JPH09273886A - Laminate type heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a structure which is suitable for a laminate type heat exchanger mounted into a housing. SOLUTION: An gate passage is arranged piercing tube elements and a part where the gate passage of the tube elements is opened is fastened on a housing 6. A separation plate 40 is interposed between the tube elements and the housing 6. This allows separation of a part for closing the gate passage of the tube elements from the housing 6 through the separation plate 40.

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 A laminated heat exchanger provided in a gas turbine or the like is provided with a plurality of box-shaped tube elements defining a first flow passage therein, and each tube element is laminated through outer fins. Has been done.

An inlet / outlet channel for guiding the fluid A to the first channel in each tube element is arranged so as to penetrate through each laminated tube element.

The fluid A flowing in the first flow path in each tube element via the inner fin is heat-exchanged with the fluid B flowing outside the tube element via the outer fin. (See, for example, JP-A-6-257982).

[0005]

However, in such a conventional laminated heat exchanger, when the tube elements are housed in a state where they are stacked inside the housing that defines the second flow path. Due to the difference in thermal expansion between the housing and each tube element, a tensile stress may occur around the inlet / outlet channel, which causes a decrease in the strength of these elements.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a structure suitable for a laminated heat exchanger housed in a housing.

[0007]

A laminated heat exchanger according to claim 1, wherein a plurality of tube elements defining a first flow path through which the fluid A flows and an inlet / outlet flow for allowing the fluid A to flow in and out of the first flow path. A passage, a housing defining the second flow path through which the fluid B flows by accommodating the laminated tube elements, an inner fin interposed inside each tube element, and an inner fin interposed between each tube element. In a laminated heat exchanger including an outer fin to be mounted, the inlet / outlet flow path is disposed through each tube element,
A portion of the tube element where the inlet / outlet passage is opened is fixed to the housing, and a non-fixed region that allows the tube element to separate from the housing is formed at least between the portion that closes the inlet / outlet passage of the tube element and the housing.

According to a second aspect of the present invention, in the laminated heat exchanger according to the first aspect of the present invention, a separate plate is provided between a portion of the tube element that closes the inlet / outlet passage and a housing. To the tube element.

According to a third aspect of the present invention, in the laminated heat exchanger according to the second aspect, the separate plate and the tube element are made of materials having the same coefficient of thermal expansion.

According to a fourth aspect of the present invention, in the laminated heat exchanger according to the second or third aspect, the separate plate and the tube element are made of the same material, and the plate thickness of the separate plate is the plate of the tube element. It is formed larger than the thickness.

The laminated heat exchanger according to a fifth aspect of the present invention is the laminated heat exchanger according to any one of the second to fourth aspects, in which a plurality of reinforcing ribs are formed in a portion of the housing facing the separate plate. Each reinforcing rib is formed orthogonal to the flow direction of the fluid B.

In the laminated heat exchanger according to a sixth aspect of the present invention, in the invention according to any one of the second to fifth aspects, the separate plate is fixed to the housing in a region where the separate plate overlaps with the inner fin.

The laminated heat exchanger according to a seventh aspect is the laminated heat exchanger according to any one of the second to sixth aspects, in which a spacer is provided around the inlet and outlet passages between the tube elements to separate the tube elements. The plate is formed in the same shape as the outer shape of the spacer.

[0014]

In the laminated heat exchanger according to claim 1, the fluid A introduced into each tube element through the inlet passage.
Flows through each tube element, and after heat exchange is performed with the fluid B flowing inside the housing via the outer fins, flows out through the outlet passage.

When the hot fluid B flows between the housing and each tube element, the housing may thermally expand more than each tube element.

In response to this, the portion of the tube element where the inlet / outlet passage is opened is fixed to the housing, but at least the portion of the tube element that closes the inlet / outlet passage is separated from the housing. The difference in thermal expansion between the housing and the housing is absorbed by the tube element leaving the housing and leaving a gap.

As a result, tensile stress does not act on the brazing portion provided around the inlet / outlet passage, so that the brazing portion is peeled off and the fluid A can be prevented from flowing out of the tube element. .

When the housing is assembled by welding so as to enclose the laminated tube elements,
Since the portion of the tube element that blocks the inlet / outlet flow path is not fixed to the housing, the housing can be assembled with high accuracy even if the tube elements are slightly misaligned.

In the laminated heat exchanger according to the second aspect of the present invention, the difference in thermal expansion between each tube element and the housing is absorbed when the separate plate is separated from the housing to form a gap.

In the laminated heat exchanger according to the third aspect, since the separate plate has the same coefficient of thermal expansion as the tube element, even if each tube element is heated by the high temperature fluid B and thermally deformed, the separate plate is separated. Is similarly thermally deformed, and the thermal stress acting on the tube element and the separate plate can be suppressed to be small.

In the laminated heat exchanger according to the fourth aspect of the present invention, since the portion of the tube element that closes the inlet / outlet passage is supported by the separate plate having a large plate thickness, the tube element is attached to the tube element by the pressure difference between the fluid A and the fluid B. It is possible to prevent cracks from occurring.

In the laminated heat exchanger according to the fifth aspect, there is a possibility that the portion of the housing facing the Pareto plate may be deformed due to the difference in pressure between the inside and the outside of the housing due to the difference in thermal expansion.

The portion of the housing facing the separate plate has its rigidity increased through a plurality of reinforcing ribs, and can be prevented from being deformed by the pressure difference between the inside and the outside of the housing.

Further, the gap between the housing and the separate plate caused by the difference in thermal expansion is generated by the fluid B.
, But the cross-sectional area of this gap is a labyrinth-like flow path that is changed by the reinforcing ribs orthogonal to the flow direction of the fluid B, so the flow rate of the fluid B passing through the gap is suppressed and the heat exchange efficiency is increased. Can be increased.

In the laminated heat exchanger according to the sixth aspect of the present invention, although both end portions of each laminated tube element are fixed to the housing, a portion of the tube element that blocks the inlet / outlet passage is separated from the housing. Due to the structure, the difference in thermal expansion between each tube element and the housing is absorbed by the tube element separating from the housing and leaving a gap.

Since the region fixed to the housing through the separate plate is provided in the region where the inner fin overlaps, the tensile stress acting on each tube element due to the difference in thermal expansion is limited to the portion where the inner fin is interposed. It Since the inner fin is firmly fixed to the tube element, it is possible to prevent the brazing portion of the tube element from being peeled off.

A gap is created between the housing and the separate plate due to the difference in thermal expansion, but since this gap is closed by the region where the housing and the separate plate are fixed to each other, the flow rate of the fluid B passing through this gap is suppressed and heat exchange is performed. You can increase efficiency.

In the laminated heat exchanger according to claim 7, both ends of each laminated tube element are fixed to the housing, but the portion that closes the inlet / outlet passage of the tube element is the outer shape of the spacer. Because of the structure in which the tube elements are separated from each other through the spacer having the same shape, the difference in thermal expansion between each tube element and the housing is absorbed when the tube elements are separated from the housing to form a gap.

A gap is created between the housing and the separate plate due to the difference in thermal expansion, but since the housing and the tube element are fixed to each other in a region other than where the separate plate is provided, the flow rate of the fluid B passing through this gap is suppressed. The heat exchange efficiency can be improved.

Since the gap generated between the tube element and the lower bracket due to the difference in thermal expansion is small only in the region where the separate plates are interposed, the bending stress generated in the separate plate due to the pressure difference between the fluids A and B is suppressed to a small level. To be As a result, the plate thickness of the separate plate can be reduced, and the weight can be reduced.

[0031]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the accompanying drawings.

As shown in FIG. 1, the housing 6 is made up of parts such as an upper bracket 41, a lower bracket 45, a side bracket 8 and the like, and a core 20 made up of each tube element 2 and outer fins 1 and the like is provided therein. Be housed.

As shown in FIG. 6, 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. 5, a first flow path 21 through which the cryogenic fluid A flows is defined inside each tube element 2.

As shown in FIG. 7, the outer fin 1 has two inlet passages 4 through which the low temperature fluid A flows into each tube element 2 and two outlet passages 5 through which the low temperature fluid A flows out 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 process 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 channel 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, in the tube element 2, a box-shaped upper plate 26 and a lower plate 27 are combined, and the 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 joined to each other, and one peripheral portion 27b is folded back so as to surround the other peripheral portion 26b and fixed by crimping, thereby forming a peripheral fixing portion 10 having a substantially square frame shape. You.

Upper plate 26 and lower plate 27
The bosses 26a and 27a are formed to project from the bosses 26a and 27a, respectively.
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.

Inside the tube element 2, a spacer 14 is interposed between the upper plate 26 and the lower plate 27 so as to surround the inlet passage 4, and bosses 26a and 27a are provided between the tube elements 2. A spacer 15 is provided so as to surround it.

The spacer 14 is formed in a C shape as shown in FIG. The spacer 15 is shown in FIG.
As shown in FIG.

Each spacer 15 is fixed to the upper plate 26 and the lower plate 27 by brazing. The airtightness of the inlet passage 4 can be secured by fixing the spacers 15 by brazing.

The upper plate 26 and the lower plate 27 of the tube element 2 are thin plates made of ferritic stainless steel. For the upper plate 26 and the lower plate 27, a clad material in which a brazing material is clad in advance on each surface is used.

The spacers 14 and 15 prevent variations in the distance between the upper plate 26 and the lower plate 27, and increase the rigidity to secure strength against external loads and impacts.

By increasing the strength of the structure in which the tube elements 2 are laminated by the spacers 14 and 15, the strength required for the inner fin 3 and the outer fin 1 is reduced, and the plate thickness of these is reduced. The pressure loss of the heat exchanger can be reduced.

As for the tube element 2 around the outlet channel 5 as well as around the inlet channel 4, the bosses 26a and 27a are fitted to each other so that each tube element 2
Spacers are provided inside and outside the so as to surround the outlet channel 5. The bosses 26a and 27a arranged at the four corners are fitted with each other in a state where the tube elements 2 are stacked with each other, so that the assembling accuracy can be sufficiently ensured.

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

The side bracket 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 bracket 8 is each convex portion 8
A concave portion 8c is formed between the holes 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.

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.

The inlet flow path 4 and the outlet flow path 5 pass through each tube element 2, and the tube element 2 in the lowermost layer.
The lower plate 27 of FIG.

As shown in FIG. 2, one separate plate 40 is interposed between the lowermost tube element 2 and the lower bracket 45.

The separate plate 40 is made of a ferritic stainless material having a coefficient of thermal expansion substantially equal to that of the upper plate 26 and the lower plate 27 of the tube element 2.

The flat plate-shaped separate plate 40 is
The lower bracket 45 and the tube element 2 have the same shape, and the lower bracket 45 is seated on the lower bracket 45 for positioning with respect to the housing 6.

The separate plate 40 is formed with a large plate thickness so that its rigidity is higher than that of the upper plate 26 and the lower plate 27 of each tube element 2.

The core 20 is fixed by brazing in a state where the separate plate 40, each tube element 2 and each outer fin 1 are laminated on each other, and these are unitized.

At the time of brazing the core 20, as shown in FIG. 3, the upper bracket 41 is placed on the jig 46, and the tube elements 2 are laminated on the upper bracket 41 with the vertical direction reversed. Tube element 2 located at the top
The separate plate 40 is placed on top of the above, and the weight 32 is placed on the separate plate 40 and put in the furnace.

At this time, the rigidity of the tube element 2 in the orthogonal direction is increased through the spacers 14 and 15 provided around the inlet flow path 4 and the outlet flow path 5, so that each tube is loaded by the weight 47. The element 2 is prevented from being deformed.

The load of the weight 47 is evenly distributed over each tube element 2 via the separate plate 40, so that no gap is formed between each tube element 2 and the outer fin 1 and the load is evenly distributed. As a result, the heat exchange amount is not reduced.

The separate plate 40 is fixed to the entire surface of the lower plate 27 of the lowermost tube element 2 through the brazing material clad with the lower plate 27.

The housing 6 has the upper bracket 41 and the tube elements 2 and the separate plate 40.
And the like, the lower bracket 45, the side bracket 8 and the inlet duct 24 are wrapped around the core 20.
And the parts such as the outlet duct 25 are assembled by welding.

With the housing 6 assembled, the inlet channel 4 and the outlet channel 5 of the uppermost tube element 2 are provided.
The spacer 15 is located at the open end of the upper bracket 41.
The passages 4 and 5 are airtightly secured by brazing, and the core 20 is suspended and supported in the housing 6 at the brazing portion.

The separate plate 40 is not fixed to the lower bracket 45 of the housing 6, but the entire surface thereof can be separated from the lower bracket 45. That is, as the gist of the present invention, the non-fixed region where the tube element 2 is separated from the housing 6 is
It is provided on the entire surface of the tube element 2 including a portion that closes the inlet passage 4 and the outlet passage 5 and the housing 6.

The configuration is as described above. Next, the operation will be described.

The fluid A guided to each tube element 2 through the inlet flow path 4 flows inside each tube element 2 and exchanges heat with the fluid B flowing inside the housing 6 via the outer fin 1. After that, it flows out through the outlet channel 5.

As the high temperature fluid B flows between the core 20 and the side bracket 8, the side bracket 8
Is heated, so that the thermal expansion may be larger than that of the core 20.

In response to this, although the upper portion of the core 20 is fixed to the housing 6, the separate plate 40 attached to the lower portion of the core 20 is not fixed to the housing 6. The difference in thermal expansion is absorbed by the separation plate 40 separating from the lower bracket 45 of the housing 6 and leaving a gap.

As a result, the inlet channel 4 and the outlet channel 5
Since tensile stress is not applied to the brazed portions of the respective spacers 14 and 15 and the tube element 2 provided around the, the brazed portion is peeled off and the fluid A is prevented from flowing out of the tube element 2. To be

The separate plate 40 includes the upper plate 26 and the lower plate 2 of the tube element 2.
7 has substantially the same coefficient of thermal expansion, so that even if each tube element 2 is heated by the high temperature fluid B and is thermally deformed, the separate plate 40 is also thermally deformed, so that the tube element 2 and the separate plate 40 The thermal stress that acts on can be kept small.

As shown in FIG. 8, the lower plate 27 of the lowermost tube element 2 is separated by the separate plate 40.
In the structure that is not supported by the pressure A, when the pressure PA of the fluid A is higher than the pressure PB of the fluid B, as the lower bracket 45 moves away from the lower plate 27 due to the difference in thermal expansion, the pressure difference (PA-PB) causes the lower bracket 45 to move away from the lower plate 27. The plate 27 may swell and crack may occur. If the plate thickness of the tube element 2 is increased in response to this, the weight is increased.

In this embodiment, since the lower plate 27 of the lowermost tube element 2 is supported by the separate plate 40 having a sufficient plate thickness, the lower plate 27 is caused by the pressure difference (PA-PB) between the fluid A and the fluid B. It is possible to prevent cracks from occurring in the.

In the housing 6, the lower bracket 45, the side brackets 8, the inlet duct 24, the outlet duct 25, and other parts are assembled by welding so that the core 20 is housed inside and then the core 20 is wrapped. Since the structure is not fixed to the core 20, the housing 6 can be accurately assembled even when the core 20 is slightly deformed by brazing.

Next, the embodiment shown in FIG. 9 will be described. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

A plurality of reinforcing ribs 51 are formed on the lower bracket 45 of the housing 6. The reinforcing ribs 51 are orthogonal to the flow direction of the fluid B and are formed with a constant interval.

As shown in FIGS. 10 and 11, the reinforcing rib 5
1 is formed to have an arcuate cross section protruding to the outside of the lower bracket 45.

The configuration is as described above. Next, the operation will be described.

As shown in FIG. 12, in the structure in which the reinforcing rib is not formed on the lower bracket 45 of the housing 6,
If the pressure on the outside of the housing 6 is higher than the pressure on the inside,
As the lower bracket 45 moves away from the tube element 2 due to the difference in thermal expansion, the pressure difference may cause the lower bracket 45 to inflate and deform. When the lower bracket 45 is deformed, the tube element 2 may be pressed as the tube element 2 is seated on the lower bracket 45 when the heat exchanger is cooled, and the tube element 2 having low rigidity may be deformed. is there.

In this embodiment, since the lower bracket 45 is provided with a number of reinforcing ribs 51, the lower bracket 4
The rigidity of 5 can be improved, and the lower bracket 45 can be prevented from being deformed by the pressure difference between the inside and the outside of the housing 6.

Further, the gap 5 generated as the lower bracket 45 separates from the separate plate due to the difference in thermal expansion.
Fluid B passes through 2 as indicated by the arrow in FIG. However, since the gap 52 has a labyrinth-like flow path whose cross-sectional area is changed by the reinforcing ribs 51 orthogonal to the flow direction of the fluid B, the flow rate of the fluid B passing through the gap 52 is suppressed and the heat exchange efficiency is improved. To be enhanced.

Next, the embodiment shown in FIG. 13 will be described. The parts corresponding to those in FIG. 9 are denoted by the same reference numerals.

A plurality of reinforcing ribs 61 are formed on the lower bracket 45 of the housing 6. The reinforcing ribs 51 are orthogonal to the flow direction of the fluid B and are formed with a constant interval.

The reinforcing rib 51 is formed so as to have an arcuate cross-section protruding inside the lower bracket 45.

The operation will be described below.

In the present embodiment, the gap 62 generated as the lower bracket 45 moves away from the tube element 2 due to the difference in thermal expansion has a labyrinth-shaped cross-sectional area narrowed by the reinforcing ribs 61 protruding inward from the lower bracket 45. Since it is the flow path, the flow rate of the fluid B passing through the gap 52 can be suppressed and the heat exchange efficiency can be improved.

Next, the embodiment shown in FIG. 14 will be described. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

The separate plate 40 is partially fixed to the lower bracket 45 of the housing 6 by brazing. The fixing area 65 where the separate plate 40 and the lower bracket 45 are fixed is provided across the central portion of the separate plate 40 as shown by the chain double-dashed line. The fixing region 65 is provided across the central portion of the region overlapping the inner fin 3 in the plan view of FIG.

The fixing region 65 is provided so as to avoid between the closed ends of the inlet flow path and the outlet flow path and the housing 6. That is, the non-fixed region where the tube element 2 is separated from the housing 6 is provided in a region including between the closed ends of the inlet passage and the outlet passage and the housing 6.

The structure is as described above. Next, the operation will be described.

Although the upper and lower parts of the core 20 are fixed to the housing 6, the separate plate 40 attached to the lower part of the core 20 has the closed ends of the inlet and outlet flow paths and the housing 6 with respect to the housing 6. Since the gap between the side bracket 8 and the side bracket 8 is avoided, both ends of the separate plate 40 are absorbed by the gap between the lower bracket 45 of the housing 6 and the gap.

As a result, no tensile stress is applied to the brazing portions of the spacers and the tube elements 2 provided around the inlet channel and the outlet channel 5, so that the brazing portions are peeled off and the fluid A is removed. Is prevented from flowing out of the tube element 2.

Although the upper and lower parts of the core 20 are fixed to the housing 6, the region 61 for fixing the lower part of the core 20 to the housing 6 is provided in the region where the inner fin 3 and the inner fin 3 overlap with each other. The tensile stress acting on the core 20 is limited to the portion where the inner fin 3 is interposed. Since the inner fins 3 are firmly fixed to the tube element, the brazing portion of the tube element can be prevented from peeling off.

Due to the difference in thermal expansion, a gap is created between the lower bracket 45 and the separate plate 40 as the lower bracket 45 moves away from the core. This gap is defined by the region 61 for fixing the central portion of the lower bracket 45 and the separate plate 40. Since it is blocked, the flow rate of the fluid B passing through this gap can be suppressed and the heat exchange efficiency can be improved.

Next, the embodiment shown in FIG. 15 will be described. The parts corresponding to those in FIG. 1 are designated by the same reference numerals.

Four separate plates 70 are provided between the lowermost tube element 2 and the lower bracket 45. Each separate plate 70 is fixed to the lower plate of the tube element by brazing.

Each separate plate 70 is a housing 6
The lower bracket 45 is not fixed to the lower bracket 45 and can be separated from the lower bracket 45. The tube element is fixed to the lower bracket 45 by brazing in a region other than the region where it is joined to each separate plate 40.
That is, as the gist of the present invention, the non-fixed region where the tube element is separated from the housing 6 is provided between the closed ends of the inlet channel and the outlet channel and the housing 6.

Each separate plate 70 having a flat plate shape
Has the same shape as the outer shape of the ring-shaped spacer 15 provided around the inlet channel and the outlet channel. When assembling, each separate plate 70 is attached to the lower bracket 45.
The core 20 is positioned with respect to the housing 6 by being seated in the recesses 8a and 8b formed at the four corners.

With the above arrangement, the operation will be described.

Although the upper and lower parts of the core 20 are fixed to the housing 6, the separate plates 70 attached to the lower part of the core 20 are connected to the housing 6 at the closed ends of the inlet and outlet flow paths and the housing. Since the gaps between the side brackets 8 and the side brackets 8 are avoided, the difference in thermal expansion from the side brackets 8 is absorbed when the separate plates 70 are separated from the lower brackets 45 of the housing 6 to form a gap.

As a result, no tensile stress is applied to the spacers provided around the inlet channel and the outlet channel and the brazing portions of the tube elements, so that the brazing portions are peeled off and the fluid A is removed from the tube elements. Outflow to the outside is avoided.

Due to the difference in thermal expansion, a gap is formed between each lower plate 45 and each separate plate 70 as the lower bracket 45 is separated from the core, and this gap is closed by the region where the tube element is fixed to the lower bracket 45. Therefore, the flow rate of the fluid B passing through this gap can be suppressed and the heat exchange efficiency can be improved.

Since the gap generated between the tube element 2 and the lower bracket 45 due to the difference in thermal expansion is limited to the area where each separate plate 70 is interposed, the fluid A
The bending stress generated in the separate plate 70 due to the pressure difference between the fluid B and the fluid B can be suppressed to be small. As a result, the plate thickness of the separate plate 40 can be reduced, and the weight can be reduced.

[0102]

As described above, in the laminated heat exchanger according to the first aspect of the invention, at least the inlet / outlet passage of the tube element is closed although the portion where the inlet / outlet passage of the tube element opens is fixed to the housing. Since the part to be closed is separated from the housing, the difference in thermal expansion between each tube element and the housing is absorbed by the gap between the tube element and the housing, leaving a brazed part around the inlet / outlet flow path. Thus, the fluid A can be prevented from flowing out of the tube element.

In the laminated heat exchanger according to claim 2, the difference in thermal expansion between each tube element and the housing is absorbed when the separate plate fixed to the tube element is separated from the housing to leave a gap, and the inlet / outlet flow is increased. It is possible to prevent the fluid A from flowing out to the outside of the tube element by peeling off the brazing part and the like around the passage.

In the laminated heat exchanger according to claim 3, since the separate plate has the same coefficient of thermal expansion as the tube element, each tube element has a high temperature fluid B.
Even if the separate plate is heated and deformed by heat, the separate plate is also similarly deformed by heat, so that the thermal stress acting on the tube element and the separate plate can be suppressed to be small, and the tube element can be prevented from being cracked.

In the laminated heat exchanger according to the fourth aspect of the present invention, since the portion that closes the inlet / outlet passage of the tube element is supported by the separate plate having a large plate thickness, the tube element is attached to the tube element by the pressure difference between the fluid A and the fluid B. It is possible to prevent cracks from occurring.

In the laminated heat exchanger according to the fifth aspect, since the portion of the housing facing the separate plate is reinforced by the plurality of reinforcing ribs, the housing is prevented from being deformed by the pressure difference between the inside and the outside. While you can
The heat exchange efficiency can be improved by reducing the gap generated between the housing and the separate plate due to the difference in thermal expansion.

In the laminated heat exchanger according to the sixth aspect of the present invention, both end portions of each laminated tube element are fixed to the housing, but the portion that closes the inlet / outlet passage of the tube element is separated from the housing. Due to the structure, the difference in thermal expansion between each tube element and the housing is absorbed by the gap between the tube element and the housing, and a gap is created between the housing and the separate plate due to the difference in thermal expansion. Exchange efficiency can be improved.

In the laminated heat exchanger according to the seventh aspect of the present invention, both end portions of each laminated tube element are fixed to the housing, but the portion that closes the inlet / outlet passage of the tube element is the outer shape of the spacer. Due to the structure that can be separated from the housing through the spacer of the same shape,
The difference in thermal expansion between each tube element and the housing is absorbed by the tube element being separated from the housing and leaving a gap, and the plate thickness of the separate plate is reduced to reduce the weight.

[Brief description of drawings]

FIG. 1 is an exploded view of a heat exchanger showing an embodiment of the present invention.

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

FIG. 3 is a sectional view showing the tube element when brazing.

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

FIG. 5 is a sectional view of the heat exchanger of the same.

FIG. 6 is a sectional view of the heat exchanger of the same.

FIG. 7 is a perspective view showing a flow path configuration of the heat exchanger in the same manner.

FIG. 8 is a sectional view of a heat exchanger showing a comparative example.

FIG. 9 is a plan view of a separate plate showing another embodiment.

FIG. 10 is a side view of the same separate plate.

FIG. 11 is a sectional view of the heat exchanger of the same.

FIG. 12 is a sectional view of a heat exchanger showing a comparative example.

FIG. 13 is a sectional view of a heat exchanger showing still another embodiment.

FIG. 14 is a plan view of a heat exchanger showing still another embodiment.

FIG. 15 is an exploded view of a heat exchanger showing still another embodiment.

[Explanation of symbols]

 1 Outer fin 2 Tube element 3 Inner fin 4 Inlet flow path 5 Outlet flow path 6 Housing 8 Side bracket 14 Spacer 15 Spacer 20 Core 21 First flow path 22 Second flow path 40 Separate plate 41 Upper bracket 45 Lower bracket 51 Reinforcing rib 61 Reinforcing rib 65 Fixed area 70 Separate plate

Front Page Continuation (72) Inventor Kiyowa Kaiho 3-5-1, Fujisaki, Kawasaki-ku, Kawasaki-shi, Kanagawa Prefecture Tokyo Radiator Manufacturing Co., Ltd.

Claims (7)

[Claims] 1. A plurality of tube elements that define a first flow path through which a fluid A flows, an inlet / outlet flow path that allows the fluid A to flow in and out of the first flow path, and a fluid B that accommodates tube elements that are stacked together.
In a laminated heat exchanger comprising: a housing defining a second flow path through which the tube flows; inner fins provided inside each tube element; and outer fins provided between the tube elements, The inlet / outlet passage is arranged so as to pass through each tube element, and a portion of the tube element where the inlet / outlet passage is opened is fixed to the housing, and a non-fixed region that allows the tube element to separate from the housing is at least the tube element. A laminated heat exchanger, characterized in that it is formed between a portion that closes the inlet and outlet flow paths of the housing and the housing. 2. The laminated heat according to claim 1, wherein a separate plate is interposed between a portion of the tube element that closes the inlet / outlet flow path and the housing, and the separate plate is fixed to the tube element. Exchanger. 3. The laminated heat exchanger according to claim 2, wherein the separate plate and the tube element are formed of materials having the same coefficient of thermal expansion. 4. The separate plate and the tube element are made of the same material, and the plate thickness of the separate plate is made larger than the plate thickness of the tube element.
5. The laminated heat exchanger according to 1. 5. A plurality of reinforcing ribs are formed at a portion of the housing facing the separate plate, and each reinforcing rib is formed orthogonally to a flow direction of the fluid B. The laminated heat exchanger according to any one of the above. 6. The laminated heat exchanger according to claim 2, wherein the separate plate is fixed to the housing in a region where the separate plate overlaps with the inner fin. 7. The spacer according to claim 2, wherein a spacer is provided around the inlet / outlet passage between the tube elements, and the separate plate is formed in the same shape as the outer shape of the spacer. The laminated heat exchanger described.