JPH05248732A - Heat-exchanger - Google Patents

Abstract

PURPOSE:To obtain the above heat-exchanger wherein drains are prevented from falling to tank parts provided downward, and the corrosion resistance of these tank parts is improved, in a refrigerant evaporator. CONSTITUTION:A refrigerant evaporator is constructed by stacking a plurality of flow pipes 22, each of which is formed by joining a pair of formed plates 21. An inlet-side tank part 26 and an outlet-side tank part 27 are formed on both ends of the formed plates 21, these tank parts are allowed to communicate with each other, and thus a flow way part 28 is formed, at which heat-exchange is done between a refrigerant and the outside air. At the upstream side of this refrigerant evaporator, from which side the outside air flows therein, an inlet part 32 communicating with the flow way part 28 through the inlet side tank part 26 is arranged and at the downstream side thereof, an overhang part 35 is arranged. When this formed plate 21 is joined with one of the formed plates 21, which faces to each other, drains flowing-down on the surfaces of these formed plates 21 are received on the overhang parts 35 and are discharged outside.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger, which constitutes a refrigeration cycle of an air conditioner for an automobile,
The present invention relates to a refrigerant evaporator that evaporates a low pressure refrigerant by exchanging heat with air.

[0002]

2. Description of the Related Art Conventionally, for example, a laminated refrigerant evaporator has been used as a heat exchanger used in an air conditioner for automobiles. As shown in FIG. 11, in the laminated refrigerant evaporator 80, a pair of molding plates 81, 81 are faced to each other and joined to each other to form a flow passage tube 82 through which a refrigerant flows. The above flow path pipe 82
Are laminated in multiple layers, and a corrugated fin 83 for heat dissipation is interposed between them.

The refrigerant flowing from the inlet pipe 84 of the laminated refrigerant evaporator 80 is a low temperature and low pressure atomized refrigerant, flows in the flow passage pipes 82 laminated in multiple layers, and flows out from the refrigerant outlet pipe 85. .. The refrigerant flowing in the flow path pipe 82 exchanges heat with the air passing through the space portion 86 in which the corrugated fins 83 are interposed via the corrugated fins 83 to remove latent heat and evaporate. At this time, the refrigerant becomes a gas, and the air deprived of latent heat is cooled.

[0004]

In the laminated refrigerant evaporator 80 described above, when the air passing through the space 86 is cooled by heat exchange with the refrigerant, the water in the air is condensed to form drain water. And adheres to the surface portion 87 of the molding plate 81. This drain water flows down on the surface portion 87, flows down and accumulates on the upper portion 881 of the inlet side tank portion 88 provided below.

The drain water accumulated in the upper portion 881 is likely to corrode the upper portion 881, and a hole is formed in the upper portion 881, and the refrigerant flowing through the laminated refrigerant evaporator 80 may leak from the hole.

Also in other heat exchangers such as radiators, moisture adheres from the outside to the flow passage pipe through which the heat exchange fluid flows, and the adhered moisture flows down to the upper portion of the tank portion provided below. May stay.

Therefore, the present invention prevents the water such as drain water from flowing down to the upper side of the tank portion and staying there, and can improve the corrosion resistance of the upper portion of the tank portion provided below. The purpose is to provide.

[0008]

In order to achieve the above-mentioned object, the present invention provides a plurality of flow path pipes through which a heat exchange fluid communicates and a first end connected to a first end of the pipe. A heat exchange having a tank part and a second tank part connected to the second end part of the pipe, wherein at least the first tank part is arranged below the first end part of the pipe. In the container, a plate-shaped eave portion that extends from the side wall on the first end side of the pipe and that collects moisture flowing down the surface of the pipe is arranged above the first tank portion. It employs a heat exchanger.

In a preferred embodiment, the eaves portion is horizontally or lowered from the windward side where the medium for exchanging heat with the heat exchange fluid flows toward the pipe to the leeward side where the medium flows out, and A leeward end of the eaves portion is located at the leeward end of the first tank portion in the flowing direction of the medium that exchanges heat with the exchange fluid. adopt.

[0010]

According to the heat exchanger of the present invention having the above structure,
The heat exchange fluid flows in the pipe from the first tank portion or the second tank portion toward the other tank portion. This heat exchange fluid exchanges heat with the medium (eg, air) flowing outside the pipe in the pipe.

In this heat exchanger, when used as an evaporator, air is cooled by exchanging heat with the heat exchange fluid flowing in the pipe. The drain water attached to the surface of the pipe due to the cooling of the air flows down on the surface of the pipe under the influence of gravity.

Since a plate-shaped eave portion is provided which extends from the side wall on the first end side of the pipe and collects water flowing down on the surface of the pipe, drain water flowing down on the surface of the pipe is provided. Spills over this eaves. Due to the eaves portion, the drain water is discharged to the outside on the leeward side without flowing down onto the first tank portion.

Moisture adhering to the pipe due to other factors is also discharged to the outside on the leeward side without flowing down on the first tank portion by the eaves portion, like the drain water. In addition, by forming the eaves horizontally or lowering from the leeward side toward the leeward side, the drain water that has flown down to the eaves portion can easily flow to the leeward side, and even more to the upper part of the first tank section. Disappear.

[0014]

Embodiments of the present invention will be described below with reference to the drawings. In this embodiment, the refrigerant evaporator will be described in detail. 1 to 4 show an example of a refrigerant evaporator according to the present invention. 1 shows a molded plate used for a flow path pipe, FIG. 2 is a sectional view taken along line 2-2 of FIG. 1, FIG. 3 is a side view of a laminated refrigerant evaporator, and FIG. 4 is a perspective view of the laminated refrigerant evaporator. The figure is shown.

The laminated refrigerant evaporator 20 used in the first embodiment of the present invention includes a flow path pipe 22 formed by joining a pair of molding plates 21 and an adjacent flow path pipe 22. Space section
A plurality of corrugated fins 23 arranged in 34 are laminated and integrally brazed.

The molding plate 21 is formed into a shallow dish by pressing a thin plate-shaped aluminum alloy. The forming plate 21 has a joint wall 24 formed on the outer peripheral edge thereof to be joined to the outer peripheral edge of the other opposing forming plate 21. When the other molding plate 21 facing each other is joined to the upper side of the paper surface of FIG. 1, a flow path pipe 22 is formed as shown in the sectional view of FIG. The dotted line part shown in FIG. 2 shows the forming plate 21 facing each other, and the solid line part shows the 2-2 sectional view of FIG.

As shown in FIG. 2, the molding plate 21 is joined to the molding plate 21 facing the joining wall 24 provided on the outer peripheral edge thereof, and the inlet side tank portion 26 (corresponding to the first tank portion) is provided at both ends. ) And the outlet side tank portion 27 (corresponding to the second tank portion) are formed so as to project. This inlet side tank section 26
A flow path portion 28 that communicates with the outlet side tank portion 27 is formed so as to project to the same side as each tank portion.

The inlet side tank portion 26 has an elliptical shape, and atomized refrigerant (dryness 0.4, that is, liquid refrigerant: refrigerant gas = 6: 4) flows from the expansion valve 29 through the inlet pipe 30. And
Each inlet-side tank section 26 disperses the atomized refrigerant flowing in from the expansion valve 29 into the flow channel section 28 of each flow channel tube 22. Further, the inlet-side tank portion 26 is the inlet-side tank portion 26 of the other adjacent flow path pipe 22.
Has a communication window 261 communicating with.

The outlet side tank portion 27 has an elliptical shape and collects the refrigerant gas flowing from each flow path pipe 22 to form an outlet pipe.
Refrigerant gas is caused to flow to the refrigerant compressor (not shown) via 31. Further, the outlet side tank portion 27 is provided with another adjacent flow path pipe 22.
Has a communication window 271 communicating with the outlet side tank portion 27.

The flow passage portion 28 has a flat shape and is a portion for evaporating the refrigerant by exchanging heat between the refrigerant passing through the inside and the air passing through the outside. Inlet tank part 26 and flow path part 28
1, an inlet portion 32 through which the atomized refrigerant flows from the inlet side tank portion 26 is formed between and.

Between the outlet side tank section 27 and the flow path section 28,
As shown in the upper end of FIG. 1, a plurality of protruding joint portions 331 are formed. Between this joint 331, 331 and the joint wall
An outlet portion 33 through which the refrigerant gas flows from the flow path portion 28 is formed between the 24 and the joint portion 331. The atomized refrigerant that has flowed in from the inlet section 32 is heat-exchanged in the flow path section 28 to become a refrigerant gas.

The inlet portion 32 is formed on the windward side (in the direction of arrow P in the drawing) through which air passes through the space portion 34 between the adjacent flow path pipes 22. An overhanging portion 35 is formed on the leeward side of the inlet 32. The overhang portion 35 is formed below the flow path portion 28 and above the inlet tank portion 26. As shown in FIG. 2, the projecting portion 35 is formed so as to project at the same height as the inlet tank portion 26 and the outlet tank portion 27. In the direction of air flow, the leeward side end of the overhanging portion 35 is formed to be on the same side of the leeward side end of the inlet side tank portion 26, and is located further downwind than that. Is formed so that the upper surface portion 351 thereof is horizontal or descends to the leeward side.

The upper portion 36 and the inlet portion 32 on the upper side of the overhang portion 35
The windward side portion 37 between the bulge and the overhanging portion 35, and the lower side lower portion 38 of the overhanging portion 35 are formed around the overhanging portion 35, and the upper side portion 36, the windward side portion 37, and the lower side portion. 38 is joined to each part of the other molding plate 21 facing each other.

When a plurality of flow path pipes 22 are laminated and brazed, the adjacent overhanging portion 35, the inlet side tank portion 26, and the outlet side tank portion 27 are joined to each other, and as shown in FIG. Twenty is formed. Adjacent overhang portions 35, 35 are joined to form a plate-shaped canopy portion 40 that straddles between the adjacent flow path portions 28, 28. Since the overhang portion 35 is formed as described above, the leeward side end portion of the eaves portion 40 is also placed in the same direction as the leeward side end portion of the inlet side tank portion 26 in the direction of air flow. The upper surface 351 is formed so as to be located further downwind, and the upper surface portion 351 is formed so as to be horizontal or downwind.

FIG. 3 is a side view seen from the leeward side (opposite arrow P in FIG. 1) through which the air that exchanges heat with the refrigerant flowing in the flow path pipe 22 flows out. Overhang space section divided by overhang section 35
41 is formed by stacking the molding plates 21, and the overhanging space portion 41 has a structure in which the leeward side communicates with the outside.

Further, a plurality of ribs 25 projecting on the flow passage surface through which the refrigerant flows are formed in the central portion of the molding plate 21. Like the joint wall 24, the joint portion 331, the upper side portion 36, the windward side portion 37, and the lower side portion 38, the rib 25 is formed by the pair of molding plates 21, 21.
When the flow path pipe 22 is formed by joining the above, the ribs 25 formed on the opposing molding plate 21 are crossed and joined.

Next, the operation of the laminated refrigerant evaporator 20 of the first embodiment will be described with reference to FIGS. The mist-like refrigerant flows from the expansion valve 29 into the inlet-side tank portion 26 of the laminated refrigerant evaporator 20 through the inlet pipe 30. The atomized refrigerant that has flowed into the inlet-side tank portion 26 flows into the flow path portion 28 from the inlet portion 32. The mist-like refrigerant flowing into the flow path portion 28 exchanges heat with the air passing through the space portion 34 and evaporates. Therefore, in the refrigerant, the amount of the gas component (gas refrigerant) gradually increases from the inlet 32 toward the outlet 33.

The air passing through the space 34 exchanges heat with the refrigerant flowing in the flow path pipe 22 and is cooled. When the air is cooled, the moisture in the air is condensed to form drain water, which adheres to the surface portion 39 of the molding plate 21 on the side of the space portion 34. The drain water attached to the surface portion 39 flows down on the surface portion 39 due to the influence of gravity, and as shown in FIG. 3, flows down to the upper surface portion 351 of the eaves portion 40 formed by joining the adjacent overhanging portions 35.

The eaves portion 40 is formed so as to be horizontal or downwind, and the air flows in the direction of the arrow. Therefore, the drain water that has flown down to the upper surface portion 351 of the eaves portion 40 flows over the upper surface of the eaves portion 40 to the outside. Is discharged to.

Therefore, the drain water that has flowed down the surface portion 39 of the molding plate 21 is provided at the inlet side tank portion 26 provided below.
Since it flows down to the upper surface 261 of the inlet and is discharged outside without staying, the upper surface 26
It is possible to prevent drain water from flowing down to 2 and to corrode the upper surface portion 262.

The drain water may corrode the upper surface portion 351 of the overhanging portion 35 forming the eaves portion 40. However, even if the upper surface portion 351 corrodes and a hole is formed, it flows over the lower surface portion 352 in the overhanging space portion 41 formed by the overhanging portion 35 and is discharged to the outside. Since the drain water flows on the lower surface portion 352, the upper surface portion 26 of the inlet side tank portion 26 provided below
It doesn't run down to 2.

When the lower surface portion 352 is also corroded by the drain water and a hole is opened, the drain water flowing down the surface portion 39 leaks from the hole and the inlet side tank portion provided below.
May fall onto the upper surface 262 of 26.

However, as shown in FIG. 11, as compared with the conventional laminated refrigerant evaporator 80 in which the overhanging portion 35 is not formed, the upper surface portion 351 of the overhanging portion 35 is formed on the upper portion of the inlet side tank portion. The two plates forming the lower surface 352 are additionally provided. The plates forming the upper surface portion 262 of the inlet side tank portion 26, the upper surface portion 351 and the lower surface portion 352 of the overhanging portion 35 have the same thickness, and therefore, the conventional laminated refrigerant evaporator 80.
Compared with the structure without the overhanging portion 35 as described above, the same effect can be obtained as when the upper surface portion 262 of the inlet side tank portion 26 provided below is substantially tripled in thickness.

The same effect can be obtained by simply forming only the upper surface portion 262 of the inlet side tank portion 26 thick.
Since the laminated refrigerant evaporator 20 is integrally formed by press working, only the upper surface portion 262 of the inlet side tank portion 26 cannot be formed thick. It is not appropriate to form the molding plate 21 as a whole thickly in consideration of problems such as heat exchange performance.

In this structure, an inlet portion 32 through which the refrigerant flows from the inlet tank portion 26 to the flow passage portion 28 is provided on the windward side,
The overhang portion 35 is provided on the leeward side. When air exchanges heat with the refrigerant flowing in the space portion 34 and flowing in the flow path pipe 22, the air is cooled by this refrigerant. The air that has flowed into the space portion 34 is not yet sufficiently cooled near the windward side, and the moisture in the air will not condense. When the air flows into the vicinity of the leeward side, it is sufficiently cooled by heat exchange with the refrigerant, and moisture in the air is condensed.

Therefore, on the leeward side, drain water generated by condensation of water in the air is generated. Therefore, by providing the overhanging portion 35 on the leeward side, the upper surface portion 26 of the inlet tank portion 26 provided below is formed.
2 It is possible to prevent the drain water from flowing down.

In this embodiment, the inlet-side tank portion 26 is provided below and the outlet-side tank portion 27 is provided above. However, the outlet-side tank portion 27 is provided below and the inlet-side tank portion 27 is provided below.
Even if 26 is provided above, the same effect can be obtained that drain water is prevented from flowing down to the upper surface of the tank section provided below.

Further, in the present embodiment, only one inlet portion 32 through which the refrigerant flows from the inlet tank portion 26 to the flow passage portion 28 is formed, but a plurality of inlet portions 32 are formed on the windward side of the overhang portion 35. May be.

As disclosed in Japanese Unexamined Patent Publication No. 51-77952, the refrigerant evaporator may have a single inlet portion 32 for flowing the refrigerant from the inlet tank portion 26 to the flow passage portion 28 as in this embodiment. It is known that the heat exchange performance of the refrigerant does not deteriorate, and that the heat exchange performance of the refrigerant evaporator deteriorates when the outlet portion 33 through which the refrigerant flows from the flow passage portion 28 to the outlet side tank portion 27 is narrowed. Therefore, as in the present embodiment, if the inlet side tank portion 26 is arranged below and only the inlet portion 32 is narrowed, the heat exchange performance will not deteriorate.

Next, a second embodiment of the present invention will be described with reference to FIG. Similar to the first embodiment, the laminated refrigerant evaporator of the present embodiment has a space between the flow path pipe 22 formed by joining the pair of molding plates 42 and the adjacent flow path pipe 22. Department
A plurality of corrugated fins 23 arranged in 34 are laminated and integrally brazed. The same components as those in the first embodiment are designated by the same reference numerals.

Like the overhanging portion 35 of the first embodiment, the overhanging portion 35 is formed so as to descend from the side of the inlet portion 32 provided on the windward side toward the leeward side. This overhanging portion 35 is bent on the leeward side and is formed up to the leeward side next to the inlet side tank portion 26.

Since the overhanging portion 35 is formed to the leeward side of the inlet side tank portion 26, the inlet side tank portion 26 is narrower than the outlet side tank portion 27. The overhang portion 35 is formed up to the lower end of the molding plate 21, and has a structure in which the lower end communicates with the outside.

As in the case of the second embodiment, even if the overhanging portion 35 is formed to overhang to the leeward side of the inlet side tank portion 26 provided below, the drain water that flows down is overhanging. 35
Is discharged to the leeward side by the
It is possible to prevent it from running down.

Next, a third embodiment of the refrigerant evaporator of the present invention will be described with reference to FIGS. The laminated refrigerant evaporator of the present embodiment is similar to the first and second embodiments in that the flow path pipe 22 formed by joining the pair of molding plates 43 and the adjacent flow path pipes are formed. A plurality of corrugated fins 23 arranged in a space 34 between the corrugated fins 22 and 22 are laminated and integrally brazed. The same components as those in the first and second embodiments are designated by the same reference numerals.

The molding plate 43 used in this embodiment is a partition wall 44 joined to the central portion of the other molding plate facing the other.
Is formed in the central part. An inlet-side tank portion 26 and an outlet-side tank portion 27 are formed at the lower end portion, and the inlet-side tank portion 26 and the outlet-side tank portion 27 are communicated above the other portion to form a U-shape for heat exchange of the refrigerant. A flow path portion 28 is formed.

The communication part 45 makes a U-turn of the refrigerant flowing from the inlet side tank part 26 and flows out to the outlet side tank part 27. An outlet side tank portion 27 is formed on the windward side (in the direction of the arrow 46 in the drawing) through which air passes through the space portion 34 between the adjacent flow path pipes 22, and an inlet side tank portion 26 is formed on the leeward side. The inlet part 32 flowing from the inlet side tank part 26 to the flow path part 28 is provided on the windward side, as in the first and second embodiments.
An overhanging portion 35 is formed on the leeward side.

Inlet side tank section 26 and outlet side tank section 27
As shown in the sectional views of FIGS. 7 and 8, the configuration is similar to that of the first and second embodiments. Also in this embodiment, when the refrigerant flowing in the flow path pipe 22 and the air flowing in from the direction of the arrow 45 exchange heat, the air is cooled. However, the air that has flowed into the space 34 is not yet sufficiently cooled near the windward side, and the moisture in the air will not condense. When the air flows into the vicinity of the leeward side, it is sufficiently cooled by heat exchange with the refrigerant, and moisture in the air is condensed.

Therefore, on the leeward side, since drain water in which moisture in the air is condensed is generated, the bulge portion 35 is not provided above the outlet side tank portion 27 provided on the windward side, and the drainage water is provided on the leeward side. By providing the overhanging portion 35 only above the inlet side tank portion 26 provided, the inlet side tank portion provided below
It is possible to prevent drain water from flowing down to the upper surface portion 262 of the 26.

In this embodiment, the inlet side tank portion 26 is provided on the windward side, and only the inlet portion flowing from the inlet side tank portion 26 to the flow passage portion 28 is narrowed, so that the heat exchange performance as the refrigerant evaporator is achieved. Will not be affected.

Next, a fourth embodiment of the refrigerant evaporator of the present invention will be described with reference to FIGS. 9 and 10. The refrigerant evaporator 50 of this embodiment includes a core part 56 for exchanging heat between the refrigerant and air, an inlet side tank 53 into which a refrigerant supplied from an expansion valve (not shown) flows from an inlet pipe 57, and a core part. It is composed of an outlet side tank 54 into which the refrigerant flows from 56, and is manufactured by integral brazing.

The core portion 56 is formed by alternately laminating a large number of flat tubes 51 and corrugated fins 52. Flat tube
The plate 51 is formed by forming one plate into a hollow flat shape and brazing the ends thereof. The flat tube 51 is provided with an inlet tank 53 at the bottom and an outlet tank 54 at the top.

In the structure of this embodiment, in addition to the above-mentioned structure known in the related art, a comb-shaped plate portion 55 (see FIG. 1) is provided above the inlet side tank 53 provided below and below the corrugated fins 52.
No. 0) is provided, and the flat tube 51 is fitted and brazed.

As shown in FIG. 10, the plate portion 55 has a hole portion 60,
It is composed of an insertion portion 61 and a support portion 62. Hole 60 is a flat tube
51 is formed so that it can be fitted, and the insertion portion 61 is formed so as to match the interval at which the flat tubes 51 are stacked.
As shown in FIG. 9, the air is a corrugated fin of the core portion 56.
It is assumed that the space 59 in which the 52 is interposed flows in from the direction of the arrow. The leeward side end portion of the support portion 62 of the plate portion 55 is provided so as to be located on the same leeward side as the leeward side of the inlet side tank 53 provided below and in the leeward side of the same in the air flow direction. There is.

Further, the plate portion 55 is arranged so as to descend horizontally or from the windward side toward the leeward side. In the refrigerant evaporator 50, the refrigerant flowing from the inlet pipe 57 into the inlet side tank 53 flows into the flat tube 51 and exchanges heat with the air flowing through the space 59 in which the corrugated fins 52 of the core 56 are interposed. .. The refrigerant that has exchanged heat with the air flows into the outlet side tank 54, and the refrigerant gas is discharged to the refrigerant compressor (not shown) through the outlet pipe 58.

Similar to the first to third embodiments, the space portion
The air passing through 59 exchanges heat with the refrigerant flowing in the flat tube 51 and is cooled. When the air is cooled, the moisture in the air is condensed to form drain water and adhere to the surface of the flat tube 51. The drain water attached to the surface of the flat tube 51 flows down on the surface of the flat tube 51 due to the influence of gravity, and then flows down to the upper surface portion 551 of the plate portion 55.

Since the plate portion 55 is arranged horizontally or descends from the windward side toward the leeward side, the drain water flowing down to the upper surface portion 551 of the plate portion 55 flows down the upper surface portion 551 and is downwind. Discharged to the side. This plate portion 55 is equivalent to the inlet side tank 53 provided below, or is provided downwind. Therefore, it is discharged to the outside without flowing down to the plate portion 55.

Therefore, the inlet side tank 53 provided below
The upper part of this tank does not corrode because it does not flow down to. This plate portion 55 is a flat tube 51,
Since it is provided as a separate member from the inlet side tank 53 and the outlet side tank 54, there is no restriction on the thickness. Therefore, by thickening the plate portion 55, it is possible to prevent drain water from flowing down, corroding the plate portion 55, and preventing holes from being formed.

Further, in the present embodiment, the inlet side tank 53 and the flat tube provided in the lower portion are arranged so that the inlet portion 32 in the first to third embodiments is narrowed to form the overhanging portion 35. In order not to narrow the connecting part with 51, even if the inlet side tank and the outlet side tank are provided in any of the upper and lower sides,
It does not affect the heat exchange performance.

The same effect can be obtained by using the comb-shaped plate portion 55 in a conventionally known laminated refrigerant evaporator. In addition, in the first to third embodiments, the overhanging portions 35 of the molding plates 21 facing each other are brazed, but the present invention is not limited to this, and only the drain water is in contact so as not to flow down. Good.

The comb-shaped plate portion 55 may be configured so that it is only fitted into the flow passage tube 22 or the flat tube 51 and is not brazed. Further, in the present embodiment, although the drain water in the refrigerant evaporator has been referred to, the present invention is not limited to this, and when water adheres to the flow passage tubes of other heat exchangers such as a radiator, this water flows off. It is possible to prevent stagnation in the tank portion provided below the flow path pipe by providing the eaves portion as described above.

[0061]

As described above, according to the present invention,
By providing the eaves portion above the first tank portion provided below, water such as drain water flowing down on the surface of the pipe flows on the eaves portion and is discharged without flowing to the upper portion of the first tank portion. It

Therefore, it is possible to prevent the water flowing down the surface of the pipe from flowing down to the upper portion of the first tank portion, and there is no risk of the upper portion of the tank portion corroding. Therefore, the upper portion of the tank portion provided below is prevented. The corrosion resistance of can be improved.

[Brief description of drawings]

FIG. 1 is a front view showing a molding plate used in a first embodiment of the present invention.

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

FIG. 3 is a side view showing an embodiment of the present invention.

FIG. 4 is a perspective view showing an embodiment of the present invention.

FIG. 5 is a front view of a molding plate showing a second embodiment of the present invention.

FIG. 6 is a front view of a molding plate showing a third embodiment of the present invention.

7 is a sectional view taken along line 7-7 of FIG.

8 is a sectional view taken along line 8-8 of FIG.

FIG. 9 is a perspective view showing a fourth embodiment of the present invention.

FIG. 10 is a diagram showing a plate member used in a fourth embodiment of the present invention.

FIG. 11 is a side view showing a conventional example.

[Explanation of symbols]

 20 Laminated Refrigerator Evaporator 21 Forming Plate 22 Flow Path Tube 23 Corrugated Fin 26 Inlet Side Tank Section 27 Outlet Side Tank Section 28 Flow Path Section 35 Overhanging Section 55 Plate Section

Claims (6)

[Claims] 1. A plurality of flow path tubes communicating with a heat exchange fluid, a first tank section connected to a first end section of the flow path tube, and a second end section of the flow path tube. A second tank part connected to the heat exchanger, wherein at least the first tank part is arranged below the first end part of the flow path pipe, A heat exchanger in which a plate-shaped eave portion extending upward from a side wall on the first end side of the flow channel pipe and for collecting water flowing down the surface of the flow channel pipe is arranged above. 2. The eaves portion is horizontal or descends from the windward side where the medium that exchanges heat with the heat exchange fluid flows toward the flow path pipe to the leeward side where the medium flows out. The heat exchanger described. 3. The leeward end of the eaves portion is located on the same side of the leeward end of the first tank portion in the flowing direction of the medium that exchanges heat with the heat exchange fluid. The heat exchanger according to claim 1, wherein the heat exchanger is located at. 4. The heat exchanger according to claim 1, wherein the eaves portion has a comb shape in which a plurality of concave portions are formed in parallel, and the concave portions of the eaves portion are fitted to the flow path pipe. 5. A pair of plates are swelled to mutually opposite sides to form the flow path pipe, the first tank portion and the second tank portion, and a plurality of the pair of plates are laminated. The heat exchanger according to claim 1, wherein 6. The eaves portion is formed by bulging the plate by the same amount as the tank portion, and the periphery of the eaves portion is formed so as to be joined to the opposing plate, and the flow passage pipe and the first The heat exchanger according to claim 5, wherein a flow path formed by bulging the plate so as to communicate with the tank is formed on the windward side of the eaves.