetermined lower water passage hole 12e of the heat exchanger 10 in the uppermost block 5a. In addition, in FIG. 3, in order to avoid complexity, some structures, such as the flange part 16 and the insertion wall 12j, are abbreviate|omitted.

The inflow pipe 20 is connected to the lower water passage hole 12e of the right front corner part of the lower heat exchanger plate 12 which forms the most downstream heat exchanger 10s. Further, in the lower water passage hole 12e of the right rear corner portion of the lower heat exchanger plate 12 forming the most downstream heat exchanger 10s, a part of the heat exchanger 1 passes through the most downstream heat exchanger 10s. An outlet pipe 21 extending upward from the to the uppermost heat exchanger 10a is inserted therethrough. The upper end of the outlet pipe 21 is inserted through the lower water passage hole 12e at the right rear corner of the lower heat exchange plate 12 forming the uppermost heat exchanger 10a.

The upper end opening of the outlet pipe 21 communicates with the internal space 14 of the uppermost heat exchanger 10a. In addition, when the outlet pipe 21 is inserted from the most downstream heat exchanger 10s to the most upstream heat exchanger 10a, the outlet pipe 21 is inserted into the internal space ( 14) and all exhaust spaces 15 between the adjacent heat exchanger 10 pass through in a non-communicable state.

Therefore, the water flowing into the inner space 14 of each heat exchanger 10 of the most downstream block 5d from the lower water passage hole 12e (inlet 71) of the right front corner is formed in the inner space ( 14) It flows in one of the left and right directions (in FIG. 3, from right to left). Further, the internal space of each heat exchanger 10 of the second downstream block 5c through the upper and lower water passage holes 11e and 12e (the outlet 72 and the inlet 71) of the left front and rear both corners. The water flowing into ( 14 ) flows in one of the left and right directions (from left to right in FIG. 3 ) in the inner space 14 . The flow path direction of the water flowing through the internal space 14 of the heat exchanger 10 of the second downstream block 5c is opposite to that of the most downstream block 5d. Further, the heat exchanger 10 of the first downstream block 5b (hereinafter referred to as " Water flowing into the inner space 14 of the second heat exchanger 10b”) flows in one of the left and right directions (from right to left in FIG. 3 ) in the inner space 14 . The flow path direction of the water flowing through the inner space 14 of the second heat exchanger 10b is opposite to that of the second downstream block 5c. In addition, the water flowing into the inner space 14 of the uppermost heat exchanger 10a through the upper and lower water passage holes 11e and 12e (the outlet 72 and the inlet 71) of the left front and rear both corners, It flows in one of the left and right directions (from left to right in FIG. 3 ) in the interior space 14 . The flow path direction of the water flowing through the inner space 14 of the uppermost heat exchanger 10a is opposite to that of the second heat exchanger 10b. Then, the water flowing in the inner space 14 of the upstream heat exchanger 10a is inserted into the lower water passage hole 12e (the outlet 72) of the right rear corner of the upstream heat exchanger 10a. It flows out through the outlet pipe (21). Water flowing out to the outlet pipe 21 flows down the outlet pipe 21 and flows out to the outside of the heat exchanger 1 . In this way, in the uppermost heat exchanger 10a and the second heat exchanger 10b in the upstream region of the gas flow path of the combustion exhaust, all water flowing into the second heat exchanger 10b is transferred to the uppermost heat exchanger 10a. ) and connected in series. Moreover, the some heat exchanger 10 of the most downstream block 5d is connected in parallel so that a some parallel flow path may be formed. The second downstream block 5c also has the same configuration as the most downstream block 5d.

Next, the manufacturing method of the heat exchanger 1 of this embodiment is demonstrated. One lower frame plate 101, a predetermined number of upper and lower heat exchange plates 11 and 12, and one upper frame plate 102 are joined together while supplying a bonding means such as brazing material to a predetermined portion. laminated. Although not shown, the outer diameter of the tubular portion 12m of the lower water passage hole 12e of the lower heat exchange plate 12 of the most downstream heat exchanger 10s is greater than the inner diameter of the opening of the corresponding lower frame plate 101 . It is set slightly small.

Then, the upper end of the inlet pipe 20 is inserted through the opening of the lower frame plate 101 through the lower water passage hole 12e on the right front side of the most downstream heat exchanger 10s. Further, through the other opening of the lower frame plate 101, the outlet pipe 21 is inserted upwardly from the lower water passage hole 12e on the right rear side of the downstream heat exchanger 10s. Then, the outer peripheral surface of the inlet pipe 20 inserted through the lower water passage hole 12e on the right front side of the most downstream heat exchanger 10s, and the lower water passage hole on the right rear side of the most downstream heat exchanger 10s ( A subassembly is prepared by supplying a bonding means such as brazing material to the outer peripheral surface of the outflow pipe 21 inserted through 12e). The heat exchanger 1 can be manufactured by injecting|throwing-in this subassembly in a furnace and performing a brazing process.

As described above, a communication path for communicating the internal space 14 of the adjacent heat exchanger 10 through the upper and lower water passage holes 11e and 12e facing up and down in the adjacent heat exchanger 10 . The water passage hole 63 used as (連通道) is formed. On the other hand, in the plate heat exchanger 1 configured by stacking a plurality of upper and lower heat exchange plates 11 and 12 , the opposed upper and lower water passage holes 11e and 12e are likely to be displaced due to assembly errors. For this reason, there exists a possibility that the assembly defect in which the upper and lower heat exchange plates 11 and 12 are not properly joined in the water passage hole flange part 64 of the peripheral part of the water passage hole 63 may arise. When such assembly defect occurs, the internal space 14 and the exhaust space 15 communicate, and water leaks from the peripheral portion of the water passage hole 63 to the exhaust space 15 .

However, according to this embodiment, since the insertion wall 12j extending downward is provided in the periphery of the lower water passage hole 12e which forms the water passage hole 63, suitably the heat exchanger 10 ) is not laminated, the insertion wall 12j protruding downward from the peripheral edge of the lower water passage hole 12e is on the upper surface of the upper heat exchange plate 11 at the peripheral edge of the upper water passage hole 11e. It sits up, and an inclination occurs in the lower heat exchange plate 12 adjacent from above. Thereby, an assembly defect can be confirmed easily.

Moreover, in this embodiment, since the claw part 12n is formed in the front-end|tip part of the insertion wall 12j so that the protrusion height in the circumferential direction may become a discontinuous state, one claw part 12n is the upper part below. Even if it is disposed in the passage hole 11e, if another claw portion 12n sits on the periphery of the upper water passage hole 11e due to an assembly error, it is also inclined to the lower heat exchange plate 12 adjacent from above. Occurs. Thereby, an assembly defect can be confirmed reliably.

In addition, according to this embodiment, since the insertion wall 12j protrudes into the inner space 14 of the adjacent heat exchanger 10 through the upper water passage hole 11e, water flows into the upper water passage hole 11e. When flowing in the vicinity, the flow resistance of water tends to increase due to the insertion wall 12j. However, according to this embodiment, since the distal end of the insertion wall 12j has a discontinuous protruding height, a notch 12p is formed in the distal end of the insertion wall 12j. For this reason, even if the insertion wall 12j protrudes into the inner space 14 of the adjacent heat exchanger 10, since water flows through the notch 12p, the water passage in the vicinity of the upper water passage hole 11e The decrease is small. Accordingly, it is possible to suppress an increase in the flow resistance of the water flowing in the inner space 14 due to the insertion wall 12j. In particular, in the present embodiment, since the upper concave portion 65 concave upward is formed on the peripheral edge of the upper water passage hole 11e into which the insertion wall 12j is inserted, the insertion wall 12j is disposed on the other side. It is possible to prevent a large protrusion into the inner space 14 of the heat exchanger 10, and furthermore, it is possible to suppress an increase in the flow resistance of water. Accordingly, it is possible to smoothly flow water from the internal space 14 of the one heat exchanger 10 to the internal space 14 of the other heat exchanger 10 . Thereby, the fall of thermal efficiency can be suppressed.

Further, according to the present embodiment, the plurality of heat exchangers 10 are disposed on the inner side of the upper peripheral junction portion W1, which is an outer peripheral flange portion provided on the peripheral edge of the upper heat exchange plate 11 , at the bottom of the lower heat exchange plate 12 . The surface peripheral edge is fitted, and the bottom peripheral edge of the upper heat exchange plate 11 is fitted inside the lower peripheral junction part W2 which is an outer peripheral flange part provided on the peripheral edge of the lower heat exchange plate 12 . Then, when the insertion wall 12j is properly inserted in the upper water passage hole 11e, the upper and lower heat exchange plates 11 and 12 are stacked so as to overlap each other with a predetermined overlapping width Hp. On the other hand, the maximum protruding height Hs of the tip of the insertion wall 12j is greater than the overlapping width Hp. For this reason, when the insertion wall 12j sits on the periphery of the upper water passage hole 11e due to an assembly error, a gap will arise between the periphery of the adjacent heat exchanger 10. FIG. That is, in the present embodiment, the upper heat exchange plate 11 of one heat exchanger 10 corresponds to one heat exchange plate, and in the upper heat exchange plate 11 in the heat exchanger 10 adjacent from above, The lower side heat exchange plate 12 on the near side corresponds to the proximity heat exchange plate. In particular, in this embodiment, since the water passage hole 63 is provided in the corner part of the periphery of the heat exchanger 10, the said clearance gap is visually confirmed easily. Thereby, an assembly defect can be confirmed reliably.

Furthermore, according to this embodiment, since the front end of the insertion wall 12j is formed so as to be located inside the upper water passage hole 11e rather than the base end, when stacking the plurality of heat exchange plates 11 and 12, the insertion The wall 12j is likely to be guided into the upper water passage hole 11e. Thereby, assembly defect can be further reduced.

In addition, in this embodiment, the insertion wall provided in the peripheral part of the lower water passage hole is inserted into the upper water passage hole which opposes. However, the insertion wall provided at the periphery of the upper water passage hole may be inserted into the opposite lower water passage hole. In this case, the upper water passage hole corresponds to one opening, and the lower water passage hole corresponds to the other opening.

(Other embodiments)

(1) In the above embodiment, each of the upper and lower heat exchange plates has upper and lower peripheral junction portions serving as outer peripheral flange portions. However, as shown in FIG. 9 , only either one of the upper and lower heat exchange plates 11 and 12 may have an outer peripheral flange portion erected on one side in the stacking direction of the heat exchanger 10 . In this case, similarly to the above embodiment, the insertion wall 12j has a maximum protrusion height Hs at the tip of the one side of the heat exchanger adjacent to the outer flange portion W1 of the upper heat exchange plate 11 on one side. The lower side heat exchange plate 12 in (10) (that is, in the heat exchanger 10 adjacent from one side, the lower side heat exchange plate on the side closer to the upper heat exchange plate 11 of the lower heat exchanger 10 ( 12)) is set to be larger than the overlap width (Hp) between the peripheral edges.

(2) In the said embodiment, a heat exchanger has several blocks from which the flow path direction of a 1st fluid differs. However, the heat exchanger may be constituted by one block. In this case, the first fluid flows in the same direction through all the heat exchangers.

(3) In the said embodiment, the burner which has a combustion surface facing downward is provided above a heat exchanger. However, a burner having a combustion surface facing upward may be provided below the heat exchanger. In this case, since the flow path of combustion exhaust is reversed up and down, the uppermost heat exchanger corresponds to the most downstream heat exchanger, and the lowermost heat exchanger corresponds to the uppermost heat exchanger. In addition, combustion exhaust may flow in a left-right direction through a plate type heat exchanger.

(4) In the said embodiment, the insertion wall extends toward the other opening from the opening edge of one opening. However, as long as the insertion wall can be inserted into the other opening, the insertion wall may extend from a predetermined position outside the opening edge of the one opening toward the other opening in the circumferential direction.

(5) In the above embodiment, a heating medium is used as the first fluid flowing through the internal space of the heat exchanger, and combustion exhaust is used as the second fluid flowing through the outside of the heat exchanger. However, combustion exhaust may be used as the first fluid, and a heating medium may be used as the second fluid.

(6) In the above embodiment, a plurality of heat exchangers are stacked vertically. However, the plurality of heat exchangers may be stacked on the left and right.

(7) In the above embodiment, a hot water heater is used, but a heat source device such as a boiler may be used.

1 plate heat exchanger
10 heat exchanger
11e upper water passage hole
12e lower water passage hole
12j insert wall
14 interior space
65 upper recess

Claims (4)

A plate type heat exchanger configured by stacking a plurality of heat exchangers,
Each heat exchanger is configured to perform heat exchange between a first fluid flowing through the internal space of the heat exchanger and a second fluid flowing outside the heat exchanger,
In the plurality of heat exchangers adjacent to each other, the internal space of one heat exchanger and the internal space of the other heat exchanger include one opening provided in the one heat exchanger and the They are stacked so as to communicate through the other opening installed in the other heat exchanger,
The one heat exchanger has an insertion wall inserted into the other opening when the one heat exchanger and the other heat exchanger are stacked on a periphery of the one opening,
The insertion wall is a plate-type heat exchanger in which a tip portion is formed to have a discontinuous protrusion height in a circumferential direction. According to claim 1,
Each of the heat exchangers is formed by joining a set of heat exchange plates,
One heat exchange plate among the set of heat exchange plates has an outer flange portion on its periphery that is erected on one side in the stacking direction of the heat exchangers,
As for the one heat exchange plate and the adjacent heat exchange plate on the side closer to the one heat exchange plate in the heat exchanger adjacent on the one side, the outer peripheral flange portion and the peripheral edge of the proximity heat exchange plate are laminated of the heat exchanger stacked to overlap each other with a predetermined overlap margin in the direction,
The insertion wall is set such that the maximum protruding height of the tip portion is greater than the overlapping width. 3. The method of claim 1 or 2,
The insertion wall is a plate type heat exchanger in which the front end is formed to be located inside the one opening rather than the base end. 4. The method according to any one of claims 1 to 3,
The said other heat exchanger has, in the peripheral part of the said other opening, the recessed part which is recessed toward the said one opening side, the plate type heat exchanger.

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