JP2001041678A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure required heat transfer performance with only the heat transfer plates constituting a refrigerant channel without requiring any fin. SOLUTION: A board part 13 and punched parts 14 projecting therefrom are formed in each of a plurality of heat transfer plates 12a-12c wherein the punched parts are formed to extend substantially orthogonally to the direction A of air flowing on the outside of the heat transfer plates. Refrigerant channels 19, 20 are formed on the inside of the punched parts 14 so that the punched parts impede straight advance of air flow and serve as a turbulence generator. Pitch of the punched parts 14 is set at 2-20 mm, thickness of the heat transfer plate is set at 0.1-0.35 mm, and pitch of the refrigerant channels 19, 20 is set at 1.4-3.9 mm.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger comprising only a plate-like member constituting an internal fluid passage through which an internal fluid flows, and is suitable for use in, for example, an evaporator for vehicle air conditioning.

[0002]

2. Description of the Related Art In a conventional heat exchanger, for example, an evaporator for a vehicle air conditioner, an air-side transmission is provided between tubes having a flat cross section formed by joining two plates in the middle. Corrugated fins with louvers are interposed to expand the thermal area. Here, increasing the speed of the airflow passing through the corrugated fins causes an excessive increase in pressure loss.
The heat exchanger is used at a relatively low air velocity, which is a laminar flow area.

Therefore, conventionally, the heat transfer coefficient on the air side is improved by reducing the thickness of the boundary layer by utilizing the louver tip effect.

[0004]

In order to improve the heat transfer coefficient on the air side, louvers have recently been miniaturized to near the processing limit, which has led to an increase in the number of processing steps for corrugated fins. In addition, assembling is deteriorated by assembling the corrugated fin between the two plates constituting the tube. Therefore, the presence of corrugated fins is a major obstacle to cost reduction and downsizing of the heat exchanger.

In view of the above, the present invention has been made to provide a heat exchanger which does not require fins such as corrugated fins and can secure required heat transfer performance only by a heat transfer plate constituting an internal fluid passage. Aim.

[0006]

In order to achieve the above object, according to the first aspect of the present invention, a plurality of projecting portions (14) are formed on a plurality of heat transfer plates (12a to 12c, 12). An internal fluid passage (19, 20) through which an internal fluid flows is formed inside the protrusion (14), and the convex top of the protrusion (14) is adjacent to the heat transfer plate (12a).
To 12c, 12) with a gap interposed therebetween, this gap forms a passage for an external fluid flowing outside the heat transfer plates (12a to 12c, 12), and the protrusion (14) The turbulence generator acts as a turbulence generator that hinders the straight flow of the fluid flow and causes turbulence. Further, the protrusion pitch (P ₁ ), which is the interval between the plurality of protrusions (14), is 2 to 20 mm. It is characterized by doing.

According to the second aspect of the present invention, the plurality of protrusions (1) forming the internal fluid passages (19, 20) through which the internal fluid flows in the heat transfer plates (12a to 12c, 12).
4), a plurality of heat transfer plates (12) are stacked and arranged to form a heat exchange core (11), and an external fluid flowing outside the heat transfer plate (12) flows in a direction of the internal fluid. And the projections (14) function as a turbulence generator that obstructs the straight flow of the external fluid and causes turbulence. Projection pitch (P ₁ )
Is set to 2 to 20 mm.

According to the first and second aspects of the present invention, the protrusion (14) constituting the internal fluid passage (19, 20) itself acts as a turbulence generator, thereby greatly increasing the heat transfer coefficient on the external fluid side. Therefore, necessary heat transfer performance can be ensured without providing a fin member on the external fluid side.

Therefore, the heat transfer plates (12a to 12c, 12) having the projections (14) forming the internal fluid passages.
Alone, a heat exchanger can be constituted, and a significant cost reduction and size reduction of the heat exchanger can be achieved.

In addition, since the heat exchanger can be formed by joining the heat transfer plates (12a to 12c, 12) without interposing a thin fin member, the pressure resistance of the heat exchanger can be improved. Therefore, the heat transfer plates (12a to 12c, 12)
The heat exchanger can be further reduced in cost and size.

Further, according to the study of the present inventor, the heat transfer performance of the heat exchanger can be improved by setting the protrusion pitch (P ₁ ) in the range of 2 to 20 mm as illustrated in FIG. It turned out that it can be improved effectively.

According to a third aspect of the present invention, a passage pitch (P ₂ ), which is an interval between the internal fluid passages (19, 20), is set to 1.4 to 3.9 mm.

As described above, the protrusion pitch (P ₁ ) = 2
The combination of 20 mm and the passage pitch (P ₂ ) = 1.4 to 3.9 mm can effectively improve the heat transfer performance of the heat exchanger while maintaining the pressure loss on the external fluid side in a predetermined range.

Further, the invention according to claim 4 is characterized in that the protrusion pitch (P ₁ ) = 10 to 20 mm and the passage pitch (P ₂ ) = 1.4 to 2.3 mm.

By setting P ₁ and P ₂ in such a range, the heat transfer performance of the heat exchanger can be more effectively improved.

According to a fifth aspect of the present invention, in the heat exchanger according to the first aspect, the heat transfer plates (12a to 12c, 12) adjacent to the convex tops of the protrusions (14).
Is preferably in the range of 0.7 to 1.95 mm to ensure heat transfer performance.

According to the present invention, the heat transfer plate includes a plurality of heat transfer plates (12a to 12c, 1).
By joining 2), the internal fluid passages (19, 20) can be formed inside the protrusion (14).

In the invention according to claim 7, the thickness (t) of the heat transfer plates (12a to 12c, 12) is set to 0.1 to 0.1.
It is characterized by 0.35 mm.

By reducing the thickness of the heat transfer plate, the weight of the heat exchanger can be reduced and the heat transfer performance per unit size can be improved.

In the invention according to claim 8, the heat transfer plates (12a to 12c, 12) are formed with small protrusions (14a) projecting from the side surfaces of the protrusions (14), thereby forming two heat transfer plates. Small protrusions (14) of the plates (12a to 12c, 12)
a) The small projections (14a) are brought into contact with each other, and the contact portions of the small projections (14a) are joined.

According to this, even if a gap is interposed between the top of the convex surface of the protruding portion (14) and the adjacent heat transfer plates (12a to 12c, 12), the small projection (14) can be used.
a) The joining (brazing) step can be performed in a state where a pressing force is applied to the contact portions of the members, and the joining surfaces of the plurality of heat transfer plates (12a to 12c, 12) can be satisfactorily adhered to each other. Therefore, the joining property can be improved.

According to the ninth aspect of the present invention, the heat transfer plates (12a to 12c, 12) are made of aluminum alloy H.
It is characterized by being formed from a material.

Here, the H material of the aluminum alloy is
It is an aluminum material defined by "JIS H 0001" and a hard material having a small elongation and increased in hardness by work hardening.

As described above, according to the present invention, the heat exchanger can be formed by joining the heat transfer plates (12a to 12c, 12) without intervening the fin member, so that the conventional corrugated fin type normal heat exchanger is used. Tanks (15 to 12c) formed on the heat transfer plates (12a to 12c, 12)
18) The launch height can be significantly reduced. as a result,
As a material for the heat transfer plate, an H material of an aluminum alloy having a small elongation rate can be used, whereby the thickness of the heat transfer plate can be further promoted.

Further, by using the H material having a small elongation at the time of forming the heat transfer plate, the erosion (erosion) of the brazing material clad on the surface of the H material can be reduced, and the corrosion resistance of the heat transfer plate can be improved.

As described in the tenth aspect, the plurality of heat transfer plates (12a to 12c, 12) specifically have a substrate portion (13) which is in contact with and joined to each other.
The protruding portion (14) may be configured to protrude outward from the substrate portion (13).

More specifically, as in the invention as set forth in claim 11, the convex top of the protruding portion (14) is constituted by the substrate portion (13) of the adjacent heat transfer plates (12a to 12c, 12). A configuration in which the convex top of the protrusion (14) is located at the concave surface and faces the concave surface of the adjacent heat transfer plate (12a to 12c, 12) at a predetermined interval can be adopted.

According to this, the heat transfer plates (12a to 12c, 12) of the same shape are formed by repeating the uneven shape.
And a heat exchanger with a comparatively small volume (physique).

More specifically, the heat transfer plates (12a to 12c, 12) have two heat transfer plates.
As one set, the two heat transfer plates (12a to 12a) are arranged such that the respective protrusions (14) face outward.
The internal fluid passages (19, 20) are formed in the protruding portions (14) of one of the heat transfer plates (12a to 12c, 12) by abutting and joining the substrate portions (13) of the heat transfer plates (12, 12a, 12c). Side and other heat transfer plates (12a to 12c, 12)
And the substrate part (13).

More specifically, a plurality of pairs of heat transfer plates (12a to 12c, 12) constituting the internal fluid passages (19, 20) are stacked. And joined.

According to the present invention, a tank portion (15a to 18a) having communication holes (15a to 18a) at both ends of the heat transfer plates (12a to 12c, 12) in the flow direction of the internal fluid. 15 to 18), and a tank portion (15 to 18) is formed between the internal fluid passages (19, 20) formed in the plural sets of heat transfer plates (12a to 12c, 12).
Can be connected.

Further, according to the present invention, the internal fluid passages (19, 20) are connected to the heat transfer plates (12a to 12a).
12c and 12) before and after the flow direction (A) of the external fluid.
And two tank portions (15-18) at both ends of the heat transfer plates (12a-12c, 12) corresponding to the two independent internal fluid passages (19, 20), respectively. It may be formed.

In the invention according to claim 16, the tank portion (16) having the communication holes (16a, 18a) at only one end in the flow direction of the internal fluid among the heat transfer plates (12a to 12c, 12). , 18) are independently formed before and after in the flow direction of the external fluid, and a plurality of sets of heat transfer plates (12a) are formed.
To 12c, 12) formed in the internal fluid passages (19, 2).
0) The tanks (15 to 18) are connected to each other, and the flow of the internal fluid is U-turned at the other end of the heat transfer plates (12a to 12c, 12) in the flow direction of the internal fluid. A U-turn portion (D) is formed.

According to this, the tank portions (16, 18) are formed only at one end of the heat transfer plates (12a to 12c, 12), and at the other end, a projecting portion (14) is formed in almost the entire area to transfer the heat. Since the heat area can be provided, the dead space due to the tank portion can be halved compared to the case where the tank portion is provided at both ends, and the heat exchanger can be further reduced in size.

As described above, in the present invention, the heat exchanger can be constituted only by the heat transfer plates (12a to 12c, 12).
2a to 12c, 12) can be formed into a shape having a heat transfer enlarged portion (11 ') projecting from a rectangular parallelepiped shape to the outside (a shape of the heat exchange core portion (11)). The capacity of the heat exchange core (11) can be increased by the addition of the heat transfer expansion part (11 '), so that the performance of the heat exchanger can be improved. In particular, since the heat transfer expansion section (11 ') can be formed by using an extra space in the air conditioning case (101), it is extremely advantageous in practical use.

As in the eighteenth aspect of the present invention, the projection (14) has a direction substantially perpendicular to the flow direction (A) of the external fluid flowing outside the heat transfer plates (12a to 12c, 12). Can be formed to extend continuously.

According to this, when used as an air cooler such as an evaporator, the heat transfer plates (12a to 1a) are arranged by arranging the protrusions (14) so as to extend vertically.
2c, 12) condensed water generated at the top of the convex surface
4) It can be smoothly discharged downward along the convex top.
Therefore, the drainage of the condensed water is improved, and the increase in the ventilation resistance due to the stagnation of the condensed water can be favorably suppressed.

The projection (14) in the present invention may have a number of independent elongated projections arranged so as to prevent the external fluid from going straight.

Further, the elongated projection (14) may be disposed so as to obliquely intersect the flow direction of the external fluid as described in claim 20, or may be arranged as described above.
Or perpendicular to the flow direction of the external fluid as described in claim 22 or, as described in claim 22, perpendicular to the flow direction of the external fluid, It can be composed of a combination with the one arranged in parallel to the flow direction.

According to the twenty-third aspect of the present invention, the shape of the hole in the heat transfer plate (12) allows the internal fluid passage (19,
20).

According to this, the internal fluid passages (19, 2)
0) is a hole shape, so that one heat transfer plate (12)
The internal fluid passages (19, 20) can be built therein, and plate joining for the internal fluid passage configuration is not required. Therefore, there is no possibility of fluid leakage in the internal fluid passages (19, 20).

According to a twenty-fourth aspect of the present invention, in the heat exchanger according to the twenty-third aspect, the heat transfer plate (1)
2) A plurality of heat transfer plates (12) are stacked and arranged, and tank members (33, 34, 46, 47) formed separately from the heat transfer plates (12) on both ends of the heat transfer plates (12).
Are arranged, and the tank members (33, 34, 34) are disposed between the internal fluid passages (19, 20) of the plurality of heat transfer plates (12).
46, 47).

And, as in the invention according to claim 25,
The space between the plurality of heat transfer plates (12) may be held by a spacer member (32) formed separately from the heat transfer plate (12), or as in the invention according to claim 26, The plurality of heat transfer plates (12) may be connected to each other at predetermined intervals by integral connecting portions (40, 41).

According to the twenty-seventh aspect, the protrusion (1)
4) and an internal fluid passage having a hole shape (19, 20)
Is characterized in that the heat transfer plate (12) having the following characteristics is formed by extrusion of an aluminum material.

According to this, the heat transfer plate (12) can be efficiently formed in one step by extrusion. Therefore, the processing cost can be significantly reduced as compared with the case where the heat transfer plate (12) is press-formed.

According to a twenty-eighth aspect of the present invention, the present invention is suitably implemented in an air-conditioning evaporator in which refrigerant of a refrigeration cycle flows as internal fluid in the internal fluid passages (19, 20) and air-conditioning air flows as external fluid. it can.

According to a twenty-ninth aspect of the present invention, there is provided the heat exchanger according to any one of the first to third aspects, wherein the refrigerant of the refrigeration cycle flows as the internal fluid in the internal fluid passages (19, 20), and An air-conditioning evaporator in which air for air-conditioning flows as a fluid, wherein a plurality of protrusions (14) have a protrusion pitch (P ₁ ) of 2 to 15 mm, which is an interval between the protrusions.

According to the study of the present inventors, by setting the protrusion pitch (P ₁ ) in the range of 2 to 15 mm in the evaporator for air conditioning, as illustrated in FIG.
It was found that the performance near the maximum performance of the air conditioning evaporator can be effectively exhibited.

In the present invention, expressions such as “plurality”, “two”, and “plurality” related to the number of heat transfer plates are referred to as plate-like sectional shapes shown in a sectional view of FIG. It means that there are a plurality (two) of heat transfer plates (plate-like members) in the direction. The plurality of heat transfer plates can be formed completely separately from each other as well as integrally formed by a connecting portion such as bending.

The reference numerals in parentheses of the above-mentioned units indicate the correspondence with the specific units described in the embodiments described later.

[0051]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) FIGS. 1 to 7 show a first embodiment of the present invention.
The example applied to 0 is shown. FIG. 1 is an exploded perspective view showing a configuration of a heat transfer plate at a refrigerant inlet / outlet side, and FIG. 2 is an exploded perspective view showing a configuration of a refrigerant passage of the entire evaporator.

The evaporator 10 has a flow direction A of 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 this evaporator 10, a core unit 11 for exchanging heat between air-conditioning air (external fluid) and refrigerant (internal fluid) is configured by simply stacking a number of heat transfer plates 12a, 12b, and 12c. .

In the first embodiment, the first heat transfer plate 12a shown in FIG. 3 and the second heat transfer plate 1 shown in FIG.
2b and first heat transfer plate 1
The core section 11 is constituted by a combination area Y of the second heat transfer plate 12c shown in FIG. 5 and the third heat transfer plate 12c shown in FIG.

Then, each of the heat transfer plates 12a, 12b,
12c is A3000 aluminum core material on both sides of A
It is made of a double-sided clad material in which a 4000 series aluminum brazing material is clad, and has a thickness t = 0.1 to 0.4 mm.
It is formed by press-molding a thin plate of the order. Each of the heat transfer plates 12a, 12b, and 12c has a substantially rectangular planar shape as shown in FIGS. 3 to 5, and has the same outer dimensions. The length in the long side direction is, for example, 245 mm. The width in the side direction is, for example, 45 mm.

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

3 to 5, each of the heat transfer plates 12
In a, 12b, and 12c, a protruding portion (rib) 14 is stamped and formed from the flat substrate portion 13 to the back side of the drawing. The projecting portion 14 is a refrigerant passage (internal fluid passage) through which the low-pressure side refrigerant flows after passing through the pressure reducing means (expansion valve or the like) of the refrigeration cycle.
19, 20 and the heat transfer plate 12
Longitudinal direction (in other words, a direction substantially orthogonal to the air flow direction A)
And a shape that extends in parallel to the shape. Also, the protrusion 14
Has a substantially trapezoidal shape as shown in FIG.

The number of protrusions of the projections 14 is six in the first heat transfer plate 12a in FIG. 3, four in the second heat transfer plate 12b in FIG. 4, and is three in the third heat transfer plate 12 in FIG. In 12c, the number is four.

Further, the second and third heat transfer plates 12b,
In 12c, a protruding portion (rib) 140 for detecting internal leakage is formed at the center in the width direction. The protruding portion 140 is also basically formed by stamping in the same form as the protruding portion 14. However, for the purpose of detecting internal leakage, the second heat transfer plate 12b has both ends 140a in the plate longitudinal direction.
At 140b, the inside of the protrusion 140 is opened to the outside of the heat exchanger.

On the other hand, the protruding portion 140 of the third heat transfer plate 12c is connected to the upper end (one end) portion 14 in the plate longitudinal direction.
0a, the heat exchanger is opened to the outside of the heat exchanger, and the lower end (other end) 14
0b forms a closed end at a position in front of a tank portion described later.

The projections 14 and 140 have the same launch height h (FIG. 6C).

As described above, in the first heat transfer plate 12a, the number of ejections is six, and in the second and third heat transfer plates 12b, 12c, the total number of the protrusions 14 and the protrusions 140 is five. As the first heat transfer plate 12a and the second,
Since the number of punches is different between the third heat transfer plates 12b and 12c, as shown in FIG. 6C, the first heat transfer plate 12a and the second heat transfer plate 12b are connected to each other by the projecting portions 14, When the protruding portions 140 face each other so as to face outward and abut each other on the substrate portions 13, the second heat transfer plate 1 is positioned between the protruding portions 14 of the first heat transfer plate 12 a.
The protrusions 14 and 140 of 2b are located.

Similarly, the first heat transfer plate 12a and the third heat transfer plate 12c are connected to each other by the projecting portions 14 and 140.
Are facing each other so that they face outward.
When the members come into contact with each other, the protrusion 1 of the first heat transfer plate 12a
4, the protrusions 14 and 140 of the third heat transfer plate 12c are located.

Then, the two heat transfer plates 12a and 12a
When the substrates 13 or 12a and 12a are brought into contact with each other and joined to each other, each of the protrusions 14, 140 of one of the heat transfer plates
Is sealed by the substrate portion 13 of the heat transfer plate on the other side, so that a passage can be formed between the inner surface side of each protrusion 14 and the substrate portion 13 of the heat transfer plate on the other side.

That is, each of the heat transfer plates 12a to 12c
In the width direction, the central portion (the internal leakage detection protrusion 14
0), a refrigerant passage 20 on the windward side is formed inside the protruding portion 14 located on the windward side of the heat transfer plate 1.
A leeward refrigerant passage 19 is formed inside the protruding portion 14 located on the leeward side of the center in the width direction of 2a to 12c. Further, a passage 141 for detecting internal leakage is formed inside the protruding portion 140 at the center.

As shown in FIG. 6, the upstream-side refrigerant passage 20 and the downstream-side refrigerant passage 19 are provided between the first heat transfer plate 12a and the second heat transfer plate 12b and between the first heat transfer plate 12a and the first heat transfer plate 12a. Between the third heat transfer plate 12c,
Five are formed in parallel.

On the other hand, the heat transfer plates 12a to 12c are divided into heat transfer plate width directions (air flow direction A) at both ends in a direction B (longitudinal direction of heat transfer plate) perpendicular to the air flow direction A. The tank portions 15 to 18 are formed two by two. The tank portions 15 to 18 are punched in the same direction as the protruding portions 14 and 140 on the heat transfer plates 12a to 12c (the back side of the paper in FIGS. 3 to 5). The same height h (FIG. 7).

As described above, the tank portions 15 to 18 are punched in the same direction as the projecting portion 14, and the concave shape due to the punching is continuous with the stamping concave shape of the tank portions 15 to 18 at both longitudinal ends of the projecting portion 14. Therefore, both ends of the leeward side refrigerant passage 20 communicate with the leeward side tank portions 17 and 18, and the leeward side refrigerant passage 19.
Are connected to the tank sections 15 and 16 on the leeward side.

The tank portions 15 and 17 at the upper end of the heat transfer plate and the tank portions 16 and 18 at the lower end of the heat transfer plate.
Is divided into two in the width direction of the heat transfer plate, and the shape of each of the tank portions 15 to 18 is substantially D-shaped in the illustrated examples of FIGS. However, as in the example shown in FIGS. 1 and 2, each of the tank portions 15 to 18 may be formed in a substantially elliptical shape.

Communication holes 15a to 18a are opened at the center of each of the tank portions 15 to 18. These communication holes 15a-1
8a, the flow paths of the tank portions 15 to 18 communicate with each other between the adjacent heat transfer plates in the left-right direction (heat transfer plate stacking direction) shown in FIGS.

That is, as shown in FIG. 7, the tops of the adjacent tank portions 15 to 18 are brought into contact with each other and joined to each other, so that the communication holes 15a to 18a communicate with each other.

The third heat transfer plate 12c shown in FIG.
Then, the lower end (other end) portion 1 of the internal leakage detection protrusion 140
40b is closed at a position in front of the tank portions 16 and 18 as described above and closed here. Instead of the protruding portion 140, a communication passage 120 for directly communicating the tank portions 16 and 18 is provided.
Is formed. The communication passage 120 can be formed by embossing an intermediate portion between the tank portions 16 and 18 in the same direction as the tank portions 16 and 18.

Further, as shown in FIGS.
In any one of the heat transfer plates 12a to 12c, the tank portion 1 on the leeward side is compared with the tank portions 17 and 18 on the leeward side.
The heights of 5 and 16 are reduced by a predetermined dimension L. This is to increase the ventilation area in the leeward side region of the core portion 11 as compared to the leeward side region, as described later.

Further, small projections 14a projecting in the width direction of the heat transfer plate (the air flow direction A) from the side surfaces of the projecting portions 14 of the heat transfer plates 12a to 12c are formed. A large number of the small projections 14 a are provided at the same position in the longitudinal direction of each projection 14.

In this embodiment, the small projections 14a of the projections 14 of the second and third heat transfer plates 12b and 12c are projected one by one in the width direction of the heat transfer plate. The plurality of small protrusions 14a of each protrusion 14 of the first heat transfer plate 12a are the same as the small protrusions 14a of the second and third heat transfer plates 12b, 12c in the width direction of the heat transfer plate. It protrudes in the direction.

For this reason, two adjacent heat transfer plates 1
The small projections 14a of the small projections 2a, 12b or 12a, 12c are brought into contact with each other, and the heat transfer plates 12a to 12c are joined to each other with a pressing force in the heat transfer plate laminating direction acting on the contact portions of the small projections 14a. can do.

On the other hand, when the small projections 14a are not formed, only the tops of the tank portions 15 to 18 at both ends contact in the longitudinal direction of the heat transfer plates 12a to 12c, and the intermediate portions in the longitudinal direction ( In the portions where the refrigerant passages 19 and 20 are formed), a state where there is no contact portion as shown in FIG. However, according to the present embodiment, due to the formation of the small projections 14a, FIGS.
As shown in (1), the contact portions between the small projections 14a can be formed even in the intermediate portion in the longitudinal direction.

Thus, the pressing force acts on the intermediate portion (the portion where the refrigerant passages 19 and 20 are formed) of the heat transfer plate 12 except for the tank portions 15 to 18 at both ends in the longitudinal direction. The entire board portions 13 can be reliably brought into contact with each other, and the contact surfaces of the board portions 13 can be satisfactorily brazed. Therefore, leakage of the refrigerant from the refrigerant passages 19 and 20 due to poor brazing can be prevented.

Incidentally, each of the heat transfer plates 12a to 12c
In the width direction (air flow direction A), a plurality of protrusions 1
As shown in FIG. 6 (c), the projections 140 of the fourth and the second and third heat transfer plates 12b and 12c are used to detect the internal leakage. And the formation position is shifted, so that each protruding portion 14, 140 is adjacent to each heat transfer plate 1.
It can be located at the concave portion formed by the substrate portion 13 of 2a to 12c.

As a result, a gap is always formed between the convex tops of the protruding portions 14 and 140 and the concave portions of the substrate portion 13 of the adjacent heat transfer plates 12a to 12c. This gap is a gap size minus the plate thickness minutes from launch height h of the protrusions 14 is, by this clearance, as the entire length of the heat transfer plate width direction (air flow direction A) of the arrow A ₁ An air passage meandering in a wave shape is continuously formed.

[0081] Thus, the conditioned air is blown in the direction of arrow A, the air passage arrow A ₁ in as the two while meandering in the corrugated heat transfer plates 12a, 12b or 12a, 1
2c.

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 to 12c
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 shown in FIGS. 1 and 2 has a refrigerant inlet hole 21a and a refrigerant outlet hole 21b near the lower end thereof. 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, it is made of a double-sided clad material in which an A4000-based aluminum brazing material is clad on both sides of an A3000-based aluminum core like the heat transfer plates 12a to 12c. 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 to 12c,
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 and right direction (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 sections 15 to 18 located at both upper and lower ends of the evaporator 10, the tank section 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 coolant outlet side tank portion 18 on the windward side is also partitioned by the partition portion 28 disposed at the intermediate position with the left channel in FIG. 2 (the channel in the region X side) and the right channel 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 an arrow b in the refrigerant passage 19 formed by the leeward projection 14 of the heat transfer plates 12a and 12b, and the upper inlet side tank 15 to go into. Next, the refrigerant moves the upper inlet side tank portion 15 to the right side area Y in FIG.
And moves down the refrigerant passage 19 formed by the leeward projections 14 of the heat transfer plates 12a and 12c 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 between the tank portions 16 and 18 is provided at an intermediate position between the tank portions 16 and 18 below the third heat transfer plate 12c incorporated in the right side region 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 area Y of the tank portion 18, the refrigerant is supplied to the windward projecting portions 1 of the heat transfer plates 12a and 12c.
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 thereafter 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, two adjacent heat transfer plates 12a, 12b or 12a, 12a on the longitudinally joined surfaces of the heat transfer plates 12a to 12c.
The small projections 14a of FIG. 3c are brought into contact with each other (see FIGS. 6A and 6B), and the pressing force in the heat transfer plate stacking direction is applied to the contact portions of the small projections 14a by the jig. Thus, the heat transfer plates 12a to 12c can be joined to each other.

Thus, the heat transfer plates 12a to 12c
Among these, the pressing force acts on 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 portion 1 of the heat transfer plates 12a to 12c is acted upon.
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.

By the way, in order to find out a product defect due to refrigerant leakage, a refrigerant leakage inspection of the evaporator 10 is performed. For example, the inspection is carried out by bringing the evaporator 10 after brazing into a closed room, Pipe 23 and refrigerant outlet pipe 2
4 is closed with an appropriate blind lid, and a leakage test fluid (for example, helium gas) is pressurized to a predetermined pressure from the other pipe and supplied to the refrigerant passage in the evaporator 10, so that the leakage to the outside of the evaporator 10 is prevented. Inspect for fluid leakage (fluid leakage into a closed chamber).

At this time, in the evaporator 10 to be inspected, if there is any brazing failure in the outer peripheral joint surface among the joint surfaces between the substrate portions 13 of the heat transfer plates 12a to 12c, this outer peripheral Since the test fluid leaks directly to the outside from the connection failure portion of the portion, the connection failure of the outer peripheral portion can be easily detected.

On the other hand, among the substrate portions 13 of the heat transfer plates 12a to 12c, the substrate portion 1 located at the central portion in the width direction.
If a joint failure occurs at the joint surface of No. 3, an internal leak state occurs in which the inlet-side refrigerant passage 19 on the leeward side and the outlet-side refrigerant passage 20 on the leeward side are in direct communication. However, the test fluid does not leak to the outside only when this internal leak condition occurs.

Therefore, in this embodiment, on the side of the second and third heat transfer plates 12b and 12c to be combined with the first heat transfer plate 12a, a protrusion for detecting internal leakage is provided at the center in the width direction of the substrate portion 13. In the second heat transfer plate 12b, both ends 140a of the plate 140 in the longitudinal direction of the plate are formed.
It is open to the outside at 140b. In the third heat transfer plate 12c, the internal leak detection passage 141 inside the protrusion 140 is opened to the outside at the upper end 140a.

For this reason, when the state of internal leakage occurs, the test fluid leaks to the outside through the internal leakage detection passage 141 inside the protruding portion 140, so that internal leakage can be easily detected.

Next, the operation of the evaporator 10 according to 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 reduced in pressure 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 12a to 12
6 (c) over the entire length in the width direction of the heat transfer plate (the air flow direction A) due to the gap formed between the protrusions 14 and 140 protruding to the outer surface side of the substrate c and the substrate portion 13.
Air passage meandering in a wave as indicated by arrow A ₁ in are formed continuously.

[0105] As a result, conditioned air, between the two heat transfer plates 12a and 12b while meandering the air passage in a wave as indicated by arrow A ₁ or 12 that is blown in the direction of arrow A
a and 12c, and the refrigerant absorbs latent heat of vaporization and evaporates from the flow of the air, so that the conditioned air is cooled and becomes 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 corresponds to the protrusions 14, 14 of the heat transfer plates 12a to 12c.
0 (a refrigerant flow direction B in the refrigerant passages 19 and 20).
140 forms a convex surface (heat transfer surface) that projects orthogonally to the air flow, so that air is projected to the projecting portion 1 that extends orthogonally.
The straight shape is prevented by the convex shape of 4,140.

For this reason, the air flow is controlled by the heat transfer plates 12a to 12a.
The gap between 12c form a flow meandering in a wave as indicated by the arrow A ₁ in FIG. 6 (c), the so disturb the flow, the air flow becomes turbulent, leap heat transfer rate on the air side Can be improved. Here, since the core portion 11 is constituted only by the heat transfer plates 12a to 12c, 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, and the required cooling performance can be secured. is there.

According to the present embodiment, the communication passage 120 is formed at a middle position between the tank portions 16 and 18 below the third heat transfer plate 12c 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 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 to 12c corresponds to the vertical direction as shown in FIGS. It is arranged and actually used. Therefore, in the use state of the evaporator 10, a gap (see FIG. 6) extending in the longitudinal direction (vertical direction) can be continuously formed between the heat transfer plates 12a to 12c.
As a result, condensed water generated on the surfaces of the heat transfer plates 12a to 12c can be smoothly dropped downward along the vertically extending gap.

A part of the condensed water tends to move to the leeward side due to the wind pressure of the blown air. On the leeward side of the tank section 15, 1
6 is reduced by a predetermined dimension L. 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 portion 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 to 12c can be effectively prevented by the decrease in the air flow velocity. Can be suppressed.

Next, the relationship between the specific design example of the heat exchanger and the heat transfer performance in the present embodiment will be described. FIG. 8 shows the heat exchanger heat transfer performance index “air-side heat transfer coefficient αa and placed vertically the product "on the air side heat transfer area Fa, taking a protrusion pitch P ₁ in the horizontal axis. Here, the protruding portion pitch P ₁ is the plurality of protrusions 14 mutual distance as shown in FIG. 6 (c) (distance between the projecting portion 14 in the air flow direction A). The refrigerant passage in the heat transfer plate laminating direction as passages pitch P ₂ shown in FIG. 8 are shown in FIG. 6 (c) 1
9, 20 (interval between heat transfer plates).

As shown in FIG. 8, the protrusion pitch P ₁
And the change in the combination of the passage pitch P _2, heat transfer performance (the product of the αa and Fa on the vertical axis) is changed.
Here, the relationship between the protrusion pitch P ₁ and the air-side heat transfer coefficient .alpha.a, the smaller the P _1, are in a relationship .alpha.a increases. This is because if P ₁ decreases, the number of protrusions 14 can be increased, so that in the air flow direction A, a portion having high heat transfer due to flow turbulence can be increased, and as a result, the heat exchanger as a whole The air-side heat transfer coefficient αa can be improved. However, the smaller the other hand P _1, so that the pressure loss on the air side is increased.

Further, as for the passage pitch P ₂ , the smaller the value of P ₂ , the more the number of heat transfer plates stacked in the same heat exchanger body (capacity) can be increased, so that the air side heat transfer area Fa can be increased. However, the smaller the other hand P _2, so that the pressure loss on the air side is increased.

FIG. 8 shows the result of calculation by computer simulation. The premise is that the air flow rate at the inlet of the heat exchanger is 2 m / s and the pressure loss on the air side is 100 Pa (constant). Projection pitch P ₁
It has set up a passage pitch P ₂ and.

The thickness t of the heat transfer plates 12a to 12c is determined according to the internal fluid (refrigerant) pressure, corrosion resistance, press-forming formability, material, and the like, and cannot be unconditionally determined. Therefore, in FIG. 8, the plate thickness t is used as a parameter, and the plate thickness t is changed in a range of 0.1 mm to 0.35 mm.

According to the calculation result of FIG. 8, the passage pitch P ₂
= When varied from 1.47Mm～3.82Mm, protrusion pitch P ₁ of the heat transfer performance becomes highest 2.48
It can be seen that the distance increases from 18 mm to 18.39 mm.

[0119] When the prerequisite of pressure loss = constant air side, protrusion pitch P ₁ by increasing the passage pitch P ₂
The than smaller, better to increase the protrusion pitch P ₁ by reducing the passage pitch P ₂ is found to be advantageous for the heat transfer performance improvement.

[0120] From the data of FIG. 8, a schematic for protrusion pitch P _1, by setting the range of 2 mm to 20 mm, it is found that can effectively improve the heat transfer performance in various channel pitch P _2. Further, schematic for passage pitch P _2, by setting the range of 1.4Mm～3.9Mm, while suppressing an increase in pressure loss on the air side, it can be seen that improved heat transfer performance. The gap between the heat transfer plates constituting the air passage is the passage pitch P ₂ × 1 / 2−
Since the plate thickness is t, approximately 0.7 mm to 1.95 mm is a suitable range.

In the conventional ordinary corrugated fin type heat exchanger, since the corrugated fin is interposed between the tubes, the height of the tank at the end of the tube (the dimension corresponding to h in FIG. 7) is 5 mm. This is necessary. Therefore,
In the conventional heat exchanger, when the aluminum plate material for a tube is press-formed, a large elongation is required for forming the above-mentioned tank portion. Therefore, an O material having good elongation (soft) is used as the aluminum plate material for a tube. I was

Here, the O material of the aluminum alloy is
An aluminum material specified in “JIS H 0001”, which is in the softest state by annealing and has a much higher elongation rate than the H material.

However, the good elongation of the O material is that the core material of the aluminum plate material is partially thinned due to the erosion (erosion) of the brazing material clad on the surface of the aluminum plate material for tubes, and the corrosion resistance is reduced. It has been known. As a result, in consideration of this reduction in corrosion resistance, conventionally, a thick aluminum plate (for example, 0.6 mm or more) has been used as an aluminum plate for a tube.

In order to prevent the erosion of the brazing material, a hard material (H material) having a small elongation may be used as the aluminum plate material. There is a problem that cracks occur.

The H material of the aluminum alloy is a material that is hardened by work hardening and has a small elongation. Specifically, H1, H2, H3, and the like specified in “JIS H 0001” are used. In addition, since H112 is a wrought material, work hardening occurs in the wrought process itself, so that it is not necessary to specifically perform a work hardening process after the wrought process.

According to the heat exchanger of the present embodiment, since the heat exchanger plates 12a to 12c can be simply laminated without interposing corrugated fins, the height h of the tank portions 15 to 18 can be increased by the protrusions 14, 140. Can be set to 2 mm or less similarly to the height h of the heat transfer plate 12a.
Even when an H material having a small elongation is used as the aluminum plate material constituting the aluminum plates 12 to 12c, the elongation at the time of press forming necessary for forming the tank portions 15 to 18 can be secured.

Therefore, even if H material is used, the tank parts 15 to 15
The heat transfer plates 12a-
12c can be press-molded to a required shape. Therefore, as shown in FIG. 8, the thickness t of the heat transfer plates 12a to 12c is made significantly thinner than in the prior art (t = 0.1 to 0.35 mm).
Even so, corrosion resistance can be ensured and the weight of the heat exchanger can be reduced.

(Second Embodiment) In the first embodiment,
The protrusions 14 of the first to third heat transfer plates 12a to 12c are formed so as to extend continuously in a direction substantially orthogonal 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 the second embodiment, as shown in FIGS. 9 to 14, a large number of independent protruding portions 14 extend obliquely at a predetermined angle θ (FIG. 10) with respect to the flow direction A of air (external fluid). It is formed in a slender projecting shape, and at the overlapping portions of the oblique projecting portions 14, the internal spaces of the many projecting portions 14 are communicated with each other to form refrigerant passages (internal passages) 19, 20.
To form

In FIG. 11, an arrow B ₁ indicates a refrigerant flow in the leeward refrigerant passage 19, and an arrow B ₂ indicates a refrigerant flow in the leeward refrigerant passage 20. Air (external fluid), as indicated by an arrow A ₂ in FIG. 11, with meandering in the plane direction of the heat transfer plate 12 (vertical direction in FIG. 11),
Also meander in the laminating direction of the heat transfer plate 12 (vertical direction in FIG. 13) as indicated by the arrow A ₁ in FIG. 13.

In the second embodiment, a concave side plate 25 is arranged outside the end plate 22,
A refrigerant passage 26 (FIG. 14) is formed between the side plate 25 and the end plate 22, and the refrigerant passage 26 communicates between the communication holes 22 a and 22 b of the end plate 22. The refrigerant passage of the entire evaporator in the second embodiment is as shown in FIG. In the second embodiment, the same reference numerals are given to the same or equivalent parts as in the first embodiment, and the other description is omitted.

Also in the second embodiment, the protrusion pitch P
₁ (FIG. 10) and the passage pitch P ₂ (FIG. 12) have the same relationship as the heat transfer performance as in the first embodiment.
The dimension ranges of P ₁ and P ₂ described based on FIG. 8 can be similarly applied to the second embodiment.

(Third Embodiment) FIGS. 15 and 16 show a third embodiment and correspond to FIGS. 10 and 11 of the second embodiment. In the second embodiment, the heat transfer plate 12 Two rows of protrusions 14 provided before and after in the air flow direction A
Are inclined in the same direction, but in the third embodiment, the inclination directions of the two rows of protrusions 14 are opposite.
Other points are the same as the second embodiment.

(Fourth Embodiment) FIGS. 17 and 18 show a fourth embodiment and correspond to FIGS. 10 and 11 of the second embodiment. In the second and third embodiments, the heat transfer plate is used. 1
2, two rows of protrusions 14 provided before and after the air flow direction A are inclined at a predetermined angle θ with respect to the air flow direction A. However, in the third embodiment, the two rows of protrusions 14 are Are arranged orthogonally to. 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 the fourth embodiment, the elongated projections 14 parallel to the longitudinal direction of the heat transfer plate 12 (refrigerant flow direction B) are arranged in a staggered manner so that two concave surfaces are joined. In one set of the heat transfer plates 12, as shown in FIG. 18, a partially overlapped portion is set between the elongated projections 14 to form the refrigerant passages 19 and 20. Therefore, according to the present example, the refrigerant flows in parallel with the longitudinal direction of the heat transfer plate 12 over the entire length of the refrigerant passages 19 and 20.

(Fifth Embodiment) FIGS. 19 and 20 show a fifth embodiment, corresponding to FIGS. 10 and 11 of the second embodiment, and are modified examples of the fourth embodiment. That is, of the two rows of protrusions 14 provided in the heat transfer plate 12 before and after in the air flow direction A, one of the protrusions 14 is arranged orthogonal to the air flow direction A, and the other protrusion 14 is It is arranged 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.

(Sixth Embodiment) FIG. 21 shows a sixth embodiment, and the flow direction A of the conditioned air is opposite to that of FIG. 9 showing the second embodiment. In the second embodiment, FIG.
As shown in the figure, the refrigerant inlet pipe 23 and the refrigerant outlet pipe 24 are independently joined to the left end plate 21. In the sixth embodiment, the refrigerant inlet pipe 23 and the refrigerant outlet pipe 24 are connected to one pipe joint block. 3
0.

For this purpose, in the sixth embodiment, as shown in FIG. 21, a side plate 31 is joined to the left end plate 21, and between the two plates 21, 31 the refrigerant inlet / outlet of the piping joint block 30 is provided. It constitutes a refrigerant passage communicating therewith. This refrigerant passage configuration will be described more specifically. The end plate 21 has a communication hole 21a communicating with the communication hole 15a of the refrigerant inlet side tank portion 15 below the heat transfer plate 12, and an upper refrigerant outlet side tank. Part 18
A communication hole 21b communicating with the communication hole 18a is formed.

The side plate 31 is the end plate 2
A3000 similar to 1,22 and side plate 25
It is made of a double-sided clad material in which an A4000-based aluminum brazing material is clad on both surfaces of a system-based aluminum core material, and has a plate thickness t larger than that of the heat transfer plate 12 (for example,
(Thickness t = about 1.0 mm) to improve the strength.

Further, the pipe joint block 30 is formed by integrally molding the refrigerant inlet pipe 23 and the refrigerant outlet pipe 24 with, for example, A6000 aluminum bare material. It is arranged on the upper side and joined.

In the side plate 31, a protruding portion 31a is stamped outward from the portion of the pipe joint block 30 to the lower side, and the upper and lower ends of the protruding portion 31a merge into one. , A plurality of sections in the vertical direction (plate longitudinal direction) (three in the illustrated example)
To increase the section modulus of the side plate 31 to increase the strength. The upper end of the refrigerant passage formed by the recess inside the protruding portion 31a communicates with the refrigerant inlet pipe 23 of the piping joint block 30, and the lower end of the refrigerant passage communicates with the communication hole 21a of the end plate 21.
Communicate with

One protruding portion 31b is formed on the side plate 31 above the piping joint block 30 by stamping outward. The refrigerant passage formed by the concave portion inside the protruding portion 31b connects the refrigerant outlet pipe 24 and the communication hole 21b of the end plate 21.

According to the sixth embodiment, the refrigerant inlet pipe 2
3 and the refrigerant outlet pipe 24 are collectively provided in one piping joint block 30, so that the evaporator 10
The piping arrangement with the external refrigerant piping is improved.

(Seventh Embodiment) FIGS. 22 to 25 show a seventh embodiment. In the first to sixth embodiments, tanks are provided at both ends of the heat transfer plate 12 in the longitudinal direction. Each of the two tanks 15 to 18 is provided in total (four in total). However, in the tanks 15 to 18, the heat transfer area between the air and the refrigerant is extremely reduced.
18 are dead spaces that hardly contribute to improving the cooling performance of the evaporator 10.

Thus, in the seventh embodiment, the tank portions 16 and 18 are provided only at one end in the longitudinal direction of the heat transfer plate 12 and the tank portions 15 and 17 at the other end are eliminated, so that the It is intended to reduce the size of the evaporator 10 while reducing the dead space by half and maintaining the cooling performance of the evaporator 10.

That is, in the seventh embodiment, as shown in FIGS. 22 to 24, the tank portions 16 and 18 are provided only at one end (upper end) in the longitudinal direction of the heat transfer plate 12, and the other end ( In the lower end portion), the tank portions 15 and 17 are eliminated, and instead, the protruding portion 14 is formed near the edge of the other end portion. Here, at the other end of the heat transfer plate 12, the U-turn portions D of the two rows of refrigerant passages 19 and 20 before and after the air flow direction A are provided.
To form (FIG. 25), the protrusions 14 are continuously formed in both the upstream and downstream regions of the air flow in the air flow direction A of the heat transfer plate 12.

As a result, the lower region F in FIGS.
, Two rows of refrigerant passages 19 before and after the air flow direction A,
Twenty U-turn portions D can be configured.

In the seventh embodiment, the protrusion 14
The formation of the two rows of refrigerant passages 19 and 20 is the same as that of the second embodiment, and the description thereof is omitted. Only the differences will be described below. In the seventh embodiment, one end of the heat transfer plate 12 in the stacking direction is provided. The refrigerant outlet pipe 24 is joined to the end plate 21 located on the side of the heat transfer plate, and the refrigerant inlet pipe 23 is connected to the end plate 22 located on the other end side in the heat transfer plate stacking direction.
Are joined.

The refrigerant outlet pipe 24 is connected to one end of the upper air upstream tank 18, and the refrigerant inlet pipe 23 is connected to the other end of the upper air upstream tank 18. Therefore, on the right end plate 22,
A communication hole 22c for communicating the refrigerant inlet pipe 23 with the upper air upstream tank portion 18 is provided. A similar communication hole (not shown) is also formed in the left end plate 21.

As shown in FIG. 25, by arranging a partition portion 27 at an intermediate position of the upper air upstream tank portion 18, two rows of refrigerant passages 19 and 20 which make a U-turn around the air flow direction A are formed. it can.

As shown in FIG. 24, the projecting portions 14 in the lower end region F of the heat transfer plate 12 form the U-turn portions D of the two rows of refrigerant passages 19 and 20 before and after the air flow direction A. In the lower end region F of the heat transfer plate 12, a heat exchange region having a high heat transfer rate due to turbulent air flow can be formed up to near the edge.

(Eighth Embodiment) FIG. 26 shows an eighth embodiment in which only the heat transfer plate 12 having the protrusions 14 constituting the refrigerant (internal fluid) passages 19 and 20 is characterized by the present invention. The evaporator 10 is formed in a different shape other than the usual rectangular parallelepiped by effectively utilizing the fact that it is not necessary to provide a fin member on the air (external fluid) side.

FIG. 26 shows a vehicle air conditioning unit 100 in which an evaporator 10 as a cooling heat exchanger and a heater core 102 as a hot water heat source as a heating heat exchanger are installed in an air conditioning case 101. . The ratio of the warm air G passing through the heater core 102 and the cool air H bypassing the heater core 102 is adjusted by the film door 103 for air mixing to adjust the temperature of the air blown out of the face and the defroster.

The face blowout opening 104, the defroster blowout opening 105, and the foot blowout opening 106
Is switched by the blow-out mode film door 107.

In such an air conditioning unit 100,
The form of the evaporator 10 is usually a rectangular parallelepiped as shown in FIG. This is one of the flat tubes 11a and the corrugated fins 11b that constitute the heat exchange core portion 11.
Because of the reason why the outer shape of the corrugated fin 11b is formed (the reason that the thin coil material is formed into a corrugated roller), FIG.
It is difficult to make the shape other than the rectangular shape shown in FIG. 8, and as a result, the shape of the evaporator 10 necessarily becomes a rectangular parallelepiped shape along the rectangular shape of the corrugated fin 11b.

However, according to the present invention, since no fin member such as the corrugated fin 11b is required, in the eighth embodiment, the evaporator 10 has a different shape along the extra space in the air-conditioning case 101. , Air conditioning case 1
01 can be utilized to the maximum extent to improve the performance of the evaporator 10.

This point will be described in detail with reference to FIG. 26. Focusing on the fact that a large excess space exists on the upstream side of the air flow of the air mix film door 103, the core 11 of the evaporator 10 is moved downstream of the air flow. It protrudes in a triangular shape toward the side (toward the air mix film door 103 side). Numeral 11 'denotes a triangular projection, which constitutes a heat transfer expansion section.

In the case of the conventional ordinary evaporator 10 shown in FIG. 27, the volume shown by the broken line I in FIG. 26 is obtained. However, according to the eighth embodiment, the volume of the core portion 11 of the evaporator 10 is made triangular. It can be increased by the shape of the protruding portion 11 ', and the performance of the evaporator 10 can be improved.

(Ninth Embodiment) FIGS. 29 and 30 show a ninth embodiment in which the drainage of condensed water generated by the cooling and dehumidifying action of the evaporator 10 is improved.

According to the experimental study of the present inventors, in the second embodiment shown in FIGS. 9 to 14, the convex surfaces of the projecting portions 14 of the heat transfer plate 12 abut against each other while being inclined in the opposite direction and crossing each other. And the contact portions are joined. Therefore, in the second embodiment, as shown in FIG. 31, the condensed water tends to stay near the abutting portions of the protruding portions 14, and a part of the air-side passage is formed by the staying of the condensed water. It was found that the airflow was blocked and the ventilation resistance increased.

Therefore, in the ninth embodiment, the abutting portions of the protruding portions 14 between the convex surfaces are eliminated to facilitate the fall of the condensed water,
This suppresses an increase in ventilation resistance due to stagnation of condensed water.

Since the entire structure of the refrigerant passage of the evaporator 10 in the ninth embodiment is the same as that of the sixth embodiment in FIG. 21, the same parts in FIG. 29 as those in FIG. Omitted. The shape of the protrusion 14 of the heat transfer plate 12 in the ninth embodiment is the same as that of the first embodiment, and the shape of the protrusion 14 of the heat transfer plate 12 is changed to a straight line along the plate longitudinal direction (vertical direction). Shape.

The evaporator 10 according to the ninth embodiment is different from the evaporator 10 shown in FIG.
As shown in FIGS. 9 and 30, the heat transfer plate 12 is arranged and used in the longitudinal direction so as to be actually used. In the use state, when the blown air passes through the air passage between the two heat transfer plates 12 while meandering in a wavy shape as shown by an arrow A ₁ , heat exchange between the blown air and the heat transfer plate 12 is performed. The condensed water (see FIG. 30) generated at the top of each projection 14 is generated most.

The state of generation of this condensed water has been experimentally confirmed. The top of the convex surface of each projection 14 is cooled best by the latent heat of evaporation of the refrigerant passing through the refrigerant passages 19 and 20, and as a result, It is considered that the largest amount of condensed water is generated at the top of the convex surface.

The convex top of each protrusion 14 faces the adjacent heat transfer plate 12 with an air gap therebetween, and does not form a joint at the entire vertical length. There is no place where condensed water stays in the middle of the convex top. Similarly, there is no remaining portion of the condensed water in other portions of the heat transfer plate 12 (the side surface of the protrusion 14 and the surface of the substrate 13).

As a result, the entire condensed water generated on the surface of the heat transfer plate 12, including the condensed water generated at the top of the convex surface of each protrusion 14, is transferred along the longitudinal direction of the heat transfer plate 12, ie, along the vertical direction. Can be smoothly dropped downward. Thus, it is possible to favorably suppress an increase in the ventilation resistance due to the accumulation of the condensed water.

The specific configuration of the ninth embodiment will be described.
A large number of heat transfer plates 12 are press-formed into basically the same shape. Then, a plurality of protrusions 14 extending continuously and parallel to the longitudinal direction (in other words, the direction perpendicular to the air flow direction A) of the heat transfer plate 12 are formed by punching out a plurality of the flat substrate portions 13 in this example, six in this example. ing.

Here, the projecting portion 14 has a substantially rectangular cross section, and the ejection height is the same as the height of the tank portions 15 to 18 located at both ends in the longitudinal direction of the heat transfer plate 12. In FIG. 30, the left heat transfer plate 12
The upper end of the group illustrates the cross-sectional shape.

As shown in FIG. 30, the plurality of protrusions 14
The heat transfer plate 12 is not bilaterally symmetric with respect to the center position in the width direction (air flow direction A), but is displaced from the center in the width direction.

For this reason, the convex surfaces of the projecting portions 14 of the two heat transfer plates 12 are directed outward from each other.
When the protrusions 14 of the two heat transfer plates 12 are arranged so as to be shifted from each other in the plate width direction (air flow direction A), and the substrate portions 13 of the two heat transfer plates 12 abut on each other, each protrusion The other heat transfer plate 12 adjacent to the portion 14
Is located at a concave portion formed by the substrate portion 13 of the second substrate.

As a result, a gap is always formed between the top of the convex surface side of each projection 14 and the concave surface of substrate portion 13 of another adjacent heat transfer plate 12. This gap is a gap corresponding to the launch height of the protruding portion 14, and as shown in FIG. 30, an air passage meandering continuously in a wavy shape over the entire length of the heat transfer plate 12 in the width direction (air flow direction A). It is formed.

[0173] Thus, the air blown from the arrow A, can pass between the two heat transfer plates 12 while meandering in a wave as the air passage A _1.

On the other hand, the substrate portion 1 of the two heat transfer plates 12
When the three members are brought into contact with each other and joined, the inner surface of each protrusion 14 is sealed by the substrate 13 of the heat transfer plate 12 on the other side, so that the inner surface of each protrusion 14 and the heat transfer plate 12 on the other side are sealed. Refrigerant passages 19 and 20 can be formed between the substrate and the substrate 13. Here, the refrigerant passage 19 is a refrigerant passage on the downstream side of the air that communicates between the tank portions 15 and 16 on the downstream side in the air flow direction A, and the refrigerant passage 20 is a tank portion on the upstream side in the air flow direction A. This is a refrigerant passage on the upstream side of the air, which communicates between the ports 17 and 18.

(Tenth Embodiment) FIGS. 32 and 33 show a tenth embodiment.
This is an embodiment of the present invention for improving the workability of the heat transfer plates 12a to 12c and the heat transfer plate 12 in the first and ninth embodiments. That is, the tenth
In the embodiment, paying attention to the fact that the shape of the protruding portion 14 of the heat transfer plate 12 is a linear shape along the plate longitudinal direction (vertical direction), an aluminum material (an aluminum bare material having no brazing material clad) is used. ) By extrusion
The heat transfer plates 12 are formed with protrusions 14 protruding on both sides in the heat transfer plate stacking direction, and the refrigerant passages 19 and 20 are formed by the hole shapes in one heat transfer plate 14. is there.

Specifically, the heat transfer plate 12 is formed by extruding the projecting portions 14 projecting from the substrate portion 13 on both front and rear sides (both sides in the heat transfer plate stacking direction) from the substrate portion 13 linearly over the entire length in the heat transfer plate longitudinal direction. Has formed. The projecting portions 14 are shifted from each other on both the front and back sides of the substrate portion 13 so that each projecting portion 14 is located within the concave surface of the adjacent heat transfer plate 12 formed by the substrate portion 13. Each of the refrigerant passages 19 and 20 has a linear hole shape formed over the entire length in the longitudinal direction of the heat transfer plate inside the portion where the protrusion 14 is formed.

The distance between the multiple heat transfer plates 12 is
It is held by interposing spacer members 32 arranged at both upper and lower ends in the longitudinal direction of the heat transfer plate. The spacer member 32 is a member formed by press-forming so as to have an uneven shape corresponding to the uneven shape of the interval between the heat transfer plates 12.
000 series clad aluminum clad material.

As shown in FIG.
Is divided into an upstream plate and a downstream plate in the air flow direction A, and the upper and lower ends of the heat transfer plates 12, 12 which are divided into two parts are respectively formed on the downstream side and the air formed separately. Tank members 33, 3 on the air upstream side
The upper and lower ends of the heat transfer plates 12 and 12 communicate with the internal spaces of the tank members 33 and 34, respectively.

The tank members 33 and 34 are also made of a double-sided clad material in which an A4000-based aluminum brazing material is clad on both sides of an A3000-based aluminum core material.
The connection between the refrigerant passages 19 and 20 is performed in the same manner as in the tank portions 15 to 18 of the second embodiment. The configuration of the refrigerant passage as the entire evaporator 10 is the same as that of the sixth embodiment of FIG.

In the tenth embodiment as well, except for the positions of the spacer members 32 at the upper and lower ends, the convex tops of the projections 14 extend over the entire length in the vertical direction of the heat transfer plate 12 at the other portions. Since no contact portion is formed, the same good drainage as in the eighth and ninth embodiments can be exhibited.

Further, since the required shape of the heat transfer plate 12 can be processed in one step by extruding aluminum, the number of processing steps for the heat transfer plate 12 can be greatly reduced as compared with press forming. Furthermore, since the refrigerant passages 19 and 20 are formed by holes formed in the portions where the protrusions 14 are formed, the refrigerant passages 19 and 20 are configured as compared with the case where the refrigerant passages 19 and 20 are formed by joining two heat transfer plates 12. There is no worry about leakage due to poor bonding.

(Eleventh Embodiment) FIGS. 34 and 35 show an eleventh embodiment.
In this embodiment, the molding of the heat transfer plate 12 using the extrusion process according to the tenth embodiment is further advanced, and the required number of heat transfer plates 12 are all integrally formed.

That is, FIG. 34 shows a state immediately after the aluminum material is extruded in the eleventh embodiment. The extruded body 35 having a substantially rectangular parallelepiped shape corresponds to the heat transfer plate 12 of the tenth embodiment. A plurality of heat transfer plates 12, projecting portions 14 protruding on both sides in the heat transfer plate stacking direction, refrigerant passages 19 and 20 formed by holes in each heat transfer plate 14, and located between the heat transfer plates 14. The gap 36 forming the air passage is integrally formed along the longitudinal direction of the rectangular parallelepiped.

In the state immediately after the extrusion, both ends of the gap 36 in the air flow direction A are closed by the outer edges 37 and 38 of the extruded body 35.
Does not function as an air passage.

Therefore, of the outer edges 37, 38 located at both ends in the air flow direction A, portions 39, 39a, 40, 40a shown by oblique lines in FIG. 34 are cut off by cutting or the like.
Both ends of the gap 36 in the air flow direction A are open to the outside. FIG. 35 shows the cut portions 39, 39a, 40, and 40.
After cutting a, the end of the gap 36 is open to the outside.

As shown in FIG. 35, this cut portion 39,
Since the cut portions 39a, 40, and 40a are divided into a plurality in the longitudinal direction of the rectangular parallelepiped, a plurality of cut portions 39, 39a, and 4a are formed.
The narrow connecting portions 41 and 42 remain between 0 and 40a,
The connecting portions 41 and 42 maintain the integrally formed state of the large number of heat transfer plates 12. Thereby, the spacer members 3 at the upper and lower ends in the tenth embodiment are formed.
2 becomes unnecessary.

Holding plates 44 and 45 having slits 43a into which the upper and lower ends of each heat transfer plate 14 can be inserted are fitted into the cut portions 39a and 40a at the upper and lower ends of the substantially rectangular extruded body 35. Be placed. Further, tank members 46, 47 are assembled to the upper and lower holding plates 44, 45.

The upper and lower holding plates 44 and 45 and the tank members 46 and 47 are all formed of aluminum, and the components are integrally joined by brazing.

In the example shown in FIG. 35, the refrigerant inlet pipe 23 is disposed in the upper tank member 46 and the refrigerant outlet pipe 24 is disposed in the lower tank member 47. Are distributed to the refrigerant passages 19 (20) by the hole shape in each heat transfer plate 14 by the tank member 46 of FIG. The refrigerant passages 1 in each heat transfer plate 14
The refrigerant having passed through 9 (20) gathers in the lower tank member 47 and flows out from the refrigerant outlet pipe 24 to the outside.

(Twelfth Embodiment) FIGS. 36 to 38 show a twelfth embodiment.
This is an embodiment, in which the form of forming the heat transfer plate 12 and the method of assembling the heat exchanger according to the first to ninth embodiments are changed.

In the first to ninth embodiments, between the two heat transfer plates 12a and 12b, or between the two heat transfer plates 12a and 12b.
2c, and two heat transfer plates 12, 12
Although the refrigerant passages (internal fluid passages) 19 and 20 are formed between the heat transfer plates 12a to 12c, the present invention does not use thin fin members. Since the heat exchanger can be constituted by the joints of 12, 12, not only two heat transfer plates, but also the necessary number of heat transfer plates in the region X or the region Y, and also the necessary number of heat transfer plates in the entire heat exchanger It is also possible to constitute the heat transfer plate from the bent shape of one plate material.

The twelfth embodiment is based on such a concept, and the heat transfer plate 12 shown in FIG.
a and the heat transfer plate 12b shown in FIG.
Are made into one unit as a set of two sheets, and the required number of plate units of the set of two sheets are integrally connected via a connection portion 48 having a smaller width.

Then, the heat transfer plates 12a and 12b are bent in the direction of arrow a at the center 50 so that the protruding surfaces of the protruding portions 14 face outward and the substrate portions 13 and 13 contact each other. To Further, the connecting portion 48 is bent in the direction of the arrow b (the direction opposite to the direction of the arrow a) at the base portions 51 and 52 at both ends thereof, thereby forming the heat transfer plates 12a and 1a.
A gap (air passage) at a predetermined interval can be formed on the outer surface side of 2b. The cross-sectional views of FIGS. 37 and 38 show the cross-sectional shape after the bending.

In the field of heat exchangers, it is a well-known technique to form an internal fluid passage by bending a single plate material having a size and shape corresponding to two heat transfer plates. According to the present invention, as described above, one plate member is bent so that two heat transfer plates 12a and 1
2b, 12a and 12c and two heat transfer plates 1
Members corresponding to 2, 2 may be formed, and refrigerant passages (internal fluid passages) 19, 20 may be formed between the two bent heat transfer plates.

That is, in FIG. 36 of the twelfth embodiment, a pair of plate units is connected to the connecting portion 4 having a smaller width.
By stopping the required number of connections through the necessary number 8 through the joints 8, only the heat transfer plates 12a and 12b are integrally formed, and then bent at the center 50 of the heat transfer plates 12a and 12b in the direction of arrow a. 38, a pair of folded plate members shown in the cross-sectional view of FIG. 38 may be formed, and the required number of the plate folded members may be laminated and joined.

Therefore, the term “a plurality of heat transfer plates” in the present specification is not limited to the completely separated plurality of heat transfer plates disclosed in the first to ninth embodiments. A plurality of plates formed by bending a single heat transfer plate are used in the meaning.

Further, as in the eleventh embodiment, the connecting portion 4
The present invention also includes a structure in which a large number of heat transfer plates 12 are integrally connected by 1, 42. Therefore, in this specification, “plurality”, “two”, “plurality” relating to the number of plates are included.
The expression simply means that there are a plurality of heat transfer plates (plate-like members) 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.

(Thirteenth Embodiment) FIG. 39 shows a thirteenth embodiment. In the heat transfer plate 12 which is joined as a set of two sheets, the projecting portions 14, 14 and the substrate portions 13, 13 of each other. Are formed at the same position in the air (external fluid) flow direction A, and the positions of the protruding portions 14 and 14 and the substrate portions 13 and 13 are shifted from the pair of heat transfer plates 12 adjacent in the plate stacking direction. Thus, a meandering air passage is formed.

(Fourteenth Embodiment) In the first embodiment, the air-side heat transfer performance is influenced by the protrusion pitch P ₁ and the passage pitch P ₂ from the calculation results by the computer simulation shown in FIG. This indicates that there is an optimum range of the pitches P ₁ and P ₂ for the performance.

However, the heat exchanger of the present invention is not used for
When used as 0, it is necessary to consider not only the air-side heat transfer performance but also the refrigerant-side heat transfer performance. The smaller the protrusion pitch P _1, an increase in the number of refrigerant passages 19, 20 increases the refrigerant passage sectional area, the refrigerant flow rate decreases, but decreases the refrigerant-side heat exchange efficiency, the refrigerant-side heat transfer area To increase.

[0202] In contrast, increasing the protrusion pitch P _1, the number of refrigerant passages 19, 20 is reduced to decrease the refrigerant passage sectional area, the refrigerant flow rate is increased, thereby improving the refrigerant side heat exchange rate However, the refrigerant-side heat transfer area decreases.

That is, the increase / decrease of the protrusion pitch P ₁ is in a reciprocal relationship with the refrigerant-side heat exchange rate and the refrigerant-side heat transfer area, and there is an optimum range of the protrusion pitch P ₁ for the refrigerant-side heat transfer performance. I do.

Therefore, the heat exchanger of the present invention is used for the air-conditioning evaporator 1.
When used as 0, it is necessary to set the value of the protrusion pitch P ₁ in the form in consideration of the optimum range for the refrigerant-side heat transfer performance to the optimal range for the air-side heat transfer performance.

FIG. 40 shows the result of calculation by computer simulation performed by the inventor based on the above viewpoint, and the vertical axis represents the heat transfer performance (W) from the air side to the refrigerant side in the air-conditioning evaporator 10. Projection pitch P of horizontal axis
₁ is the same definition as in FIG. 8, and is the interval between the plurality of projections 14 (the interval between the tops of the projections 14 in the air flow direction A) as shown in FIG. Also, the passage pitch P ₂ has the same definition as that of FIG.
As shown in the figure, the refrigerant passage 1 in the heat transfer plate stacking direction
9, 20 (interval between heat transfer plates).

Here, the main conditions of the computer simulation will be described. The temperature of the inlet air of the evaporator 10 is 27 ° C., the relative humidity of the inlet air is 50%, the inlet air flow rate is 2 m / s, and the air Side pressure loss = 10
As will be 0 Pa (constant), it has set a protrusion pitch P ₁ and the passage pitch P _2.

Further, as the refrigerant side conditions, the outlet refrigerant temperature of the evaporator 10: 10 ° C., the outlet refrigerant pressure of the evaporator 10: 28
0 kPa (abs). The heat exchange part of the evaporator 10 has a physical size of 170 mm in the stacking direction of the heat transfer plates 12a to 12c (horizontal size in FIG. 1), 40 m in the width direction of the heat transfer plate (dimension in the direction of the arrow A in FIG. 1), Among the heat transfer plates 12a to 12c, the height dimension of the heat exchange portion (the height dimension of the portion where the plurality of protrusions 14 are formed) is 220 mm.

In FIG. 40, heat transfer plates 12a to 12a-1
The plate thickness t of 2c is determined by the refrigerant pressure inside the evaporator, corrosion resistance, formability of press working, material and the like,
I can't make a clear decision. For this reason, FIG. 40 shows, as a parameter of the plate thickness t, the protrusion pitch P ₁ at which the maximum performance is obtained at each plate thickness t.

From the calculation results shown in FIG. 40, the protrusion pitch P ₁
And by selecting a range of P ₁ = 5.92~7.73mm, it can be seen that the maximum performance of the evaporator 10 is obtained. Here, in the heat exchanger field, in practice, a performance difference of about 10% from the maximum performance is generally allowed. Therefore, the points at which the performance decreases by 10% from the maximum performance at each plate thickness t are plotted by the circles at the right end of each graph in FIG.

[0209] As can be understood from this ○ mark, by limiting the maximum value of the protrusion pitch P ₁ within 15 mm, can be exhibited more than 90% of the performance for the evaporator maximum performance (100%).

[0210] On the other hand, the minimum value of the protrusion pitch P _1, in order to prevent the refrigerant passage 19 gallery clogging during brazing, and the 2 mm. This protrusion pitch P
_Since the point where the minimum value of ₁ is 2 mm is closer to the pitch P ₁ where the maximum performance is higher than the maximum value, 90% or more of the maximum performance (100%) of the evaporator 10 is sufficiently exhibited. it can.

As described above, the protrusion pitch P ₁ = 2 to 15
By setting the thickness in the range of mm, it is possible to always exert 90% or more of the maximum performance of the evaporator (performance near the maximum performance) at each plate thickness t serving as a parameter.

(Other Embodiments) In each of the above embodiments, the flow direction A of the air (external fluid) is
The case where the coolant flow direction (plate longitudinal direction) B of 2a to 12c and 12 is set to be orthogonal to the heat transfer plate 12a has been described.
12c, 12 refrigerant flow direction (plate longitudinal direction) B
May be inclined by a predetermined angle with respect to the air flow (external fluid) flow direction A and the heat transfer plates 12a to 12a-1.
It suffices that the refrigerant flow direction (plate longitudinal direction) B of 2c and 12 intersects.

In each of the above embodiments, the low-temperature refrigerant on the low pressure side of the refrigeration cycle flows through the refrigerant passages (internal fluid passages) 19 and 20 of the heat transfer plate 12.
Although the case where the present invention is applied to the evaporator 10 which evaporates the refrigerant by absorbing the latent heat of evaporation of the refrigerant from the air-conditioned air while the conditioned air flows outside the above has been described, the present invention is not limited thereto. It is needless to say that the present invention is widely applicable to heat exchangers that perform heat exchange between fluids for various applications.

[Brief description of the drawings]

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

FIG. 2 is an exploded perspective view showing a refrigerant passage according to the first embodiment.

FIG. 3 is a plan view of a first heat transfer plate in the first embodiment.

FIG. 4 is a plan view of a second heat transfer plate according to the first embodiment.

FIG. 5 is a plan view of a third heat transfer plate in the first embodiment.

FIG. 6 is a sectional view taken along line AA, BB, and CC of FIG. 3;
It is sectional drawing which shows a cross section.

FIG. 7 is a cross-sectional view of a tank unit according to the first embodiment.

FIG. 8 is a graph showing a relationship between a protrusion pitch P ₁ and a passage pitch P ₂ and heat transfer performance.

FIG. 9 is an exploded perspective view showing a second embodiment.

FIG. 10 is a plan view of a heat transfer plate according to a second embodiment.

FIG. 11 is a plan view showing a superposed state of two heat transfer plates used in the second embodiment.

FIG. 12 is a sectional view taken along line XX of FIG. 11;

FIG. 13 is a sectional view taken along line YY of FIG. 11;

FIG. 14 is a schematic perspective view showing a refrigerant passage according to a second embodiment.

FIG. 15 is a plan view of a heat transfer plate used in the third embodiment.

FIG. 16 is a plan view showing a superposed state of two heat transfer plates used in the third embodiment.

FIG. 17 is a plan view of a heat transfer plate used in the fourth embodiment.

FIG. 18 is a plan view showing a superposed state of two heat transfer plates used in the fourth embodiment.

FIG. 19 is a plan view of a heat transfer plate used in the fifth embodiment.

FIG. 20 is a plan view showing a superposed state of two heat transfer plates used in the fifth embodiment.

FIG. 21 is an exploded perspective view showing a sixth embodiment.

FIG. 22 is an exploded perspective view showing a seventh embodiment.

FIG. 23 is a plan view of a heat transfer plate used in the seventh embodiment.

FIG. 24 is a plan view showing a superposed state of two heat transfer plates used in the seventh embodiment.

FIG. 25 is a schematic perspective view showing a refrigerant passage configuration according to a seventh embodiment.

FIG. 26 is a longitudinal sectional view of a vehicle air conditioning unit equipped with an evaporator according to an eighth embodiment.

FIG. 27 is a schematic perspective view of a normal evaporator as a comparative example of the evaporator according to the eighth embodiment.

28A is a front view of a corrugated fin used in the ordinary evaporator of FIG. 27, and FIG. 28B is a side view of FIG.

FIG. 29 is an exploded perspective view showing a ninth embodiment.

30 is an enlarged perspective view of a main part of FIG. 29.

FIG. 31 is an explanatory diagram of a falling state of condensed water in a comparative example (second embodiment) of the ninth embodiment.

FIG. 32 is an exploded perspective view showing a tenth embodiment.

FIG. 33 is an enlarged perspective view of a main part of FIG. 32;

FIG. 34 is a perspective view of an extruded product used in the eleventh embodiment.

FIG. 35 is an exploded perspective view showing an eleventh embodiment.

FIG. 36 is a plan view of the heat transfer plate used in the twelfth embodiment in a partially developed state.

FIG. 37 is a sectional view taken along line AA of FIG. 36.

FIG. 38 is a sectional view taken along line BB of FIG. 36;

FIG. 39 is an exploded perspective view showing a thirteenth embodiment.

FIG. 40 is a graph showing the relationship between the protrusion pitch P ₁ and the passage pitch P ₂ according to the fourteenth embodiment, and the evaporator heat transfer performance.

[Explanation of symbols]

12a to 12c, 12: heat transfer plate, 14: protrusion,
15-18: tank part, 19, 20 ... refrigerant passage (internal fluid passage).

Claims (29)

[Claims] A plurality of heat transfer plates (12a-12)
c, 12), a plurality of protrusions (14) are formed, and internal fluid passages (19, 20) through which an internal fluid flows are formed inside the protrusions (14). The convex top faces the adjacent heat transfer plates (12a to 12c, 12) with a gap interposed therebetween, and the heat transfer plates (12a to 12c, 1
In addition to forming a passage for the external fluid flowing on the outer side of 2), the protruding portion (14) functions as a turbulence generator for preventing the flow of the external fluid from going straight and causing turbulence. a heat exchanger, wherein the plurality of protrusions (14) are mutually spacing protrusion pitch (P ₁₎ was 2 to 20 mm. 2. A heat transfer plate (12a to 12c, 12).
A plurality of protrusions (14) forming internal fluid passages (19, 20) through which an internal fluid flows are formed, and a plurality of the heat transfer plates (12) are stacked and arranged to form a heat exchange core (11). The external fluid flowing outside the heat transfer plate (12) flows in a direction intersecting with the flow direction of the internal fluid, and the protrusion (14) prevents the flow of the external fluid from going straight. The heat generating means is adapted to function as a turbulence generator for causing turbulence, and the protrusion pitch (P ₁ ), which is an interval between the plurality of protrusions (14), is 2 to 20 mm. Exchanger. 3. The heat exchange according to claim 1, wherein a passage pitch (P ₂ ), which is an interval between the internal fluid passages (19, 20), is 1.4 to 3.9 mm. vessel. 4. The protrusion pitch (P ₁ ) = 10 to 20
mm, and the passage pitch (P ₂ ) = 1.4 to 2.3 m
The heat exchanger according to any one of claims 1 to 3, wherein m is set to m. 5. The heat exchanger according to claim 1, wherein the gap is set to 0.7 to 1.95 mm. 6. The plurality of heat transfer plates (12a-1)
2c, 12), the protrusions (1
The heat exchanger according to any one of claims 1 to 5, wherein the internal fluid passages (19, 20) are formed inside (4). 7. The heat transfer plates (12a to 12c, 1
The heat exchanger according to claim 6, wherein the plate thickness (t) of 2) is 0.1 to 0.35 mm. 8. The heat transfer plates (12a to 12c, 1
2), a small projection (14a) projecting from the side surface of the projecting portion (14) is formed, and the small projections (14a) of the heat transfer plates (12a to 12c, 12) are brought into contact with each other. 8. The heat exchanger according to claim 6, wherein the small protrusions (14 a) are joined to each other at abutment portions thereof. 9. 9. The heat transfer plates (12a to 12c, 1
The heat exchanger according to any one of claims 6 to 8, wherein 2) is formed of an H material of an aluminum alloy. 10. The plurality of heat transfer plates (12a to 12a).
12c, 12) has a substrate part (13) which is brought into contact with and joined to each other, and said protruding part (14) protrudes outward from said substrate part (13). Any one of 9
The heat exchanger according to any one of the above. 11. The protruding portion (14) in which a convex top portion of the protruding portion (14) is positioned on a concave portion formed by a substrate portion (13) of an adjacent heat transfer plate (12a to 12c, 12). Of the adjacent heat transfer plate (1
The heat exchanger according to claim 10, wherein the heat exchanger faces the concave portions of 2a to 12c and 12) at predetermined intervals. 12. The heat transfer plate (12a to 12c,
12), a pair of two heat transfer plates (12a to 12c, 12) are brought into contact with each other so that the protrusions (14) face outward from each other. The internal fluid passages (19,
20) is one of the heat transfer plates (12a to 12c, 12)
And the other heat transfer plate (12).
The heat exchanger according to claim 10, wherein the heat exchanger is configured to be provided between the heat exchanger and a substrate part (a). 13. The pair of heat transfer plates (12a to 12c, 12a to 12c,
The heat exchanger according to claim 12, wherein a plurality of sets of (12) are laminated and joined. 14. The heat transfer plate (12a-12c,
12) The tank portion (15-1) having communication holes (15a-18a) at both ends in the flow direction of the internal fluid.
8), and connecting the internal fluid passages (19, 20) formed in the plurality of sets of heat transfer plates (12a to 12c, 12) with the tank portions (15 to 18). The heat exchanger according to claim 13, characterized in that: 15. The internal fluid passage (19, 20)
The heat transfer plates (12a to 12c, 12) are independently formed before and after in the flow direction (A) of the external fluid, and the tank portions (15 to 18) are formed with the two independent internal fluid passages (15). The heat exchanger according to claim 14, wherein two heat exchanger plates (12a to 12c, 12) are formed at both ends corresponding to the heat exchangers (19, 20), respectively. 16. The heat transfer plate (12a-12c,
12) The tank portion (1) having communication holes (16a, 18a) only at one end in the flow direction of the internal fluid.
6, 18) are independently formed before and after in the flow direction of the external fluid, and the internal fluid passages (19, 20) formed in the plurality of sets of heat transfer plates (12a to 12c, 12) are mutually connected. The space is connected by the tank portions (15 to 18), and the flow of the internal fluid is U-turned at the other end of the heat transfer plates (12a to 12c, 12) in the flow direction of the internal fluid. 14. The heat exchanger according to claim 13, wherein a U-turn part (D) is formed. 17. The heat transfer plate (12a to 12c,
The heat exchange according to any one of claims 13 to 16, wherein the plurality of stacked shapes of (12) have a shape having a heat transfer expansion portion (11 ') projecting outward from a rectangular parallelepiped shape. vessel. 18. The projecting portion (14) extends continuously in a direction intersecting a flow direction (A) of an external fluid flowing outside the heat transfer plates (12a to 12c, 12). The heat exchanger according to any one of claims 1 to 17, wherein the heat exchanger is formed. 19. The projection according to claim 1, wherein the projection has a plurality of independent elongated projections arranged so as to prevent the external fluid from going straight.
The heat exchanger according to any one of the above. 20. The heat exchanger according to claim 19, wherein the elongated projections are arranged obliquely to a flow direction of the external fluid. 21. The heat exchanger according to claim 19, wherein the elongated projections (14) are arranged orthogonal to the flow direction of the external fluid. 22. The elongated projection (14) is arranged orthogonal to the flow direction of the external fluid;
20. The heat exchanger according to claim 19, wherein the heat exchanger comprises a combination with a member arranged in parallel to the flow direction of the external fluid. 23. The heat exchanger according to claim 1, wherein the internal fluid passage is formed by a hole shape in the heat transfer plate. . 24. A plurality of the heat transfer plates (12) are stacked and arranged, and the plurality of heat transfer plates (1) are arranged.
Tank members (33, 34, 46, 47) formed separately from the heat transfer plate (12) are disposed at both ends of 2), and the internal fluid passages of the plurality of heat transfer plates (12) are arranged. (19, 20) The space between the tank members (33, 3
24. The heat exchanger according to claim 23, wherein the heat exchangers are connected by 4, 46, 47). 25. The apparatus according to claim 24, wherein a distance between the plurality of heat transfer plates (12) is maintained by a spacer member (32) formed separately from the heat transfer plates (12). The heat exchanger as described. 26. The heat exchanger according to claim 24, wherein the plurality of heat transfer plates (12) are connected to each other at predetermined intervals by integral connecting portions (40, 41). 27. The heat transfer plate (12) having the projecting portion (14) and the internal fluid passages (19, 20) having the hole shape is formed by extruding an aluminum material. Item 27. The heat exchanger according to any one of items 23 to 26. 28. The heat exchanger according to claim 1, wherein the internal fluid passages (19, 2) are provided.
The evaporator for air conditioning, wherein the refrigerant of the refrigeration cycle flows as the internal fluid of 0), and air for air conditioning flows as the external fluid. 29. The heat exchanger according to claim 1, wherein the internal fluid passages (19, 2) are provided.
0) An air conditioning evaporator in which a refrigerant of a refrigeration cycle flows as an internal fluid and air for air conditioning flows as an external fluid, wherein a plurality of protrusions (14) has a protrusion pitch (P _1). ) Is 2 to 15 mm.