JP2003148891A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger to be downsized without causing the increase of ventilation resistance and the deterioration of adhesive property of a heat transfer plate constituting a passage. SOLUTION: In an evaporator (the heat exchanger) for exchanging heat between air-conditioning air and a refrigerant by allowing the air-conditioning air and the refrigerant to flow in a mutually intersecting manner, a passage for the flow of air-conditioning air is formed by combining an air passage 30a and an air passage 30b of different passage shape. The air passage 30a is provided with a large number of projecting parts 14 for making the flow of air-conditioning air turbulent, and a passage space H2 is made narrower than a passage space H1. The air passage 30b is not provided with the projections 14.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a heat exchanger,
More specifically, the present invention relates to a heat exchanger that is suitable for use in a vehicle air-conditioning evaporator, a condenser, a heater core, a radiator, and the like, and that is composed of only plates that form an internal fluid passage through which an internal fluid flows.

[0002]

2. Description of the Related Art In a conventional heat exchanger, for example, a vehicle air conditioner evaporator, heat transfer on the air side is performed between tubes having a flat cross section formed by joining two plates in the middle. A corrugated fin with a louver was interposed to expand the area.

However, in this type of heat exchanger, the cost reduction and downsizing of the heat exchanger have reached their limits due to the limitation of the number of man-hours for processing the louver.

Therefore, in Japanese Patent Laid-Open Nos. 11-287580 and 2000-205785, the corrugated fins are not required, and the required heat transfer performance can be ensured only by the heat transfer plate forming the refrigerant flow path. A finless type heat exchanger for cooling has been proposed.

FIG. 13, FIG. 2 to FIG. 4, and FIG. 14 show the structure of the heat exchanger (vehicle air-conditioning evaporator) proposed in Japanese Patent Laid-Open No. 2000-205785. Note that FIG. 13 is an exploded perspective view showing the configuration of the entire evaporator, and FIGS. 2, 3, and 4 are configurations of the heat transfer plate 12a, the heat transfer plate 12b, and the heat transfer plate 12c used in the evaporator, respectively. 14A and 14B are sectional views of the heat transfer plate 12a and the heat transfer plate 12b (12c) taken along the line A- in FIG. It is sectional drawing in A and the cut surface BB.

As shown in FIG. 13, this evaporator has a cross flow heat in which a flow direction A of the air conditioning air and a flow direction B of the refrigerant in the heat transfer plate portion (vertical direction in FIG. 13) are substantially orthogonal to each other. It is configured as an exchange. This evaporator comprises a core portion for exchanging heat between air for air conditioning and a refrigerant, which is formed by laminating a large number of heat transfer plates 12a, 12b, 12c.

The detailed structure of the heat transfer plates 12a to 12c will be described later, but each heat transfer plate 12a to 12c.
The protrusion 12c has a large number of protrusions formed on one side for disturbing the flow of fluid, and the pitch P1 of each protrusion (see FIG. 14B) is the same for all heat transfer plates. Then, the heat transfer plate 12a and the heat transfer plate 1
2b or the heat transfer plate 12c is arranged so that the positions of the respective protrusions are displaced, and flat portions other than the protrusions (hereinafter referred to as "substrate portions") are adhered to each other. The core portion is configured by stacking a plurality of heat transfer plate pairs. Therefore, FIG. 14 (B)
In FIG. 14 (B), a plurality of air-conditioning air passages having the same shape are lined up in the vertical direction on the paper surface of FIG.

In this evaporator, as shown in FIG. 13, arrow o direction, arrow p direction, arrow q direction, arrow r direction, arrow s direction, arrow t direction, arrow u direction, arrow v direction, arrow w.
The heat is exchanged between the refrigerant and the air for air conditioning by flowing the air in the direction A while flowing the refrigerant in the order of directions.

According to this evaporator, the heat transfer plate 12a
Due to the action of the large number of protrusions provided on the to 12c, the air flow forms a wave-like meandering flow in the gap between the heat transfer plates 12a to 12c and disturbs the flow, so that the air flow becomes a turbulent state. The heat transfer coefficient (heat transfer performance) on the air side can be dramatically improved.

By the way, in order to reduce the size of such a finless type heat exchanger without lowering the heat transfer performance, it is first necessary to improve the heat transfer performance with the same size.

Therefore, in the finless type heat exchanger as shown in FIG. 13, in order to improve the heat transfer performance, in the technique disclosed in Japanese Patent Laid-Open No. 2001-41678, each heat transfer plate is used. It is necessary to reduce the pitch P1 of the protrusions and increase the number of protrusions.

[0012]

However, when the number of protrusions is increased, there is a problem that the ventilation resistance generated by the flow of the fluid inside the heat exchanger increases. An increase in ventilation resistance leads to an increase in power for flowing the fluid, which is not preferable.

Further, in the technique described in the publication, the pitch P
The smaller 1 is, the adhesion margin of each heat transfer plate (see FIG. 14).
There is also a problem in that (see (B)) becomes narrower and the adhesiveness of each heat transfer plate deteriorates. This is because heat transfer plates formed with protrusions for disturbing the flow of fluid at the same pitch are arranged so that the positions of the protrusions are displaced, and the core portions are bonded by bonding the respective substrate portions to each other. It occurs because it is configured.

The present invention has been made in order to solve the above-mentioned problems, and the heat which can be miniaturized without increasing the ventilation resistance and deteriorating the adhesiveness of the heat transfer plate constituting the flow path. The purpose is to provide a exchanger.

[0015]

In order to achieve the above object, a heat exchanger according to claim 1 is configured so that a low temperature first fluid and a second fluid higher than the first fluid intersect each other. A heat exchanger that performs heat exchange between the first fluid and the second fluid by flowing the fluid, wherein at least one flow path of the first fluid and the second fluid has a plurality of flow path shapes. It is formed by a combination. In the following, the case where the temperature of the first fluid is lower than the temperature of the second fluid and the present invention is applied to an evaporator for air conditioning will be described. However, the temperature of the first fluid is set to the second fluid. By raising the temperature to a higher temperature, the present invention can be applied to a radiator or a condenser for air conditioning.

According to the heat exchanger of the first aspect, at least one flow path of the first fluid at a low temperature and the second fluid at a higher temperature than the first fluid is formed by a combination of a plurality of flow path shapes. It

That is, as described above, the smaller the ventilation resistance is, the more advantageous it is in terms of power. However, if the ventilation resistance is reduced, the heat transfer performance is also lowered. Therefore, there is a trade-off between the ventilation resistance and the heat transfer performance. Have a relationship. Further, it goes without saying that the ventilation resistances of different flow channel shapes are different from each other.

Utilizing these points, in the present invention, FIG.
As in the conventional heat exchanger shown in FIG.
In this case, the flow path for air conditioning air) is not formed by stacking only one type of flow path shape, but is formed by a combination of multiple types of flow path shapes, and ventilation resistance for the entire heat exchanger is required. By determining the shape of each flow path so that it has the minimum resistance that can ensure heat transfer performance, it is possible to prevent an increase in ventilation resistance. This allows
Since it is possible to improve the heat transfer performance in the same size,
As a result, the heat exchanger can be downsized without increasing the ventilation resistance.

Even in the conventional heat exchanger described above, the ventilation resistance can be adjusted by adjusting the shape of the flow passage. However, in the present invention, by using a plurality of kinds of flow passage shapes, for example, Some flow channel shapes have many protrusions to improve heat transfer performance, and other flow channel shapes allow fine adjustment such as reducing protrusions to reduce ventilation resistance. Has improved the superiority of.

As described above, according to the heat exchanger of the first aspect, at least one flow path of the first fluid and the second fluid for heat exchange is formed by combining a plurality of kinds of flow path shapes. Therefore, without causing an increase in ventilation resistance,
The size can be reduced while ensuring the required heat transfer performance.

Further, in the heat exchanger according to the second aspect, in the invention according to the first aspect, one of the first fluid and the second fluid is formed by a combination of a plurality of types of flow passage shapes. At this time, the plurality of types of flow passage shapes are formed so that a flow passage for the other fluid can be formed.

According to the heat exchanger of the second aspect, in the invention of the first aspect, one of the first fluid and the second fluid is formed by a combination of a plurality of types of flow passage shapes. At this time, the plurality of types of flow channel shapes are formed so as to be able to form the other fluid flow channel.

This means that when the flow path according to the present invention is constructed by stacking a plurality of heat transfer plates as shown in FIG. 13, either one of the first fluid and the second fluid flows. When stacking heat transfer plates to form the paths,
This corresponds to making the shape of the heat transfer plate into a shape capable of forming the flow path of the other fluid.

As described above, according to the heat exchanger of the second aspect, the same effect as that of the invention of the first aspect can be obtained, and in the invention of the first aspect, a plurality of kinds of flow passage shapes are obtained. When one of the flow paths of the first fluid and the second fluid is formed by the combination of the above, the plurality of types of flow path shapes are shaped so that the flow path of the other fluid can be formed. The member for forming the passage can also be used as the member for forming the passage of the other fluid, and the heat exchanger can be downsized and the cost can be reduced.

Further, the heat exchanger according to claim 3 is the heat exchanger according to claim 1 or 2, wherein the plurality of types of flow passage shapes are a first flow passage having a large number of projections for disturbing the flow. A channel width narrower than the first channel and having a smaller number of the protrusions than the first channel, or a protrusion having a ventilation resistance smaller than that of the protrusions of the first channel, or the protrusion There are two types of shapes, that is, a second flow path having no.

According to the third aspect of the heat exchanger, the plurality of types of flow passage shapes in the first or second aspect of the invention include a first flow passage having a large number of protrusions for disturbing the flow.
The width of the flow path is narrower than that of the first flow path, and the number of the projections is smaller than that of the first flow path, or the projection of the first flow path has a ventilation resistance smaller than that of the projections of the first flow path. There are two types of shapes: a second flow path that does not have.

That is, in the present invention, the first flow path is provided with a large number of projections for disturbing the flow to make it a flow path having high heat transfer performance, while the second flow path is defined as the first
The heat transfer performance is lower than that of the first flow passage, but the air flow resistance is lower than that of the first flow passage by reducing the number of flow passages to be less than that of the first flow passage Is a small flow path, and the heat exchanger is formed by combining the first flow path and the second flow path with different characteristics, which ensures the ventilation resistance of the heat exchanger as a whole and the required heat transfer performance. In addition, the minimum resistance is set.

Further, in the present invention, when it is assumed that the widths of the first flow path and the second flow path are equal, the heat transfer performance in the second flow path is lower than that in the first flow path. . Therefore, in the present invention, in order to prevent the deterioration of the heat transfer performance of the second flow passage, the flow passage width of the second flow passage is made narrower than that of the first flow passage.

Further, in the present invention, the shape of the second flow path has a smaller number of protrusions than the first flow path (including 0 (zero)).
Since it has a shape, when each flow path is formed by stacking a plurality of heat transfer plates, the area of the substrate portion of the heat transfer plate forming the second flow path can be increased, and the first flow path can be formed. The heat transfer plate used to form the heat transfer plate and the heat transfer plate used to form the second flow path have an adhesion margin with the number of protrusions of the second flow path equal to that of the first flow path, and The width of the heat transfer plate can be increased as compared with the case of forming the pitch, and as a result, the adhesion of the heat transfer plate can be prevented from being deteriorated as the heat exchanger is downsized.

As described above, according to the heat exchanger of claim 3, the same effect as that of the invention of claim 1 or 2 can be obtained, and at the same time, the heat exchanger of claim 1 or 2 can be obtained. A plurality of types of flow path shapes in the invention, a first flow path having a large number of projections for disturbing the flow, and a flow path width narrower than the first flow path, and having a smaller number of the projections than the first flow path,
Alternatively, since the flow path has two types of shapes, that is, a projection having a ventilation resistance smaller than the projection of the first flow path or a second flow path having no projection, the flow path is formed by bonding a plurality of heat transfer plates. It is possible to prevent the adhesiveness of the heat transfer plate from being deteriorated due to the miniaturization of the heat exchanger when the heat exchanger is formed.

[0031]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below in detail with reference to the drawings. Here, a case where the heat exchanger of the present invention is applied to a vehicle air conditioning evaporator (hereinafter, simply referred to as “evaporator”) will be described.

[First Embodiment] FIGS. 1 to 7 show a first embodiment of the present invention, and FIG. 1 is an exploded perspective view showing the entire structure of an evaporator 10 according to the present embodiment. , FIG. 2, FIG. 3, and FIG. 4 are respectively used in the evaporator 10,
It is a front view which shows the structure of the heat transfer plate 12a with a protrusion for disturbing a flow, the heat transfer plate 12b, and the heat transfer plate 12c, and FIG.5 and FIG.6 is each used with the evaporator 10, and the said protrusion is provided. FIG. 7 is a front view showing a configuration of a heat transfer plate 22a and a heat transfer plate 22b whose surfaces are not smoothed and whose surfaces are substantially smooth. FIG. 7 shows each heat transfer plate 12a, 12b (in a state of being incorporated in the evaporator 10). 12c), 2
It is sectional drawing in the cutting plane CC (refer FIG.2 and FIG.5) of 2a, 22b.

As shown in FIG. 1, the evaporator 10 has a cross-flow heat in which a flow direction A of the air conditioning air and a flow direction B of the refrigerant in the heat transfer plate portion (vertical direction in FIG. 1) are substantially orthogonal to each other. It is configured as an exchange. The evaporator 10 includes a core portion 11 for exchanging heat between air for air conditioning and a refrigerant only by stacking a large number of heat transfer plates 12a, 12b, 12c, 22a, 22b.

In this embodiment, the first heat transfer plate 12a shown in FIG. 2, the second heat transfer plate 12b shown in FIG.
Combined area X of the fourth heat transfer plate 22a shown in FIG. 6 and the fifth heat transfer plate 22b shown in FIG. 6, the first heat transfer plate 12a, the third heat transfer plate 12c shown in FIG.
The core area 11 is configured by the combined area Y of the heat transfer plate 22a and the fifth heat transfer plate 22b.

Each heat transfer plate 12a-12c, 22a,
22b has A on both sides of the A3000 series aluminum core material.
It consists of a double-sided clad material in which 4000 series aluminum brazing material is clad, and has a plate thickness t = 0.1 to 0.4 mm.
It is a press-molded thin plate. The heat transfer plates 12a to 12c, 22a and 22b have a substantially rectangular plane shape as shown in FIGS. 2 to 6, all have the same outer dimensions, and the length in the long side direction is, for example, 245 m.
m, the width in the short side direction is, for example, 45 mm.

The heat transfer plates 12a to 12c may basically have the same ejection shape, but the specific shapes thereof are, for example, establishment of a refrigerant passage, assembling of an evaporator, brazing, drainage of condensed water, and the like. Is different for the reason. 2 to 4,
Each of the heat transfer plates 12a to 12c is formed by stamping a protrusion (rib) 14 from the flat substrate portion 13 to the back side of the paper surface. The protrusion 14 is provided on the heat transfer plate 22a or 22b.
The refrigerant passages 19 and 20 through which the low-pressure side refrigerant flows after passing through the pressure reducing means (expansion valve or the like) of the refrigerating cycle are configured by adhesion with the end plate 21 or the end plate 23 described later. The heat transfer plate 12 has a shape continuously extending in parallel with the longitudinal direction. Further, the cross-sectional shape of the protrusion 14 is substantially trapezoidal as shown in FIG. 7.

As shown in FIGS. 2 to 4, the number of protrusions 14 is six in the first heat transfer plate 12a and four in the second and third heat transfer plates 12b and 12c. . Further, the second and third heat transfer plates 12b and 12c are formed with a protrusion (rib) 140 for detecting internal leakage at the center in the width direction. This protrusion 140 is also the protrusion 1
Although it is stamped and formed in the same manner as that of No. 4, since the purpose is to detect internal leakage, the second heat transfer plate 12b has both ends 140a and 140b in the plate longitudinal direction to move the inside of the protrusion 140 to the outside of the heat exchanger. It is open. On the other hand, the protrusion 140 of the third heat transfer plate 12c is open to the outside of the heat exchanger only at the upper end (one end) 140a in the plate longitudinal direction, and the lower end (other end) 140b is located in front of the tank part described later. The closed end is formed at the position. The projections 14 and 140 have the same launch height h (FIG. 7) and are, for example, about 1.5 mm.

As described above, the first heat transfer plate 12a has six ejections, and the second and third heat transfer plates 12 are
In b and 12c, the number of shots is set to the protrusion 14 and the protrusion 140.
As shown in FIG. 7, the first heat transfer plate 12a and the second and third heat transfer plates 12b and 12c have different numbers of shots.
2a and second heat transfer plate 12b or third heat transfer plate 1
2c and 2c are laminated so as to face each other so that their protrusions face inward, the protrusions 14 of the second heat transfer plate 12b or the third heat transfer plate 12c are provided in the middle of the protrusions 14 of the first heat transfer plate 12a. The protrusion 140 is located.

Further, a small protrusion 14a is formed so as to project in the width direction (air flow direction A) of the heat transfer plate from the side surface of each protrusion 14 of the heat transfer plates 12a to 12c. A large number of the small protrusions 14a are provided at the same position in the longitudinal direction of each protrusion 14. In the present embodiment, the large number of small protrusions 14a of each of the protrusions 14 of the second and third heat transfer plates 12b and 12c are projected in the opposite direction one by one in the width direction of the heat transfer plate. , 1st heat transfer plate 1
The large number of small protrusions 14a of each protrusion 14 of the second heat transfer plate 12a of the second heat transfer plate 12a in the width direction of the heat transfer plate 12a.
The protrusions b and 12c project in the same direction as the small protrusion 14a.

On the other hand, in FIGS. 5 and 6, each heat transfer plate 22a, 22b is formed by punching out a small projection 24a from the flat substrate portion 23 to the back side of the paper surface. This small protrusion 24a
Is for forming an air passage 30b (see also FIG. 7) described later by bonding the heat transfer plate 22a and the heat transfer plate 22b. The small protrusion 24a has a substantially trapezoidal cross section.

The small protrusions 24a of the heat transfer plate 22a, when laminated with another heat transfer plate, are used for the heat transfer plate 12a.
The small protrusion 14a of a is formed at the same position as the longitudinal direction and the width direction of the plate, and the heat transfer plate 22b is formed.
The small protrusions 24a are formed at the same position in the plate longitudinal direction and the width direction as the small protrusions 14a of the heat transfer plate 12b when laminated with another heat transfer plate.

The core portion 11 of the evaporator 10 according to this embodiment
Makes the small protrusions 24a of the heat transfer plate 22a and the heat transfer plate 22b contact each other, and
a and the heat transfer plate 12b, or the small protrusions 14a of the heat transfer plate 12a and the heat transfer plate 12c are brought into contact with each other, and the board portion 23 of the heat transfer plate 22a and the board portion 13 of the heat transfer plate 12b or 12c Abut
Also, the substrate portion 23 of the heat transfer plate 22b and the heat transfer plate 1
It is configured by abutting and joining the substrate portion 13 of 2a.

Therefore, the heat transfer plates 12a to 12c, 2c, 2c, 2c are pressed with the pressing force in the stacking direction of the heat transfer plates acting on the contact portions between the small protrusions 24a and the contact portions between the small protrusions 14a.
2a and 22b can be joined to each other.

Further, by this joining, the heat transfer plate 1
2a and the heat transfer plate 22b between the heat transfer plate 12a
A passage for flowing the refrigerant is formed by the protrusion 14 of the heat transfer plate 12b or 12c and the heat transfer plate 22.
A passage for flowing the refrigerant is formed between the a and the a by the protrusion 14 of the heat transfer plate 12b.

That is, each heat transfer plate 12a-12c
In the width direction of, the windward side refrigerant passage 20 is formed inside the protrusion 14 located on the windward side of the central portion (position of the protrusion 140), and in the width direction of each of the heat transfer plates 12a to 12c. Projection 1 located on the lee side from the center
A leeward side refrigerant passage 19 is formed on the inner side of 4. In addition, an internal leakage detecting passage 141 is formed inside the central protruding portion 140.

Here, the heat transfer plate 22a or 22 joined to the substrate portion 13 of each of the heat transfer plates 12a to 12c.
Although the substrate portion 23 of b has a recess for forming the small protrusion 24a in a part thereof, since it has a flat shape in most of the area, the heat transfer plates 12a to 12c and the heat transfer plate 22a are formed.
Alternatively, the adhesion margin with 22b can be increased.
Therefore, the contact between the substrate portions of the heat transfer plates can be favorably brazed, and the refrigerant passage 1 due to poor brazing can be achieved.
It is possible to prevent leakage of the refrigerant from 9 and 20.

On the other hand, the heat transfer plates 12a-12c, 22
a and 22b, at both ends of a direction (longitudinal direction of the heat transfer plate) B orthogonal to the air flow direction A, the tank parts 15 to 15 are divided in the width direction of the heat transfer plate (air flow direction A).
Two 18 are formed. This tank part 15-18
In each of the heat transfer plates 12a to 12c, 22a, and 22b, the protrusions 14 and 140 and the small protrusions 24a are punched out in the same direction (on the back side of the paper surface of FIGS. 2 to 6). , 140, and the small protrusion 24a.

As described above, the tank portions 15 to 18 are punched out in the same direction as the projecting portion 14, and the recessed shape formed by the punching is continuous with the projecting concave shape of the tank portions 15 to 18 at both ends in the longitudinal direction of the projecting portion 14. Therefore, both ends of the refrigerant passage 20 on the windward side communicate with the tank portions 17 and 18 on the windward side, and both ends of the refrigerant passage 19 on the leeward side communicate with the tank portions 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 are
Since the heat transfer plate is divided into two in the width direction, the stamped shapes of the tank portions 15 to 18 are substantially D-shaped in the illustrated examples of FIGS. 2 to 6. However, as in the illustrated example of FIG. 1, the tank portions 15 to 18 may be formed in a substantially oval shape.

Communication holes 15a to 18a are opened at the central portions of the tank portions 15 to 18, respectively. These communication holes 15a-1
By 8a, in the left-right direction (heat transfer plate stacking direction) shown in FIG. 1, the flow paths of the tank parts 15 to 18 are communicated between the adjacent heat transfer plates.

In the heat transfer plate 12c shown in FIG. 4, the lower end (the other end) 140b of the protrusion 140 is finished at a position before the tanks 16 and 18 as described above, and is closed here. Instead of the protrusion 140, a communication passage 120 for directly communicating the tank 16 and the tank 18 is formed. The communication passage 120 can be formed by driving an intermediate portion between the tank portion 16 and the tank portion 18 in the same direction as the tank portions 16 and 18.

Further, as shown in FIGS. 2 to 6, in any of the first to third heat transfer plates 12a to 12c and the fourth and fifth heat transfer plates 22a and 22b, the tank portion 17 on the windward side, As compared with 18, the height of the tank portions 15 and 16 on the leeward side is reduced by a predetermined dimension L. This is to increase the ventilation area in the leeward region in the core portion 11 as compared with the leeward region as described later.

By the way, in the width direction (air flow direction A) of the heat transfer plates 12a to 12c, a plurality of protrusions 1 are formed.
As shown in FIG. 7, the fourth and the second and third heat transfer plates 12b and 12c have a protrusion 140 for detecting internal leakage, and the protrusions 1 of the heat transfer plates 12a to 12c are adjacent to each other.
4, 140 and the forming position are deviated from each other, so that the protrusions 14 and 140 are adjacent to the heat transfer plates 12a to 1a.
It can be located in the concave portion formed by the substrate portion 13 of 2c.

As a result, a gap is always formed between the tops of the projections 14 and 140 on the convex surface side and the concave surfaces of the substrate portions 13 of the other adjacent heat transfer plates 12a to 12c. This clearance is a clearance of a size obtained by subtracting the plate thickness of the projection height h of the protrusion 14, and this clearance allows the entire length in the width direction (air flow direction A) of the heat transfer plate as indicated by an arrow A1. The air passage 30a meandering in a wavy shape is formed.

Therefore, the conditioned air blown in the direction of the arrow A meanders in the air passage 30a in a wavy manner as shown by the arrow A1 and passes between the two heat transfer plates 12a and 12b or between the heat transfer plates 12a and 12c. You can pass through.

On the other hand, the heat transfer plates 22a adjacent to each other
Since the small protrusions 24a are in contact with each other and 22b, a gap is always formed between the heat transfer plates 22a and 22b. This gap has a size which is twice the value obtained by subtracting the plate thickness of the small protrusion 24a from the height of the small protrusion 24a, and this gap allows the arrow to extend over the entire length in the heat transfer plate width direction (air flow direction A). A linear air passage 30b is formed like A2.

Therefore, the conditioned air blown in the direction of the arrow A can pass straight through the air passage 30b as shown by the arrow A2.

The air passage 30a corresponds to the first passage of the present invention, and the air passage 30b corresponds to the second passage of the present invention.

Next, a portion for entering and exiting the refrigerant with respect to the core portion 11 will be described. As shown in FIG. 1, the heat transfer plates 12a to 12a are provided on both end sides in the heat transfer plate stacking direction.
End plates 21 and 23 having the same size as c are arranged. The end plate 21 has a flat plate shape that is in contact with the concave surface sides of the substrate portion 13 and the tank portions 15 to 18 of the heat transfer plate 12b and joined to the heat transfer plate 12b, and the end plate 23 is the heat transfer plate 12a. It has a flat plate shape that abuts on the concave surfaces of the base plate portion 13 and the tank portions 15 to 18 and is joined to the heat transfer plate 12a.

The end plate 21 on the left side of FIG. 1 has a refrigerant inlet hole 21a and a refrigerant outlet hole 2 at positions near its lower end.
1b is opened, the refrigerant inlet hole 21a communicates with the communication hole 16a of the leeward tank portion 16 at the lower end of the heat transfer plate 12b, and the refrigerant outlet hole 21b is the windward tank at the lower end of the heat transfer plate 12b. It communicates with the communication hole 18a of the portion 18. A refrigerant inlet pipe 24 and a refrigerant outlet pipe 25 are joined to the refrigerant inlet hole 21a and the refrigerant outlet hole 21b of the end plate 21, respectively.

One end plate 21 has a refrigerant inlet,
For joining with the outlet pipes 24 and 25, the heat transfer plates 12a to 12c are formed of a double-sided clad material in which both sides of an A3000 series aluminum core material are clad with an A4000 series aluminum brazing material. The other end plate 23 is A4000 only on one surface of the A3000 series aluminum core material (the surface on the side joined to the heat transfer plate 12a).
It consists of a single-sided clad material in which a system aluminum brazing material is clad. Further, both end plates 21 and 23 have a larger plate thickness t than the heat transfer plate 12 (for example, plate thickness t
= 1.0 mm) to improve the strength.

A gas-liquid two-phase refrigerant whose pressure has been reduced by a pressure reducing means such as an expansion valve (not shown) flows into the refrigerant inlet pipe 24, and the refrigerant outlet pipe 25 is connected to a compressor suction side (not shown) so that the evaporator 10 can be used. The vaporized gas refrigerant is guided to the compressor suction side. Each heat transfer plate 12a-12c, 22
In a and 22b, since the refrigerant from the refrigerant inlet pipe 24 flows into the leeward side refrigerant passage 19, it constitutes an inlet side refrigerant passage in the entire refrigerant passage of the evaporator, and the windward side refrigerant passage 20 is The refrigerant that has passed through the leeward side (inlet side) refrigerant passage 19 flows into the refrigerant outlet pipe 25, thus forming an outlet side refrigerant passage.

Next, the refrigerant passage of the entire evaporator 10 will be described with reference to FIG. In the evaporator 10 according to the present embodiment, the refrigerant passage structure is realized by the following means.

First, in the left-right direction (heat transfer plate stacking direction) in FIG. 1, in the half region X on the side of one end plate 21, four heat transfer plates 12a, 12b, 22 are provided.
a, 22b are set as one set, and in the half region Y on the side of the other end plate 23, four heat transfer plates 12a, 12c, 22a, 22b are set as one set, and each heat transfer plate is stacked. The core portion 11 is configured by joining the heat plates.

Of the tank portions 15 to 18 located at the upper and lower ends of the evaporator 10, the tank portion 15 on the leeward side,
16 constitutes the refrigerant inlet side tank portion, and the windward tank portions 17 and 18 constitute the refrigerant outlet side tank portion. The refrigerant inlet side tank portion 16 on the leeward side is provided with a partition portion 27 arranged at an intermediate position (boundary portion between the region X and the region Y) of the heat transfer plate 12 in the stacking direction. Flow path on the X side) and the flow path on the right side of FIG. 1 (flow path on the region Y side)
It is divided into

Similarly, the refrigerant outlet side tank portion 18 on the windward side is also divided by the partition portion 28, which is also arranged at the intermediate position, into the flow passage on the left side in FIG. 1 (the flow passage on the region X side) and the flow passage on the right side in FIG. It is partitioned into a flow path (flow path on the region Y side). These partition portions 27 and 28 are the heat transfer plates 12a to 12 described above.
Among the c, 22a, and 22b, only the heat transfer plate located at the corresponding portion is provided with the communication holes 15a of the tank portions 15 and 18,
It can be constructed by using a blind lid shape in which the portion 18a is closed.

According to the evaporator 10 of the present embodiment, the low pressure gas-liquid two-phase refrigerant decompressed by the expansion valve is fed from the refrigerant inlet pipe 24 to the inlet side tank portion 16 on the leeward side as shown by the arrow a. to go into. Since the flow path of the inlet side tank portion 16 is divided into the left and right regions X and Y by the partition part 27, the refrigerant enters only the flow path of the left side region X of the inlet side tank portion 16. Then, in the left side area X of FIG. 1, the refrigerant is located on the leeward side projection portion 14 of the heat transfer plate 12a and the heat transfer plate 22.
b or the refrigerant passage 19 formed by the leeward-side protrusion 14 of the heat transfer plate 12b and the heat transfer plate 22a or the end plate 21 ascends as shown by the arrow b to enter the upper inlet side tank portion 15.

Next, the refrigerant moves through the upper inlet tank portion 15 to the right side area Y in FIG. 1 as indicated by the arrow c, and the leeward protrusion 14 of the heat transfer plate 12a and the heat transfer plate 22b or the end plate. 23, or the flow path in the right side region Y of the lower inlet side tank portion 16 by descending the refrigerant passage 19 formed by the leeward protrusion 14 of the heat transfer plate 12c and the heat transfer plate 22a as shown by an arrow d. to go into.

Here, at the intermediate position between the tank portion 16 and the tank portion 18 on the lower side of the third heat transfer plate 12c incorporated in the right side region Y, both tank portions 16 and 18 are directly connected to each other. Since the communication passage 120 is formed, the refrigerant in the right side region Y of the tank portion 16 is next transferred to the communication passage 1
The outlet side tank portion 1 on the windward side through 20 as shown by arrow e
Enter 8.

Here, since the flow path of the outlet side tank section 18 is divided into the left and right regions X and Y by the partition section 28, the refrigerant enters only 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 located on the windward side projection portion 14 of the heat transfer plate 12a and the heat transfer plate 22b or the end plate 23, or on the windward side projection portion 14 of the heat transfer plate 12c. And heat transfer plate 2
The refrigerant passage 20 formed by 2a rises as shown by 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 moves through the upper outlet side tank portion 17 to the left side area X in FIG. 1 as indicated by an arrow g, and thereafter, the windward side projection portion 14 of the heat transfer plate 12a and the heat transfer plate 22b. Alternatively, the refrigerant passage 20 formed by the windward protrusion 14 of the heat transfer plate 12b and the heat transfer plate 22a or the end plate 21 descends as indicated by an arrow h to move to the left side region X of the lower outlet side tank part 18. Enter the channel. The refrigerant flows to the left in the outlet side tank portion 18 as indicated by an arrow i, and flows out of the evaporator from the refrigerant outlet pipe 25.

In the present embodiment, the refrigerant passage of the evaporator 10 is configured as described above, and the components shown in FIG. 1 are laminated in a state of abutting each other, and the laminated state (assembled state) ) Is carried by an appropriate jig and carried into a brazing furnace, and the assembly is heated to the melting point of the brazing material to integrally braze the assembly. As a result, the assembling of the evaporator 10 can be completed.

In this integral brazing, the four heat transfer plates 12a, 12 which are adjacent to each other are joined at the joint surfaces in the longitudinal direction of the heat transfer plates 12a-12c, 22a, 22b.
b, 22a, 22b or heat transfer plates 12a, 12
Small protrusions 14a of c, 22a, 22b, small protrusion 24a
The small projections 14a and the small projections 2 are brought into contact with each other.
Heat transfer plates 12a to 4a are pressed against each other by applying a pressing force in the stacking direction of the heat transfer plates to the abutting portions of the heat transfer plates 4a.
12c, 22a, 22b can be joined to each other.

As a result, the pressing force acts on the heat transfer plate 12 even at an intermediate part (a part where the refrigerant passages 19 and 20 are formed) of the heat transfer plate 12 except for the tank parts 15 to 18 at both ends in the longitudinal direction. Substrate 13 and heat transfer plate 22
The base plate portion 23 can be surely brought into contact with the entire surface, and the contact surface between the base plate portions can be satisfactorily brazed, and the refrigerant leakage from the refrigerant passages 19 and 20 due to poor brazing can be prevented. .

By the way, in order to find a defective product due to refrigerant leakage, a refrigerant leakage inspection of the evaporator 10 is performed. In this inspection, for example, the evaporator 10 after brazing is carried into a closed chamber and the refrigerant is cooled. By closing one of the inlet pipe 24 and the refrigerant outlet pipe 25 with a suitable blind lid, pressurizing the leak test fluid (for example, helium gas) to a predetermined pressure from the other pipe and supplying it to the refrigerant passage in the evaporator 10. The presence or absence of fluid leakage to the outside of the evaporator 10 (fluid leakage into the closed chamber) is inspected.

Next, the operation of the evaporator 10 according to this embodiment will be described. The evaporator 10 is housed in an air conditioning unit case (not shown) with the vertical direction in FIG. 1 vertically, and air is blown in the direction of arrow A by the action of an air conditioning blower (not shown).

When the compressor of the refrigeration cycle operates, the low pressure gas / liquid 2 is decompressed by the expansion valve (not shown).
The phase refrigerant flows according to the above-described passage configuration of arrows a to i in FIG.

On the other hand, the heat transfer plates 12a ...
Protrusions 14 and 14 protruding in a convex shape on the outer surface side of 12c
The gap formed between 0 and the substrate portion 13 causes the arrow A to extend over the entire length in the heat transfer plate width direction (air flow direction A).
1, the air passage 30a meandering in a wave shape is formed, and the small projection 24a protruding in a convex shape to the outer surface side of the adjacent heat transfer plates 22a and 22b allows the arrow A2 to extend over the entire length in the width direction of the heat transfer plate. The linear air passage 30a is formed as shown in FIG.

As a result, the conditioned air blown in the direction of the arrow A meanders in the air passage 30a in a wavy manner as shown by the arrow A1, and the two heat transfer plates 12a and 12b.
Or between the heat transfer plates 12a and 12c, and the air passage 30b can linearly pass between the two heat transfer plates 22a and 22b as shown by an arrow A2. .

Since the refrigerant absorbs latent heat of vaporization and evaporates from this air flow, the conditioned air is cooled and becomes cold air.
At this time, with respect to the flow direction A of the conditioned air, the inlet side refrigerant passage 19 is provided on the leeward side and the outlet side refrigerant passage 20 is provided on the windward side.
By arranging, the refrigerant inlet and outlet with respect to the air flow have a counterflow relationship.

Further, on the air side, the air flow direction A
Is the protrusions 14 and 140 of the heat transfer plates 12a to 12c.
Longitudinal direction (refrigerant flow direction B in the refrigerant passages 19 and 20)
The direction is orthogonal to the projections 14, 14
Since 0 forms a convex surface (heat transfer surface) that protrudes orthogonally to the air flow, the air has a protrusion 14 that extends in the orthogonal direction.
The convex shape of 140 hinders straight traveling.

Therefore, the air flow is generated by the heat transfer plates 12a ...
A gap between the 12c forms a wavy meandering flow as shown by an arrow A1 in FIG. 7 and disturbs the flow, so that the air flow becomes a turbulent state, and the heat transfer coefficient on the air side is dramatically improved. You can

Here, the core portion 11 is the heat transfer plate 12a.
~ 12c, 22a, since it is composed of only 22b,
Compared with a conventional evaporator equipped with a conventional fin member, the heat transfer area on the air side is greatly reduced, but the heat transfer coefficient on the air side is dramatically improved by setting the turbulent flow state.
The reduction of the air-side heat transfer area can be compensated by the improvement of the air-side heat transfer coefficient, and the required cooling performance can be secured.

Further, according to the present embodiment, the communication passage 120 is formed at the intermediate position between the tank portion 16 and the tank portion 18 on the lower side of the third heat transfer plate 12c incorporated in the right side region Y, and this communication passage 120 is formed. Both tank parts 16 and 18 are provided by the passage 120.
Since the spaces are directly communicated with each other, it is not necessary to form a refrigerant passage in the end plate 23 portion, and it is sufficient to use one simple flat plate as the end plate 23. Therefore, the heat transfer plate arrangement volume in the core portion 11 can be increased, and the heat transfer performance can be improved as the volume is increased.

Next, the drainability of the condensed water of the evaporator 10 according to this embodiment will be described. The evaporator 10 includes heat transfer plates 12a to 12c, 22a and 22b as shown in FIG.
Are actually used by arranging so that the longitudinal direction thereof is the vertical direction. Therefore, in the use state of the evaporator 10, a gap (see FIG. 7) extending in the longitudinal direction (vertical direction) can be continuously formed between the heat transfer plates. As a result, the condensed water generated on the surface of each heat transfer plate can be smoothly dropped downward along the vertically extending gap.

Although a part of the condensed water tends to move to the leeward side due to the wind pressure of the blown air, according to the present embodiment, in any of the heat transfer plates 12a to 12c, 22a and 22b, the tank portion on the windward side. The height of the tank portions 15 and 16 on the leeward side is made smaller than the heights of 17 and 18 by a predetermined dimension L. As a result, the ventilation area in the leeward region of the core portion 11 can be increased as compared to the leeward region, and the air flow velocity in the leeward region can be reduced.

Therefore, even if a part of the condensed water moves to the leeward side, it is possible to prevent the condensed water from being scattered to the downstream side from the leeward side end portions of the heat transfer plates 12a to 12c, 22a, 22b. Can be effectively suppressed.

By the way, since the heights of the leeward tank portions 15 and 16 are reduced by a predetermined dimension L as compared with the windward tank portions 17 and 18, the windward tank portions 17 and 18 are accordingly increased. Compared to 18, the tank parts 15 and 16 on the leeward side
Although there is a concern that the pressure loss of the refrigerant flow path will increase due to the smaller cross-sectional area of the refrigerant, the tank parts 15 and 16 on the leeward side are the inlet side of the refrigerant in the refrigerant passages of the entire evaporator, and the refrigerant is dry. Since the degree of cooling is small and the specific volume of the refrigerant (m ³ / kg) is small, it is possible to reduce the influence of the pressure loss increase due to the decrease in the cross-sectional area of the flow path. From this point as well, the refrigerant passage configuration of the present embodiment is extremely convenient. is there.

FIG. 8 shows an example of the result of heat flow analysis performed using each of the conventional heat exchanger shown in FIG. 13 and the evaporator 10 according to this embodiment. In addition, here, the temperature of the air for air conditioning is 27 ° C., and the temperature of the refrigerant is 6 ° C.
It was set to 0 ° C. Further, the flow path interval H2 shown in FIG.
5 mm, flow path distance H1 is 2.5 mm, pitch P
1 was set to 6.8 mm.

As shown in FIG. 8, as compared with the conventional heat exchanger shown in FIG. 13, the evaporator 10 according to the present embodiment is found to have an equivalent ventilation resistance and an improved heat transfer performance of about 10%. It was
This is because the flow passage distance H2 is smaller than the flow passage distance H1 by 0.5.
By setting the value to be mm, the temperature gradient of the plate wall surface (value obtained by dividing the temperature difference between the air and the heat transfer plate by the flow path interval), which is important for heat exchange, is increased, and at the same time, the protrusion is provided. This is an effect obtained by increasing the heat transfer area as compared with the case where the heat exchanger is composed of only the first flow path.

As described in detail above, in the evaporator 10 according to the present embodiment, there are a plurality of types of flow paths (air passage 30a and air passage 30b in the present embodiment) through which the air for air conditioning for heat exchange flows. Since it is formed by a combination of two types of flow path shapes, the evaporator 10 can be downsized while ensuring the necessary heat transfer performance without increasing the ventilation resistance.

Further, in the evaporator 10 according to the present embodiment, the plurality of kinds of flow passage shapes are formed so that the flow passages of the refrigerant (in this embodiment, the refrigerant passages 19 and 20) can be formed. The heat transfer plate for forming the flow path for the refrigerant and the heat transfer plate for forming the flow path for the refrigerant can be used together, and the evaporator 10 can be downsized and reduced in cost.

Further, in the evaporator 10 according to the present embodiment, the plurality of types of flow passage shapes are provided in the air passage 30a having a large number of protrusions for disturbing the air flow, and the air passage 30a.
Air passage 3 having a narrower flow passage width and having no protrusion
Since it has two types of shapes, 0b, the evaporator 10 in the case of being formed by adhering a plurality of heat transfer plates
It is possible to prevent the adhesiveness of the heat transfer plate from being deteriorated due to the miniaturization.

Second Embodiment In the second embodiment, a modified example of the air passage 30a and the air passage 30b (corresponding to the first flow passage and the second flow passage of the present invention) will be described.

As shown in FIG. 9, in the second embodiment,
The windward tip portion 3 of each of the heat transfer plates 12a to 12c
4 and the tip portion 32 on the windward side of each of the heat transfer plates 22a and 22b is formed with an inclined surface that is inclined toward the stacking direction of the heat transfer plates.

As a result, in the heat exchanger according to the second embodiment, the front stagnation area of the protrusion 14 can be reduced, and as a result, when the inclined surface is not formed at the tip of each heat transfer plate. The heat transfer performance can be improved in comparison with.

Since the parts other than the air passage are the same as those of the evaporator 10 according to the first embodiment, the description thereof will be omitted here.

As described in detail above, in the evaporator according to the second embodiment, the same effect as that of the evaporator according to the first embodiment can be obtained, and the tip of the heat transfer plate on the windward side. Since the part is provided with the inclined surface for reducing the stagnation area of the air, the heat transfer performance can be further improved as compared with the case where the inclined surface is not provided.

[Third Embodiment] In the third embodiment, another modification of the air passage 30a and the air passage 30b will be described.

In order to miniaturize the evaporator without lowering the heat transfer performance, the pitch P1 of the projections 14 of each of the heat transfer plates 12a to 12c is reduced to increase the number of projections, or the launch height L1 is set to be smaller. When it is increased, the ventilation resistance of the air passage 30a increases.

Therefore, in the evaporator according to the third embodiment, in order to prevent an increase in ventilation resistance, the flow passage interval H2 of the air passage 30b is increased as shown in FIG. However, if the flow path interval H2 is simply increased, the air passage 30b
The flow rate of is greatly increased, and the heat transfer performance is reduced.

Therefore, in the third embodiment, the air passage 3
So that the aperture 36 can be formed at the tip of the windward side of 0b.
An L-shaped bent portion is formed at the tip of each of the heat transfer plates 22a and 22b. The throttle height L2 is determined according to the balance between ventilation resistance and heat transfer performance. This makes it possible to correct the distribution of the flow rate of air between the air passage 30a and the air passage 30b.

Since the parts other than the air passage are the same as those of the evaporator 10 according to the first embodiment, the description thereof will be omitted here.

As described in detail above, in the evaporator according to the third embodiment, the same effect as that of the evaporator according to the first embodiment can be obtained, and the air passage 30
Since the throttle 36 for adjusting the amount of inflow of air is provided at the windward end of b, it is possible to correct the flow rate distribution of the air conditioning air between the air passage 30a and the air passage 30b.

[Fourth Embodiment] In the fourth embodiment as well, another modification of the air passages 30a and 30b will be described.

As shown in FIG. 11, in the fourth embodiment, a second small protrusion 24b having a launch height smaller than that of the small protrusion 24a for disturbing the flow of air is provided for the heat transfer plates 22a and 22b. It is formed by stamping.

As shown in the figure, the position of the second small protrusion 24b in the plate width direction is the same position as the protrusion 14 of the heat transfer plate 12 to be bonded.

As a result, the refrigerant flow path 1 can be formed without deteriorating the adhesiveness between the heat transfer plate 12 and the heat transfer plate 22.
The cross-sectional area of 9 and 20 is enlarged, the ventilation resistance of the refrigerant is reduced, and the heat transfer promotion effect of the second small protrusions 24b is
The heat transfer performance for the air for air conditioning can be improved.

Since the parts other than the air passage are the same as those of the evaporator 10 according to the first embodiment, the description thereof is omitted here.

As described in detail above, in the evaporator according to the fourth embodiment, the same effect as that of the evaporator according to the first embodiment can be obtained, and the air passage 30 is provided.
Since the second small protrusions 24b are provided on the heat transfer plates 22a and 22b that form b, it is possible to reduce the ventilation resistance of the refrigerant and to transfer the air for air conditioning as compared with the case where the second small protrusions 24b are not provided. The thermal performance can be improved.

[Fifth Embodiment] In the fifth embodiment as well, another modification of the air passage 30a and the air passage 30b will be described.

As shown in FIG. 12, in the fifth embodiment, the heat transfer plate 22a and the heat transfer plate 12b or 1 are used.
One or more holes 38 are provided at the site where 2c is joined.
Thereby, air can be mixed between the air passage 30a and the air passage 30b, and as a result, the heat transfer performance can be improved as compared with the case where air is not mixed.

Since the parts other than the air passage are the same as those of the evaporator 10 according to the first embodiment, the description thereof is omitted here.

As described in detail above, the evaporator according to the fifth embodiment can achieve the same effects as the evaporator according to the first embodiment, and the air passage 30 can be obtained.
Since the hole for mixing the air for air conditioning is provided between a and the air passage 30b, the heat transfer performance can be improved as compared with the case where the hole is not provided.

In each of the above-described embodiments, the case where only one fluid (air for air conditioning) that exchanges heat is formed with the flow passages by combining a plurality of types of flow passage shapes has been described, but the present invention is not limited to this. For example, the flow paths of both fluids (air conditioning air and refrigerant) that exchange heat may be formed by combining a plurality of flow path shapes. in this case,
An increase in ventilation resistance can be prevented for both fluids, and as a result, heat transfer performance can be significantly improved. Furthermore, the present invention is applicable not only to air conditioning but also to radiators.

[0117]

According to the heat exchanger of the present invention, since at least one flow path of the first fluid and the second fluid for heat exchange is formed by a combination of a plurality of kinds of flow path shapes, ventilation is performed. The effect that the size can be reduced while ensuring the required heat transfer performance without increasing the resistance is obtained.

[Brief description of drawings]

FIG. 1 is an exploded perspective view showing an overall configuration of an evaporator 10 according to an embodiment.

FIG. 2 is a front view showing a configuration of a heat transfer plate 12a used in the evaporator 10 according to the embodiment.

FIG. 3 is a front view showing a configuration of a heat transfer plate 12b used in the evaporator 10 according to the embodiment.

FIG. 4 is a front view showing a configuration of a heat transfer plate 12c used in the evaporator 10 according to the embodiment.

FIG. 5 is a front view showing the configuration of a heat transfer plate 22a used in the evaporator 10 according to the embodiment.

FIG. 6 is a front view showing a configuration of a heat transfer plate 22b used in the evaporator 10 according to the embodiment.

FIG. 7 is a cross-sectional view taken along a cross section CC of each heat transfer plate in a state where it is incorporated in the evaporator 10.

FIG. 8 is a graph for explaining the effect of the present invention, and is a graph showing an example of a result of heat flow analysis performed using each of the conventional heat exchanger and the evaporator 10 according to the first embodiment.

FIG. 9 is a cross-sectional view taken along a cross section CC of each heat transfer plate in a state where the heat transfer plate is incorporated in the evaporator 10 according to the second embodiment.

FIG. 10 is a cross-sectional view taken along the cut plane C-C of each heat transfer plate in a state where the heat transfer plate is incorporated in the evaporator 10 according to the third embodiment.

FIG. 11 is a cross-sectional view taken along a cross section CC of each heat transfer plate in a state where the heat transfer plate is incorporated in the evaporator 10 according to the fourth embodiment.

FIG. 12 is a cross-sectional view taken along the cut plane C-C of each heat transfer plate in a state where the heat transfer plate is incorporated in the evaporator 10 according to the fifth embodiment.

FIG. 13 is an exploded perspective view showing a configuration example of the entire conventional evaporator.

14 is a cross-sectional view of the heat transfer plate 12a and the heat transfer plate 12b (12c) taken along the cut surfaces AA and BB in the state shown in FIG.

[Explanation of symbols]

10 Vehicle air conditioning evaporator 11 Core part 12a-12c Heat transfer plate 13 Board part 14 Projection 14a Small protrusion 15-18 Tank part 19, 20 Refrigerant passage 22a, 22b Heat transfer plate 23 Board part 24a small protrusion 30a Air passage (first flow path) 30b Air passage (second flow path)

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Yuji Nagata             Aichi Prefecture Nagachite Town Aichi District             Ground 1 Toyota Central Research Institute Co., Ltd. (72) Inventor Yutaka Yokoi             Aichi Prefecture Nagachite Town Aichi District             Ground 1 Toyota Central Research Institute Co., Ltd. (72) Inventor Masahiro Shimotani             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO F term (reference) 3L103 AA05 AA13 BB38 BB39 DD12                       DD22 DD57

Claims (3)

[Claims] 1. A heat exchange for exchanging heat between the first fluid and the second fluid by causing a low-temperature first fluid and a second fluid having a higher temperature than the first fluid to flow so as to intersect each other. A heat exchanger in which at least one flow path of the first fluid and the second fluid is formed by combining a plurality of kinds of flow path shapes. 2. When the flow path of one of the first fluid and the second fluid is formed by a combination of flow path shapes of a plurality of types, the flow path shapes of the plurality of types are used as a flow path of the other fluid. The heat exchanger according to claim 1, which has a shape capable of forming 3. A plurality of kinds of flow channel shapes, a first flow channel having a large number of protrusions for disturbing the flow, a flow channel width narrower than the first flow channel, and a number smaller than the first flow channel. Claim 1 or Claim 2 which has said projection, or has a 2nd flow path which does not have the said protrusion of the said 1st flow path, has a protrusion with a ventilation resistance smaller than the said protrusion, or 2nd shape. The heat exchanger according to 2.