JPH06331296A - Lamination type heat exchanger - Google Patents

Abstract

PURPOSE:To improve strength and efficiency of a lamination type heat exchanger by a method wherein a triangle plate to divide fluid which goes into and out of an inner fin into two directions is interposed into either an inlet space on the upstream side of the inner fin in a tube element or an outlet space on the downstream side. CONSTITUTION:Inside a tube element 2, a triangle plate 28 to divide fluid A which goes into and out of an inner fin 3 into two directions is interposed into a space 16 on the upstream side of the inner fin 3 and another space 17 on the downstream side respectively. The triangle plate 28 has a top 28a which protrudes toward an end of the inner fin 3. The space 16 on the upstream side of the inner fin 3 is divided by the triangle plate 28 to define two spaces 16a and 16b which communicate with each inlet flow passage 4. On the other hand, the space 17 on the downstream side of the inner fin 3 is divided by the triangle plate 28 to define two spaces 17a and 17b which communicate with each outlet flow passage 5. The ends of the respective triangle plate 28 are jointed with each spacer 14.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a laminated heat exchanger.

[0002]

2. Description of the Related Art As a conventional laminated heat exchanger, for example, there is one as shown in FIG. 20 (Actual No. Sho 63-49189).
Gazette, reference).

Explaining this, a plurality of tube elements 51 defining the first flow path 54 are provided inside by joining the peripheral portions 57 of the box-shaped plates 52 and 53 to each other. It is laminated via the outer fins 55.

As shown in FIG. 21, the fluid flowing in each tube element 51 flows from one inlet channel 58 through the inlet space 59 along the inner fin 3 and then through the outlet channel 60 to one outlet. Heat is exchanged with the fluid flowing out to the flow path 61 and flowing outside the tube elements 51 via the outer fins 55.

[0005]

However, in such a conventional laminated heat exchanger, the inlet space 59 or the outlet space 60 constitutes a flow path for greatly bending the flow of fluid, and the inlet space 59 or A stagnation portion of the fluid is generated at the corner of the outlet space 60 as shown by putting a lattice in the figure. The stagnation of the fluid at the corners of the inlet space 59 or the outlet space 60 not only increases the pressure loss in the tube element 51, but the tubing element 51 locally becomes hot at the site where the stagnation of the fluid occurs. , Thermal stress may act and cracks may occur.

Further, it is considered that the inlet space 59 or the outlet space 60 may cause the rigidity of the tube element 2 to be lowered. When each tube element 51 and each outer fin 55 are fixed to each other by brazing, a weight is placed on a stack of each tube element 51 and each outer fin 55 and placed in a furnace for heating. The element 51 concentrates in the inlet space 59 or the outlet space 60, which has a relatively low rigidity, and causes deformation in each tube element 51, or each tube element 51.
There is a possibility that a gap is formed between the outer fin 55 and the outer fin 55, and the amount of heat exchange is reduced.

The present invention addresses the above problems and aims to improve the strength and efficiency of a laminated heat exchanger.

[0008]

SUMMARY OF THE INVENTION The present invention accommodates a plurality of tube elements defining a first flow path through which a fluid A flows and tube elements that are laminated together, and a second flow path through which a fluid B flows. In a laminated heat exchanger including a demarcating housing, inner fins provided inside each tube element, and outer fins provided between the tube elements, the heat exchanger is upstream of the inner fins inside the tube element. At least one of the inlet space on the side and the outlet space on the downstream side of the inner fin is provided with a triangular plate for dividing the fluid A flowing in and out of the inner fin into two directions.

According to a second aspect of the present invention, the tops of the triangular plates projecting toward the inner fins are provided offset from the center line of the inner fins, and the two spaces partitioned by the tops are provided inside the triangular plate. A cooling passage communicating with each other is formed.

According to the third aspect of the present invention, the inside of the triangular plate communicates with the two spaces partitioned by the apex, and a cooling passage opening at the apex facing the inner fin is formed.

[0011]

The fluid A flows into each tube element from each inlet flow passage, flows along the inner fins, and then flows out to each outlet flow passage, while the fluid B flows along the outer fins to form the fluid A. Heat exchange takes place between them.

The triangular plate smoothly diverts the flow of the fluid A in the inlet space or the outlet space and suppresses the stagnation of the flow of the fluid A in the inlet space or the outlet space, thus smoothing the flow of the fluid A. The pressure loss in the tube element can be reduced, and the hot spot where the tube element locally becomes high in temperature can be eliminated to improve the heat resistance.

The triangular plate enhances the rigidity of the structure in which the tube elements are laminated and prevents the tube elements from being deformed during brazing.

According to the second aspect of the present invention, the top portion of the triangular plate projecting toward the inner fin is provided offset from the center line of the inner fin, so that the two spaces partitioned by the top portion of the triangular plate are separated. A pressure difference is generated between them, and a flow of the fluid A that passes through the cooling passage formed inside the triangular plate is generated. As a result, the triangular plate is cooled, and it is possible to suppress overheating around the triangular plate of the tube element.

According to the third aspect of the invention, the triangular plate is communicated with the two spaces partitioned by the apex, and a cooling passage is formed at the apex facing the inner fin to open and close the inner fin. Since the flowing fluid A linearly flows in and out of the cooling passage opened at the top of the triangular plate, the pressure loss in the tube element can be suppressed to a small level.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to the accompanying drawings.

As shown in FIG. 2, in the laminated heat exchanger, a second flow path 22 through which the high temperature fluid B flows is defined by the housing 6, and a plurality of tube elements are provided inside the housing 6 via outer fins 1. 2 are stacked. An inlet duct 24 of the second flow path 22 is formed at one end of the housing 6, and an outlet duct 25 is formed at the other end. The hot fluid B passes from the inlet duct 24 to the outlet duct 25 through the second flow path 22 as shown by the arrow in the figure, and flows around the tube elements 2 in the housing 6 via the outer fins 1.

As shown in FIG. 1, a first flow path 21 through which the cryogenic fluid A flows is defined inside each tube element 2.

As shown also in FIG. 3, the outer fin 1 has two inlet passages 4 for letting the low temperature fluid A into each tube element 2 and two outlet passages 5 for letting out the low temperature fluid A from each tube element 2. It is formed so as to project outward from the side portion 1a.

The low temperature fluid A flows in from the upper end of each inlet channel 4 as shown by the arrow in the figure, is distributed from each inlet channel 4 to each first channel 21, and in the course of flowing through each first channel 21, the high temperature fluid A After exchanging heat with the fluid B, it flows out from the upper end of each outlet channel 5.

The cryogenic fluid A is supplied to the upper end of each inlet passage 4 through a duct 4a arranged outside the housing 6. The low temperature fluid A is discharged from the upper end of each outlet flow path 5 through each duct 5a arranged outside the housing 6.

As shown in FIG. 4A, the tube element 2 is formed by combining a box-shaped upper plate 26 and a lower plate 27, and an inner fin 3 is interposed between the upper plate 26 and the lower plate 27. .

Upper plate 26 and lower plate 27
Has peripheral portions 26b and 27b that are joined to each other, and one peripheral portion 27b is folded back so as to wrap around the other peripheral portion 26b and fixed by caulking, whereby the peripheral fixing portion 10 having a substantially rectangular frame shape is formed. It

Upper plate 26 and lower plate 27
The bosses 26a and 27a are respectively formed on the protrusions, and the bosses 26a and 27a are fitted to each other so that the inlet passage 4
Is defined. Since the inlet channel 4 and the outlet channel 5 are arranged at the four corners of each tube element 2, the positioning accuracy of each tube element 2 is improved.

As shown in FIG. 8, an upper plate 26 and a lower plate 27 are provided inside the tube element 2.
A spacer 14 is interposed between the tube elements 2 so as to surround the inlet flow path 4, and a boss 26 is provided between each tube element 2.
A spacer 15 is interposed so as to surround a and 27a.

The spacer 14 is formed in a C shape as shown in FIG. 4 (B). The spacer 15 is shown in FIG.
As shown in FIG.

Also around the outlet channel 5, the tube elements 2 are mutually bosses 2 in the same manner as around the inlet channel 4.
6a and 27a are fitted to each other, and spacers 14 and 15 are provided inside and outside each tube element 2 so as to surround the outlet channel 5. When the tube elements 2 are stacked on each other, the bosses 26a and 27a arranged at the four corners are fitted to each other, whereby sufficient assembly accuracy can be ensured.

At the four corners of each tube element 2, an outer wall 2a of each inlet channel 4 and an outer wall 2b of each outlet channel 5 are formed so as to project outward from the side portion 1a of the outer fin 1. Therefore, a recess 12 is formed on the side of each tube element 2 between the outer walls 2a and 2b.

The side plate 8 constituting the side portion of the housing 6 has a convex portion 8 which is curved along each outer wall 2a, 2b.
a and 8b are formed. Side plate 8 is each convex portion 8
A recess 8c is formed between a and 8b. Each outer wall 2a, 2b of each tube element 2 and the spacer 15
A gap 11 is provided between the outer peripheral surfaces 15a of the.

Outer walls 2a, 2b of each tube element 2
By forming the convex portions 8a and 8b of the side plate 8 and the side plate 8 respectively in a curved manner, a gap 11 defined between them is formed.
Has a portion 13 that is largely curved, the flow path resistance imparted to the high temperature fluid B flowing through the second flow path 22 is 1
1 is locally raised at the greatly curved portion 13 of the first portion, the flow rate of the fluid flowing around the gap 11 and flowing between the outer fins 1 is increased, and heat exchange between the low temperature fluid A and the high temperature fluid B is promoted.

The inner fins 3 and the outer fins 1 are each formed in a corrugated plate shape and are arranged so that their folds are parallel to each other. Each inlet channel 4 is the second channel 2
2 is arranged so as to be close to the outlet duct 25 of the second flow passage, and each outlet flow passage 5 is arranged so as to be close to the inlet duct 24 of the second flow passage 22,
The flow direction of the low temperature fluid A guided by the inner fin 3 is made to face the flow direction of the high temperature fluid B guided by the outer fin 1.

As shown by the arrows in FIG. 1, the cryogenic fluid A flows into the tube element 2 from each inlet channel 4, flows along the inner fins 3, and then flows out to each outlet channel 5, while The high temperature fluid B flows from the inlet duct 24 of the housing 6, flows along the outer fins 1, and flows into the low temperature fluid A.
After heat exchange is performed between and, it flows out from the outlet duct 25.

By making the flow direction of the low temperature fluid A guided by the inner fin 3 opposite to the flow direction of the high temperature fluid B guided by the outer fin 1, the temperature distribution of each tube element 2 is made uniform and the low temperature fluid is The heat exchange efficiency can be improved and the heat exchanger can be downsized as compared with the conventional device in which A and the high-temperature fluid B flow orthogonally.

As shown in FIG. 6, the sectional area of the inlet channel 4 is S ₄ , the sectional area of the inlet 30 of each tube element 2 opening in the inlet channel 4 is t ₄ , and the number of laminated tube elements 2 is Is set to N, S ₄ = t ₄ × N ... (1) is set to be satisfied.

Similarly, assuming that the cross-sectional area of the outlet channel 5 is S ₅ and the cross-sectional area of the outlet 31 of each tube element 2 opening in the outlet channel 5 is t ₅ , then S ₅ = t ₅ × N ... (2 ) Is satisfied.

The inlet temperature of the low temperature fluid A is T ₄ , and the low temperature fluid A is
Let V _{4 be} the inlet flow velocity of, the outlet temperature of the low temperature fluid A be T ₅ , and the outlet flow velocity of the low temperature fluid A be V ₅ .

[0037]

[Equation 1]

It is set so that the above formula is satisfied.
This makes it possible to reduce the change in momentum of the low temperature fluid A in the inlet flow path 4 and the outlet flow path 5 and reduce the pressure loss.

As shown in FIG. 5, a space 16 upstream of the inner fin 3 is provided inside the tube element 2.
In the space 17 on the downstream side, a triangular plate 28 for dividing the fluid A flowing in and out of the inner fin 3 into two directions is interposed.

The triangular plate 28 is the tube element 2
It is formed of a metal having a higher thermal conductivity.

Each triangular plate 28 has a top portion 28a projecting toward the end of the inner fin 3, and the space 16 on the upstream side of the inner fin 3 has two spaces communicating with each inlet flow path 4 by the triangular plate 28. 16 a and 16 b are defined, and the space 17 on the downstream side of the inner fin 3 is formed by two triangular spaces 28 that communicate with the respective outlet flow paths 5.
7a and 17b are defined. Both ends of each triangular plate 28 are joined to each spacer 14.

The center line of the top portion 28a of each triangular plate 28 is formed to be offset from the center line of the inner fin 3 by a predetermined distance Δd so that the distance to the two inlet channels 4 or the two outlet channels 5 is different. It has become.

Two provided inside each triangular plate 28
One space 16a, 16b or two space 17a, 17
As shown in FIG. 7, cooling grooves 20 that open to the upper surface of each triangular plate 28 are formed as cooling passages that communicate b with each other. The cooling groove 20 is formed in a linear shape orthogonal to the flow path direction of the inner fin 3. The cooling groove 20 is arranged at the base of the top portion 28a.

Each triangular plate 28, each spacer 14, 1
5, each upper plate 26 and each lower plate 27
Are fixed to each other by brazing. 7 or 14
In the above, 29 is a brazing material.

Next, the operation will be described.

Each triangular plate 28 and each spacer 14, 1
5 prevents variation in the distance between the upper plate 26 and the lower plate 27, and increases rigidity to ensure strength against external loads and impacts.

When brazing each tube element 2,
The weight is placed in a furnace in a state where a weight is placed above each of the laminated tube elements 2 which are laminated with each other and heated.
When, for example, pure copper is used as the brazing material 29, the tube element 2 is heated to 1100 ° C. or higher.

Each triangular plate 28 and each spacer 1
By increasing the rigidity of the structure in which the respective tube elements 2 are laminated by 4, 15, it is possible to prevent the respective tube elements 2 from being deformed as shown in FIG. 9 during the brazing. On the other hand, when the triangular plate 28 is removed from the inside of the tube element 2, the center portion of each tube element 2 is deformed downward due to the weight of the weight when brazing, as shown in FIG. Of.

By increasing the rigidity of the structure in which the tube elements 2 are laminated by the triangular plates 28, the strength required for the inner fins 3 and the outer fins 1 is reduced, and the plate thickness of these is reduced to reduce the heat. The pressure loss of the exchanger can be reduced.

As shown by the arrow in FIG. 1, the low temperature fluid A is 2
After flowing from one inlet flow path 4 through the inlet space 16 along the inner fin 3, it flows out to two outlet flow paths 5 via the outlet space 17. Considering the inlet space 16 or the outlet space 17 as a kind of elbow, since the triangular plates 28 are arranged along the streamlines of the cryogenic fluid A, they function to smoothly divide the flow of the cryogenic fluid A, The pressure loss in the element can be suppressed to a small level. In this way, by reducing the pressure loss through each triangular plate 28, the volume of the inlet space 16 or the outlet space 17 is reduced, and the tube element 2 can be downsized.

Further, since each triangular plate 28 is formed along the streamline of the cryogenic fluid A, the stagnation of the flow of the cryogenic fluid A is suppressed at the center of the inlet space 16 or the outlet space 17, It is possible to smooth the flow of the low temperature fluid A, reduce the pressure loss applied to the low temperature fluid A, and suppress the tube element 2 from being locally overheated.

The triangular plate 28 is attached to the tube element 2
Since it is formed of a metal having a higher thermal conductivity, it is possible to make the temperature distribution around the triangular plate 28 uniform and suppress the tube element 2 from being locally overheated.

Two inlet channels 4 or two outlet channels 5
Flow path cross-sectional areas of the triangular plates 28 are equal to each other, while the two inlet spaces 16a, 16b or the two outlet spaces 17a, 17 are partitioned by the tops 28a of the triangular plates 28.
Since the volumes of b are different from each other, each inlet space 16
A pressure difference is generated between a and 16b or each of the outlet spaces 17a and 17b, and a flow of the cryogenic fluid A passing through the cooling groove 20 is generated as shown by an arrow in FIG. As a result, each triangular plate 28 is cooled, and the surroundings of each triangular plate 28 can be prevented from being overheated.

On the other hand, when the triangular plate 28 is abolished, a stagnation part of the flow of the cryogenic fluid A occurs at the center of the inlet space 16 or the outlet space 17 as shown by putting a lattice in FIG. In the outlet space 17 where the high temperature fluid B flows into the outside, a hot spot that locally becomes high in temperature is generated in the central portion where the flow of the low temperature fluid A stagnates, which causes cracks and the like in the tube element 2. is there.

Each triangular plate 28 has its own top 28.
Since a projects from the central portions of the spaces 16 and 17, it is possible to effectively increase the rigidity of the structure in which the tube elements 2 are stacked.

On the other hand, as shown in FIG. 13, when a strip-shaped plate 41 is inserted in the space 17 of the tube element 2 instead of the triangular plate 28, the plate 41
There is a possibility that the thermal stress acting near the central edge portion of the above becomes high and the central portion 42 of the lower plate 27 facing the space 17 is deformed to generate the crack 43.

Next, in another embodiment shown in FIG. 15, two spaces 17a, 1 provided inside the triangular plate 28 are provided.
The cooling grooves 20 that open on the upper surface of each triangular plate 28 are formed in a curved shape, with the cooling passages 7b communicating with each other. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

In the cooling groove 20, one end 20a for the outlet space 17a having a relatively large volume opens in the middle of the top portion 28a of the triangular plate 28, and the outlet space 1 having a relatively small volume.
The other end 20b with respect to 7a is the top 28 of the triangular plate 28.
Open at the base of a.

In this case, the low temperature fluid A is prompted to flow into the one end 20a of the cooling groove 20, and the flow rate of the low temperature fluid A passing through the cooling groove 20 can be increased.

Further, since the cooling groove 20 is formed in a curved shape, the upper plate 2 of the tube element 2 is formed.
6 or the lower plate 27 does not come into contact with the linear edge portion with respect to the cooling groove 20, and it is possible to suppress deformation or cracking along the cooling groove 20.

Next, in another embodiment shown in FIG. 16, a large number of wave-shaped recesses 41 are formed on the surface of the triangular plate 28 facing the spaces 17a and 17b. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

In this case, each space 17 of the triangular plate 28
The triangular plate 28 has a larger surface area facing a and 17b.
The heat radiation from the low temperature fluid A is promoted.

Further, since the edge portion of the triangular plate 28 is formed in a wavy shape, the upper plate 26 and the lower plate 27 of the tube element 2 are in contact with the linear edge portion of the triangular plate 28. Therefore, it is possible to suppress the occurrence of deformation and cracks along the edge of the triangular plate 28.

Next, in another embodiment shown in FIG. 17, the top 28a of the triangular plate 28 is joined to the end of the inner fin 3, and the upper surface of the triangular plate 28 is used as a cooling passage provided in the triangular plate 28. The Y-shaped cooling groove 40 is formed in the. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

The top 28a of the triangular plate 28 is formed symmetrically with respect to the center line of the inner fin 3, and the top 28a
The volumes of the outlet spaces 17a and 17b partitioned by a are equal to each other.

The cooling groove 40 has an upstream portion 40c linearly extending on the center line of the inner fin 3, and two downstream portions branching from the upstream portion 40c in a Y shape and curved to the outlet spaces 17a, 17b. It has parts 40a and 40b.

In this case, the low temperature fluid A passing through the inner fins 3 linearly flows into the upstream portion 40c of the cooling groove 40, passes through the downstream portions 40a and 40b, and exits the outlet spaces 17 respectively.
Since the flow is divided into a and 17b at a uniform flow rate, the pressure loss applied by the triangular plate 28 can be suppressed to be small.

By not providing a gap between the top portion 28a of the triangular plate 28 and the inner fin 3, the supporting rigidity of the upper plate 26 and the lower plate 27 of the tube element 2 can be increased, and the edge portion of the triangular plate 28 can be improved. It is possible to suppress the occurrence of deformation and cracks along the line.

Next, in another embodiment shown in FIGS. 18 and 19, the triangular plate 28 provided inside the tube element 2 is formed by a thin plate 44 which is curved in a wave shape. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

The top portion 28a of the triangular plate 28 is formed offset with respect to the center line of the inner fin 3, and the volume of one outlet space 17a partitioned by the top portion 28a is formed larger than the volume of the other outlet space 17b at a predetermined ratio. To be done.

The triangular plate 28 is the tube element 2
The upper plate 26 and the lower plate 27 are fixed to each other via the brazing portion 45. Corrugated triangular plate 28
A large number of cooling grooves 46 are formed between the upper plate 26 and the lower plate 27. Each cooling groove 46 is formed in a linear shape orthogonal to the flow path direction of the inner fin 3.

The two outlet channels 5 have the same channel cross-sectional area, while the two outlet spaces 17a and 17b partitioned by the apex 28a of the triangular plate 28 have different volumes. Space 17a, 17b
Between the cooling grooves 46 from the outlet space 17a.
A flow of the cryogenic fluid A that flows through to the outlet space 17b is generated. As a result, each triangular plate 28 is cooled,
It is possible to prevent the tube element 2 around each triangular plate 28 from being overheated.

[0073]

As described above, according to the present invention, the plurality of tube elements defining the first flow path through which the fluid A flows and the tube elements stacked on each other are accommodated, and the second flow path through which the fluid B flows. And a inner fin that is interposed inside each tube element,
In a laminated heat exchanger comprising outer fins interposed between the tube elements, at least one of an inlet space upstream of the inner fins or an outlet space downstream of the inner fins in the tube element,
Since the triangular plate that divides the fluid A entering and exiting the inner fin in two directions is interposed, the flow of the fluid A is smoothly guided through the triangular plate to reduce the pressure loss in the tube element, and the tube element is locally By eliminating hot spots that become extremely hot, the heat resistance of the heat exchanger can be increased, and the rigidity of the structure in which each tube element is laminated by the triangular plate is increased,
It is possible to prevent the tube element from being deformed when brazing.

According to a second aspect of the present invention, the tops of the triangular plates projecting toward the inner fins are provided offset from the center line of the inner fins, and the two spaces partitioned by the tops are provided inside the triangular plate. Since the cooling passages communicating with each other are formed, heat dissipation from the triangular plate to the fluid A passing through the cooling passages is promoted, the hot spot where the tube element locally becomes high in temperature is eliminated, and the heat resistance of the heat exchanger is enhanced.

According to the third aspect of the present invention, the inside of the triangular plate communicates with the two spaces partitioned by the apex, and the cooling passage opening at the apex facing the inner fin is formed.
Can linearly move in and out of the cooling passage opened at the top of the triangular plate, so that the heat resistance of the heat exchanger can be improved and the pressure loss in the tube element can be suppressed to be small.

[Brief description of drawings]

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

FIG. 2 is a sectional view of the heat exchanger.

FIG. 3 is a perspective view of the heat exchanger of the same.

FIG. 4 is a transverse sectional view of the heat exchanger of the same.

FIG. 5 is an exploded perspective view of the tube element of the same.

FIG. 6 is a perspective view showing a flow path configuration of the heat exchanger in the same manner.

FIG. 7 is a vertical sectional view of the tube element.

FIG. 8 is a vertical sectional view of the heat exchanger of the same.

FIG. 9 is a transverse sectional view of each tube element.

FIG. 10 is a transverse cross-sectional view showing a state in which each tube element is deformed when the triangular plate is abolished.

FIG. 11 is a plan view of the inside of the tube element showing the manner in which the fluid A flows.

FIG. 12 is a plan view of the inside of the tube element showing how the low temperature fluid A flows when the triangular plate is abolished.

FIG. 13 is a perspective view showing how the tube element deforms when a strip plate is inserted instead of the triangular plate.

FIG. 14 is a vertical sectional view of a tube element showing another embodiment.

FIG. 15 is a plan view of a tube element showing still another embodiment.

FIG. 16 is a plan view of the inside of a tube element showing still another embodiment.

FIG. 17 is a plan view of the inside of a tube element showing still another embodiment.

FIG. 18 is a plan view of a tube element showing still another embodiment.

FIG. 19 is a vertical cross-sectional view of the tube element taken along the line AA of FIG.

FIG. 20 is a cross-sectional view of a heat exchanger showing a conventional example.

FIG. 21 is a plan view of the inside of the tube element.

[Explanation of symbols]

 1 Outer fin 2 Tube element 3 Inner fin 4 Inlet channel 5 Outlet channel 6 Housing 16 Inlet space 17 Outlet space 20 Cooling groove 21 First channel 22 Second channel 28 Triangular plate 28a Top 40 Cooling groove 46 Cooling groove

Claims (3)

[Claims] 1. A plurality of tube elements that define a first flow path through which a fluid A flows, a housing that houses tube elements that are stacked together, and a housing that defines a second flow path through which a fluid B flows, and each tube. In a laminated heat exchanger including an inner fin interposed inside the element and an outer fin interposed between each tube element, in an inlet space or an inner fin upstream of the inner fin inside the tube element, A laminated heat exchanger characterized in that a triangular plate for diverting a fluid A flowing in and out of an inner fin in two directions is provided in at least one of the outlet spaces on the downstream side. 2. A triangular plate is provided with a top portion projecting toward the inner fin, offset from the center line of the inner fin, and a cooling passage is formed inside the triangle plate to connect two spaces partitioned by the top portion to each other. The laminated heat exchanger according to claim 1, wherein 3. The laminated heat exchange device according to claim 1, wherein a cooling passage is formed inside the triangular plate so as to communicate with two spaces partitioned by the top portion and open to the top portion facing the inner fin. vessel.