JPH06257983A - Lamination type heat exchanger - Google Patents

Abstract

PURPOSE:To provide a structure suitable for a lamination type heat exchanger received in a housing. CONSTITUTION:In a lamination type heat exchanger 3, in which a plurality of tube elements 4, defining a first flow passages 1, are laminated through outer fins 5 and respective tube elements 4 are received in a housing 6 defining second flow passages 2, reinforcing plates 7, interposed between the housing 6, are fixed to the tube elements 4 while the rigidity in the direction of surface of the reinforcing plate 7 is formed so as to be smaller than the same of the tube element 4 and the rigidity in a direction orthogonal to the surface of the reinforcing plate 7 is formed so as to be higher than the same of the tube element 4.

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. 11 (Actual No. Sho 63-49189).
Gazette, reference).

Explaining this, a plurality of tube elements 51 that define 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. Are laminated via outer fins 55.

First channel 5 in each tube element 51
The fluid flowing through 4 through the inner fins 50 exchanges heat with the fluid flowing through the outside of each tube element 51 through the outer fins 55.

[0005]

However, in such a conventional laminated heat exchanger, as shown in FIG. 12, each tube element is provided inside the housing 59 which defines the second flow path 58. When 51 is stacked and housed, a temperature difference occurs between the housing 59 exposed to the outside air and each tube element 51 in which fluid flows, and thermal stress is applied to the housing 59 and each tube element 51. This causes a decrease in these strengths.

That is, the housing 5 exposed to the outside air
9 rises from room temperature by ΔTo, and each tube element 51 through which the fluid flows rises from room temperature by ΔTe, the materials of the housing 59 and the tube element 51 are the same, and their linear thermal expansion coefficient is K. When the length of the portion where the housing 59 and the housing 59 are fixed to each other is L, the difference in thermal expansion between the two is K × L × (ΔT
e−ΔTo), and there is a possibility that this difference in thermal expansion will be absorbed as, for example, the deformed portion 51a that occurs in the central portion of the tube element 51.

When the tube elements 51 and the outer fins 55 are fixed to each other by brazing, for example, the tube elements 51 and the outer fins 5 are attached.
The weight is placed on the stacked 5 and placed in a furnace for heating, but the load of the weight is locally applied to each tube element 51,
There is a concern that each tube element 51 may be deformed or a gap may be formed between each tube element 51 and the outer fin 55 to reduce the heat exchange amount.

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.

[0009]

SUMMARY OF THE INVENTION According to the present invention, a plurality of tube elements defining a first flow path are stacked via outer fins, and each tube element is housed inside a housing defining a second flow path. In the mounted laminated heat exchanger, a reinforcing plate interposed between the housing and the housing is fixed to the tube element so that the rigidity of the reinforcing plate in the surface direction is smaller than that of the tube element and the rigidity of the reinforcing plate in the direction orthogonal to the surface of the reinforcing plate is increased. The rigidity is made higher than that of the tube element.

[0010]

The heat exchange is performed between the fluid flowing in the first flow path defined inside each tube element and the fluid flowing in the second flow path defined inside the housing outside each tube element. Although there is a temperature difference between the housing exposed to the outside air and each tube element through which fluid flows inside and outside, since the rigidity of the reinforcing plate in the surface direction is smaller than that of the tube element, The difference in thermal expansion generated between the tube element and the housing is absorbed, and it is possible to prevent the housing or the tube element from being deformed or cracked due to thermal stress.

When the tube elements, the outer fins, and the reinforcing plate are fixed to each other by, for example, brazing, the tube elements, the outer fins, and the reinforcing plate are stacked, and a weight is placed on the reinforcing plate to form a furnace. Put in and heat.

At this time, since the rigidity of the reinforcing plate in the direction orthogonal to the plane is higher than that of the tube element, the load of the weight is evenly distributed over the core through the reinforcing plate, and the load of the weight causes Prevents the tube element from deforming.

Furthermore, since the weight load is evenly distributed over the entire core through the reinforcing plate, it is possible to prevent gaps between the tube elements and the outer fins and to perform brazing uniformly. It becomes possible and the amount of heat exchange is not reduced.

[0014]

Embodiments of the present invention will be described with reference to the accompanying drawings.

As shown in FIG. 3, the laminated heat exchanger 3 has
A second flow path 2 is defined by the housing 6, a plurality of tube elements 4 are stacked inside the housing 6 via outer fins 5, and a first flow path 1 is defined inside each tube element 4. .

An inlet 2a of the second flow path 2 is formed at one end of the housing 6, and an outlet 2b is formed at the other end thereof.
The fluid B passes through the second flow path 2 as indicated by the arrow in the figure, and flows around each tube element 4 in the housing 6 via the outer fins 5. The housing 1 has an inlet 1 communicating with the first flow path 1 in each tube element 4.
a and the outlet 1b are respectively formed. As a result, the fluid A flows from the inlet 1a into the first flow path 1 as shown by the arrow in the figure, and after heat exchange with the fluid B is performed in the process of flowing inside each tube element 4, the fluid A is discharged from the outlet 1b. It is supposed to be leaked.

As shown in FIG. 4, the tube element 4 is a combination of a pair of box-shaped upper plate 11 and lower plate 12, and an inner fin 13 is interposed between the upper plate 11 and the lower plate 12.

Upper plate 11 and lower plate 12
An inlet 14 and an outlet 15 are formed in each. The fluid A flowing into the tube element 4 from the inlet 14 partially flows toward the outlet 15 through the inner fin 13 and the rest is joined to the other tube as shown by an arrow in the figure. It flows into the inside of the element 4.

Upper plate 11 and lower plate 12
Has peripheral portions 11a and 12a joined to each other, and one peripheral portion 12a is folded back so as to wrap the other peripheral portion 11a and fixed by caulking.

As shown in FIGS. 1 and 2, a reinforcing plate 7 is interposed between the uppermost and lowermost tube elements 4 and the housing 6.

The reinforcing plate 7 is formed with a large number of projections 8 in a box shape at regular intervals in both vertical and horizontal directions, the rigidity in the plane direction thereof is smaller than that of the tube element 4, and the rigidity in the direction orthogonal to the plane is the tube. It is formed higher than the element 4. Therefore, the plate thickness and material of the reinforcing plate 7 are appropriately set according to the rigidity of the tube element 4.

The reinforcing plate 7 provided on the upper side is fixed to the upper plate 11 of the uppermost tube element 4 by brazing, while the reinforcing plate 7 provided on the lower side is fixed to the lower plate 12 of the lowermost tube element 4. It is fixed by attaching.

The upper and lower reinforcing plates 7, the tube elements 4 and the outer fins 5 are fixed to each other by brazing in a laminated state, and a core 10 having these as a unit is provided.

A spacer 26 is provided at the inner edge of each tube element 4 and a spacer 24 is provided at the outer edge of the adjacent tube elements 4 so as to fill these gaps.

The housing 6 is formed by being divided into an upper housing plate 23, a lower housing plate 21, a side housing plate 22 and the like, and after the core 10 is housed in the housing 6, the whole or a part thereof is assembled by welding.

Outlet 15 of the uppermost tube element 4
And a spacer 24 located at the opening edge of the inlet 16 is fixed to the upper housing plate 23 by brazing,
The airtightness of the first channel 1 is ensured, and the core 10 is suspended and supported in the housing 6 at this brazed portion.

The upper and lower reinforcing plates 7 are slidably joined to the housing 6 on their entire surfaces. The reinforcing plate 7 may be partially fixed to the housing 6 and most of the reinforcing plate 7 may be slidably joined to the housing 6.

Next, the operation will be described.

As shown by the arrow in FIG. 3, the fluid A introduced into each tube element 4 through the inlet 1a flows inside each tube element 4, and the outer fin 5 with the fluid B flowing inside the housing 6. After heat exchange is performed via the outlet 1b, a temperature difference occurs between the housing 6 exposed to the outside air and the core 10 in which the fluids A and B flow inside.

Since the reinforcing plate 7 is formed so that its rigidity in the surface direction is smaller than that of each tube element 4 and each reinforcing plate 7 is slidably joined to the housing 6, the reinforcing plate 7 is not provided between the core 10 and the housing 6. It is possible to absorb the difference in thermal expansion that occurs in the housing 6 and prevent the housing 6 or the tube element 4 from being deformed or cracked due to thermal stress.

As described above, by reducing the thermal stress applied to the core 10 during heat exchange, the plate thickness of the tube element 4 and the outer fin 5 can be reduced,
The weight of the heat exchanger 3 can be reduced.

When brazing the core 10, as shown in FIG. 5, the upper housing plate 23 is placed on the base 31, and the core 10 is set upside down on the upper housing plate 23 and set at the uppermost position. The weight 32 is placed on the reinforcing plate 7 located in the furnace.

At this time, the rigidity of the reinforcing plate 7 in the direction orthogonal to its surface is higher than that of the tube element 4, so that the load of the weight 32 is evenly distributed over the core 10 through the reinforcing plate 7. The deformation of each tube element 4 due to the load of the weight 32 is prevented.

Furthermore, since the load of the weight 32 is evenly distributed over the core 10 through the reinforcing plate 7, it is possible to prevent a gap from being formed between each tube element 4 and the outer fin 5 and to make a uniform soldering. As a result, the heat exchange amount is not reduced.

On the other hand, as shown in FIG. 6, when the reinforcing plate 7 is omitted and the weight 32 is directly placed on the core 10, the load of the weight 32 locally acts on the core 10 and The core 10 is deformed as it is heated above 1000 ° C, which is the melting temperature of the brazing material, inside the core.

In order to prevent this, the reinforcing plate 7
Alternatively, a plate-shaped weight to be bonded to the entire upper surface of the core 10 may be placed on the core 10 for brazing, but in that case, the weight may be fixed to the core 10 during brazing. There is a nature.

The housing 6 is wholly or partially housed in the core 10 and then assembled,
Even if the core 10 is slightly deformed by brazing,
The housing 6 can be accurately assembled.

Next, another embodiment shown in FIG. 7 and FIG.
The upper housing plate 23 is provided with a casing 35 that keeps the brazed portion of the core 10 warm. The parts corresponding to those in the above-described embodiment are designated by the same reference numerals.

Outlet 15 of the uppermost tube element 4
A spacer 24 is fixed to the upper housing plate 23 by brazing at the opening edge of the core 10, and the core 10 is suspended and supported in the housing 6 by this brazing portion.

The casing 35 is fixed to the upper surface of the upper housing plate 23 so as to cover the opening 25 of the upper housing plate 23, and the outlet 1b for the fluid A is fixed to the upper portion of the casing 35. The opening 25 and the outlet 1b of the upper housing plate 23 are arranged on both sides of the upper housing plate 23, and a heat retaining channel 36 is defined between the casing 41 and the upper housing plate 23.

Next, the operation will be described.

At the time of heat exchange, the fluid B that has passed through the flow passage 1 of the core 10 is guided to the outlet 1b through the heat retention flow passage 6, so that the opening 25 of the upper housing plate 23 is formed.
Is exposed to the outside air and is brought close to the temperature of the core 10, and the spacer 24 and the upper housing plate 2 are
It is possible to reduce the difference in thermal expansion between the openings 25 of No. 3 and to prevent cracks or the like from occurring in the brazed portion connecting the two.

Next, in another embodiment shown in FIG. 9, the reinforcing plate 37 is formed of a honeycomb material. The parts corresponding to those in the above-described embodiment are designated by the same reference numerals.

The reinforcing plate 37 includes a large number of horizontal plates 38,
A corrugated plate 39 connecting the lateral plates 38 is formed in a honeycomb shape, and the lateral plates 38 and the corrugated plate 39 are orthogonally coupled to the upper housing plate 23.

As a result, the rigidity of the reinforcing plate 37 in the surface direction is lower than the rigidity of the tube element 4, and the rigidity of the reinforcing plate 37 in the direction orthogonal to the surface is higher than that of the tube element 4.

Since the rigidity of the reinforcing plate 37 in the direction orthogonal to the surface is formed higher than that of the tube element 4, the load of the weight 32 of the core 10 is applied via the reinforcing plate 37 during brazing as shown in FIG. It is evenly distributed over the whole and prevents each tube element 4 from being deformed by the load of the weight 32.

In this case, the reinforcing plate 37 fills the gap between the tube element 4 and the housing 6,
The entire amount of the fluid B flowing in the second flow path 2 can be passed around the outer fins 5, and the heat exchange rate can be increased.

Further, compared with the structure in which the heat insulating layer is formed between the tube element 4 and the housing 6 through the reinforcing plate 37 to suppress the heat radiation from the housing 6 to the outside air, and the tube element 4 directly contacts the housing 6. The heat exchange rate can be further increased.

[0049]

As described above, according to the present invention, a plurality of tube elements that define the first flow path are stacked via outer fins, and each tube element is provided inside the housing that defines the second flow path. In a stacked heat exchanger that has been housed, a reinforcing plate that is interposed between the housing and the housing is fixed to the tube element so that the rigidity of the reinforcing plate in the plane direction is smaller than that of the tube element, and the direction is orthogonal to the plane of the reinforcing plate. Since the rigidity of the tube element is higher than that of the tube element, it is possible to absorb the difference in thermal expansion between the tube element and the housing through the reinforcing plate and prevent the housing or tube element from being deformed or cracked due to thermal stress. Can be increased.

[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 perspective view showing a state in which tube elements and the like are similarly stacked.

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

FIG. 4 is an exploded perspective view of the tube element of the same.

FIG. 5 is a sectional view of the heat exchanger during brazing.

FIG. 6 is a cross-sectional view of the heat exchanger when a reinforcing plate is not used during brazing.

FIG. 7 is a perspective view of a housing showing another embodiment.

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

FIG. 9 is a perspective view showing a state in which tube elements and the like showing still another embodiment are stacked.

FIG. 10 is a perspective view of the tube element and the like during brazing.

FIG. 11 is a cross-sectional view of a conventional heat exchanger.

FIG. 12 is a sectional view of a heat exchanger including a housing.

[Explanation of symbols]

 1 1st flow path 2 2nd flow path 3 Laminated heat exchanger 4 Tube element 5 Outer fin 6 Housing 7 Reinforcement plate

Claims (1)

[Claims] 1. A laminated heat exchanger in which a plurality of tube elements that define a first flow path are stacked via outer fins, and each tube element is housed inside a housing that defines a second flow path. By fixing the reinforcing plate interposed between the housing and the housing to the tube element, the rigidity of the reinforcing plate in the surface direction is made smaller than that of the tube element, and the rigidity in the direction orthogonal to the surface of the reinforcing plate is made higher than that of the tube element. A laminated heat exchanger characterized by the above.