JP2002130977A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a heat-transfer coefficient between a heat-transfer plate and an external fluid by further disturbing the flow of the external fluid exchanging heat with the plate, in a finless heat exchanger. SOLUTION: A height H3 of a small protrusion is made different from a height H1 of a protrusion to produce a level-difference between the protrusion end 14a of a protrusion 14 and the protrusion end 140a of the small protrusion 140. Thus, the air-flow through the external air flow path 10a is further disturbed, as compared with the conventional case, where the height H1 and the height H3 are made the same. Thus, the heat transfer coefficient between the heat-transfer plates 12a, 12b and the external fluid can be increased, and the cooling performance of a vaporizer 10 is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a finless type heat exchanger comprising only a heat transfer plate constituting an internal fluid passage through which an internal fluid flows, and eliminating fins. It is suitable for use in an evaporator.

[0002]

2. Description of the Related Art Hitherto, Japanese Patent Application Laid-Open No. 11-287580 has proposed the above-mentioned finless type heat exchanger. In this prior art, the heat exchanger is applied to an evaporator for vehicle air conditioning, and is press-molded so that a rib-shaped protrusion for a flow passage, a positioning contact portion, and a tank portion protrude to the same surface side. The heat transfer plates are stacked and arranged. A coolant (internal fluid) passage is formed inside the flow passage protrusion, and a convex top of the heat transfer plate forms an air (external fluid) passage between adjacent heat transfer plates.

[0003] With the above-described structure, the projecting portion for the flow passage having a protruding shape acts as a turbulence generator that obstructs the straight flow of the air flowing through the air passage and generates a turbulent flow. The heat transfer coefficient between them can be improved, and a finless type heat exchanger is realized.

[0004]

As described above, in a finless type heat exchanger, the degree of improving the heat transfer coefficient by disturbing the flow of air flowing through the air passage greatly affects the performance of the heat exchanger. Therefore, it is required to further disturb the air flow to improve the heat transfer coefficient.

In view of the above, the present invention provides a finless type heat exchanger in which the flow of an external fluid that exchanges heat with a heat transfer plate is further disturbed, and the heat transfer coefficient between the heat transfer plate and the external fluid is increased. The purpose is to improve.

[0006]

SUMMARY OF THE INVENTION The present invention achieves the above object based on the following points. If the present invention is described using an evaporator (heat exchanger) illustrated in FIG. The heat plates (12a, 12b) are provided with a flow path protrusion (14) and a flow path protrusion (1) extending vertically in a rib shape.
4) Positioning contact portions (140, 14) protruding to the side
1) is formed by press forming so as to protrude on the same surface side, and the two heat transfer plates (12a, 12b) are opposed to each other so that the protruding surfaces face outward, and the flow passage protruding portion is formed. Refrigerant passages (19, 20) through which the refrigerant (internal fluid) flows are formed inside (14).

[0007] A plurality of sets of the heat transfer plates (12a, 12b) are stacked and arranged as one set of two sheets, and air is interposed between the stacks of the heat transfer plates (12a, 12b) adjacent to each other on the protruding surface side. Air passage (10a) through which (external fluid) flows
Is composed.

[0008] The protruding ends (140a) of the positioning abutting portions (140, 141) adjacent to each other in the laminating direction are brought into contact with each other, whereby a plurality of heat transfer plates (12a,
12b) is positioned in the stacking direction.

In the evaporator disclosed in the above publication, the height of the protrusion of the flow passage projection (14) (hereinafter referred to as the height of the protrusion) is determined by the height of the projections of the positioning abutting portions (140, 141). (Hereinafter referred to as the contact portion height). In the evaporator having such a structure, the projecting end (14a) of the flow passage projecting portion (14) and the positioning contact are formed. It has been found that the protruding end surface comprising the protruding end (140a) of the portion (140, 141) is flattened, and therefore does not sufficiently disturb the air flow in the air passage (10a).

The present invention has been made in view of this point, and aims to achieve the above object. According to the first aspect of the present invention, the heat transfer plates (12a, 12b) arranged in layers The channel protrusion (14) and the positioning abutment (140, 141) protrude in the same plane, and the internal fluid passages (19, 20) are provided inside the flow passage protrusion (14).
And positioning abutting portions (14) adjacent in the laminating direction.
The heat transfer plates (12a, 12b) are positioned in the stacking direction by abutting the protruding ends (140a) of the protruding portions (0, 141), and the convex tops of the flow path protruding portions (14) are adjacent to each other. A heat exchanger in which the external fluid passage (10a) is constituted by the gap between the heat transfer plates (12a, 12b), and the flow passage protrusion (14) acts as a turbulence generator for the flow of the external fluid. , The protrusion height (H1) of the flow passage protrusion (14) is formed to be different from the protrusion height (H3) of the positioning abutment (140, 141).

As a result, the protruding end (14a) of the flow path protruding portion (14) and the positioning abutment (140, 14).
Since there is a step with the protruding end (140a) of (1), the external fluid is higher than when the protruding part height (H1) and the abutment part height (H3) are formed at the same height as in the prior art. Flow can be further disturbed. Therefore, the heat transfer plate (12
a, 12b) and the external fluid can be improved in heat transfer coefficient, and the heat exchange performance of the heat exchanger can be improved.

According to the second aspect of the present invention, each of the plurality of heat transfer plates (12a, 12b) is provided with a tank portion (19) for communicating between the internal fluid passages (19, 20) in the laminating direction. 15 to 18) are positioning contact portions (1).
40, 141), and the projecting height (H2) of the tank portion (15-18) is the same as the projecting height (H3) of the positioning contact portion (140, 141). And a positioning contact portion (14) adjacent in the laminating direction.
0, 141) and the protruding ends (15b-18b) of the tank portions (15-18) are brought into contact with each other, whereby a plurality of heat transfer plates (12a,
2b) is positioned in the stacking direction.

By the way, the optimum specifications of the heat exchange performance (the amount of heat exchangeable per unit time (J / s)) and the flow resistance (Pa) of the external fluid in the heat exchanger differ depending on the type of the heat exchanger. For example, when the heat exchanger is applied to a vehicle air-conditioning heat exchanger, if the air-conditioning duct is extended from the heat exchanger arranged inside the instrument panel to the rear of the passenger compartment, the pressure loss of air in the air-conditioning duct is large. Become.
In such a case, a specification is desired in which the ventilation resistance (Pa) is reduced even if the heat exchange performance (J / s) is reduced. In addition, in order to make the mounting space a common size regardless of the specifications of the heat exchanger, it is desired that the specifications can be changed while keeping the outer dimensions the same.

Conventionally, the following method can be cited as a specific example of changing the specifications while keeping the external dimensions the same. That is, the number of the flow path protrusions (14) is changed, and the protrusion height (H1) of the flow path protrusions (14) is changed. As a result, the heat transfer plates (12a, 12a
In b), the area for heat exchange with the external fluid is changed, so that the heat exchange performance is adjusted and the ventilation resistance is adjusted.

However, as described above, the flow path protrusion (1)
If it is attempted to change the specification of the heat exchanger by changing the number of 4) and the height of protrusion (H1), the ratio of the flow passage protrusion (14) occupying the surface area of the heat transfer plates (12a, 12b) is large. The shape change portions of the heat transfer plates (12a, 12b) are increased, and the heat transfer plates (12a, 12b) are changed.
It is difficult to reduce the cost of the press mold by changing the shape of only the shape-changed part of the press mold for press molding of b), and a new mold is required for each changed specification. Cost increases.

On the other hand, in the invention according to claim 2,
The projecting portion height (H1) is different from the tank portion height (H2) and the contact portion height (H3), and the projecting ends (140a) of the positioning contact portions (140, 141).
And the protruding ends (15b-) of the tank portions (15-18)
18b) Since a plurality of heat transfer plates (12a, 12b) are positioned in the stacking direction by abutting each other, regardless of the protrusion height (H1),
The width of the external fluid passage (10a) in the stacking direction can be adjusted by adjusting the protruding height of the tanks (15 to 18) (hereinafter referred to as tank height (H2)) and the height of the abutment (H3). Can be adjusted.

If the width of the external fluid passageway (10a) is changed while keeping the external dimensions of the heat exchanger the same, the number of heat transfer plates (12a, 12b) to be stacked can be changed, and the external fluid passage (12a, 12b) can be changed. The heat exchange area can be changed.

For example, as shown in FIG. 9, when the height of the tank portion (H2) and the height of the contact portion (H3) are formed lower than the height of the protruding portion (H1), the outer shape of the heat exchanger Of those having the same dimensions, the height of the external fluid passage (10a) is smaller than the case where the height of the tank portion (H2) and the height of the contact portion (H3) are the same as the height of the protruding portion (H1). The passage width is narrowed, the number of stacked heat transfer plates (12a, 12b) is increased, the heat exchange area is increased, and the heat exchange performance is improved. On the contrary, the flow resistance of the external fluid is increased.

On the other hand, as illustrated in FIG. 5, the height of the tank portion (H2) and the height of the contact portion (H3) are changed to the height of the protruding portion (H).
1) When the height is higher than the tank height (H2)
In addition, the flow resistance of the external fluid is reduced as compared with the case where the height (H3) of the contact portion is equal to the height (H1) of the protrusion, and as a contradiction, the heat exchange performance is reduced.

As described above, according to the second aspect of the invention, the height of the tank portion (H2) and the height of the contact portion (H3) are adjusted regardless of the height of the protrusion (H1). Thus, the specifications can be changed while keeping the outer dimensions of the heat exchanger the same.

Here, the tank portions (15 to 18) and the positioning contact portions (140, 141) occupy the surface area of the heat transfer plates (12a, 12b) in comparison with the flow passage protrusions (14). The heat transfer plate (12
(a, 12b) can be reduced in shape change portion, and the shape of only the shape change portion of the press die for press-molding the heat transfer plates (12a, 12b) is changed to reduce the cost of the press die. Can be easily done.

According to the third aspect of the present invention, the projection height (H1) of the flow path projection (14) and the projection height (H3) of the positioning abutment (140, 141) are determined. The difference is
It is characterized by being within 0.2 mm.

According to the invention described in claim 4, the heat transfer plates (12a, 12b) are added to the pressing mold (100).
And a main body punch (110) for molding a portion excluding the positioning contact portions (140, 141) and the tank portions (15 to 18), and the positioning punches (140, 141) are attached to the main body punch (110). 141) and the tank section (15-1)
8) A slide punch (120) for molding only the slide punch is provided in a state where the slide punch (120) is slidable in the pressing direction so that the position can be adjusted.

As a result, the positioning contact portions (140,
141) and the slide punch (120) for forming only the tank part (15-18) can be adjusted in the pressing direction with respect to the main body punch (110), so that the main body punch (110) and the slide punch (120) can be used. If the position of the slide punch (120) is adjusted before pressing against the metal plate, the height of the tank (H2) and the height of the contact portion (H3) can be easily adjusted. Therefore,
As described above, when changing the specifications while keeping the external dimensions of the heat exchanger the same, the specifications are changed only by adjusting the position of the slide punch (120) without requiring a new press die for each change in the specifications. Therefore, the cost of the mold (100) can be reduced.

The reference numerals in parentheses of the above means are examples showing the correspondence with specific means described in the embodiments described later.

[0026]

(First Embodiment) FIGS. 1 to 7 show an embodiment of the present invention, and show an example in which the present invention is applied to an evaporator 10 for a vehicle air conditioner. FIG. 1 is an exploded perspective view showing the configuration of a heat transfer plate on the refrigerant inlet / outlet side.
FIG. 3 is an exploded perspective view showing a refrigerant passage configuration of the entire evaporator.

The evaporator 10 has a flow direction A for air-conditioning air.
And the cross-flow direction B (the vertical direction shown in FIG. 2) in the heat transfer plate portion is configured as a cross-flow heat exchanger that is substantially orthogonal. In the evaporator 10, a core portion 11 for exchanging heat between air-conditioning air (external fluid) and a refrigerant (internal fluid) is configured by simply stacking a number of heat transfer plates 12a and 12b.

In this embodiment, the core portion 11 is constituted by a combination of the first heat transfer plate 12a shown in FIG. 3A and the second heat transfer plate 12b shown in FIG. 3B.

The heat transfer plates 12a, 12b
Is A400 series aluminum core material on both sides of A400
A thin plate having a thickness t of about 0.1 to 0.4 mm is press-formed from a double-sided clad material clad with a system 0 aluminum brazing material (the press-forming method will be described later in detail).
It was done. Each of the heat transfer plates 12a and 12b has a substantially rectangular planar shape as shown in FIGS. 3A and 3B, and has the same outer dimensions, and a length in the long side direction is, for example, 245 mm. In the short side direction, for example,
45 mm.

The shape of the heat transfer plates 12a and 12b may be basically the same, but the specific shapes thereof include the formation of the refrigerant passage, the assembling property of the evaporator, the brazing property, and the drainage property of the condensed water. It is different for such reasons.

The first heat transfer plate 12a shown in FIG.
Is formed by projecting a protruding portion (flow passage rib) 14 from the flat substrate portion 13 toward the front side of the drawing. On the other hand, the second heat transfer plate 12b shown in FIG. 3B is formed by stamping out a protruding portion (flow passage rib) 14 from the flat substrate portion 13 to the back side of the drawing.

The protruding portions 14 constitute refrigerant passages (internal fluid passages) 19 and 20 through which the low-pressure side refrigerant after passing through the pressure reducing means (expansion valve or the like) of the refrigeration cycle flows. Twelve longitudinally extending in other words (in other words, a direction substantially orthogonal to the air flow direction A). FIG. 4A is a cross-sectional view taken along line AA of FIG. 3B, and the cross-sectional shape of the protrusion 14 is substantially trapezoidal.

The number of projections of the projections 14 is 5 for both the first and second heat transfer plates 12a and 12b, and as shown in FIG. The launch height (hereinafter, referred to as a protrusion height) H1.

The projections 14 are formed between the first heat transfer plate 12a and the second heat transfer plate 12b.
Since the launch position is shifted in the air flow direction A,
As shown in FIG. 4 (b), when the first heat transfer plate 12a and the second heat transfer plate 12b face each other such that the projecting portions 14 face outward, and the board portions 13 contact each other. The protrusion 14 of the second heat transfer plate 12b is located between the protrusions 14 of the first heat transfer plate 12a.

Then, the two heat transfer plates 12a and 12a
When the substrate portions 13 of b are brought into contact with each other and joined together, the inner surface side of each protrusion 14 of one heat transfer plate is sealed by the substrate portion 13 of the other heat transfer plate. Refrigerant passages 19 and 20 can be formed between the heat transfer plate and the substrate portion 13 of the counterpart heat transfer plate.

That is, each heat transfer plate 12a, 12b
In the width direction (the air flow direction), the inside of the protruding portion 14 located on the windward side from the center portion is provided with the refrigerant passage 2 on the windward side.
0 are formed, and the protruding portion 1 is located on the leeward side from the central portion.
Four refrigerant passages 19 on the leeward side are formed on the inside of 4.

On the other hand, as shown in FIG.
Two tank portions 15 to 18 divided into the heat transfer plate width direction (air flow direction A) are provided at both ends of the direction B (longitudinal direction of the heat transfer plate) perpendicular to the direction A of air flow. It is formed one by one. FIG. 6 shows FIG.
FIG. 3B is an enlarged view of a portion C of FIG. 3, and the tank portions 15 to 18 are formed in the respective heat transfer plates 12 a and 12 b in the same direction as the protruding portion 14 and formed in a substantially cylindrical shape.

FIGS. 7 (a) and 7 (b) show DD lines in FIG.
It is sectional drawing and EE sectional drawing, and the cross-sectional shape of tank part 15-18 is substantially trapezoidal. And these tank parts 1
The ejection height H2 of 5 to 18 (hereinafter, referred to as tank height) is formed to be different from the height H1 of the protrusion. In this embodiment shown in FIGS. 4 and 7, the tank portion height H2 is formed to be higher than the protruding portion height H1.

Then, the tank portions 15 to 18 are
In the same direction as in FIG.
5-18, the ends of the leeward side refrigerant passage 20 are communicated with the leeward side tank portions 17 and 18, and both ends of the leeward side refrigerant passage 19 are connected to each other. It communicates with the tank sections 15 and 16 on the leeward side. In addition,
In the present embodiment, the shapes of the tank portions 15 to 18 are formed to be substantially circular, but they may be formed to be substantially D-shaped or may be formed to be substantially oblong.

Further, communication holes 15a to 18a are opened in the center of each of the tank portions 15 to 18. This communication hole 15
The flow paths of the tank portions 15 to 18 are communicated between adjacent heat transfer plates in the horizontal direction (heat transfer plate stacking direction) shown in FIGS. That is, the tank protruding ends 15b to 18b, which are the ejection tops of the adjacent tank portions 15 to 18, come into contact with each other and are joined to each other, so that the communication holes 15a to 18a communicate with each other.

As shown in FIG. 3, in both the first and second heat transfer plates 12a, 12b, the leeward tank portions 15, 1 are compared with the leeward tank portions 17, 18.
6 is reduced by a predetermined dimension L1. this is,
As described later, this is for increasing the ventilation area in the leeward side region in the core portion 11 as compared with the leeward side region.

As shown in FIGS. 3 and 5 (a), small projections expanding in the width direction of the heat transfer plate (air flow direction A) from the side surfaces of the protrusions 14 of the heat transfer plates 12a and 12b. (Positioning contact ribs) 140 are formed. A large number of the small projections 140 are provided at the same position in the longitudinal direction of each projection 14.

The large number of small protrusions 140 of each projection 14 of the first heat transfer plate 12a expand in the direction opposite to the small protrusions 140 of the second heat transfer plate 12b in the width direction of the heat transfer plate. It is formed as follows. And FIG.
As shown in (a) and (b), the ejection height (hereinafter, referred to as small projection height) H3 of these small projections 140 is formed to be the same as the tank section height H2. .
That is, the small protrusion height H3 is also formed to be different from the protrusion height H1, similarly to the tank portion height H2.

Incidentally, in the present embodiment, the height H1 of the protruding portion is set.
1.45 mm, the tank height H2 is 1.4 mm, and the small protrusion height H3 is 1.4 mm.

With the above configuration, the protruding ends 15b to 15h, which are the apex tops of the tank portions 15 to 18 adjacent in the laminating direction.
As shown in FIG. 5B, the small projections 140a, which are the tops of the small projections 140 adjacent to each other in the stacking direction, are brought into contact with each other. Thus, the heat transfer plates 12a and 12b are positioned in the stacking direction, and the small protrusions 140a of the small protrusions 140 and the tank protrusions 1 of the tank portions 15 to 18 are disposed.
The heat transfer plates 12a and 12b can be joined to each other in a state where the pressing force in the heat transfer plate stacking direction acts on 5b to 18b.

On the other hand, when the small projections 140 are not formed, the tank protruding ends 15b to 15d of the tank portions 15 to 18 at both ends in the longitudinal direction of each of the heat transfer plates 12a and 12b.
Only when the contact portion 18b abuts, a state in which there is no contact portion at the intermediate portion in the longitudinal direction (the portion where the refrigerant passages 19 and 20 are formed) due to the small projection projecting end 140a as shown in FIG. Become. However, according to the present embodiment, by forming the small protrusions 140, as shown in FIG. 5B, the contact portions of the small protrusions 140 can be formed even in the intermediate portion in the longitudinal direction.

Thus, the heat transfer plates 12a, 12b
Of these, the pressing force is applied to the intermediate portions (the portions where the refrigerant passages 19 and 20 are formed) except for the tank portions 15 to 18 at both ends in the longitudinal direction, so that the substrate portions 13 of the heat transfer plate 12 are entirely and reliably connected. By contact, the contact surfaces of the substrate portions 13 can be brazed satisfactorily. Therefore, leakage of the refrigerant from the refrigerant passages 19 and 20 due to poor brazing can be prevented.

By the way, as shown in FIG. 4B, the width direction of each heat transfer plate 12a, 12b (air flow direction A)
In this embodiment, the positions of the plurality of protrusions 14 are different from the positions of the protrusions 14 of the adjacent heat transfer plates 12a and 12b.
Each protrusion 14 can be located on the concave surface formed by the substrate 13 of 2b.

As a result, the other heat transfer plates 12a adjacent to the protruding end 14a, which is the top on the convex side of each protruding portion 14,
A gap is always formed between the concave portion of the substrate portion 12b and the concave portion. Due to this gap, an air passage (external fluid passage) 10a meandering in a wavy shape as shown by an arrow A1 is continuously formed over the entire length in the heat transfer plate width direction (air flow direction A).

Therefore, the conditioned air blown in the direction of arrow A can pass between the two heat transfer plates 12a and 12b while meandering in the air passage 10a in a wave shape as shown by arrow A1.

The stacking pitch P of the heat transfer plates 12a and 12b (see FIGS. 1, 4 (b) and 5 (b)) which determines the width of the air passage 10a is determined by the height H1 of the protruding portion.
Irrespective of this, it is determined by the tank portion height H2 and the small protrusion height H3. Accordingly, when the outer dimensions of the evaporator 10 are the same, the stacking pitch P can be changed by changing the tank portion height H2 and the small protrusion height H3.

For example, as shown in FIGS. 9 and 10, when the height H2 of the tank portion and the height H3 of the small protrusions are reduced, the lamination pitch P is reduced, and the number of heat transfer plates 12a and 12b is increased, thereby reducing the heat transfer. As the area increases, the air flow velocity increases, and the heat transfer coefficient increases. On the contrary,
The width of the flow path of the air flow indicated by the arrow A1 decreases, and the ventilation resistance of the air increases. Incidentally, in the heat transfer plates 12a and 12b shown in FIG. 9 and FIG.
45 mm, the height H2 of the tank portion is 1.3 mm, and the height H3 of the small protrusion is 1.3 mm.

Next, a portion for allowing the refrigerant to flow into and out of the core portion 11 will be described. As shown in FIGS.
Heat transfer plates 12 are provided at both ends in the heat transfer plate stacking direction.
End plate 2 having the same size as a and 12b
1, 22 are provided. This end plate 21,
Each of the heat transfer plates 22 abuts on the projecting portion 14 of the heat transfer plate 12a and the convex side of the tank portion 15-18.
It has a flat plate shape to be joined to 2a.

The left end plate 21 in FIGS. 1 and 2 has a refrigerant inlet hole 21a and a refrigerant outlet hole 21b near the lower end thereof, and the refrigerant inlet hole 21a is located downstream of the lower end of the heat transfer plate 12a. The refrigerant outlet hole 21b communicates with the communication hole 16a of the side tank portion 16, and the communication hole 18a of the windward tank portion 18 at the lower end of the heat transfer plate 12a.
Communicate with Also, the refrigerant inlet hole 2 of the end plate 21
A refrigerant inlet pipe 23 and a refrigerant outlet pipe 24 are respectively joined to 1a and the refrigerant outlet hole 21b.

One end plate 21 has a refrigerant inlet,
For joining with the outlet pipes 23 and 24, like the heat transfer plates 12a and 12b, it is made of a double-sided clad material in which an A4000-based aluminum brazing material is clad on both surfaces of an A3000-based aluminum core material. The other end plate 22 has an A4000-based aluminum core material on only one surface (the surface on the side joined to the heat transfer plate 12a).
It consists of a single-sided clad material clad with an aluminum brazing material. Further, both end plates 21 and 22 have a plate thickness t larger than the heat transfer plate 12 (for example, the plate thickness t =
(About 1.0 mm) to improve the strength.

A gas-liquid two-phase refrigerant decompressed by a decompression means such as an expansion valve (not shown) flows into the refrigerant inlet pipe 23, and a refrigerant outlet pipe 24 is connected to a compressor suction side (not shown). The gas refrigerant evaporated in the step is guided to the compressor suction side.

In each of the heat transfer plates 12a and 12b,
Since the refrigerant from the refrigerant inlet pipe 23 flows into the leeward-side refrigerant passage 19, the leeward-side refrigerant passage 20 constitutes an inlet-side refrigerant passage in the refrigerant passage of the entire evaporator. The refrigerant passing through the refrigerant passage 19 (side) flows into the refrigerant outlet pipe 24 and flows out to the refrigerant outlet pipe 24, so that an outlet-side refrigerant passage is formed.

Next, the refrigerant passage as the entire evaporator 10 will be described with reference to FIG. 2. First, in the left-right direction (the heat transfer plate laminating direction) in FIGS. In the half region Y on the side of the other end plate 22, a large number of sets are laminated with the two heat transfer plates 12 a and 12 c as one set. The core portion 11 is formed by joining the heat transfer plates.

Then, of the tank portions 15 to 18 located at the upper and lower ends of the evaporator 10, the tank portion 15 on the leeward side,
16 constitutes a refrigerant inlet side tank part, and the windward side tank parts 17 and 18 constitute a refrigerant outlet side tank part. The lower refrigerant inlet side tank portion 16 on the leeward side is separated from the heat transfer plate 12 by a partition portion 27 disposed at an intermediate position (a boundary portion between the region X and the region Y) in the laminating direction. X side flow path) and FIG. 2 right side flow path (area Y side flow path)
And is divided into.

Similarly, the lower refrigerant outlet side tank portion 18 on the windward side is also divided by the partition portion 28 disposed at the intermediate position, and is connected to the left flow path in FIG. 2 (the flow path on the area X side) and the right flow path in FIG. It is partitioned into a flow path (a flow path on the area Y side). These partition portions 27 and 28 are connected to the heat transfer plates 12a to 12
Of c, only the heat transfer plate located at the corresponding site can be easily configured by using a blind lid-shaped one in which the communication holes 15a and 18a of the tank portions 15 and 18 are closed.

According to the evaporator 10 of this embodiment, the low-pressure gas-liquid two-phase refrigerant reduced in pressure by the expansion valve is supplied to the refrigerant inlet pipe 23.
As shown by arrow a, the lower inlet side tank portion 16 on the leeward side
to go into. The flow path of the inlet side tank portion 16 is a partition portion 27.
Since the refrigerant is further divided into left and right regions X and Y, the refrigerant enters only the flow path in the left region X of the inlet-side tank portion 16.

Then, in the left region X of FIG. 2, the refrigerant rises as indicated by the arrow b in the refrigerant passage 19 formed by the leeward projecting portions 14 of the heat transfer plates 12a and 12b, and the upper inlet side tank portion 15 to go into. Next, the refrigerant moves the upper inlet side tank portion 15 to the right side area Y in FIG.
And the refrigerant passage 19 formed by the leeward projections 14 of the heat transfer plates 12a and 12b is lowered as shown by the arrow d and enters the flow path in the right region Y of the lower inlet tank 16. .

Here, a communication passage for directly communicating the tank portions 16 and 18 is provided at an intermediate position between the tank portions 16 and 18 below the second heat transfer plate 12c incorporated in the right side area Y. 120 is formed, the tank part 1
Next, the refrigerant in the right side region Y of 6 enters the outlet-side tank portion 18 on the windward side as shown by the arrow e through the communication passage 120.

Here, since the flow path of the outlet side tank section 18 is divided into left and right areas X and Y by the partition section 28, the refrigerant enters only the flow path of the right side area Y of the outlet side tank section 18. . Next, in the right side region Y of the tank portion 18, the refrigerant is supplied to the windward projecting portions 1 of the heat transfer plates 12a and 12b.
4 rises in the refrigerant passage 20 as shown by the arrow f and enters the right side region Y of the upper outlet side tank portion 17.

From the right side area Y, the refrigerant passes through the upper outlet side tank portion 17 to the left side area X in FIG. 2 as indicated by an arrow g, and is formed by the windward projection 14 of the heat transfer plates 12a and 12b. Down the refrigerant passage 20 as shown by the arrow h, and enters the flow path in the left region X of the lower outlet side tank portion 18. The refrigerant flows to the left side in the outlet side tank portion 18 as shown by an arrow i, and flows out of the evaporator from the refrigerant outlet pipe 24.

In this embodiment, the refrigerant passage of the evaporator 10 is configured as described above, and the respective components shown in FIGS. 1 and 2 are stacked in a state where they are in contact with each other, and the stacked state (assembly state) State) is held by a suitable jig, carried into a brazing heating furnace, and the assembled body is heated to the melting point of the brazing material, thereby integrally brazing the assembled body. Thereby, the evaporator 10
Can be completed.

In this integral brazing, the small projections 140 of two adjacent heat transfer plates 12a and 12b abut on the joint surfaces in the longitudinal direction of the heat transfer plates 12a and 12b (see FIG. 5B). Then, the heat transfer plates 12a and 12b can be joined to each other while the pressing force in the heat transfer plate stacking direction is applied to the contact portions of the small projections 140 by the jig.

Thus, the heat transfer plates 12a, 12b
Among these, the pressing force is applied to the intermediate portion (the portion where the refrigerant passages 19 and 20 are formed) except for the tank portions 15 to 18 at both ends in the longitudinal direction, so that the substrate portions 1 of the heat transfer plates 12a and 12b are actuated.
The three members can be reliably brought into contact with each other over the entire surface, and the contact surfaces of the substrate members 13 can be satisfactorily brazed, and leakage of the refrigerant from the refrigerant passages 19 and 20 due to poor brazing can be prevented.

Next, the operation of the evaporator 10 of the present embodiment will be described. The evaporator 10 is housed in an air conditioning unit case (not shown) with the vertical direction of FIGS. By the operation, air is blown in the direction of arrow A.

When the compressor of the refrigeration cycle operates, the gas-liquid 2 on the low pressure side, which is decompressed by an expansion valve (not shown),
The phase refrigerant flows according to the above-described passage configurations indicated by arrows a to i in FIG. On the other hand, the heat transfer plates 12 a and 12
b and the protruding portion 14 protruding outward from the substrate
3, an air passage 10a meandering in a wavy shape as shown by an arrow A1 in FIG. 4B is continuously formed over the entire length in the heat transfer plate width direction (air flow direction A).

As a result, the conditioned air blown in the direction of the arrow A can pass between the two heat transfer plates 12a and 12b while meandering in the air passage 10a in a wavy manner as indicated by the arrow A1. The refrigerant absorbs the latent heat of evaporation and evaporates from the flow, so that the conditioned air is cooled and turned into cool air.

At this time, with respect to the flow direction A of the conditioned air,
By disposing the inlet-side refrigerant passage 19 on the leeward side and the outlet-side refrigerant passage 20 on the leeward side, the refrigerant inlet / outlet with respect to the air flow has a counterflow relationship.

Further, on the air side, the air flow direction A is perpendicular to the longitudinal direction of the protrusion 14 of the heat transfer plates 12a, 12b (the refrigerant flow direction B in the refrigerant passages 19, 20). Since the projecting portion 14 forms a convex surface (heat transfer surface) projecting orthogonally to the air flow,
The air is hindered from going straight by the convex shape of the projecting portion 14 extending orthogonally.

For this reason, the air flow is generated by the heat transfer plates 12a,
As shown by an arrow A1 in FIG. 4B, a gap between the gaps 12b forms a wave-like meandering flow and disturbs the flow, so that the air flow becomes turbulent and the heat transfer coefficient on the air side is dramatically increased. Can be improved. Here, since the core portion 11 is composed of only the heat transfer plates 12a and 12b, the heat transfer area on the air side is greatly reduced as compared with a normal evaporator having a conventional fin member. Since the heat transfer coefficient on the air side is dramatically improved by setting the turbulent flow state, it is possible to compensate for the decrease in the heat transfer area on the air side by improving the heat transfer coefficient on the air side. Can be secured.

Further, in this embodiment, the height H3 of the small projection is formed to be different from the height H1 of the projection. Therefore, a step occurs between the protruding end 14a of the protruding portion 14 and the protruding end 140a of the small protrusion 140. Therefore,
The flow of the air passing through the external air passage 10a can be further disturbed as compared with the case where the protrusion height H1 and the small protrusion height H3 are formed at the same height as in the related art. Therefore,
The heat transfer coefficient between the heat transfer plates 12a, 12b and the external fluid can be improved, and the cooling performance of the evaporator 10 can be improved.

Further, according to the present embodiment, the communication passage 120 is formed at an intermediate position between the tank portions 16 and 18 below the second heat transfer plate 12b incorporated in the right region Y,
Since the tank portion 16 and the tank portion 18 are directly communicated with each other by the communication passage 120, there is no need to form a refrigerant passage in the end plate 22 portion, and only a single flat plate-shaped end plate 22 is used. Good. Therefore, the heat transfer plate arrangement volume in the core portion 11 can be increased, and the heat transfer performance can be improved with the increase in the volume.

Next, the drainage of the condensed water of the evaporator 10 in the present embodiment will be described. In the evaporator 10, the longitudinal direction of the heat transfer plates 12a and 12b is the vertical direction as shown in FIGS. It is arranged and actually used. Accordingly, in the use state of the evaporator 10, a gap (see FIG. 4B) extending in the longitudinal direction (vertical direction) can be continuously formed between the heat transfer plates 12a and 12b. As a result, along the gap extending in the vertical direction,
Condensed water generated on the surfaces of the heat transfer plates 12a and 12b can be smoothly dropped downward.

Although a part of the condensed water tends to move to the leeward side due to the wind pressure of the blast air, according to the present embodiment, in both of the heat transfer plates 12a and 12b, the tanks 17 and 18 on the windward side are provided. On the leeward side of the tank section 15, 1
6 is reduced by a predetermined dimension L1. Thereby, the ventilation area in the leeward side region can be enlarged in the core portion 11 as compared with the leeward side region, and the air flow velocity in the leeward side region can be reduced.

Therefore, even if a part of the condensed water moves to the leeward side, the scattering of the condensed water to the downstream side from the leeward ends of the heat transfer plates 12a and 12b can be effectively prevented by the decrease in the air flow velocity. Can be suppressed.

By the way, the optimum specifications of the heat exchange performance (the amount of heat exchangeable per unit time (J / s)) and the ventilation resistance (Pa) of the vehicle air conditioner evaporator 10 differ for each vehicle type. For example, the air-conditioning evaporator 10 arranged inside the instrument panel
Therefore, when cooling the space behind the passenger compartment, it is necessary to extend the air conditioning duct from the inside of the instrument panel to the rear of the passenger compartment, and the pressure loss of air in the air conditioning duct increases. In such a case, a specification is desired in which the ventilation resistance (Pa) is reduced even if the heat exchange performance (J / s) is reduced. The above-mentioned optimum specifications also differ depending on the size of the vehicle interior, the amount of air blown into the vehicle interior, and the like.

Conventionally, the following method can be cited as a specific example of this specification change. That is, the heat transfer plate 12
By increasing the number of protrusions 14 and increasing the height H1 of the protrusions without changing the number of stacked layers a and 12b, the ventilation resistance when the blown air passes through the external air passage 10a of the evaporator 10 is reduced. In contrast, the heat exchange performance of the evaporator 10 is improved. On the other hand, by reducing the number of the protrusions 14 or reducing the height H1 of the protrusions, the ventilation resistance is reduced and the heat exchange performance is reduced.

However, if the specification of the evaporator 10 is changed by changing the number of the protrusions 14 and the height H1 of the protrusions, the protrusions 14 occupy a large proportion of the surface area of the heat transfer plates 12a and 12b. Therefore, the heat transfer plates 12a, 1
Since the shape change portion of 2b increases, it is not possible to reduce the cost of the press mold 100 by changing the shape of only the shape change portion of the press mold 100 for press-molding the heat transfer plates 12a and 12b. It is difficult and requires a new mold for each changed specification, resulting in high cost.

On the other hand, in the present embodiment, the height H1 of the protrusion is formed so as to be different from the height H2 of the tank and the height H3 of the small protrusion. For example, as shown in FIGS. When the section height H2 and the small protrusion height H3 are formed to be lower than the protrusion height H1, the tank section height H2 and the small protrusion height H3 of the evaporator 10 having the same outer dimensions are projected. The width of the external air passage 10a is narrowed, the number of stacked heat transfer plates 12a, 12b is increased to increase the heat exchange area, and the air flow rate is reduced, as compared with the case where the air passage is formed at the same height as the section height H1. To increase the heat transfer coefficient. Therefore, compared with the case where the tank portion height H2 and the small protrusion height H3 are formed at the same height as the protrusion portion height H1, the specification that the ventilation resistance is large but the heat exchange performance is high can be achieved.

On the other hand, as shown in FIGS. 4 and 7, when the height H2 of the tank portion and the height H3 of the small protrusion are formed higher than the height H1, the outer dimensions of the evaporator 10 are made the same. Among them, tank height H2 and small projection height H3
Is formed at the same height as the height H1 of the protruding portion, the width of the external air passage 10a is increased,
The heat exchange area can be reduced by reducing the number of stacked layers 2a and 12b, and the heat transfer rate can be increased by reducing the air flow rate. Therefore, compared with the case where the tank portion height H2 and the small protrusion height H3 are formed to be the same height as the protrusion portion height H1, the specification can be made such that the heat exchange performance is low but the ventilation resistance is small.

As described above, the specifications of the evaporator 10 can be changed without changing the number of the protrusions 14 and the height H1 of the protrusions, but by changing the height H2 of the tank portion and the height H3 of the small protrusions while keeping the outer dimensions the same. Can be changed. Therefore, the shape change portions of the heat transfer plates 12a and 12b can be reduced, and only the shape of the tank portions 15 to 18 and the small protrusions 140 which are the shape change portions in the press die 100 for press-molding the heat transfer plates 12a and 12b. Can be easily changed to reduce the cost of the press die 100.

Next, the heat transfer plate 12a of this embodiment
To explain the press forming method 12b, FIG. 11 shows a punch portion of a press die 100, and this punch is constituted by a main body punch 110 and a slide punch 120.

The main body punch 110 is connected to the heat transfer plate 12.
a, 12b, the small protrusion 140 and the tank portions 15-1
The slide punch 120 is for molding only the small projection 140 and the tank portions 15 to 18 except for the portion 8. And the slide punch 120
Is mounted on the main body punch 110 in a state where the position of the is adjustable by sliding in the pressing direction (the arrow direction in FIG. 11) with respect to the main body punch 110.

By the above-described press molding method, the small projections 14 are formed.
Since the position of the slide punch 120 for forming only the main body punch 110 and the slide punch 120 can be adjusted in the pressing direction with respect to the main body punch 110, the slide punch 120 is pressed before pressing the main body punch 110 and the slide punch 120 toward the metal plate. 120 positions can be adjusted. This allows
The specifications can be changed while keeping the outer dimensions of the evaporator 10 the same. Therefore, a new press die is not required for each specification change, and the cost of the die can be reduced.

Next, a description will be given of an experimental result by the present inventors with reference to FIG. 12. In the case where the outer dimensions of the evaporator 10 are the same, the heights of the tank height H2 and the small protrusion height H3 are changed. The cooling performance (the amount of heat (J) that can be exchanged per unit time (s)) and the ventilation resistance (Pa) due to the difference in the lamination pitch P of the heat transfer plates 12a and 12b
Shows the change.

FIG. 12 shows an evaporator in which the tank height H2 and the small projection height H3 are set to 1.4 mm.
Reduces the height H3 of the tank and the height H3 of the small protrusions by 0.2 mm from the heights of the heat transfer plates 12a and 12b.
This is the case of an evaporator in which the stacking pitch P of
Increases the height H3 of the tank and the height H3 of the small protrusions by 0.2 mm, so that the heat transfer plates 12a, 12b
This is the case of the evaporator in which the lamination pitch P is increased.

With respect to these three types of evaporators 10, the pressure loss (pressure loss due to ventilation resistance) of the air passing through the external air passage 10a measured under the following experimental conditions (P
a) and the cooling performance (J / s) of the evaporator 10 are shown on the vertical axis. The vertical axis indicates the pressure loss and the cooling performance of the evaporator as a reference (100%) and the pressure loss and the cooling performance of the evaporator as a ratio to the evaporator. The solid line in the figure indicates the change in the cooling performance, and the dotted line in the figure indicates the pressure loss due to the ventilation resistance.

The horizontal axis represents the tank height H2 (mm) and the small projection height H3 (mm). The horizontal axis is
3 shows the difference between the tank height H2 and the small protrusion height H3 of the evaporator.

The experimental conditions were as follows: the amount of air blown to the evaporator: 500 m
³ / h, temperature of air flowing into the evaporator (Ta): 27 ° C,
Humidity of air flowing into the evaporator (RH): 50%, low-pressure pressure (PL) on the evaporator outlet side as conditions on the refrigeration cycle side:
0.28 MPa, superheat degree (SH) of refrigerant on the evaporator outlet side:
10 ° C., high pressure (PH): 1.74 MPa, degree of supercooling of high pressure liquid refrigerant (SC): 3 ° C., core part 11 of evaporator
1 are 300 mm in width in the left-right direction, 220 mm in height, and 36 mm in the air flow direction in FIG.

As shown by the solid line in FIG. 12, under the above-described experimental conditions, the cooling performance decreases as the tank height H2 and the small protrusion height H3 increase from. As shown by the dotted line in FIG. 12, the pressure loss due to the ventilation resistance decreases as the tank height H2 and the small protrusion height H3 increase. And assuming that the cooling performance is 100%,
Cooling performance is slightly greater than 105%,
Was found to have a cooling performance slightly smaller than 95%. That is, the tank height H in the evaporator
It has been found that the cooling performance of the evaporator can be changed by ± 5% by adjusting the tank height H2 and the small projection height H3 by ± 0.2 mm based on the height 2 and the small projection height H3.

As described above, the optimum specifications of the cooling performance (the amount of heat exchangeable per unit time (J / s)) and the ventilation resistance (Pa) of the vehicle air conditioner evaporator 10 differ for each vehicle type. However, the specification change of the evaporator 10 can sufficiently be changed for passenger cars by changing the cooling performance by ± 5%.

Therefore, the tank height H in the evaporator is
By adjusting the tank height H2 and the small protrusion height H3 within a range of ± 0.2 mm based on the height 2 and the small protrusion height H3, it is possible to correspond to the optimum specification of the air-conditioning evaporator for each type of passenger car. it can.

(Second Embodiment) In the first embodiment,
The protrusions 14 of the first and second heat transfer plates 12a and 12b are formed so as to extend continuously in a direction substantially perpendicular to the flow direction A of the air (external fluid). It may be formed of a large number of independent elongated projections formed so as to extend obliquely to the flow direction A of the (external fluid).

In this embodiment, as shown in FIGS. 13 and 14, the projecting portion 14 is formed in a large number of independent elongated projecting shapes which extend obliquely at a predetermined angle θ (FIG. 13) with respect to the air flow direction A. Then, as shown in FIG. 14, refrigerant passages 19 and 20 are formed by mutually communicating the internal spaces of the many protrusions 14 at the overlapping portions of the protrusions 14 in the oblique direction.

In FIG. 14, arrow B1 indicates the flow of the refrigerant in the leeward refrigerant passage 19, and arrow B2 indicates the flow of the refrigerant in the refrigerant passage 20 on the leeward side. Air is indicated by arrow A in FIG.
As shown in FIG. 2, meandering occurs in the plane direction of the heat transfer plates 12a and 12b (vertical direction in FIG. 13), and also meanders in the stacking direction of the heat transfer plates 12 (perpendicular direction in FIG. 14).

In this embodiment, as in the first embodiment, the projection height of the overlapping portion 141 of the portion of the projecting portion 14 surrounded by the dotted line in FIG. 13 (hereinafter, referred to as the overlapping portion height). ) H3 is formed at a height different from the height H1 of the protrusion, and a step is formed between the protrusion end 14a of the protrusion 14 and the protrusion end of the overlapping portion 141. Thereby, similarly to the first embodiment, the heat transfer coefficient between the heat transfer plates 12a and 12b and the external fluid can be improved.

(Third Embodiment) FIGS. 15 and 16 show a third embodiment, corresponding to FIGS. 13 and 14 of the second embodiment.
Although the two rows of protrusions 14 provided before and after the air flow direction A in FIGS. 12A and 12B are inclined at a predetermined angle θ with respect to the air flow direction A, in this embodiment, the two rows of protrusions 14 are A is disposed orthogonal to A. In other words, the elongated projections 14 are arranged parallel to the longitudinal direction of the heat transfer plate 12 (the refrigerant flow direction B).

Here, in this embodiment, the heat transfer plate 1
By arranging the elongated protrusions 14 in a staggered manner in parallel with the longitudinal direction (refrigerant flow direction B) of the two heat transfer plates 12a and 12b to which the concave surfaces are joined,
As shown in FIG. 16, the refrigerant passages 19 and 20 are formed by partially setting the overlapping portion 141 between the elongated protrusions 14. Therefore, according to the present embodiment, the refrigerant flows in the entire length of the refrigerant passages 19 and 20 in parallel with the longitudinal direction of the heat transfer plates 12a and 12b.

(Fourth Embodiment) FIGS. 17 and 18 show a fourth embodiment, corresponding to FIGS. 13 and 14 of the second embodiment, and are modified examples of the third embodiment. That is, of the two rows of protrusions 14 provided on the heat transfer plates 12a and 12b before and after the air flow direction A, one of the protrusions 14 is arranged orthogonally to the air flow direction A, and the other protrusion 14 14 are arranged in parallel to the air flow direction A.

Therefore, according to the present embodiment, the refrigerant passages 19, 2
The coolant flows inside the heat transfer plate 12 while alternately changing its direction in the longitudinal direction of the heat transfer plate 12 and in a direction orthogonal to the longitudinal direction.

(Other Embodiments) In the above-described first embodiment, the small projections 140 are formed so as to be enlarged from the side surfaces of the projections 14, but the small projections 140 are not adjacent to the projections 14. Small protrusions 14 on the substrate portion 13.
0 may be formed at a position distant from the protrusion 14. Similarly, in the second to fourth embodiments, the overlapping portion 141 may be formed at a position away from the projecting portion 14.

In the first to fourth embodiments, the refrigerant passages (internal fluid passages) 19 of the heat transfer plates 12a and 12b are provided.
The present invention is applied to the evaporator 10 in which the low-temperature refrigerant on the low pressure side of the refrigeration cycle flows through 20 and the conditioned air flows outside the heat transfer plates 12a and 12b, and the refrigerant evaporates by absorbing the latent heat of evaporation of the refrigerant from the conditioned air. Although the above description has been made, the present invention is not limited to this, and it is needless to say that the present invention can be widely applied to heat exchangers for performing heat exchange between fluids for various uses.

In the first to fourth embodiments, the two first and second heat transfer plates 12a and 12b are formed as one set, but they may be formed by bending one heat transfer plate. . And since the present invention also includes such a structure formed by bending, in the present specification, “multiple”, “two”,
The expression “plurality of sets” simply means that there are a plurality of heat transfer plates in the plate laminating direction that appear as a plate-like cross-sectional shape, and it does not matter whether they are integrated or separate.

[Brief description of the drawings]

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

FIG. 2 is an exploded perspective view showing a refrigerant passage of the heat exchanger of FIG.

3A is a plan view showing a first heat transfer plate of FIG. 1, and FIG. 3B is a plan view showing a second heat transfer plate of FIG.

FIG. 4A is a sectional view taken along line AA of FIG. 3B,
FIG. 4B is a cross-sectional view illustrating a stacked state of the first and second heat transfer plates in the AA cross section.

FIG. 5A is a sectional view taken along line BB of FIG. 3B,
(B) is sectional drawing which shows the lamination state of the 1st and 2nd heat transfer plate in BB cross section.

FIG. 6 is an enlarged view of a portion C in FIG. 3 (b).

7A is a sectional view taken along the line DD in FIG. 6, and FIG. 7B is a sectional view taken along the line EE in FIG.

8A and 8B show a state in which the height of the small protrusions of the small protrusions shown in FIG. 4 is lowered, wherein FIG. 8A is a cross-sectional view taken along the line AA, and FIG. It is sectional drawing which shows the lamination state of 2 heat transfer plates.

9A and 9B show a state in which the height of the small protrusions of the small protrusions shown in FIG. 4 is reduced, where FIG. 9A is a cross-sectional view taken along the line BB, and FIG. It is sectional drawing which shows the lamination state of 2 heat transfer plates.

10 shows a state in which the height of the tank portion of the tank portion shown in FIG. 7 is reduced, and FIG.
(B) is EE sectional drawing.

FIG. 11 is a perspective view showing a punch portion of a press die for press-working the heat transfer plate of the first embodiment.

FIG. 12 is an explanatory diagram illustrating an experimental result by the present inventors.

FIG. 13 is a plan view of a second heat transfer plate according to a second embodiment of the present invention.

FIG. 14 is a plan view showing a superposed state of first and second heat transfer plates according to the second embodiment.

FIG. 15 is a plan view of a second heat transfer plate according to a third embodiment of the present invention.

FIG. 16 is a plan view showing a superposed state of first and second heat transfer plates according to a third embodiment.

FIG. 17 is a plan view of a second heat transfer plate according to a fourth embodiment of the present invention.

FIG. 18 is a plan view showing a superposed state of first and second heat transfer plates according to a fourth embodiment.

[Explanation of symbols]

10 evaporator, 10a air passage (external fluid passage), 1
2a: first heat transfer plate, 12b: second heat transfer plate,
14: Projecting portion (rib for flow passage), 14a: Projecting end of projecting portion, 15 to 18: Tank portion, 19, 20 ... Refrigerant passage (internal fluid passage), 140 ... Small protrusion (abutment rib for positioning) , 140a: projecting end of small projection, 141: overlapping portion, H
1 ... Projection height, H2 ... Tank height, H3 ... Small projection height.

Claims (4)

[Claims] A plurality of heat transfer plates (12a, 12b) arranged in a stack are provided on each of the plurality of heat transfer plates (12a, 12b).
4) and the positioning abutment portions (140, 141) protrude on the same surface side, and form internal fluid passages (19, 20) through which an internal fluid flows inside the flow passage protruding portion (14); The positioning contact portions (140, 1
The plurality of heat transfer plates (12a, 12b) are positioned in the stacking direction by abutting the protruding ends (140a) of 41), and the convex tops of the flow path protruding portions (14) are adjacent to each other. The heat transfer plate (12a, 12b) is opposed to the heat transfer plate (12a, 12b) via a gap, and the gap forms an external fluid passage (10a) flowing outside the heat transfer plate (12a, 12b). A heat exchanger, wherein the projecting portion (14) acts as a turbulence generator for preventing the flow of the external fluid from going straight and causing turbulence; (H1) is a protruding height (H) of the positioning contact portions (140, 141).
A heat exchanger characterized by being formed differently from 3). 2. The heat transfer plate (12a, 1
2b), the internal fluid passages (19, 2
0) A tank part (1) for communicating between the tanks in the laminating direction.
5-18) are the positioning contact portions (140, 14).
1), and the projecting height (H2) of the tank portion (15-18) is adjusted to the projecting height (H) of the positioning contact portion (140, 141).
3) is formed at the same height as the positioning contact portion (14) adjacent in the laminating direction.
0, 141) and the protruding ends (15b-18b) of the tank portions (15-18) are brought into contact with each other, whereby the plurality of heat transfer plates (1) are brought into contact with each other.
The heat exchanger according to claim 1, wherein the heat exchangers (2a, 12b) are positioned in the stacking direction. 3. The projecting height (H1) of the flow passage projecting portion (14) and the positioning contact portion (140, 141).
The heat exchanger according to claim 1 or 2, wherein a difference from the protrusion height (H3) is within 0.2 mm. 4. The heat transfer plate (12) according to claim 2,
a press forming apparatus for press forming the heat transfer plate (12) into a press die (100).
a, 12b), the positioning contact portions (140, 1
41) and a main body punch (110) for forming a part excluding the tank part (15 to 18). 15-18)
A heat-transfer plate press-forming apparatus, wherein a slide punch (120) for forming only the heat-transfer plate is provided so as to be slidable in the pressing direction and adjustable in position.