JPH1114156A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To develop a heat exchanger of smaller outer size, packed with high density, and having the structure of balanced heat absorption, the smaller deviation of the temperature among the fluid flow paths, and easier control of the water temperature flowing through the flowing paths. SOLUTION: A heat exchanger comprises a square tube body, an input side aggregated pipes, an output side aggregated pipes four plate form fluid flow paths 5a, 5b, 5c, and 5d, and fins 6a, 6b and 6c. The fluid flow paths comprise a pair of overlapped palm shape plate bodies, and a series of the flowing paths are formed with recessed grooves on both of them. Fins 6a and 6c arranged to both ends are longer than the central fin 6b and have larger heat propagating areas.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger. The heat exchanger of the present invention is particularly suitable for performing heat exchange between combustion gas or the like and water, and is preferable as a heat exchanger used for a water heater.

[0002]

2. Description of the Related Art An apparatus for heating water by a flame, such as a household water heater or a bath, has a built-in heat exchanger. As a heat exchanger incorporated in these devices, a heat exchanger having a simple structure in which a fin is attached to a copper pipe is generally used.

[0003]

In recent years, there has been a high demand for a hot water supply system for supplying water from a single water heater to a number of places such as a bath, a lavatory, or a kitchen, and a heat exchanger built in the water heater has been increasing in capacity. Request is strong. On the other hand, the installation space of the water heater is limited, and the outer shape of the heat exchanger must be as small as possible. For this reason, the heat exchanger needs to incorporate the fluid flow path at a high density and is required to have high heat exchange efficiency. However,
In a heat exchanger having a structure in which fins are attached to a copper pipe as in the prior art, there is a limit in increasing the density of the fluid flow path and improving the heat exchange efficiency.

[0004] In addition, the heat exchanger of the prior art has a problem in that the copper pipe is bent to form a fluid flow path through which water passes, so that it takes time and effort to manufacture the heat exchanger. In particular, in order to increase the density of the fluid flow path with the structure of the prior art, it is necessary to make a long flow path by folding the copper pipe over and over again in a small volume, which requires a significant amount of time and effort in manufacturing. There's a problem. Therefore, the present inventors have intensively studied to solve these problems, and have developed a heat exchanger in which a fluid passage is formed by a plate instead of the copper pipe of the related art. The heat exchanger developed by the present inventors will be briefly described as follows.

That is, the heat exchanger developed by the present inventors is composed of a rectangular cylindrical body, a collecting pipe portion, a plurality of fluid flow paths branched from the collecting pipe portion, and fins. The feature of this heat exchanger is that a fluid passage is constituted by a plate. That is, the fluid flow path is formed by laminating two plates provided with concave grooves, and the concave grooves constitute a series of fluid flow paths. The above-mentioned fluid flow paths (combination of two plate bodies) are arranged in parallel in a tubular body. The inlet-side collecting pipe section vertically penetrates each fluid flow path, and the penetrating portion of the inlet-side collecting pipe section opens at one end of the flow path of the fluid flow path. The same applies to the outlet-side collecting pipe section, penetrating each fluid flow path in the vertical direction,
The penetrating portion of the outlet-side collecting pipe portion is open at the other end of the fluid flow path. Fins are welded between the fluid flow paths. For example, four fluid flow paths 30a, 30b, 30
In the case of a heat exchanger provided with c and 30d, three fins 31a, 31b and 31c are used as shown in FIG.

The heat exchanger developed by the present inventors has plate-shaped fluid flow paths arranged in parallel, so that a large number of fluid flow paths can be built in a narrow volume. Also, the bending work of the copper pipe, which is indispensable in the prior art, is unnecessary, and the manufacture is easy. However, during the trial production of the above-described heat exchanger and repeated experiments, it was found that it was difficult for the above-mentioned heat exchanger to secure the heat absorption balance of each fluid flow path, and that the temperature variation of each fluid flow path was large. . In addition, it was found that the temperature of the water was not ideal even when each fluid flow path was viewed individually.

That is, in the heat exchanger having the above-described structure, fins are welded to the fluid flow path in order to secure a heat transfer area. However, in order to prevent heat from escaping to the cylindrical body, the fin is connected to each fluid flow path. Need to be placed only between roads. Therefore, when four fluid flow paths 30a, 30b, 30c, and 30d are arranged as shown in FIG.
30c has fins 31a, 31b or 31b on both sides,
31c is welded, but the fluid flow paths 30a, 30
At d, the fin 31a or 31c is welded to only one surface.

Therefore, the fluid flow paths 30a,
Only about half of the fins are welded to 30d compared to the central part. Therefore, the heat transfer area of the fluid flow paths 30a and 30d at both ends is smaller than that at the center,
a, The temperature rise of water passing through 30d is inferior.

Further, when each fluid flow path is viewed individually, the temperature rise is sharp on the heat medium introduction side near the burner side due to the high ambient temperature, and the heat medium outlet side far from the burner side is the ambient temperature. , The temperature rise is slow. The difference between the heating curve on the heating medium inlet side and the heating medium outlet side is
Although a phenomenon that occurs in any type of heat exchanger, the heat exchanger having the above configuration, coupled with the large difference in temperature between the fluid flow paths, makes it extremely difficult to control the water temperature of each part of the fluid flow path. Become. As a result, there are problems such as partial boiling and low temperature parts.

Therefore, the present invention further improves the above-described heat exchanger, and develops a heat exchanger which has a good endothermic balance, has small temperature variations in each fluid flow path, and can easily control the temperature of the water flowing through the fluid flow paths. That is the task.

[0011]

According to a first aspect of the present invention, there is provided a plate-like member comprising a tubular body through which a heat medium passes and two or more plate-like members overlapped with each other. A plate-like fluid flow path through which a fluid to be heated or cooled between the gaps flows, and a fin provided between the fluid flow paths and in contact with the fluid flow path, and the plate-like body is provided in a cylindrical body. A heat exchanger in which four or more fluid flow paths are arranged in parallel, wherein the fins in contact with the fluid flow paths located at the ends have a larger heat transfer area than other fins. It is a vessel.

The heat exchanger of the present invention has fins provided between the fluid flow paths and in contact with the fluid flow paths, similarly to the heat exchanger described above, but comes into contact with the fluid flow paths located at the ends. Fins having a larger heat transfer area than other fins are employed. Therefore, the total heat transfer area of the fluid flow path located at the end is increased, and the total heat transfer area close to the total heat transfer area of the fluid flow path arranged at the center is secured.

According to a second aspect of the present invention, the fin in contact with the fluid flow path located at the end is longer in the heat medium passing direction than the other fins. A heat exchanger according to claim 1.

According to the second aspect of the present invention, the length of the fin in the heat medium passing direction is changed, and the heat transfer area of the fin in contact with the fluid flow path located at the end is made larger than that at the center. Things.

According to another aspect of the present invention, a fin in contact with the fluid flow path located at the end is longer in the direction of the space between the fluid flow paths than the other fins. The heat exchanger according to claim 1 or 2, wherein:

According to the third aspect of the present invention, the length of the fin in the direction of the flow path of the fin is changed, and the heat transfer area of the fin in contact with the fluid flow path located at the end is made smaller than that of the center. It is a big one.

Another object of the present invention for achieving the above object is to heat or cool a gap between the plate members which is constituted by laminating a cylindrical member through which a heat medium passes and two or more plate members. A plate-like fluid flow path through which a fluid flows, and a fin in contact with the fluid flow path, wherein the plate-like fluid flow path is arranged in parallel in a cylindrical body, and at least one of the heat exchangers Is a heat exchanger characterized in that the heat transfer area on the heat medium introduction side is smaller than the heat transfer area on the heat medium discharge side.

In the heat exchanger of the present invention, the heat transfer area on the heat medium introduction side is smaller than the heat transfer area on the heat medium discharge side, so that the temperature rise curve on the heat medium introduction side is relatively gentle. Become. Further, on the heat medium discharge side, a heat medium having a relatively high calorific value flows, so that the temperature rise curve is relatively steep.

According to a fifth aspect of the present invention, the pitch of the fins is smaller on the heat medium discharge side than on the heat medium introduction side. A heat exchanger as described.

According to a fifth aspect of the present invention, the heat transfer area on the heat medium introduction side is made smaller than the heat transfer area on the heat medium discharge side by providing a change in the pitch of the fins.

According to a sixth aspect of the present invention, which shows the same specific mode, a notch is provided at an end of the fin on the heat medium introduction side. It is a heat exchanger described in 3.

The heat transfer area on the heat medium introduction side is made smaller than the heat transfer area on the heat medium discharge side by providing a notch at the heat medium introduction side end of the fin. Things.

According to a seventh aspect of the present invention, which is an improvement of the above-described aspect, the fluid flow path is formed by laminating two or more plates, and a continuous groove is formed on the inner surface side of at least one plate. The heat exchanger according to any one of claims 1 to 6, wherein the heat exchanger is provided, and a fluid flows in the concave groove.

The present invention has a configuration based on the development history described above, and is applied to a heat exchanger in which a fluid flow path is formed by laminating two or more plates.

[0025]

Embodiments of the present invention will be described below. FIG. 1 is an exploded perspective view of the heat exchanger according to the embodiment of the present invention. FIG. 2 is an exploded perspective view of a fluid flow path employed in the heat exchanger of FIG. FIG. 3 is an enlarged sectional view of a collecting pipe mounting portion of a plate constituting a fluid flow path. FIG.
FIG. 3 is an enlarged cross-sectional view of a flow path portion of a plate body forming a fluid flow path. FIG. 5 is a perspective view of a fin employed in the heat exchanger of FIG. FIG. 6 is a plan view of the heat exchanger of FIG. FIG. 7 is a sectional view taken along line AA of FIG. FIG. 8 is a cross-sectional view of a heat exchanger according to another embodiment of the present invention at a position corresponding to FIG. 6. FIG. 9 is a perspective view of a fin employed in the heat exchanger of the embodiment of FIG. 10 to 12 are cross-sectional views of a heat exchanger according to another embodiment of the present invention at a position corresponding to FIG. FIG. 13 is a perspective view and a plan view of a fin employed in a heat exchanger according to another embodiment of the present invention.

In FIG. 1, reference numeral 1 denotes a heat exchanger according to an embodiment of the present invention. The basic configuration of the heat exchanger 1 of the present embodiment is the same as that of the heat exchanger described in the section of “Problems to be Solved by the Invention”, and includes a rectangular cylindrical body 2 and an inlet-side collecting pipe section 3. And outlet-side collecting pipe part 4, four fluid flow paths 5 and 3
The fins 6 are formed.

To explain sequentially, the tubular body 2 is made of a thin plate of a metal material such as a steel plate, a tin-plated iron plate, a zinc-plated iron plate, or stainless steel, and has a rectangular opening shape. That is, the cylindrical body 2 is
And a rectangular tube surrounded by a wall surface 8 on the short side. Flanges 10 and 11 for joining with other members such as a burner and an exhaust pipe are provided in the opening portions at both ends of the cylindrical body 2.

The inlet-side collecting pipe section 3 and the outlet-side collecting pipe section 4
Are pipes each having a circular cross-sectional shape, and openings 12 are provided on the side surface at regular intervals.

As shown in FIG. 2, the fluid flow path 5 is formed by superposing two antipodal plates 15 and 16 on top of each other. That is, the plates 15 and 16 are formed by pressing a material having excellent heat conductivity such as copper, and are provided with a series of concave grooves 17. The concave groove 17 starts from one corner of the plates 15 and 16, extends in the longitudinal direction of the plates 15 and 16, returns to a “U” shape at one end, reaches the other end, and repeats this. It spreads over the whole area of the plate bodies 15 and 16 in a meandering manner. The concave groove 17 ends at a diagonal position of the starting point.

The sectional shape of the starting point and the ending point of the concave groove 17 of the plates 15 and 16 is as shown in FIG. 3, and an opening 20 is provided at the center. The end of the opening 20 is burring-processed and protrudes outward. The cross-sectional shape of the other portion of the concave groove 17 is as shown in FIG. 4, and the concave groove 17 is provided with a slight flat portion 21 interposed therebetween.

The plate members 15 and 16 are overlapped by welding or bending the end portions thereof so that the concave grooves 17 coincide with each other and the flat surface portions 21 and the peripheral surface portions are joined in a liquid-tight manner. As a result, the four surfaces are closed by the concave grooves 17. The gap formed by the concave grooves 17 forms a series of flow paths that extend in a meandering manner over the entire area of the plates 15 and 16. In addition, the fluid channel 5 is the plate 1
5 and 16 may be separately pressed and manufactured and then overlapped. However, the plate 15 and the concave groove 17 of the plate 15 are pressed adjacent to one thin plate, and the intermediate portion between the two is bent. It is also possible to manufacture by integrating them. That is, the fluid flow path 5 includes two plate members 15 as shown in FIG.
16 may be joined together after pressing separately, or an unfolded plate in which one of the sides of the two plates 15 and 16 is joined together is press-formed and bent. You may.

The fins 6 are corrugated fins (corrugated fins) as shown in FIG. 5, and are formed by folding thin plates made of a material excellent in heat conduction such as copper in alternate directions at an appropriate angle.

The heat exchanger 1 of the present embodiment has four sets of fluid flow paths 5a, 5b, 5c, 5d (all of which are combinations of the plates 15, 16). Are arranged in parallel with the longitudinal wall surface 7. The longitudinal end 18 of each fluid flow path 5 is welded to the short side wall surface 8 of the tubular body 2.

The openings 20 at the start point and the end point of the concave groove 17 of each fluid flow path 5 are arranged in the same straight line, and they are communicated in the vertical direction so that the inlet-side collecting pipe section 3 and the outlet-side collecting pipe section 4 are connected. Has been inserted. As described above, the inlet-side collecting pipe section 3 and the outlet-side collecting pipe section 4 are provided with openings 12 at regular intervals, and each of these openings is located in the concave groove 17 of each fluid flow path 5. . The opening 20 of the concave groove 17 and the inlet-side collecting pipe 3
And it is welded between the outlet side collecting pipe part 4 so as not to leak water.

Inlet-side collecting pipe 3 and outlet-side collecting pipe 4
Are vertically communicated through the plates 15 and 16 constituting the fluid flow path 5, extend parallel to the short side wall surface 8, penetrate the long wall surface 7, and are drawn out to the outside. In the heat exchanger 1 of the present embodiment, the inlet-side collecting pipe 3 and the outlet-side collecting pipe 4
Is located at a position close to the wall surface 8 on the short side of the cylindrical body 2,
It is desirable that the collecting pipe portions 3 and 4 are in contact with the wall surface 8 on the short side. If it is structurally difficult to make the two abut each other, it is recommended that the gap d (FIG. 1) between the two is designed to be within 5 mm. That is, by providing the inlet-side collecting pipe portion 3 at a position close to the wall surface 8 on the short side of the tubular body 2, the inlet-side collecting pipe section 3 is on the burner side of the tubular body 2 and on the short side side. The combustion gas near the wall 8 on the short side is blocked by the inlet-side collecting pipe 3 and flows toward the center.

Further, by providing the outlet-side collecting pipe section 4 at a position close to the wall surface 8 on the short side of the tubular body 2, the part of the outlet-side collecting pipe section 4 on the burner side is locally at high pressure. ,
The combustion gas stagnates and most of the combustion gas escapes to the center. As a result, the amount of combustion gas passing therethrough is small near any of the short side wall surfaces 8, and the temperature rise of the short side wall surface 8 is small. Also, since the combustion gas originally passing near the wall surface 8 on the short side flows to the central portion of the tubular body 2, it comes into contact with the fluid flow path and contributes to heat exchange, thereby improving heat exchange efficiency.

The fins 6a, 6b, 6c are arranged between the fluid flow paths 5a, 5b, 5c, 5d, and the bent portions are welded to the surfaces of the plates 15, 16. That is, the fin 6a is located between the fluid flow paths 5a and 5b and is welded to both of the fluid flow paths 5a and 5b. The fin 6b is located between the fluid flow paths 5b and 5c,
b, 5c. Further fins 6c
Are located between the fluid flow paths 5c and 5d,
d. In the heat exchanger 1 of the present embodiment, the fins 6 have a function of fixing the fluid flow path 5 in addition to a function of increasing the heat transfer area.

What is important here is that, in the heat exchanger 1 of the present embodiment, the fins 6a, 6b, 6c have different heat transfer areas, and the fins 6a, 6d contact the fluid flow paths 5a, 5d located at the ends. 6c is a point having a larger heat transfer area than the central fin 6b. That is, in the heat exchanger 1 of the present embodiment, as shown in FIG.
Is the third to fifth lengths counted from the burner side (heat medium introduction side) among the five convex portions (back surfaces of the concave grooves 17) on the surface of the fluid flow path 5a. On the other hand, the fins 6a and 6c in contact with the fluid flow paths 5a and 5d located at the ends have a length extending over all five convex portions. In other words, the length of the fins 6a, 6c in contact with the fluid flow paths 5a, 5d located at the ends in the heat medium passing direction is equal to the length of the fin 6 provided at the intermediate portion.
b is about twice the length of the fin 6
The heat transfer areas a and 6c have about twice the heat transfer area as compared with the center fin 6b.

When the viewpoint is changed, the central fin 6b
It can be said that the heat transfer area on the burner side (heat medium introduction side) is smaller than the heat transfer area on the heat medium discharge side.

Next, the operation of the heat exchanger 1 of the present embodiment will be described. The heat exchanger 1 of the present embodiment is built in a water heater or the like. Then, the inlet-side collecting pipe section 3 is connected to a water supply source, and the outlet-side collecting pipe section 4 is connected to a hot water tap such as a curan. Water is
The heat enters the heat exchanger 1 through the inlet-side collecting pipe section 3. Then, the water is divided into three equal parts from the opening 12 of the inlet-side collecting pipe part 3 and is equally introduced into each fluid flow path 5. The water further flows in parallel through the fluid flow paths defined by the concave grooves 17 of the respective fluid flow paths 5, and is collected by the outlet-side collecting pipe section 4 to reach the hot water tap.

The tubular body 2 of the heat exchanger 1 is connected to a heat source such as a gas burner. Then, the combustion gas (heat medium) generated by the gas burner or the like flows through the cylindrical body 2 in the axial direction, and hits each of the fluid flow paths 5 and the fins 6 to perform heat exchange.

Here, the heat exchanger 1 of the present embodiment is similar to the heat exchanger under development, in that the fluid passages 5b and 5c at the center are provided.
Fins 6a, 6b, 6c are welded on both sides, and fins 6a are provided only on one surface in the fluid flow paths 5a, 5d at both ends.
a, 6c are welded, but fluid flow paths 5 at both ends
The length of the fins 6a, 6c welded to the a and 5d in the heat medium passing direction is about twice the length of the fin 6b in the intermediate portion, and the total transmission of the fluid flow paths 5a, 5b, 5c, 5d. The difference in thermal area is small. Therefore, each of the fluid flow paths 5a, 5b, 5c,
The amount of heat received in 5d is almost uniform, and the heat absorption balance is good.

The center fin 6b has a smaller heat transfer area on the burner side (heat medium introduction side) than the heat transfer area on the heat medium discharge side. The heating curve becomes relatively gentle. Conversely, on the heat medium discharge side, a heat medium having a relatively high calorific value flows, so that the temperature rise curve becomes slightly steep. Therefore, the temperature rise curve of the water flowing through the fluid flow path 5 is smoothed and becomes almost ideal. Furthermore, in the heat exchanger 1 of the present embodiment, there is no fin at a position on the burner side (heat medium introduction side) near the flame, which is the center of the cylindrical body 2 where the heat of the burner tends to be too strong. . Therefore, there is no fear that the fin is burned or deformed by the flame.

In the above-described embodiment, the fins 6a, 6
The heat transfer area on the burner side is reduced by changing the heat transfer area on the burner side (heat medium introduction side) of the fin 6b provided at the center. It was smaller than the area. However, the present invention is not limited to this configuration, and the heat transfer area of the fins 6a and 6c in contact with the fluid flow paths 5a and 5d located at the ends is made larger than the heat transfer area of the central fin 6b. If so, a considerable effect can be expected. Also, as long as the heat transfer area on the burner side (heat medium introduction side) is smaller than the heat transfer area on the heat medium discharge side, a considerable effect can be expected.

In the following, the heat transfer area of the fins 6a, 6c in contact with the fluid flow paths 5a, 5d located at the ends is increased by another measure as compared with that of the central fin 6b.
The configuration in which the heat transfer area on the burner side is reduced as compared with the heat transfer area on the heat medium discharge side by other measures will be listed. In the heat exchanger 1 described below, the amount of heat received by each of the fluid flow paths 5a, 5b, 5c, 5d is substantially equal, and the heat absorption balance is good. The temperature rise curve of the water flowing through the fluid flow path 5 is smooth.

FIG. 8 shows an arrangement in which a notch 25 having an inverted "U" shape is provided at the burner side (heat medium introduction side) of the central fin 6b. FIG. 9 is a perspective view of the fin 6b used in the present configuration, and the notch 25 is provided over the entire area in the longitudinal direction of the fluid flow paths 5a and 5d. In the heat exchanger 1 of the present embodiment, the heat transfer area of the central fin 6b is reduced by the area of the notch 25, so that the fins 6a and 6c relatively contact the fluid flow paths 5a and 5d located at the ends. Has a larger heat transfer area than the central fin 6b.
Further, the heat transfer area on the burner side (heat medium introduction side) is smaller than the heat transfer area on the heat medium discharge side by the area of the notch 25. Accordingly, the temperature rise curve of the water flowing through the fluid flow path 5 is smooth, and there is no fear that the fin is burned or deformed by the flame.

FIG. 10 shows the flow paths 5a, 5b, 5c, 5
The distance d is set to be non-uniform, and the fin 6
The ones having different widths according to the intervals of the fluid flow paths 5 are arranged. That is, in the heat exchanger 1 shown in FIG. 10, of the intervals X and Y between the fluid channels 5a, 5b, 5c and 5d, the interval Y between the intermediate fluid channels 5b and 5c is the same as the fluid channel 5 at the end.
It is shorter than the interval X between a, 5b or 5c, 5d. Therefore, the central fin 6b has a small width and a small heat transfer area, and conversely, the fin 6b in contact with the fluid flow paths 5a and 5d located at the ends.
a and 6c have a larger width and a larger heat transfer area than the central fin 6b.

FIG. 11 shows the above-mentioned fluid flow paths 5a, 5b,
This is an example in which a measure for setting the intervals of 5c and 5d to be non-uniform and a measure for removing the burner-side (heat medium introduction side) portion of the fin 6b provided at the center as shown in FIG. 7 are used in combination. That is, in the heat exchanger 1 shown in FIG. 11, the distance Y between the fluid flow paths 5b and 5c at the intermediate portion is shorter than the distance X between the fluid flow paths 5a and 5b or 5c and 5d at the end. The fins 6a and 6c in contact with the flow paths 5a and 5d have a larger heat transfer area than the central fin 6b. Also, the central fin 6
In b, the heat transfer area on the burner side (heat medium introduction side) is small only in the missing part of the heat transfer area on the heat medium discharge side, the temperature rise curve of water is smooth, and there is no fear that the fins are burned by the flame.

FIG. 12 shows the fluid flow paths 5a and 5a.
FIG. 8 shows a method of setting the intervals of b, 5c and 5d to be non-uniform.
This is an example in which a method of providing an inverted “U” -shaped notch 25 as described above is also used. That is, in the heat exchanger 1 shown in FIG. 12, the distance Y between the intermediate fluid flow paths 5b and 5c is shorter than the distance X between the fluid flow paths 5a and 5b or 5c and 5d at the end. Fins 6a in contact with flow paths 5a, 5d,
6c has a larger heat transfer area than the central fin 6b.
The center fin 6b is on the burner side (heat medium introduction side).
Is smaller by the area of the notch 25 in the heat transfer area on the heat medium discharge side, the temperature rise curve of the water is smooth, and there is no fear that the fin is burned by the flame.

In each of the above examples, it is assumed that the pitch of the fins 6 is constant in the heat medium passing direction. However, by changing the pitch of the fins 6 in the heat medium passing direction, the heat transfer on the burner side is performed. The area may be smaller than the heat transfer area on the heat medium discharge side.

FIG. 13 shows an example in which the pitch of the fins 6 is changed in the heat medium passing direction. In the heat exchanger 1 of the present embodiment, the fins 6 include the fluid flow paths 5a, 5b, 5c,
Two each are arranged between 5d. The fin 6 is constituted by a combination of two fins as shown in FIG. FIG. 13B is a plan view of the upper fin 28, and FIG. 13C is a front view of the lower fin 29. In other words, fins 29 having a large pitch are arranged in the gap between the fluid flow paths 5 on the burner side (heat medium introduction side) as shown in FIGS. On the side, fins 28 having a small pitch are arranged as shown in FIGS. In the heat exchanger 1 of the present embodiment,
Since the pitch of the fins 29 provided on the burner side is large, the heat transfer area is smaller than that of the heat medium discharge side.

In the embodiments described above, the fins are all corrugated fins, but other fins can be used.

The embodiment described above is an example in which the effect of the present invention is most remarkably exhibited.
5 and 16 are illustrated as an example, but if one of the plates has a concave groove, the other plate may be flat.

[0054]

According to the heat exchanger of the first aspect, the fins which are in contact with the fluid flow path located at the end have a larger heat transfer area than the other fins. Therefore, in the heat exchanger of the present invention, the total heat transfer area of the fluid flow path located at the end is increased, and the total heat transfer area close to the total heat transfer area of the fluid flow path arranged at the center is secured. It has an effect and has an effect of being excellent in heat absorption balance. Therefore, the problem that the fluid in the heat exchanger partially boil is eliminated.

In the heat exchanger according to the second aspect, the heat transfer area of the fin in contact with the fluid flow path located at the end portion is changed to that of the central portion by providing a change in the length of the fin in the heat medium passing direction. This makes it possible to increase the size, thereby providing an effect of improving the heat absorption balance.

In the heat exchanger according to a third aspect of the present invention, the heat transfer area of the fin in contact with the fluid flow path located at the end can be reduced by providing a change in the length of the fin in the space direction of the fluid flow path. It is possible to increase the size as compared with that of the above, and there is an effect that the heat absorption balance is excellent.

In the heat exchanger according to the fourth aspect, the heat transfer area on the heat medium introduction side is larger than the heat transfer area on the heat medium discharge side.
The temperature rise curve on the heat medium introduction side is relatively gentle. On the heat medium discharge side, a heat medium having a high calorific value flows, so that the temperature rise curve is relatively steep. Therefore, the heat exchanger according to the fourth aspect has an effect that the temperature rise curve is smoothed and becomes almost ideal.

According to the fifth aspect of the present invention, by providing a change in the pitch of the fins, the heat transfer area on the heat medium introduction side becomes smaller than the heat transfer area on the heat medium discharge side, so that the temperature rise curve is ideal. There is an effect that is close.

According to a sixth aspect of the present invention, a notch is provided at an end of the heat medium introduction side of the fin so that the heat transfer area on the heat medium introduction side is smaller than the heat transfer area on the heat medium discharge side. This has the effect that the temperature rise curve becomes close to ideal.

The heat exchanger according to claim 7 has an effect that, in addition to the above-described effects, a large number of fluid flow paths can be built in a narrow volume, and has an excellent effect that manufacturing is easy. .

[Brief description of the drawings]

FIG. 1 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention.

FIG. 2 is an exploded perspective view of a fluid channel adopted in the heat exchanger of FIG.

FIG. 3 is an enlarged sectional view of a collecting pipe mounting portion of a plate constituting a fluid flow path.

FIG. 4 is an enlarged cross-sectional view of a channel portion of a plate constituting a fluid channel.

FIG. 5 is a perspective view of a fin employed in the heat exchanger of FIG.

FIG. 6 is a plan view of the heat exchanger of FIG.

FIG. 7 is a sectional view taken along line AA of FIG. 6;

FIG. 8 is a cross-sectional view of a heat exchanger according to another embodiment of the present invention at a position corresponding to FIG. 6;

FIG. 9 is a perspective view of a fin employed in the heat exchanger of the embodiment of FIG.

FIG. 10 is a sectional view of a heat exchanger according to another embodiment of the present invention at a position corresponding to FIG. 6;

FIG. 11 is a cross-sectional view of a heat exchanger according to another embodiment of the present invention at a position corresponding to FIG. 6;

FIG. 12 is a sectional view of a heat exchanger according to another embodiment of the present invention at a position corresponding to FIG. 6;

FIG. 13 is a perspective view and a plan view of a fin employed in a heat exchanger according to another embodiment of the present invention.

FIG. 14 is a sectional view of a developing heat exchanger at a position corresponding to FIG. 6;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Cylindrical body 3 Inlet-side collecting pipe part 4 Outlet-side collecting pipe part 5a, 5d Fluid flow path 5b, 5c located at end part Fluid flow path 6a, 6b, 6c, fin 7 located at the center Wall surface 8 Short side wall surface 15, 16 Plate 17 Groove

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tomohiro Nishihata 93 Edo-cho, Chuo-ku, Kobe-shi, Hyogo Noritsu Co., Ltd. (72) Inventor Jitsuzo Uno 3-25-3 Yoyogi, Shibuya-ku, Tokyo Toyo Radiator (72) Inventor Tsuyoshi Murakami 3-25-3 Yoyogi, Shibuya-ku, Tokyo Toyo Radiator Co., Ltd. (72) Inventor Koji Narita 3-25-3, Yoyogi, Shibuya-ku, Tokyo Toyo Radiator Co., Ltd. ( 72) Inventor Jun Jun Onishi 3-25-3 Yoyogi, Shibuya-ku, Tokyo Inside Toyo Radiator Co., Ltd.

Claims (7)

[Claims] 1. A tubular body through which a heat medium passes, and a plate-like fluid flow path formed by laminating two or more plate bodies, through which a fluid for heating or cooling a gap between the plate bodies flows.
A heat exchanger having fins provided between the fluid flow paths and in contact with the fluid flow paths, wherein the plate-shaped fluid flow paths are arranged in four or more rows in parallel in a cylindrical body. A heat exchanger characterized in that the fins in contact with the fluid flow path located at a larger heat transfer area than other fins. 2. The heat exchanger according to claim 1, wherein the fin in contact with the fluid flow path located at the end is longer in the heat medium passing direction than other fins. 3. The heat exchanger according to claim 1, wherein a fin in contact with the fluid flow path located at the end is longer in the direction of the space between the fluid flow paths than other fins. 4. A cylindrical fluid body through which a heat medium passes, and a plate-shaped fluid flow path formed by laminating two or more plate bodies, through which a fluid for heating or cooling a gap between the plate bodies flows.
A heat exchanger having fins in contact with the fluid flow path, wherein the plate-shaped fluid flow paths are arranged in parallel in a cylindrical body, and at least one of the fins in contact with any of the fluid flow paths is provided with a heat medium. A heat exchanger characterized in that the heat transfer area on the heat transfer side is smaller than the heat transfer area on the heat medium discharge side. 5. The heat exchanger according to claim 1, wherein the pitch of the fins is smaller on the heat medium discharge side than on the heat medium introduction side. 6. The heat exchanger according to claim 1, wherein a notch is provided at an end of the fin on the heat medium introduction side. 7. The fluid flow path is formed by stacking two or more plate members, and a continuous groove is provided on an inner surface side of at least one plate member, and a fluid flows through the groove. The heat exchanger according to any one of claims 1 to 6, wherein: