JP2003343992A - Laminated type heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a laminated type heat exchanger minimizing a non-flow passage part to increase heat exchange efficiency and reducing manufacturing cost and having a compact and simple configuration. <P>SOLUTION: A second heat exchanger 5 of laminated type is constituted by laminating a plurality of flow passage forming bodies 10 and a plurality of external fins 12 alternately. Each flow passage forming body 10 of the second heat exchanger 5 has a pair of plate members 20, 21 forming a flow passage 10a inside it and an inner fin 31 provided fixedly in the flow passage 10a between a pair of plate members 20 and 21. The inner fin 30 has a beltlike partition wall 31 for partitioning a part between a flow passage 41 and a flow passage 42 adjacent to the flow passage 41. A U-shaped flow passage 40 is formed by the partition wall 31. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a laminated heat exchanger formed by stacking a plurality of flow passage forming bodies, and more particularly to a flow passage and an adjoining flow passage formed by a partition wall of inner fins of each flow passage forming body. The present invention relates to a partition that partitions the flow path.

[0002]

2. Description of the Related Art Hitherto, various laminated heat exchangers each having a plurality of flow passage forming bodies each having a flat flow passage formed therein have been put to practical use. For example, JP-A-6-123581
In the laminated heat exchanger described in the publication, a plurality of flow passage forming bodies (flat tubes) and a plurality of external fins (corrugated fins) are alternately laminated, and each flow passage forming body is arranged in a facing manner. It has a pair of plates provided and corrugated inner fins fixedly provided between the pair of plates.

The pair of plates are each formed with partition grooves extending in the lengthwise direction such that the central portion in the width direction is recessed from the outer side to the inner side. The pair of partition groove portions are closely contacted with each other through inner fins. The partition grooves divide the spaces between the channels to form flat U-shaped channels. still,
Grooves different from the partition grooves are formed in the pair of plates, and inner fins are fixed in a sandwiched manner between the partition grooves and the grooves.

Further, in the laminated heat exchanger described in Japanese Utility Model Registration No. 2515795, Japanese Patent Laid-Open No. 6-
Similarly to the Japanese Patent No. 123581, a plurality of flow path forming bodies (tube elements) and a plurality of external fins are alternately stacked, and each flow path forming body includes a pair of plates arranged to face each other. And a corrugated inner fin fixedly provided between the plates.

In this laminated heat exchanger, a flat U-shaped flow path is formed by forming a part of the inner fin in the width direction into a partition part in the length direction for partitioning the flow paths. In detail, so as to partition the fluid inlet and the fluid outlet arranged in parallel,
The pair of plates are each formed with a projection that extends slightly in the longitudinal direction so as to be recessed from the outside to the inside.
The inner fin is sandwiched by the pair of convex portions, and the two channels of the corrugated inner fin including the sandwiched portion partition the space between the flow paths.

[0006]

[Problems to be Solved by the Invention]
No. 81, a partition groove is formed in each of a pair of plates to form a flat U-shaped flow path.
In the case where the pair of partitioning groove parts are closely adhered to each other to partition the flow paths, the partitioning part becomes a relatively large non-flowing part that does not form a flow path, and moreover, it is located on the outer surface side of the partitioning groove of the plate. Since it becomes difficult to arrange and closely contact the external fins, in order to obtain the desired heat exchange efficiency (to ensure the required flow channel capacity (flow channel length)), the flow channel forming body, that is, the laminated type The heat exchanger becomes large.

In the laminated heat exchanger disclosed in Japanese Unexamined Patent Publication No. 6-123581, in order to sandwich and fix the inner fins with a pair of plates, a groove different from the partition groove is formed in the pair of plates. Therefore, the non-flow path portion becomes larger, and the stacked heat exchanger becomes larger in size to obtain the desired heat exchange efficiency. Moreover, since the partition groove and the groove must be formed in the pair of plates, the plate molding becomes complicated, and as a result, the manufacturing cost of the laminated heat exchanger becomes expensive.

In the laminated heat exchanger of Japanese Utility Model Registration No. 2515795, in each flow passage forming member, a part in the width direction of the inner fin is a partition portion in the length direction for partitioning the flow passages. The part becomes two peaks of the corrugated inner fin, and the part becomes a large non-flow path part that does not form a flow path, so the flow path forming body becomes large to obtain the desired heat exchange efficiency, and the laminated type The manufacturing cost of the heat exchanger is also high.

An object of the present invention is to provide inner fins fixedly in the flow passage of the flow passage forming member, and to provide a space between the flow passage and the flow passage adjacent to the flow passage by a strip-shaped partition wall of the inner fin. By partitioning, the non-flow path portion is made as small as possible to improve heat exchange efficiency, and it is possible to provide a laminated heat exchanger that can be made compact and simple and can be manufactured at low cost.

[0010]

Means for Solving the Problems The laminated heat exchanger according to claim 1 is a laminated heat exchanger formed by laminating a plurality of flow passage forming bodies each having a flat flow passage formed therein. The channel forming body has a pair of plate members forming a channel therein, and an inner fin fixedly provided in the channel between the pair of plate members. It is characterized in that it has a strip-shaped partition wall for partitioning the flow path adjacent to the flow path, and the partition wall forms a U-shaped or meandering flow path.

In this laminated heat exchanger, the inner fins are fixedly provided in the flow passage between the pair of plate members of each flow passage forming member, and the flow passages are formed by the strip-shaped partition walls of the inner fins. The flow path adjacent to the flow path is partitioned to form a U-shaped or meandering flow path. Each flow path forming body is heated from the outside, and the heat is transferred to the fluid in the flow path via the plate member and the inner fins to exchange heat.

Since the flow path and the flow path adjacent to the flow path are partitioned by the strip-shaped partition wall of the inner fin, the non-flow path portion by this partition wall can be made as small as possible, and the desired In order to obtain heat exchange efficiency (to secure the required flow path capacity (flow path length)), it is not necessary to make the flow path forming body, that is, the laminated heat exchanger larger than the conventional one. . That is, it is possible to improve the heat exchange efficiency and reduce the size of the stacked heat exchanger by eliminating the useless portion that hardly contributes to heat absorption. Moreover, since it is not necessary to form partition grooves or the like on each plate to partition the flow paths, the plate molding is simplified, and the laminated heat exchanger can be easily configured. The manufacturing cost of can be reduced.

A laminated heat exchanger according to a second aspect of the present invention is characterized in that, in the first aspect of the present invention, at least a portion of the plate member facing the inner fin is formed in a flat plate shape. In the case of configuring a laminated heat exchanger by alternately laminating a plurality of flow path forming members and a plurality of external fins, etc., on the outer surface side of the flat plate-shaped portion facing at least the inner fins of the plate member, The external fins can be easily and surely arranged and brought into close contact with each other, and the external fins can be formed on the outer surface of the partition of the flow path, so that the heat exchange efficiency can be further enhanced.

A laminated heat exchanger according to a third aspect of the present invention is characterized in that, in the second aspect of the present invention, band-shaped contact portions that are in contact with the plate member are integrally formed on both edges of the partition wall of the inner fin. It is a thing. The partition wall of the inner fin can reliably partition the flow path from the flow path adjacent to the flow path.

The laminated heat exchanger according to claim 4 is characterized in that
In the invention of any one of 3 above, the inner fin has a plurality of partitions that intermittently partition a pair of plate members, and the plurality of partitions are intermittently arranged in a flow direction. It is what The heat exchange efficiency can be improved by increasing the surface area of the inner fins that come into contact with the fluid in the flow path and generating turbulent flow.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. The present embodiment is an example of the case where the present invention is applied to a gas water heater. As shown in FIGS. 1 and 2, the gas water heater 1 includes a burner 2, a fan 3, a first heat exchanger 4, and a second heat exchanger 5, and the fan 3 is arranged below the burner 2. , The first heat exchanger 4 is disposed above the burner 2, and the second heat exchanger 4 is disposed above the first heat exchanger 4.
A heat exchanger 5 is provided.

A water inlet pipe 6 and a hot water outlet pipe 7 are connected to the gas water heater 1, and the water supplied from the water supply or the like through the water inlet pipe 6 is first introduced into the second heat exchanger 5 to generate the second heat. It is introduced into the first heat exchanger 4 from the exchanger 5 via the relay pipe 8, and is led out to the outside from the first heat exchanger 4 via the tap pipe 7.

Fuel gas is supplied to the burner 2 from a gas supply pipe 9, and when the fuel gas is burned in the burner 2, the combustion gas passes through a first heat exchanger 4 and then a second heat exchange. After passing through the heat exchanger 5, the sensible heat and latent heat of the combustion gas are given to the first and second heat exchangers 4 and 5, and the inside of the first and second heat exchangers 4 and 5 is thereby given. The water passing through is heated and hot water is discharged from the hot water discharge pipe 7 to the outside.

In the present embodiment, the present invention is applied to the second heat exchanger 5. However, the present invention may be applied to the first heat exchanger 4. Hereinafter, the second heat exchanger 5 will be described in detail. The front and left sides of FIGS. 2 and 3 will be described as the front and left sides.

As shown in FIGS. 2 to 7, the second heat exchanger 5
Includes a plurality of flow path forming bodies 10 each having a flat flow path 10a formed therein and a plurality of external fins 11, and the plurality of flow path forming bodies 10 and the plurality of external fins 11 are alternated in the left-right direction. Is a laminated heat exchanger laminated on the
A passage 13 for the combustion gas is formed between the two flow passage forming bodies 10 that are adjacent to each other via 1. The second heat exchanger 5 is arranged inside the heat exchanger case 12, and the second heat exchanger 5 is provided.
The end plates 28 and 29 are fixed to the side wall 12a of the heat exchanger case 12 with screws.

As shown by the arrow in FIG. 4, the combustion gas is introduced laterally inward from the opening 12c formed in the rear wall 12b of the heat exchanger case 12, and the combustion gas is guided by the partition plate 14. And flows downward and passes through the plurality of passages 13 of the second heat exchanger 5 from the upper side to the lower side.
The combustion gas that has passed through the passage 13 passes through the front side of the second heat exchanger 5 and is discharged to the outside from the opening 12e formed in the front wall 12d of the heat exchanger case 12.

Mainly, while the combustion gas passes through the passage 13, the latent heat of the combustion gas is given to the flow path forming member 10 directly or via the external fin 11. The combustion gas gives latent heat to the second heat exchanger 5 to condense when the temperature becomes below the dew point, and drain water is generated in the vicinity of the second heat exchanger 5. The drain water generated in the heat exchanger case 12 is
2 falls to the bottom wall 12f that is inclined forward and downward, flows along the bottom wall 12f, and then flows down from the discharge port 15 to a neutralization device (not shown).

As shown in FIGS. 4 to 8, the second heat exchanger 5
Each of the flow path forming bodies 10 is fixedly provided in the flow path 10a between the pair of plate members 20 and 21 made of stainless steel, which forms the flow path 10a therein, and between the pair of plate members 20 and 21. And an inner fin 30 made of stainless steel. Outer edge portions of the pair of plate members 20 and 21 are in surface contact with each other, and further, the outer edge portion of the plate member 21 is bent to engage with the outer edge portion of the plate member 20 and fixed in a liquid-tight manner by brazing. These plate members 20, 2
A hot water outlet portion 23 and a water inlet portion 22 are vertically formed at the front end portion of 1, and a flow path 10a is formed between the plate members 20 and 21 on the rear side.

The water inlet portion 22 and the hot water outlet portion 23 are respectively provided in the flow path 10a.
And the water inlet portions 22 of the adjacent flow passage forming bodies 10 are fluid-tightly communicated with each other, and the hot water outlet portions 2 of the adjacent flow passage forming bodies 10 are communicated with each other.
The three are fluid-tightly connected to each other. The water inlet port 2 in which the end plate 28 is fixed to the flow path forming body 10 at the left end of the second heat exchanger 5 and is fixed to the left end side of the end plate 28
6 and the hot water outlet port 27 are fluid-tightly connected to the water inlet portion 22 and the hot water outlet portion 23 via end plates 28, respectively.
The water inlet port 26 is connected to the water inlet pipe 6, and the hot water outlet port 27 is connected to the relay pipe 8.

Each of the water inlet 22 and the hot water outlet 23 is open at the left and right sides for connecting the adjoining water inlet 22 and hot water outlet 23, but a flow path is formed at the right end of the second heat exchanger 5. End plates 29 are fixed in contact with the water inlet 22 and the hot water outlet 23 of the body 10 to close their openings. In this way, the water supplied to the water inlet port 26 is introduced into the plurality of flow path forming bodies 10 from the water inlet portion 22, heated, and then led out of the hot water outlet portion 23, and led out of the hot water outlet port 27 to the relay pipe 8.

As shown in FIGS. 6 to 8, each flow path forming member 5
The inner fins 30 include a partition plate 31, a plurality of partition pieces 3
2. A plurality of vertical piece portions 33 and 34 are integrally formed. The inner fin 30 is, for example, a rectangular shape having a thickness substantially equal to the width between the pair of plate members 20 and 21 and slightly longer in the front-back direction in a side view when the plate-shaped base material is press-molded with a large number of cuts. And is housed in almost the entire flow path 10a.

The partition wall 31 is formed in a strip shape that is long in the front-rear direction at the central portion in the up-down direction, and the inner fin 3 is formed.
It is formed substantially parallel to the horizontal plane in the front-rear length 3/4 portion from the front end of 0. The partition wall 31 separates a wide straight rectilinear flow passage 41 from a similar wide straight rectilinear flow passage 42 adjacent to the flow passage 41, and also the U-turn portion 43.
Are formed, and the flow paths 41, 42 and the U-turn portion 43 form a flat U-shaped flow path 40. A substantially V-shaped partition portion 24 is integrally formed on the plate member 21 at the front end boundary portion of the flow channel 10a, and a corner portion of the partition portion 24 is brought into close contact with the partition wall 31 to form the flow channels 41 and 42. It is completely partitioned.

The plurality of partitions 32 partition the pair of plate members 20, 21 intermittently, and are arranged in a plurality of rows intermittently in the front-rear direction (flow direction). Multiple vertical strips 3
3, 34 are formed so as to be continuous with the partition wall 31 and the plurality of partition pieces 32, the vertical piece portion 33 is closely attached to the plate member 20 and fixed by brazing, and the vertical piece portion 34 is closely attached to the plate member 21 and brazed. It is fixed by. A pair of strip-shaped contact portions 35 and 36 forming a part of the vertical piece portions 33 and 34 that are in close contact with the plate members 20 and 21 are integrally formed on both left and right edges of the partition wall 31 of the inner fin 30.

The operation and effect of the second heat exchanger 5 will be described. The second heat exchanger 5 includes a plurality of flow path forming bodies 10 each having a flat U-shaped flow path 40 and a plurality of external fins 1.
1 and 2 are alternately laminated, and each flow path forming body 10 includes a pair of plate members 20 and 21 that form a flow path 10a therein.
And the flow path 10 between the pair of plate members 20 and 21.
The inner fin 30 is fixedly provided in a, and the inner fin 30 has a strip-shaped partition wall 31 that partitions between the flow channel 41 and the flow channel 42 adjacent to the flow channel 41.

In each flow path forming body 10 of the second heat exchanger 5, the flow path 41 and the flow path 41 are adjacent to each other by the strip-shaped partition wall of the inner fin 30 fixedly provided in the flow path 10a. The flow path 42 is partitioned from the flow path 42, the U-turn portion 43 is formed, and the flat U-shaped flow path 40 is formed. The combustion gas generated by the gas combustion of the burner 2 forms each flow path of the second heat exchanger 5. Latent heat is applied to the body 10 to heat each flow path forming body 10, and the heat is transferred to the water flowing in the flow path 40 through the plate members 20 and 21 and the inner fins 30 to exchange heat.

Since the flow path 41 and the flow path 42 adjacent to the flow path 41 are partitioned by the band-shaped partition wall 31 of the inner fin 30, the non-flow path portion by the partition wall 31 is made as small as possible. In order to obtain a desired heat exchange efficiency, that is, in order to secure a necessary flow channel capacity (flow channel length), the flow channel forming member 10, that is, the second heat exchanger, is different from the conventional one. It is not necessary to make 5 large. That is,
It is possible to eliminate the useless portion that hardly contributes to heat absorption, improve the heat exchange efficiency of the second heat exchanger 5, and reduce the size. The pressure resistance of the flow path forming body 10 can be improved by providing the inner fin 30 inside.

Moreover, since it is not necessary to form partition grooves or the like in the plate members 20 and 21 in order to partition the flow paths 41 and 42, the plate members 20 and 21 can be easily molded (the plate member 20 is omitted. In order to provide the inner fins in almost the entire flat U-shaped flow passage 40, one inner fin 30 may be provided in each flow passage forming body 10 in order to form a flat plate shape and very easy to form. Since it is good, the number of parts of the second heat exchanger 5 can be reduced, and thus the second heat exchanger 5 can be reduced.
The heat exchanger 5 can be simply configured to reduce the manufacturing cost of the second heat exchanger 5.

Further, since at least a portion of the plate members 20 and 21 facing the inner fin 30 can be formed in a flat plate shape, a plurality of flow path forming bodies 10 and a plurality of outer fins 11 are alternately laminated. And then the second heat exchanger 5
When configuring the above, the external fins 11 can be easily and reliably arranged and adhered to the outer surface side of at least the flat plate-shaped portion of the plate members 20 and 21 facing the inner fins 30, and the flow path partitioning can be performed. Since it is possible to form the external fins also on the outer surface portion of the portion, the heat exchange efficiency of the second heat exchanger 5 can be further enhanced.

The strip-shaped close contact portions 3 that are in close contact with the plate members 20 and 21 are provided at both edges of the partition wall 31 of the inner fin 30.
Since 5, 5 are integrally formed, the partition wall 31 of the inner fin 30 can reliably partition the flow path 41 and the flow path 42 adjacent to the flow path 41.

The inner fin 30 is a plurality of partitions 32 which partition the pair of plate members 20 and 21 intermittently and which are arranged in a plurality of rows intermittently in the flow direction. Therefore, the heat exchange efficiency of the second heat exchanger 5 can be increased by increasing the surface area of the inner fins 30 in contact with the water in the flow path 40 and generating a turbulent flow.

In each flow path forming member 10, a plurality of band-shaped partition walls may be formed on the inner fin 30, and the meandering flow paths may be formed by these partition walls. As a result, the flow path length can be made longer than that of the U-shaped flow path of the above embodiment, and the heat exchange efficiency can be improved. For example, as shown schematically in FIG. 9, when three strip-shaped partition walls 50 to 52 are formed on the inner fin 30, a meandering flow passage 55 having three U-turn portions 56 to 58 is formed. You can

Further, a plurality of inner fins may be provided in each flow path forming body 10, and the inner fins may be arranged in a direction in consideration of the flow direction and the like. However, the inner fin having the partition wall that partitions the flow path from the flow path adjacent to the flow path is disposed over the adjacent flow path.

In addition, various modifications can be added and implemented without departing from the gist of the present invention. Further, as in the above embodiment, the heat exchanger is not limited to the second heat exchanger of the gas water heater, and may be a laminated heat exchanger formed by stacking a plurality of flow passage forming bodies each having a flat flow passage. It is possible to apply the present invention.

[0039]

According to the laminated heat exchanger of claim 1,
Each flow path forming body has a pair of plate members forming a flow path therein, and an inner fin fixedly provided in the flow path between the pair of plate members. Since there is a band-shaped partition wall for partitioning between the flow channel and the flow channel adjacent to the flow channel, and the U-shaped or meandering flow channel is formed by this partition wall, the non-flow channel portion by this partition wall Can be made as small as possible to eliminate a wasteful part that hardly contributes to heat absorption, and the heat exchange efficiency of the laminated heat exchanger can be improved to achieve miniaturization. Moreover, in order to partition the flow paths, it is not necessary to form partition grooves or the like on each plate, so that plate molding becomes easy and a laminated heat exchanger can be easily configured.
It is possible to reduce the manufacturing cost of the laminated heat exchanger.

According to the laminated heat exchanger of the second aspect, since at least the portion of the plate member facing the inner fins is formed in a flat plate shape, the plurality of flow path forming bodies and the plurality of outer fins are alternately arranged. When the laminated heat exchanger is formed by stacking the external fins, the external fins can be easily and reliably arranged and adhered to at least the outer surface side of the flat plate-shaped portion of the plate member facing the inner fins. ,
Since the external fins can be formed on the outer surface of the partition of the flow path, the heat exchange efficiency of the laminated heat exchanger can be further improved.

According to the laminated heat exchanger of the third aspect, since the strip-shaped close contact portions that are in close contact with the plate member are integrally formed on both edges of the partition wall of the inner fin, the partition wall of the inner fin allows the flow to flow. It is possible to reliably partition the passage from the passage adjacent to the passage.

According to the laminated heat exchanger of the fourth aspect, the inner fins are a plurality of partitions for intermittently partitioning the pair of plate members, and the plurality of partitions are arranged intermittently in the flow direction. The heat exchange efficiency can be improved by increasing the surface area of the inner fins that come into contact with the fluid in the flow path and generating a turbulent flow because the partition is included.

[Brief description of drawings]

FIG. 1 is a schematic view of a hot water supply device.

FIG. 2 is a side view of a main part including first and second heat exchangers.

FIG. 3 is a front view of a main part including a second heat exchanger.

FIG. 4 is a side view of a second heat exchanger.

FIG. 5 is a front view of a second heat exchanger.

6 is a sectional view taken along line VI-VI of FIG.

7 is a sectional view taken along line VII-VII of FIG.

FIG. 8 is a perspective view of inner fins of the second heat exchanger.

FIG. 9 is a view corresponding to FIG. 6 according to the modification.

[Explanation of symbols]

1 gas water heater 5 Second heat exchanger 10 Flow path forming body 20,21 Plate member 30 Inner fin 31,50-52 Partition wall 32 pieces 35,36 close contact part 40-42,55 channels 43, 56-58 U-turn section

Claims (4)

[Claims] 1. A stacking type heat exchanger in which a plurality of flow path forming bodies each having a flat flow path formed therein are stacked, wherein each of the flow path forming bodies forms a pair of flow paths therein. Plate member and an inner fin fixedly provided in the flow path between the pair of plate members, the inner fin connecting the flow path and a flow path adjacent to the flow path. A laminated heat exchanger having a partition wall in the form of a partition, and the partition wall forming a U-shaped or meandering flow path. 2. The laminated heat exchanger according to claim 1, wherein at least a portion of the plate member facing the inner fin is formed in a flat plate shape. 3. The laminated heat exchanger according to claim 2, wherein strip-shaped contact portions that are in close contact with the plate member are integrally formed on both edges of the partition wall of the inner fin. 4. The inner fin has a plurality of partitions for intermittently partitioning the pair of plate members, and the plurality of partitions are intermittently arranged in a flow direction. The laminated heat exchanger according to claim 1.