JPH10206043A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To blaze the edge parts of heat transferring plates securely without high precision finishing work to the edge parts of the heat transferring plates in a heat exchanger formed with the paths of combustion gas and paths of air being formed with heat transferring plates alternately. SOLUTION: Combustion gas inlets 11 and air outlets 16 are formed along the pair of the edges of a chevron shape by cutting the edge parts of the heat transferring plates S1 and S2 being formed by folding zigzag folding material at the folding lines of L1 and L2 to the chevron shape and blazing the top parts of the chevron shape formed by overlapping the folded flange parts 26 each other alternately in surface contact states. Compared with the case of blazing the flange of other material to the cutting surface being formed by cutting the top part of the chevron shape, the precision finishing of the cutting surface is eliminated and blazing strength is increased.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger in which a plurality of first heat transfer plates and a plurality of second heat transfer plates are alternately arranged to define a high-temperature fluid passage and a low-temperature fluid passage alternately. About the vessel.

[0002]

2. Description of the Related Art Such a heat exchanger is disclosed in Japanese Patent Application Nos. 7-193208 and 8-27505 filed by the present applicant.
No. 7 has already proposed.

[0003]

By the way, in the conventional heat exchanger, a partition plate is brazed to a cut surface obtained by cutting a vertex of a heat transfer plate formed in a mountain shape, thereby forming a high-temperature fluid passage inlet. And a partition between the low-temperature fluid outlet and a low-temperature fluid passage inlet and a high-temperature fluid outlet.
For this reason, the junction between the cut surface of the heat transfer plate and the partition plate comes into line contact, and not only requires precise finishing of the cut surface to perform brazing reliably, but also performs the finishing. However, there is a problem that it is difficult to obtain sufficient bonding strength.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to provide a sufficient bonding strength without subjecting an end portion of a heat transfer plate to precise finishing.

[0005]

According to the first aspect of the present invention, the first heat transfer plate and the second heat transfer plate, which are alternately arranged, are bent at the apexes cut into a chevron so that the flange portion is formed. The flange portions are overlapped and joined to each other in surface contact with each other. The joined flange portion partitions between the fluid passage entrance and exit formed along the edge of the chevron. The flanges of the heat transfer plate are joined in surface contact, which not only increases the joining strength, but also eliminates the need for precise finishing of the cut surface at the top of the chevron, thus joining the projections of the heat transfer plate. And the joining of the flange can be completed in one process.

Further, in the invention described in claim 2, the first aspect
A folded plate material in which a heat transfer plate and a second heat transfer plate are alternately connected via a first fold line and a second fold line is manufactured, and the folded plate material is zigzag along the first fold line and the second fold line. The high-temperature fluid passages and the low-temperature fluid passages can be formed alternately by bending the fluid passages. The number of parts is reduced as compared with the case where the first heat transfer plate and the second heat transfer plate are formed of different members and are joined to each other, and the positions of the first heat transfer plate and the second heat transfer plate are also reduced. The processing accuracy can be improved by preventing the displacement.

Further, in the invention described in claim 3, the first
The flange portions of the heat transfer plate and the second heat transfer plate are bent in an arc shape and overlapped. At this time, the height of the ridges formed along the mountain-shaped edges of the first heat transfer plate and the second heat transfer plate so as to close the fluid passage entrance / exit gradually decreases at the flange portion, so that they are mutually contacted at the flange portion. It is possible to prevent a gap from being formed between the ridges while preventing interference between the ridges that are in contact with each other.

According to the invention described in claim 4, the short sides of the first heat transfer plate and the second heat transfer plate which are alternately arranged are bent to form a flange portion, and these flange portions are formed. Are superimposed and joined to each other in a plane contact state. By joining the end wall to the joined flange portion, the space between the fluid passage ports formed at both ends in the long side direction of the bottom wall is partitioned. Since the flange portion of the heat transfer plate is joined in surface contact, not only increases the joining strength, but also eliminates the need for precise finishing of the short side cut surface of the heat transfer plate.
The joining of the protrusions of the heat transfer plate and the joining of the flange can be completed in one process.

[0009] In the invention described in claim 5, the first aspect is provided.
A folded plate material in which a heat transfer plate and a second heat transfer plate are alternately connected via a first fold line and a second fold line is manufactured, and the folded plate material is zigzag along the first fold line and the second fold line. The high-temperature fluid passages and the low-temperature fluid passages can be formed alternately by bending the fluid passages. The number of parts is reduced as compared with the case where the first heat transfer plate and the second heat transfer plate are formed of different members and are joined to each other, and the positions of the first heat transfer plate and the second heat transfer plate are also reduced. The processing accuracy can be improved by preventing the displacement.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

1 to 12 show a first embodiment of the present invention. FIG. 1 is an overall side view of a gas turbine engine, FIG. 2 is a sectional view taken along line 2-2 of FIG. 1, and FIG. 2 is an enlarged sectional view taken along line 3-3 (a sectional view of a combustion gas passage), and FIG.
3 is an enlarged sectional view of the line (a sectional view of the air passage), and FIG.
FIG. 6 is an enlarged sectional view taken along line -5 of FIG. 5, FIG. 7 is an enlarged sectional view taken along line 7-7 of FIG. 3, FIG.
FIG. 9 is a perspective view of a main part of the heat exchanger, FIG. 10 is a schematic diagram showing the flow of combustion gas and air, FIG. 11 is a graph for explaining the operation when the pitch of the projections is made uniform, and FIG. 6 is a graph for explaining an operation when is made non-uniform.

As shown in FIGS. 1 and 2, the gas turbine engine E includes an engine body 1 in which a combustor, a compressor, a turbine, and the like (not shown) are housed. An annular heat exchanger 2 is arranged in such a manner as to perform the heat treatment. The heat exchanger 2 has a combustion gas passage 4 through which a relatively high temperature combustion gas passing through the turbine passes.
And air passages 5 through which relatively low-temperature air compressed by the compressor passes are alternately formed in the circumferential direction (see FIG. 5). The cross section in FIG. 1 corresponds to the combustion gas passages 4, and air passages 5 are formed adjacent to the front side and the rear side of the combustion gas passages 4.

The cross-sectional shape of the heat exchanger 2 along the axis is a flat hexagon that is long in the axial direction and short in the radial direction, and its outer peripheral surface in the radial direction is closed by a large-diameter cylindrical outer casing 6. The radially inner peripheral surface is closed by a small-diameter cylindrical inner casing 7. Heat exchanger 2
The front end side (left side in FIG. 1) of the vertical section is cut into an unequal-length mountain shape, and an end plate 8 connected to the outer periphery of the engine body 1 is brazed to a portion corresponding to the vertex of the mountain shape. Further, the rear end side (right side in FIG. 1) of the cross section of the heat exchanger 2 is cut into an unequal-length chevron, and an end plate 10 connected to the outer housing 9 is brazed to a portion corresponding to the vertex of the chevron. You.

Each combustion gas passage 4 of the heat exchanger 2 has a combustion gas passage inlet 11 and a combustion gas passage outlet 12 at the upper left and lower right in FIG. A downstream end of a space (shortly, a combustion gas introduction duct) 13 formed along the outer periphery for introducing the combustion gas is connected, and the combustion gas passage outlet 12 discharges the combustion gas extending into the engine body 1. The upstream end of a space (abbreviated combustion gas exhaust duct) 14 is connected.

Each air passage 5 of the heat exchanger 2 has an air passage inlet 15 and an air passage outlet 16 at the upper right and lower left in FIG. 1, and the air passage inlet 15 extends along the inner periphery of the outer housing 9. The downstream end of the formed air introduction space (abbreviated air introduction duct) 17 is connected, and the air passage outlet 16 has a space (abbreviated air discharge duct) for discharging air extending inside the engine body 1. 18 upstream ends are connected.

In this manner, as shown in FIGS. 3, 4 and 10, the combustion gas and the air flow in mutually opposite directions and intersect with each other, so that the counter flow and the heat exchange efficiency are high. A so-called cross flow is realized. That is, by flowing the high-temperature fluid and the low-temperature fluid in mutually opposite directions, the temperature difference between the high-temperature fluid and the low-temperature fluid can be kept large over the entire length of the flow path, and the heat exchange efficiency can be improved.

The temperature of the combustion gas driving the turbine is about 600 to 700 at the combustion gas passage inlets 11.
° C, and when the combustion gas passes through the combustion gas passages 4, heat is exchanged with air to be cooled to about 300 to 400 ° C at the combustion gas passage outlets 12. On the other hand, the temperature of the air compressed by the compressor is about 200 to 300 ° C. at the air passage inlets 15.
When the air passes through the air passages 5 and performs heat exchange with the combustion gas, the air is heated to about 500 to 600 ° C. at the air passage outlets 16.

Next, the structure of the heat exchanger 2 will be described with reference to FIGS.

As shown in FIG. 3, FIG. 4 and FIG.
The main body of the vessel 2 is made of a thin metal plate such as stainless steel in a predetermined shape.
After cutting in advance, the surface is pressed and processed to make it uneven.
It is manufactured from the folded plate material 21 subjected to. Folded board material 2
1 alternates between the first heat transfer plates S1... And the second heat transfer plates S2.
It is arranged, and the mountain fold line L₁And valley fold line L _Two
Is folded in a zigzag manner. In addition, with mountain fold
Means to fold convexly toward the front side of the paper.
Is to fold convexly toward the other side of the paper. Each mountain fold
Line L₁And valley fold line L_TwoIs not a sharp straight line,
A predetermined space between the first heat transfer plate S1 and the second heat transfer plate S2.
Actually consists of an arc-shaped fold line to form
You.

Each of the first and second heat transfer plates S1 and S2 has a large number of first projections 22...
Are press-formed. In FIG. 8, the first protrusions 22 indicated by crosses project toward the near side of the drawing, and the second protrusions 23 indicated by circles project out of the drawing.

Each of the first and second heat transfer plates S1 and S2 has, at the front end and the rear end thereof cut into a mountain shape, first protruding strips 24 _F ... Protruding toward the near side of the drawing in FIG. 24 _R …
And a second protruding ridge 25 protruding toward the other side of the paper surface.
_F ..., 25 _R. First heat transfer plate S1
And both of the first and second heat transfer plates S2
Projections 24 _F, 24 _R are disposed at diagonal positions, front and rear pair of second projections 25 _F, 25 _R are disposed on the other diagonal line.

Incidentally, the first projections 22..., The second projections 23..., The first projections 24 _F , 24 _R ... Of the first heat transfer plate S1 shown in FIG.
And the second ridges 25 _F ... 25 _R ... Have a reversed concavo-convex relationship with the first heat transfer plate S1 shown in FIG. This is because the state is seen.

Referring to FIG. 5 and FIG.
The first heat transfer plate S1 of the folded plate material 21 and the second heat transfer plate
S2 ... is the mountain fold line L₁And heat transfer plates S1 ... S
When the combustion gas passages 4 are formed between the two, the first heat transfer plate
The tip of the second projection 23 of S1 and the second projection of the second heat transfer plate S2
The tips of the fins 23 are in contact with each other and brazed. Ma
In addition, the second ridge 25 of the first heat transfer plate S1_F, 25_RAnd the second biography
Second ridge 25 of hot plate S2 _F, 25_RAnd abut each other
Lower left part of the combustion gas passage 4 which is brazed and shown in FIG.
And the upper right part of the first heat transfer plate S1
1 ridge 24_F, 24_RAnd the first ridge 24 of the second heat transfer plate S2
_F, 24_RAre opposed to each other with a gap, as shown in FIG.
In the upper left and lower right portions of the combustion gas passage 4
Forming a combustion gas passage inlet 11 and a combustion gas passage outlet 12
You.

The folding plate first heat-transfer plates S1 ... and second heat-transfer plates S2 ... folded in valley fold line L ₂ both heat transfer plates S material 21
When the air passages 5 are formed between 1,..., S2,
The tips of the first protrusions 22 of the heat transfer plate S1 and the tips of the first protrusions 22 of the second heat transfer plate S2 come into contact with each other and are brazed. Further, the first projections 24 _F, 24 _R of the first projections 24 _F, 24 _R and the second heat-transfer plate S2 of the first heat-transfer plate S1 is brazed in contact with each other, shown in FIG. 4 The upper left and lower right portions of the air passage 5 are closed and the first heat transfer plate S1 is closed.
The second projections 25 _F, 25 _R and the second projections 25 _F, 25 and _R are to exist a gap opposite to each other, the upper right portion of the air passage 5 shown in FIG. 4 of the second heat-S2 of An air passage entrance 15 and an air passage exit 16 are formed in the lower left portion, respectively.

The first projections 22 and the second projections 23 have a substantially frustoconical shape, and their tips come into surface contact with each other to increase the brazing strength. Also the first ridge 24 _F
, 24 _R, and the second ridges 25 _F , 25 _{R, etc.} also have a substantially trapezoidal cross section, and their tips also come into face contact with each other to increase the brazing strength.

As is clear from FIG.
Is automatically closed because it corresponds to the bent portion (valley fold line L ₂ ) of the folded plate material 21, but the radially outer portion of the air passages 5 is open. The opening is brazed to the outer casing 6 and closed. On the other hand, the radially outer peripheral portion of the combustion gas passages 4 is automatically closed because it corresponds to the bent portion (mountain fold line L ₁ ) of the folded plate material 21. The peripheral portion is open, and the open portion is brazed to the inner casing 7 and closed.

The folding plate is convex fold L ₁ How to can not be brought into direct contact with adjacent when folding the blank 21 to zigzag shape, and the convex fold L ₁ by the first projections 22 are in contact with each other The distance between them is kept constant. Although with how concave fold L ₂ adjacent can not be brought into direct contact with, the valley-folding lines L ₂ mutual distance by the second protrusion 23 ... are in contact with each other is kept constant.

When the main body of the heat exchanger 2 is manufactured by bending the folded plate material 21 in a zigzag manner, the first heat transfer plates S1 and the second heat transfer plates S2 are radiated from the center of the heat exchanger 2. Placed in Therefore, the adjacent first heat transfer plates S1.
The distance between the first heat transfer plate S2 and the second heat transfer plate S2 is maximum at the radially outer peripheral portion contacting the outer casing 6, and is minimum at the radially inner peripheral portion contacting the inner casing 7. For this purpose, the first projections 22, the second projections 23, the first ridges 24 _F , 24 _R and the second ridges 25 _F , 25 _F ,
25 The height of the _R are gradually increased from the radially inside to the outside, whereby the first heat-transfer plates S1 ... and the second heat transfer plate S2
Can be accurately arranged radially (see FIG. 5).

By employing the above-mentioned radial folded plate structure, the outer casing 6 and the inner casing 7 can be positioned concentrically, and the axial symmetry of the heat exchanger 2 can be precisely maintained.

As is clear from FIGS. 7 and 9, the first and second heat transfer plates S1... And the second heat transfer plates S2. By bending in the direction by an angle slightly smaller than 90 °, rectangular small-piece-shaped flange portions 26 are formed. When the folded plate material 21 is folded in a zigzag shape,
The flanges 26 of the first heat transfer plates S1 ... and the second heat transfer plates S2 ...
Are superposed on a part of the flange portions 26 adjacent thereto and brazed in a surface contact state to form a joining flange 27 which forms an annular shape as a whole. The joint flange 27 is joined to the front and rear end plates 8 and 10 by brazing.

At this time, the front surface of the joining flange 27 has a step-like shape, and a slight gap is formed between the end plates 8 and 10. The gap is closed by the brazing material (see FIG. 7). Also, the flange portions 26 are provided with the first heat transfer plates S1.
And the first ridges 24 _F , 24 formed on the second heat transfer plates S2.
_R and second projections 25 _F, 25 are bent from the vicinity of the tips of the _R, but the first projections of the folding plate blank 21 when folded in mountain fold lines L ₁ and valley-folding lines L ₂ 24 _F, 24 Although a slight gap is formed also between the _R and the second projections 25 _F, 25 _R of the tip and the flange portion 26 ..., the gap is closed by a brazing material (see FIG. 7).

By the way, the first heat transfer plates S1... And the second heat transfer plates S2. The first heat transfer plate S1 is bent by bending the plate material 21.
... and second heat-transfer plates S2 ... first and second projections 22 and 23 ... and the first projections 24 _F, 24 _R and the second projections 25 of the
After brazing the _F and _25R to each other, it is necessary to perform a precise cutting process on the apex portion and braze the end plates 8 and 10, and the brazing is performed in two steps and the number of steps is increased. In addition, high processing accuracy is required for the cut surface, which increases the cost, and it is difficult to obtain sufficient strength for brazing on a small-sized cut surface. However, by brazing the bent flange portions 26, the first projections 22 and the second projections 2 are formed.
3 ... and the first projections 24 _F, 24 _R and the second projections 2
Not only can the brazing of 5 _F and 25 _{R and} the brazing of the flange portions 26 be completed in one process, but also the precise cutting of the peaks of the chevron becomes unnecessary, and the flanges that are in surface contact Part 26... Brazing strength greatly increases because brazing is performed between the parts. Furthermore, the flange portion 26 ...
Since the joining flange 27 itself is constituted, it is possible to contribute to a reduction in the number of parts.

The folded plate material 21 is bent radially and in a zigzag manner to form a first heat transfer plate S1 and a second heat transfer plate S1.
Are formed continuously so that a large number of independent first heat transfer plates S1 and a large number of independent second heat transfer plates S1 are individually formed one by one.
As compared with the case where the heat transfer plates S2 are alternately brazed, not only the number of parts and brazing points can be significantly reduced, but also the dimensional accuracy of the completed product can be increased.

As is clear from FIGS. 5 and 6, when a single folded plate material 21 formed in a belt shape is folded in a zigzag manner to form the main body of the heat exchanger 2, the folded plate material 21 Both ends are integrally joined at a radially outer peripheral portion of the heat exchanger 2. Therefore the edges of the first heat-transfer plate S1 and the second heat-transfer plates S2 adjacent to each other with the joint is cut into a J-shape in the vicinity of the crest-folding line L _1, for example the first heat transfer plate S
The outer periphery of the J-shaped cut portion of the second heat transfer plate S2 is fitted and brazed to the inner periphery of the first J-shaped cut portion. Since the J-shaped cut portions of the first and second heat transfer plates S1 and S2 are fitted to each other, the J-shaped cut portion of the outer first heat transfer plate S1 is expanded and the inner second heat transfer plate S1 is expanded. The J-shaped cut portion of the plate S2 is compressed and the second inner heat transfer plate S2 is further compressed radially inward of the heat exchanger 2.

By employing the above structure, a special joining member is not required for joining both ends of the folded plate material 21, and no special processing such as changing the shape of the folded plate material 21 is required. Therefore, the number of parts and the processing cost are reduced, and an increase in the heat mass at the joint is avoided. Also, not the combustion gas passage 4 but the air passage 5 ...
Since no dead space is generated, the increase in flow path resistance is minimized, and there is no danger that the heat exchange efficiency will decrease. Furthermore, although the J-shaped cut portions of the first and second heat transfer plates S1 and S2 are apt to generate minute gaps due to deformation of the joint portion, the main body of the heat exchanger 2 is formed by a single folded plate material 21. With this configuration, it is possible to minimize the number of the joints to one, and to minimize fluid leakage. Further, when one folded plate material 21 is bent in a zigzag manner to form the main body of the annular heat exchanger 2, the number of the first and second heat transfer plates S1,. Otherwise, the circumferential pitches of the adjacent first and second heat transfer plates S1..., S2.
There is a possibility that the tip of ... may be separated or crushed. However, the pitch in the circumferential direction can be easily finely adjusted only by changing the cutting position of the folded plate material 21 and appropriately changing the number of the first and second heat transfer plates S1..., S2. be able to.

During operation of the gas turbine engine E, the pressure in the combustion gas passages 4 becomes relatively low, and the pressure in the air passages 5 becomes relatively high. A bending load acts on the plates S1 and the second heat transfer plates S2, but the first projections 22 and the second projections 23 contacted with each other and brazed have sufficient rigidity to withstand the loads. Obtainable.

The first projections 22 and the second projections 23 are provided.
The surface areas of the first heat transfer plates S1 and the second heat transfer plates S2 (that is, the surface areas of the combustion gas passages 4 and the air passages 5) increase, and the flows of the combustion gas and the air are agitated. Therefore, the heat exchange efficiency can be improved.

By the way, the number _Ntu of heat transfer units representing the heat transfer amount between the combustion gas passages 4 and the air passages 5 is as follows: N _tu = (K × A) / [C × (dm / dt)] ( 1) given by

In the above equation (1), K is the first heat transfer plate S
1 and the second heat transfer plates S2 ..., A is the area (heat transfer area) of the first heat transfer plates S1 ... and the second heat transfer plates S2 ..., C is the specific heat of the fluid, and dm / dt is The mass flow rate of the fluid flowing through the heat transfer area. Although the heat transfer area A and the specific heat C are constants, the heat transfer rate K and the mass flow rate dm / dt are equal to the pitch P between the adjacent first protrusions 22 or between the adjacent second protrusions 23 (FIG. 5). ).

When the number _{Ntu of} heat transfer units changes in the radial direction of the first heat transfer plates S1... And the second heat transfer plates S2.
Not only does the temperature distribution of the first heat transfer plate S2 and the second heat transfer plate S2 become non-uniform in the radial direction, the heat exchange efficiency decreases, but also the first heat transfer plate S1 and the second heat transfer plate S2. Thermal expansion non-uniformly and undesired thermal stress is generated. Therefore, the first
The arrangement pitch P in the radial direction of the projections 22 and the second projections 23 is appropriately set, and the number _{Ntu of} heat transfer units is equal to the first heat transfer plates S1.
And the second heat transfer plates S2... Can be fixed at each radial position to solve the above-mentioned problems.

When the pitch P is constant in the radial direction of the heat exchanger 2 as shown in FIG.
As shown in FIG. 11 (C), the number N _tu of heat transfer units is large in the radially inner portion and smaller in the radially outer portion.
, The temperature distribution of the first heat transfer plates S1... And the second heat transfer plates S2. On the other hand, as shown in FIG. 12A, if the pitch P is set so as to be large at the radially inner portion of the heat exchanger 2 and small at the radially outer portion,
As shown in FIGS. 12B and 12C, the number _Ntu of heat transfer units and the temperature distribution can be made substantially constant in the radial direction.

As is clear from FIGS. 3 to 5, in the heat exchanger 2 of the present embodiment, the first heat transfer plates S1.
The first projections 22... And the second projections 2.
A region R ₁ where the arrangement pitch P of the projections 23 in the radial direction is small.
, And a radial arrangement pitch P of the first protrusions 22... And the second protrusions 23.
A region R ₂ is provided larger. As a result, the number _{Ntu of} heat transfer units is substantially constant over the entire axially intermediate portion of the first heat transfer plates S1 and the second heat transfer plates S2..., Thereby improving heat exchange efficiency and reducing thermal stress. Becomes possible.

The overall shape of the heat exchanger 2 and the first protrusions 22
.. And the second protrusions 23 have different shapes, the heat transmittance K and the mass flow rate dm / dt also change, so that the arrangement of the appropriate pitches P is also different from that in this embodiment. Therefore, in addition to the case where the pitch P gradually decreases outward in the radial direction as in the present embodiment, the pitch P may gradually increase outward in the radial direction. However, if the arrangement of the pitch P is set such that the above equation (1) is satisfied, the overall shape of the heat exchanger and the first protrusions 22.
Regardless of the shape of the second projections 23 and the like, the above-described effects can be obtained.

As is clear from FIGS. 3 and 4, at the intermediate portion in the axial direction of the first heat transfer plate S1 and the second heat transfer plate S2, the adjacent first projections 22 and the adjacent second protrusions 22 are disposed.
The protrusions 23 are not aligned in the axial direction of the heat exchanger 2 (the flow direction of the combustion gas and the air), but are aligned at a predetermined angle with respect to the axial direction. In other words, it is considered that the first projections 22 are not continuously arranged on the straight line parallel to the axis of the heat exchanger 2 or the second projections 23 are not continuously arranged. . Thereby, the first
At the axially intermediate portions of the heat transfer plates S1 and the second heat transfer plates S2, the combustion gas passage 4 and the air passage 5 are
.. And the second projections 23 can be formed in a maze shape to enhance the heat exchange efficiency.

Further, a first heat transfer plate S1... And a second heat transfer plate S2
The first protrusions 22 and the second protrusions 23 are arranged in the angled portions at both ends in the axial direction at an arrangement pitch different from that of the intermediate portion in the axial direction. In the combustion gas passage 4 shown in FIG. 3, the combustion gas flowing in the direction of arrow a from the combustion gas passage inlet 11 turns in the axial direction and flows in the direction of arrow b, and further turns in the direction of arrow c to turn into the combustion gas passage outlet 12. Spill out of. When the combustion gas changes direction in the vicinity of the combustion gas passage inlet 11, the flow path P _{S of the} combustion gas is shortened inside the swirling direction (outside in the radial direction of the heat exchanger 2), and outside the swirling direction (in the heat exchanger 2). flow path P _L radially inner) the combustion gas becomes long. on the other hand,
When the combustion gas changes direction in the vicinity of the combustion gas passage outlet 12, the flow path P _{S of the} combustion gas is shortened inside the swirling direction (radially inside the heat exchanger 2) and outside the swirling direction (in the heat exchanger 2). flow path P _L radially outward) the combustion gas becomes long. If a difference in the flow path length of the combustion gas occurs inside and outside the swirling direction of the combustion gas as described above, the combustion gas is deviated from the outside of the swirling direction toward the inside of the swirling direction where the flow path resistance is small because the flow path length is short. The flow of the combustion gas becomes uneven and the heat exchange efficiency is reduced.

Therefore, the combustion gas passage inlet 11 and the combustion gas
Region R near passage exit 12_Three, R _ThreeThen, of the combustion gas
The first protrusions 22 in the direction orthogonal to the flow direction and the second protrusions
23 ... from the outside to the inside in the turning direction.
And gradually change to be denser. Like this
Area R_Three, R_ThreeAnd the second protrusion 23
By making the arrangement pitch of non-uniform, the combustion gas
Because the flow path length is short, the flow path resistance is small.
1 protrusion 22 ... and 2nd protrusion 23 ...
And the region R_Three, R_ThreeFlow path resistance throughout
The resistance can be made uniform. This causes the drift
And prevent heat exchange efficiency from lowering.
You. In particular, the first ridge 24_F, 24_R1 adjacent to the inside of
All the projections in the row are second projections projecting into the combustion gas passage 4.
23 ... (indicated by an X in FIG. 3)
The arrangement pitch of the second protrusions 23 is made non-uniform.
Thus, the drift prevention effect can be effectively exhibited.

Similarly, in the air passage 5 shown in FIG. 4, the air flowing from the air passage entrance 15 in the direction of arrow d turns in the axial direction and flows in the direction of arrow e, and further turns in the direction of arrow f to turn the air. It flows out of the passage outlet 16. When the air changes direction in the vicinity of the air passage inlet 15, the air flow path becomes shorter inside the turning direction (radially outside the heat exchanger 2), and becomes shorter outside the turning direction (radially inside the heat exchanger 2). The air flow path becomes longer. On the other hand, when the air changes direction in the vicinity of the air passage outlet 16, the air flow path becomes shorter inside the turning direction (radially inside the heat exchanger 2), and outside the turning direction (radially outside the heat exchanger 2). In), the air flow path becomes longer. If a difference occurs in the flow path length of the air between the inside and outside of the swirling direction of the air as described above, the air flows in the swirling direction with small flow path resistance due to the short flow path length, and the heat exchange efficiency decreases. Resulting in.

Therefore, in the regions R ₄ and R ₄ near the air passage inlet 15 and the air passage outlet 16, the first protrusions 22 and the second protrusions 23 in the direction perpendicular to the air flow direction.
Are changed so that the pitch gradually increases from the outside toward the inside in the turning direction. Thus, in the regions R ₄ , R ₄ , the first protrusions 22 and the second protrusions 23.
The first protrusions 22 and the second protrusions 23 are arranged densely inside the turning direction because the flow resistance of the air is short due to the short flow path length of the air, thereby increasing the flow resistance. As a result, the flow path resistance can be made uniform over the entire regions R ₄ and R ₄ . Thus, the occurrence of the drift can be prevented, and a decrease in the heat exchange efficiency can be avoided. In particular, the first protrusion 22 protruding to the second projections 25 _F, 25 protrusions of the first column adjacent to the inside of _R are all the combustion gas passage 4 ...
(Indicated by an X mark in FIG. 4).
By making the arrangement pitch of the projections 22 non-uniform, a drift prevention effect can be effectively exhibited.

Incidentally, in FIG. 3, the combustion gas is supplied to the regions R ₃ and R ₃ .
₃ flows in the regions R ₄ , R ₄ adjacent to
_Since the arrangement pitch of the first projections 22 and the second projections 23 in R ₄ and R ₄ is not uniform in the direction of the flow of the combustion gas, the arrangement pitch of the first projections 22 and the second projections 23. Has little effect on the flow of combustion gases. Similarly, it flows regions R _3, R ₃ which air is adjacent to the region R _4, R ₄ in FIG. 4, the area R _3, the first projection 22 in the R ₃ ... and the second protrusion 23 ... arrangement pitch of The arrangement pitch of the first projections 22 and the second projections 23 hardly affects the air flow because the direction of the air flow is uneven.

As is clear from FIGS. 3 and 4, at the front end and the rear end of the heat exchanger 2, the first heat transfer plates S1 and the second heat transfer plates S2 have long sides and short sides, respectively. The combustion gas passage inlet 11 and the combustion gas passage outlet 12 are formed along the long sides of the front end side and the rear end side, respectively, and the short end of the rear end side and the front end side are formed. An air passage entrance 15 and an air passage exit 16 are respectively formed along the sides.

As described above, the combustion gas passage inlet 11 and the air passage outlet 16 are formed along the two sides of the chevron at the front end of the heat exchanger 2, and the cheeks are formed at the rear end of the heat exchanger 2. Since the combustion gas passage outlet 12 and the air passage inlet 15 are respectively formed along the sides, the inlets 11 and 15 and the outlets 12 and 16 are formed without cutting the front end and the rear end of the heat exchanger 2 into a mountain shape. , The inlets 11 and 15 and the outlets 12 and 16
And the pressure loss can be minimized. Moreover, since the inlets 11 and 15 and the outlets 12 and 16 are formed along the two sides of the chevron, the flow paths of the combustion gas and air flowing into and out of the combustion gas passages 4 and the air passages 5 are smoothed to reduce pressure loss. Not only can it be reduced further, but also the inlets 11,15 and the outlets 12,1
The duct connected to 6 is arranged along the axial direction without sharply bending the flow path, and the radial dimension of the heat exchanger 2 can be reduced.

By the way, compared with the volume flow rate of the air passing through the air passage inlet 15 and the air passage outlet 16, the fuel is mixed with the air, burned, and further expanded by the turbine to reduce the pressure of the combustion gas. The flow rate increases. In the present embodiment, the unequal length chevron reduces the lengths of the air passage inlet 15 and the air passage outlet 16 through which the air having a small volume flow passes, and the combustion gas passage inlet 11 through which the combustion gas having a large volume flow passes. In addition, the length of the combustion gas passage outlet 12 is increased, whereby the flow velocity of the combustion gas is relatively reduced, so that the occurrence of pressure loss can be more effectively avoided.

As is apparent from FIGS. 3 and 4, the outer housing 9 made of stainless steel is
Outer wall members 28, 29 and inner wall members 30, 31 to define
And a front flange 32 joined to the rear ends of the front outer wall member 28 and the inner wall member 30 and a rear flange joined to the front ends of the rear outer wall member 29 and the inner wall member 31. 33 are connected with a plurality of bolts 34. At this time, an annular sealing member 35 having an E-shaped cross section is sandwiched between the front flange 32 and the rear flange 33, and the sealing member 35 seals a joint surface between the front flange 32 and the rear flange 33. Air introduction duct 1
The mixing of the air inside 7 and the combustion gas in the combustion gas introduction duct 13 is prevented.

The heat exchanger 2 is made of the same material as the heat exchanger 2.
Via a heat exchanger support ring 36 made of Conel plate
And connected to the rear flange 33 of the outer housing 9.
It is supported by the inner wall member 31. Connected to rear flange 33
Since the axial dimension of the inner wall member 31 is small,
The member 31 is considered substantially as a part of the rear flange 33.
Can be Therefore, the heat exchanger support ring 36 is
Instead of joining to member 31, directly to rear flange 33
Joining is also possible. Heat exchanger support ring 36
The first ring portion 36 joined to the outer peripheral surface of the heat exchanger 2
₁And the first phosphorus connected to the inner peripheral surface of the inner wall member 31.
Group 36₁Second ring portion 36 having a larger diameter than _TwoAnd the first,
Second ring portion 36₁, 36_TwoConnection to connect diagonally
Part 36_ThreeAnd is formed in a step shape in cross section.
Combustion gas passage inlet 1 by heat exchanger support ring 36
1 and the air passage entrance 15 are sealed.

The temperature distribution on the outer peripheral surface of the heat exchanger 2 is low on the air passage inlet 15 side (axial rear side) and high on the combustion gas passage inlet 11 side (axial front side). By providing the heat exchanger support ring 36 at a position closer to the air passage inlet 15 than the combustion gas passage inlet 11, the difference in the amount of thermal expansion between the heat exchanger 2 and the outer housing 9 is minimized to reduce thermal stress. Can be done.
Also, the heat exchanger 2 and the rear flange 3
When the heat exchanger 3 and the outer housing 9 are relatively displaced, the displacement is absorbed by the elastic deformation of the heat exchanger support ring 36 made of a plate material, and the thermal stress acting on the heat exchanger 2 and the outer housing 9 can be reduced. In particular, since the cross section of the heat exchanger support ring 36 is formed in a step shape, the bent portion can be easily deformed, and the difference in the amount of thermal expansion can be effectively absorbed.

13 to 17 show a second embodiment of the present invention. FIG. 13 is a perspective view of a heat exchanger, and FIG.
14-14 line enlarged sectional view (sectional view of the combustion gas passage),
15 is an enlarged sectional view taken along line 15-15 of FIG. 13 (a sectional view of the air passage), FIG. 16 is a sectional view taken along line 16-16 of FIG. 14, and FIG. 17 is an enlarged sectional view taken along line 17-17 of FIG.

The heat exchanger 2 comprises an upper bottom wall 41 and a lower bottom wall 4
2, the front end wall 43 and the rear end wall 44, and the left side wall 45 and the right side wall 46 to form a rectangular parallelepiped as a whole. At the front and rear of the upper bottom wall 41, a combustion gas passage inlet 11 and a combustion gas passage outlet 12 extending in the left-right direction are opened, and at the rear and front of the lower bottom wall 42, an air passage extending in the left-right direction. An inlet 15 and an air passage outlet 16 open. Inside the heat exchanger 2, a _first rectangular heat transfer plate S 1 is formed by folding the folded plate material 21 in a zigzag manner through a mountain fold line L ₁ and a valley fold line L ₂ .
And the second heat transfer plates S2 are alternately arranged.

Between the first heat transfer plate S1 and the second heat transfer plate S2, the combustion gas passage inlet 11 and the combustion gas passage outlet 1
2 and the air passage inlet 1
5 and the air passages 5 connected to the air passage outlet 16 are alternately formed. At this time, the first heat transfer plates S1.
The plurality of first protrusions 22 formed on the heat transfer plates S2 and the second
By brazing the tips of the projections 23, the distance between the first heat transfer plates S1 and the second heat transfer plates S2 is kept constant.

The folded plate material 21 is brazed to the upper bottom wall 41 at the mountain fold lines L ₁ ... And brazed to the lower bottom wall 42 at the valley fold lines L ₂ . Also, the first heat transfer plate S1
And the short side portions (ie, the front end and the rear end) of the second heat transfer plates S2 are bent by an angle slightly smaller than 90 ° to form rectangular flange portions 26. The flange portions 26 are overlapped with each other and brazed in a surface contact state to form a generally rectangular joint flange 27,
The joining flange 27 is connected to the front end wall 43 and the rear end wall 44.
And joined by brazing. The gap between the joining flange 27 and the front and rear end walls 43, 44 is closed by the brazing material (see FIG. 17). By brazing the flange portions 26 obtained by bending the ends of the first heat transfer plates S1 and the second heat transfer plates S2 in this manner, the first heat transfer plates S1 and the second heat transfer plates S2 are formed. Since precise cutting of the end of the
The brazing of the first projections 22 and the second projections 23 and the brazing of the flanges 26 can be performed in one step, and the flanges 26 in surface contact are brazed together. Brazing strength is also greatly increased.

As shown in FIGS. 14 and 15, first projections 2 formed on first heat transfer plates S1 and second heat transfer plates S2.
2 and the second protrusions 23 are arranged in the middle portion in the front-rear direction of the first heat transfer plate S1 and the second heat transfer plate S2, and both end portions in the front-rear direction (in the combustion gas passage inlet 11 and the air passage outlet 16). (A portion facing the combustion gas passage outlet 12 and the air passage inlet 15).

That is, the first heat transfer plate S1 and the second heat transfer plate S
The first projections 22 and the second projections 23 are arranged at the same pitch in the vertical direction and at the same pitch in the front-rear direction at the middle part in the front-rear direction of 2. On the other hand, the first protrusions 22 and the second protrusions 23 are arranged at equal pitches in the vertical direction at both ends in the front-rear direction, but are arranged at irregular pitches in the front-rear direction. Specifically, in the portion facing the combustion gas passage inlet 11 and the air passage outlet 16, the arrangement pitch in the front-rear direction becomes denser as the distance from the front end increases, and the combustion gas passage outlet 12 and the air passage inlet 15 , The arrangement pitch in the front-rear direction increases with distance from the rear end.

Accordingly, in FIG. 14, when the combustion gas flowing from the combustion gas passage inlet 11 in the direction of arrow g turns 90 ° in the direction along the combustion gas passage 4, the combustion gas easily turns due to the short flow path length. The flow path resistance of the passage on the inner side in the direction is reduced by the densely arranged first protrusions 22 and second protrusions 23.
Thus, the flow rate of the combustion gas inside and outside the turning direction can be made uniform. Further, the combustion gas flowing in the direction along the combustion gas passage 4 turns by 90 ° and the combustion gas passage outlet 12
When the gas flows out of the passage in the direction of arrow h, the flow passage resistance of the passage inside the swirl direction in which the combustion gas easily flows due to the short flow passage length is increased by the densely arranged first protrusions 22 and second protrusions 23. As a result, the flow rate of the combustion gas inside and outside the turning direction can be made uniform.

Similarly, in FIG. 15, the air flowing from the air passage inlet 15 in the direction of arrow i
When turning 90 ° in the direction along the axis, the flow path resistance of the path inside the turning direction in which air is easy to flow due to the short flow path length is increased by the densely arranged first projections 22 and second projections 23. As a result, the flow rate of the combustion gas inside and outside the turning direction can be made uniform. Further, when the air flowing in the direction along the air passage 5 turns by 90 ° and flows out from the air passage outlet 16 in the direction of arrow j, the flow path resistance of the passage inside the turning direction where the air is easy to flow due to the short flow path length is reduced. The first protrusions 22 and the second protrusions 23 arranged densely increase the flow rate of air inside and outside the turning direction.

Next, a modification of the first embodiment will be described with reference to FIGS.

As shown in FIG. 18, the first heat transfer plate S1 and the second heat transfer plate S2 of the folded plate material 21 of this modified example have the shape of the flange portion 26 at the top of the chevron slightly different from that of the first embodiment. Is different. 19 and 20 show the shape of the flange portion 26 of the first heat-transfer plate S1, the flange portion 26 is bent section height of the first projections 24 _F and second projections 25 _F gradually decreases 26 ₁ is constituted by a flat portion 26 ₂ which contiguous to the tip of the bent portion 26 _1, the flat portion 26 the length of ₂ is long in the first heat-transfer plate S1, shorter in the second heat-transfer plates S2 It is formed (see FIG. 18).

As apparent from FIG. 21, the first
Flange 26 of the heat transfer plate S1 and the second heat transfer plate S2 is bent in an arc over 90 ° at the bent portion 26 ₁ of the section, surface contact its flat portion 26 ₂ is the end plate 8 Brazed in. At this time, since the height of the first projections 24 _F and second projections 25 _F is gradually reduced in the folded portion 26 _1, the first and if projections 24 _F, or to what the second projections 25 _F is brazed The gap can be minimized. Moreover, the flange portion 26 of the second heat transfer plate S2
Because the length of the flat portion 26 ₂ of the
It prevents _{the second} tip interferes with the first projections 24 _F and second projections 25 _F of the first heat-transfer plate S1 adjacent, occurrence of a gap can be more effectively prevented. Although FIGS. 19 to 21 show the flange portions 26 at one end of the first heat transfer plate S1 and the second heat transfer plate S2, the flange portions 26 at the other end have the same structure.

According to this modification, the first ridges 24 _F , 2
4 _R How to contact portion and the second projections 25 _F of 25 to suppress a gap occurring in abutment with what _R minimized, thereby enhancing the sealing of the fluid.

Although the embodiments of the present invention have been described in detail, various design changes can be made in the present invention without departing from the gist thereof.

For example, in the first and fourth aspects of the present invention, the first heat transfer plate S1
And the second heat transfer plates S2 may be formed of separate members and joined to each other.

[0070]

As described above, according to the first aspect of the present invention, in the annular heat exchanger in which both ends in the axial direction of the heat transfer plate are cut into a mountain shape to form a fluid passage inlet / outlet, Since the flanges formed by bending the peaks of the chevrons are overlapped and joined to each other, and the partition plate is joined to the overlapped flanges, the partition between the fluid passage inlet and outlet is performed. Compared to the case where the partition plate is joined to the cut end face in line contact, the overlapped flange can be joined in face contact, not only increasing the joining strength, but also the precision of the cut surface Since no complicated finishing is required, the joining of the projections of the heat transfer plate and the joining of the flange can be completed in one step, thereby reducing the machining cost.

According to the second aspect of the present invention,
A folded plate material in which the first heat transfer plate and the second heat transfer plate are alternately connected via the first fold line and the second fold line is bent in a zigzag manner at the first fold line and the second fold line. , First
Since the fold line was joined to the radially outer peripheral wall and the second fold line was joined to the radially inner peripheral wall, the first heat transfer plate and the second heat transfer plate were joined.
In addition to reducing the number of parts compared to the case where the heat transfer plates are formed of separate members and joined to each other, the processing accuracy is prevented by preventing the first heat transfer plate and the second heat transfer plate from being displaced. Can be enhanced.

According to the third aspect of the present invention,
The flange portion is bent in an arc shape and overlapped, and the height of the ridge formed along the chevron edges of the first heat transfer plate and the second heat transfer plate to close the fluid passage entrance and exit is adjusted in the flange portion. Since the width is gradually reduced, it is possible to prevent a gap from being formed between the ridges while preventing interference between the ridges that are in contact with each other in the flange portion, thereby improving the sealing performance of the fluid.

According to the fourth aspect of the present invention,
A pair of long sides of a plurality of rectangular heat transfer plates are respectively joined to the bottom wall and a pair of short sides are respectively joined to the end walls, and fluid passage ports are formed at both ends of the bottom walls in the long side direction. In the rectangular parallelepiped heat exchanger, the flange portions formed by bending the short sides of the heat transfer plate are overlapped and joined together, and the end wall is joined to the overlapped flange portion, so that the fluid passage entrance and exit are formed. Since the partition between them is made, it is possible to join the overlapped flange parts in face contact compared to joining the end wall in line contact with the cut end face of the heat transfer plate Not only increases strength, but also eliminates the need for precise finishing of the cut surface, so that joints between the projections of the heat transfer plate and the flanges can be completed in one process, reducing machining costs Is done.

According to the fifth aspect of the present invention,
A folded plate material in which the first heat transfer plate and the second heat transfer plate are alternately connected via the first fold line and the second fold line is bent in a zigzag manner at the first fold line and the second fold line. , First
The fold line is joined to the first bottom wall and the second fold line is connected to the second bottom wall.
Since the first heat transfer plate and the second heat transfer plate are joined to the bottom wall, not only the number of parts is reduced, but also the first heat transfer plate and Processing accuracy can be enhanced by preventing the second heat transfer plate from being displaced.

[Brief description of the drawings]

FIG. 1 is an overall side view of a gas turbine engine.

FIG. 2 is a sectional view taken along line 2-2 of FIG.

FIG. 3 is an enlarged sectional view taken along line 3-3 of FIG. 2 (a sectional view of a combustion gas passage).

FIG. 4 is an enlarged sectional view taken along line 4-4 of FIG. 2 (a sectional view of an air passage);

FIG. 5 is an enlarged sectional view taken along line 5-5 of FIG. 3;

FIG. 6 is an enlarged view of part 6 of FIG.

FIG. 7 is an enlarged sectional view taken along line 7-7 of FIG. 3;

FIG. 8 is a development view of a folded plate material.

FIG. 9 is a perspective view of a main part of the heat exchanger.

FIG. 10 is a schematic diagram showing flows of combustion gas and air.

FIG. 11 is a graph illustrating the operation when the pitch of the protrusions is made uniform.

FIG. 12 is a graph illustrating the operation when the pitch of the protrusions is made non-uniform;

FIG. 13 is a perspective view of a heat exchanger according to a second embodiment.

14 is an enlarged sectional view taken along line 14-14 of FIG. 13 (a sectional view of a combustion gas passage).

FIG. 15 is an enlarged sectional view taken along line 15-15 of FIG. 13 (a sectional view of an air passage);

FIG. 16 is a sectional view taken along line 16-16 of FIG. 14;

FIG. 17 is an enlarged sectional view taken along line 17-17 of FIG. 14;

FIG. 18 according to a modification of the first embodiment and corresponding to FIG. 8;

19 is an enlarged view of a main part of FIG. 18;

20 is a view taken in the direction of the arrow 20 in FIG. 19;

FIG. 21 is a view corresponding to FIG. 7 of the first embodiment.

[Explanation of symbols]

Reference Signs List 4 combustion gas passage (high-temperature fluid passage) 5 air passage (low-temperature fluid passage) 6 outer casing (radial outer peripheral wall) 7 inner case (radial inner peripheral wall) 11 combustion gas passage entrance (high-temperature fluid passage entrance) 12 combustion gas passage Outlet (high-temperature fluid passage exit) 15 Air passage entrance (low-temperature fluid passage entrance) 16 Air passage exit (low-temperature fluid passage exit) 21 Folded plate material 22 First projection (projection) 23 Second projection (projection) 24 _F first projection Line (convex line) 24 _R First convex line (convex line) 25 _F Second convex line (convex line) 25 _R Second convex line (convex line) 26 Flange part 41 Upper bottom wall (first bottom wall) 42 Lower part Bottom wall (second bottom wall) 43 Front end wall (first end wall) 44 Rear end wall (second end wall) L ₁ mountain fold line (first fold line) L ₂ valley fold line (second fold line) ) S1 First heat transfer plate S2 Second heat transfer plate

Claims (5)

[Claims] 1. A plurality of first heat transfer plates (S1) and a plurality of second heat transfer plates (S2) in an annular space defined between a radial outer peripheral wall (6) and a radial inner peripheral wall (7). ) Are arranged radially, and a plurality of protrusions (22, 23) formed on the first heat transfer plate (S1) and the second heat transfer plate (S2) are joined to each other to form an adjacent first heat transfer plate. (S1) and the second heat transfer plate (S
2) A heat exchanger in which high temperature fluid passages (4) and low temperature fluid passages (5) are alternately formed in the circumferential direction between the first heat transfer plate (S1) and the second heat transfer plate ( S2) cuts both ends in the axial direction into a chevron shape having two edges, and closes one of the two edges and opens the other at one end in the axial direction of the high-temperature fluid passage (4) to thereby increase the temperature. A high-temperature fluid passage outlet (12) is formed by forming a fluid passage inlet (11) and closing one of the two edges and opening the other at the other axial end of the high-temperature fluid passage (4). At the one end in the axial direction of the low-temperature fluid passage (5), the other of the two edges is closed and one is opened to form a low-temperature fluid passage outlet (16). At the other axial end, close the other of the two edges In a heat exchanger in which one end is opened to form a low-temperature fluid passage inlet (15), a flange (26) formed by bending one of the peaks of the chevron is overlapped and joined to each other. The hot fluid passage inlet (1) is overlapped with the overlapped flange portion (26).
1) and the low-temperature fluid passage outlet (16), a flange (26) formed by bending the other of the peaks of the chevron is overlapped and joined together, and the overlapped flange (26) is joined. The high-temperature fluid passage outlet (12)
A heat exchanger having a partition between the low-temperature fluid passage inlet (15). 2. A first heat transfer plate (S1) and a second heat transfer plate (S1).
2) first folding line (L ₁₎ and a second fold line (L ₂₎ formed by consecutively alternately through the folding plate blank (21) a first fold line (L ₁₎ and the folding second folded zigzag shape in a line (L _2), and joined to the first folding line (L ₁₎ second fold line as well as joined to the radially outer peripheral wall (6) (L ₂₎ of the radially inner peripheral wall (7) 2. The method of claim 1, wherein
A heat exchanger according to item 1. 3. The method according to claim 1, wherein the flange portion (26) is bent in an arc shape and overlapped with each other.
12, 15, 16) to close the ridges (24 _F , 24 _R , 25 _F , 25) formed along the chevron edges of the first heat transfer plate (S 1) and the second heat transfer plate (S 2). Heat exchanger according to claim 1, characterized in that the height of _R ) is gradually reduced at the flange (26). 4. A plurality of first heat transfer plates (S) formed in a rectangular shape.
1) and the plurality of second heat transfer plates (S2), with their long sides joined to the first bottom wall (41) and the second bottom wall (42), and their short sides joined to the first bottom wall (41). The first heat transfer plate (S1) is connected to the end wall (43) and the second end wall (44).
By joining a plurality of projections (22, 23) formed on the heat transfer plate (S2) to each other, an adjacent first heat transfer plate (S2) is formed.
A heat exchanger comprising a high-temperature fluid passage (4) and a low-temperature fluid passage (5) alternately formed between 1) and a second heat transfer plate (S2), wherein the high-temperature fluid passage (4) is connected to the high-temperature fluid passage (4). Forming a fluid passage inlet (11) and a hot fluid passage outlet (12) in the first bottom wall (41) along the first end wall (43) and the second end wall (44), respectively; Cryogenic fluid passage inlet (1) connected to passage (5)
5) and the cold fluid passage outlet (16) are connected to the second end wall (4).
4) and a heat exchanger formed on the second bottom wall (42) along the first end wall (43), wherein the pair of short sides is bent to form a flange portion (26). The first and second end walls (43, 4) are joined to the overlapped flange portion (26).
(4) A heat exchanger, wherein each of the heat exchangers is joined. 5. A first heat transfer plate (S1) and a second heat transfer plate (S1).
2) to the first fold line (L₁) And the second fold line (L_Two) Via
The folded plate material (21), which is alternately and continuously provided, is first folded.
Line (L₁) And the second fold line (L_Two)
Bend in the shape of the first fold line (L₁) To the first bottom wall (4
1) and the second fold line (L _Two) To the second bottom wall
The method according to claim 4, characterized in that it is joined to (42).
Heat exchanger.