JP2000241093A - Air heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the draining ability of an air heat exchanger provided with flat perforated heat transfer tubes and corrugated fins. SOLUTION: This air heat exchanger is provided with flat perforated heat transfer tubes 1, 1,... each having a plurality of refrigerant flowing holes 2, 2,... inside and the tubes 1, 1,... are vertically arranged in parallel. In addition, corrugated fins are brazed among the tubes 1, 1,.... In this case, drainage ditches 3 having depths which are about 1/2 of the thicknesses of the tubes 1, 1,... are provided on the surfaces of the tubes 1, 1,... not corresponding to either one or both of the flat heat transfer surfaces 1a and 1b of the tubes 1, 1,... which become the brazing surfaces for the corrugated fins.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of a flat heat transfer tube of an air heat exchanger having a multi-hole flat heat transfer tube and a corrugated fin.

[0002]

2. Description of the Related Art Recently, an air heat exchanger provided with a flat heat transfer tube and a corrugated fin has been provided, for example, as a heat exchanger for an air conditioner.

FIGS. 48 to 51 show a general air heat exchanger including such a flat heat transfer tube and a corrugated fin, and the structure of each part.

As shown in FIG. 48, for example, the air heat exchanger 10 is connected to pipe-shaped upper and lower headers 12A and 12B through which a refrigerant is introduced and discharged, and communicates between the upper and lower headers 12A and 12B. The plurality of flat heat transfer tubes 1, 1... Extending in the vertical direction while maintaining a predetermined interval from each other in the longitudinal direction, and the upper and lower portions between the plurality of flat heat transfer tubes 1, 1. Are arranged in a state of being continuously bent in a substantially rectangular shape in the direction, and the outer end of the bent surface is a flat heat transfer surface (brazing surface) 1a of the corresponding flat heat transfer tube 1, 1. 1b are heat-welded to the corrugated fins 11, 11...

The flat heat transfer tubes 1, 1..., For example, as shown in FIG. Have a multi-hole structure having a plurality of refrigerant circulation holes 2, 2... Having a rectangular cross section, and are introduced and distributed from the outside via the upper header 12A. The refrigerant flows evenly into each of the refrigerant flow holes 2, 2,..., And the flat heat transfer surfaces 1a, 1b and the corrugated fins 11, 1,.
The heat exchange between the internal refrigerant and the external air is performed efficiently with a sufficiently large heat transfer area via the fin surfaces of 1.

[0006] Such an air heat exchanger is generally called a multi-flow air heat exchanger, and has been relatively frequently used as a condenser since it has a low pressure loss, a high heat exchange performance, and can be made compact. .

Recently, attempts have been made to apply such a multi-flow type air heat exchanger to an evaporator.

However, in the case of an evaporator, unlike a condenser,
There is a problem that condensed water (condensed water) is generated. When the heat exchanger structure having the above configuration is applied to the evaporator as it is, the core portion (flat heat transfer tubes 1, 1... And corrugated fins) are exchanged during heat exchange. The condensed water (condensed water) generated in the portions 11, 11,...
Since it is difficult to smoothly drain the water downward, it is easy to cause frost due to stagnation or water splash behind the air flow, and it is hard to say that the heat exchange efficiency is perfect.

Therefore, when the multi-flow type air heat exchanger functions as an evaporator as described above, the performance of discharging condensed water (condensed water) in the heat exchanger core is effectively improved, and the efficiency is improved. For the purpose of realizing good heat exchange performance, for example, as shown in FIG. 50 or FIG. 51, the corrugated fins 1 of the flat heat transfer tubes 1, 1,.
The condensed water (condensed water) is supplied to the flat heat transfer tubes 1, 1... On the left and right surfaces of the front edge A side or the rear edge B side of the flat heat transfer surfaces 1 a, 1 b. And corrugated fins 11,
There has been proposed an air heat exchanger in which concave drain grooves 13, 13 are formed from the upper end to the lower end so as to be allowed to flow downward from between 11 and 11 (see, for example, JP-A-10-197173).

In such a configuration, the flat heat transfer tubes 1, 1.
Is provided so as to extend vertically, condensed water (condensed water) generated in the core tends to flow downward from above. In such a case, the condensed water (condensed water) is drained by the drain grooves 13, 13 provided on the corrugated fins 11, 11,... Of the flat heat transfer tubes 1, 1,. Flowing down through the grooves 13, 13, the discharge of the condensed water (condensed water) is not hindered by the corrugated fins 11, 11. Therefore, relatively smooth condensed water (condensed water) discharge performance is realized.

[0011]

However, when the flat heat transfer tubes 1 are provided with drain grooves 13, 13 on both sides 1a, 1b of the same portion on the left and right sides corresponding to each other in front-to-back relationship as in the conventional example, In order to secure the rigidity of the heat transfer tube, the drain grooves 13, 13 have a depth t which is considerably smaller than a thickness (t / 2) of 1/2 of the thickness t of the flat heat transfer tube as shown in the figure.
Only the groove of o can be formed.

Therefore, in a configuration like the above-mentioned conventional example,
Cannot discharge a sufficient amount of condensed water (condensation water). In addition, there is a problem that the drainage grooves 13 are closed by the brazing material when brazing the corrugated fins.

The present invention has been made in order to solve such a problem, and the heat transfer surface on one side of the flat heat transfer tube as described above or the two flat surfaces having different positions which do not correspond to each other are respectively provided. By providing a drainage groove with a sufficient depth of about 1/2 of the thickness of the entire heat transfer tube, it is possible to prevent the clogging by the brazing material when attaching the corrugated fins and to provide an air heat exchanger with a sufficiently large drainage capacity. It is intended to provide.

[0014]

Means for Solving the Problems Each invention of this application is provided with the following means for solving the problems in order to solve the above-mentioned problems.

(1) The air heat exchanger according to the present invention has a multi-hole flat heat transfer tube 1, 1,... Having a plurality of refrigerant circulation holes 2, 2,.
Are arranged in parallel to extend in the up-down direction and the plurality of flat heat transfer tubes 1, 1.
The corrugated fins 11, 11,... Of the flat heat transfer tubes 1, 1,.
A drain groove 3 having a depth of at least about の of the thickness of the flat heat transfer tubes 1, 1... On either side of the left and right flat heat transfer surfaces 1 a, 1 b serving as a brazing surface. Is provided.

In this configuration, the drain groove 3 is provided only on one of the left and right brazing surfaces 1a and 1b of the flat heat transfer tubes 1, 1... The depth is at least の of the thickness t of the flat heat transfer tubes 1, 1...
It can be formed sufficiently deep before and after, and can be configured as a drainage groove having a sufficient drainage capacity, and can be prevented from being blocked by the adhesion of the brazing material when the corrugated fin brazing is attached.

(2) The air heat exchanger according to the present invention has a multi-hole flat heat transfer tube 1, 1,... Having a plurality of refrigerant circulation holes 2, 2,.
Are arranged in parallel to extend in the up-down direction and the plurality of flat heat transfer tubes 1, 1.
The corrugated fins 11, 11,... Of the flat heat transfer tubes 1, 1,.
The flat heat transfer tubes 1, 1... At positions that do not correspond to each other on the left and right flat heat transfer surfaces 1 a and 1 b, which are the brazing surfaces for
And a drain groove 3 having a depth of at least about の of the thickness of.

In this configuration, the drain groove 3 is provided only at a position that does not correspond to each of the surfaces 1a, 1b of the two left and right brazing surfaces 1a, 1b of the flat heat transfer tubes 1, 1,. The depth can be formed to be sufficiently deep at least about 1/2 of the thickness t of the flat heat transfer tubes 1, 1... The corrugated fins 11, 11,... Are not blocked by the adhesion of the brazing material at the time of brazing.

(3) The third aspect of the present invention provides an air heat exchanger having a flat heat transfer tube having a multi-hole structure having a plurality of refrigerant circulation holes 2, 2,.
Are arranged in parallel to extend in the up-down direction and the plurality of flat heat transfer tubes 1, 1.
The corrugated fins 11, 11,... Of the flat heat transfer tubes 1, 1,.
A drain groove having a depth of at least about 1/2 of the thickness of the flat heat transfer tubes 1, 1... On one of the left and right flat heat transfer surfaces 1a, 1b excluding the brazing surface 3 is provided.

In this configuration, the drain groove 3 is formed only on one of the flat heat transfer surfaces 1a and 1b excluding the two left and right brazing surfaces of the flat heat transfer tubes 1, 1. Since it is not provided, it is necessary to form the depth sufficiently deep at least about 1/2 of the thickness t of the flat heat transfer tubes 1, 1... It is possible to form a drainage groove having a sufficient drainage capacity, and it is possible to prevent the corrugated fins 11, 11,.

(4) The air heat exchanger according to the present invention has a multi-hole flat heat transfer tube 1, 1,... Having a plurality of refrigerant circulation holes 2, 2,.
Are arranged in parallel to extend in the up-down direction and the plurality of flat heat transfer tubes 1, 1.
The corrugated fins 11, 11,... Of the flat heat transfer tubes 1, 1,.
The flat heat transfer tubes 1, 1... At positions that do not correspond to each other on the left and right flat heat transfer surfaces 1a, 1b except for the brazing surfaces
And a drain groove 3 having a depth of at least approximately one half of the thickness of the drain groove 3 is provided.

In this configuration, the drain groove 3 is provided only on one of the flat heat transfer surfaces 1a and 1b excluding the two right and left brazing surfaces of the flat heat transfer tubes 1, 1. Since it is not provided, it is necessary to form the depth sufficiently deep at least about 1/2 of the thickness t of the flat heat transfer tubes 1, 1... It is possible to form a drainage groove having a sufficient drainage capacity, and it is possible to prevent the corrugated fins 11, 11,.

[0023]

As described above, according to the air heat exchanger of the present invention, it is possible to provide an air heat exchanger for an evaporator having a high heat exchange performance provided with a flat heat transfer tube and a corrugated fin.

[0024]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (Embodiment 1) FIGS.
3 shows the structure of a flat heat transfer tube portion of an air heat exchanger according to a basic example of Embodiment 1 of the present invention and various modifications 1 to 4 thereof.

-Basic Example- The flat heat transfer tubes 1, 1...
For example, as shown in FIG. 1, the front edge A side and the rear edge B side end portions which are sectioned and arranged side by side in the inner width direction via a partition are semicircular in cross section, and those between them are rectangular in cross section. Has a multi-hole structure having a plurality of refrigerant circulation holes 2, 2,..., And the entire inner peripheral surface of each of the refrigerant circulation holes 2, 2,. A large number of projections having, for example, a triangular cross section are provided at predetermined pitches to increase the heat transfer area accordingly.

Then, as shown in FIG. 48 described above, a plurality of the members extend in the vertical direction and are juxtaposed, and as shown in FIG.
Between them, the bent surfaces of the corrugated fins 11, 11,... Are brazed over substantially the entire flat heat transfer surfaces 1a, 1b from their leading edge A to trailing edge B, respectively. , The refrigerant introduced and distributed from the outside via the upper header 12A flows evenly into the respective refrigerant circulation holes 2, 2,..., And the corrugated fins 11 integrated adjacently on both sides thereof , 11..., Heat exchange is efficiently performed between the refrigerant flowing inside and the outside air with a heat transfer area as large as possible.

The flat heat transfer surfaces 1a, 1b of the flat heat transfer tubes 1, 1,... To be brazed to the corrugated fins 11, 11,.
The second and third refrigerant flow holes on the front edge A side are formed in the solid portion 1c instead of the refrigerant flow holes, and the solid portion 1c
The flat heat transfer tubes 1, 1,..., As far as they can secure the necessary and sufficient rigidity of the solid portion 1 c.
A drain groove 3 having a depth t1 of about 1/2 of the thickness t of the _first or second or more is provided.

Therefore, as shown in FIG. 44, substantially the entire surface of the flat heat transfer surfaces 1a and 1b except for at least the respective end surfaces on the front edge A side and the rear edge B side is formed as a brazing surface. Also when the bent surfaces of the fins 11, 11,... Are brazed, the corrugated fins 11, 11,.
Are formed between the bent surface and the flat heat transfer surface 1a, and the drain groove 3 having a necessary and sufficient cross-sectional area (width × depth) is formed. Drainage action is ensured.

In the configuration of this basic example, as described above, the flat heat transfer surface on either one of the left and right flat heat transfer surfaces 1a, 1b to be brazed surfaces of the flat heat transfer tubes 1, 1,... Since the drain groove 3 is provided only on the side 1a, the depth t ₁ is set to be equal to the thickness t of the flat heat transfer tubes 1, 1,... / 2 or more, and by setting the width to an arbitrary size (in this example, two coolant circulation holes), it has a sufficient drainage capacity. The corrugated fins 11, which can be formed in the drain grooves 3,
11 ... The drain groove 3 is not blocked even by the adhesion of the brazing material at the time of brazing.

Further, since the drain groove 3 is provided on the front edge A side where the temperature difference between the refrigerant and the air is large and the amount of condensed water and the amount of frost generated are large, the generated large amount of water is generated. Will be effective and appropriate for emission.

Therefore, according to the air heat exchanger, the flat heat transfer tubes 1, 1,... And the corrugated fins 11, 11,.
.. Having a high heat exchange performance can be provided.

(Modification 1) Next, FIG. 2 shows a structure of the basic example shown in FIG. 1 in which the width of the drain groove 3 is reduced to one of the coolant circulation holes 2 so that the front edge A side 2 It is characterized in that it is provided in the second refrigerant flow hole portion.

The other structure is the same as the basic example shown in FIG.

In the case of such a configuration, the same operation and effect as in the case of the above basic example can be obtained. In comparison with the basic example of FIG. 1 described above, the drainage capacity is reduced by the smaller width of the drainage groove 3, but only one refrigerant circulation hole is reduced. I'm done.

(Modification 2) Next, FIG. 3 shows that the width of the drain groove 3 is changed to the width of the refrigerant flow hole 2 by one as in the configuration of Modification 1 of FIG.
The same drainage groove 3 was provided in the refrigerant flow hole portion in the intermediate portion between the front edge portion A side and the rear edge portion B side while being opened to the flat heat transfer surface 1a side. It is a feature.

The other structures are the same as those of the basic example of FIG. 1 and the modified example 2 of FIG.

In the case of such a configuration, the flat heat transfer surface 1
In the middle part from the air flow upstream to the downstream of a, condensed water droplets flowing from the upstream to the downstream due to the air flow can be collected and drained, and reach the air flow from the upstream to the downstream. An effective drainage action can be obtained over a wide area. As a result, water splash on the trailing edge B side is also reduced.

(Modification 3) Next, FIG. 4 shows that the width of the drain groove 3 is made as narrow as one of the coolant circulation holes 2 as in the configuration of Modification 1 of FIG. 2 and Modification 2 of FIG. On the other hand, a similar drainage groove 3 is provided by providing a solid portion 1c in the second refrigerant flow hole portion from the rear end of the rear edge portion B side.

Other configurations are shown in the basic example of FIG. 1 to FIG.
Is the same as the second modification.

In the case of such a configuration, the flat heat transfer surface 1
The condensed water droplets conveyed from the upstream side to the downstream side in the downstream side of the air flow can be reliably captured near the downstream rear edge B and drained downward, and the water splash prevention effect is particularly improved. .

(Modification 4) Next, FIG. 5 shows a configuration of the basic example of FIG. 1 described above, in which a similar drain groove 3 is used to flow the second and third refrigerant from the rear end of the rear edge B side. It is characterized by being provided in a hole portion.

The other structure is the same as the basic example shown in FIG.

In the case of such a configuration, a large amount of condensed water generated on the upstream side of the air is quickly drained to secure effective heat transfer performance on the front edge A side, while the downstream side of the air flow is provided with effective heat transfer performance. Condensed water droplets conveyed from the upstream side to the downstream side of the air flow can be reliably captured near the downstream rear edge B and drained downward. In addition, the effect of preventing water splashing is improved.

(Embodiment 2) Next, FIGS. 6 to 15 show a second embodiment of the present invention in which drain grooves are provided at positions on the left and right sides of the flat heat transfer surface of the flat heat transfer tube which do not correspond to each other. The structure of the flat heat transfer tube part of the air heat exchanger which concerns on a basic example and its various modifications 1-8 is shown.

-Basic Example- The flat heat transfer tubes 1, 1...
For example, as shown in FIG. 8, the front edge A side and the rear edge B side end sections which are sectioned and arranged side by side in the inner width direction with a partition wall are semicircular in cross section, and those between them are cross sections. It has a multi-hole structure having a plurality of coolant circulation holes 2, 2,... Having a rectangular cross section, and the entire inner peripheral surface of each of the coolant circulation holes 2, 2,. A large number of projections having, for example, a triangular cross section are provided at predetermined pitches to increase the heat transfer area as needed.

The flat heat transfer tube 1 is the same as that shown in FIG.
As shown in FIG. 44, a plurality of the flat heat transfer surfaces 1a and 1b extend from the front edge A side to the rear edge B side between them, as shown in FIG. In a state in which the bent surfaces of the corrugated fins 11, 11,... Are brazed and installed over substantially the entire surface, the refrigerant introduced and distributed from the outside via the upper header 12A is distributed to the heat exchanger. With the refrigerant flowing evenly in each of the refrigerant flow holes 2, 2,..., And flowing through the corrugated fins 11, 11,. Performs efficient heat exchange with external air.

The flat heat transfer surfaces 1a, 1b of the flat heat transfer tubes 1, 1,... To be brazed to the corrugated fins 11, 11,. The third and third and fourth and fifth non-corresponding refrigerant flow holes are respectively formed in the solid portions 1c, 1c, and the solid portions 1c, 1c are respectively formed in the solid portions 1c, 1c. The thickness t of the flat heat transfer tubes 1, 1,... Is changed to the respective coolant circulation holes within a range where the necessary and sufficient rigidity of the portion can be secured.
Drains 3 and 3 having a depth t ₁ of about 1/2 or more than
Is provided.

Therefore, in this configuration, as shown in FIG. 44, for example, substantially the entire surface of the flat heat transfer surfaces 1a and 1b except for the end surfaces on the front edge A side and the rear edge B side is brazed. When the bent surfaces of the corrugated fins 11, 11,... Are brazed, the corrugated fins 11, 11,.
The drainage grooves 3 and 3 having a necessary and sufficient cross-sectional area (width × depth) are formed between the bent surface and the flat heat transfer surface 1a near the front edge A thereof. In other words, effective drainage of condensed water and the like in the vicinity of the leading edge portion A where the generation amount is large is secured.

As described above, in the configuration of this basic example, the flat heat transfer surfaces 1a, 1b, which are the brazing surfaces of the flat heat transfer tubes 1, 1,. thermal surface 1a, so only 1b side culvert 3 not provided, their depth t ₁ respectively the Naijitsu section 1c, in a range that can ensure the rigidity of 1c, the flat heat transfer tubes 1, 1
.. Can be formed deep enough to be about 1/2 or more of the thickness t of itself, and can be formed into a drainage groove having a sufficient drainage capacity. , 11... Even when the brazing material adheres at the time of brazing, the drain grooves 3 are not closed.

Further, the drain grooves 3, 3 are provided on the front edge A side where the temperature difference between the refrigerant and the air is large and the amount of condensed water generated and the amount of frost generated are large. Effective and appropriate for draining water.

Therefore, according to the air heat exchanger, the flat heat transfer tubes 1, 1... And the corrugated fins 11, 11
.. Having a high heat exchange performance can be provided.

In particular, in the case of this structure, the flat heat transfer surfaces 1a and 1b, which are the brazing surfaces on both right and left sides, are provided with the drain grooves 3 and 3, respectively, so that only one flat heat transfer surface 1a is drained. For example, as shown in FIG. 7, the corrugated fins 11, 11,...
The portion of the bent surface that contacts the drain grooves 3, 3 is increased, and condensed water can be more smoothly discharged from the corrugated fins 11, 11,....

(Modification 1) Next, FIG. 8 shows a configuration of the basic example shown in FIG. 6 in which the width of the drain grooves 3 is reduced to one of the coolant circulation holes 2 so that It is characterized in that it is provided in the second and third refrigerant flow holes that do not correspond to each other.

The other structure is the same as that of the basic example shown in FIG.

In the case of such a structure, the same operation and effect as in the case of the above basic example can be obtained. Can be reduced to half, so that the degree of decrease in heat transfer performance can be minimized.

(Modification 2) Next, FIG. 9 shows a drainage groove 3 similar to that of FIG.
3 is provided at the front edge portion A side second and third and one and the fifth and sixth non-corresponding refrigerant flow holes are provided.

The other structure is the same as that of the basic example shown in FIG.

In the case of such a configuration, the solid parts 1c,
1c, there is one coolant circulation hole 2, and the drain grooves 3, 3 provided on the left and right flat heat transfer surfaces 1a, 1b are not adjacent to each other. While being secured, the same effective drainage action as in the above-described basic example can be obtained in a relatively wide area in the upstream and downstream directions of the front edge portion A.

(Modification 3) Next, FIG. 10 shows that the widths of the drain grooves 3 and 3 in the basic example of FIG. 6 are reduced to one of the coolant circulation holes 2 as in Modification 1 of FIG. Front edge A side and rear edge B
Drainage grooves 3, 3 are provided in the same relationship between the front and rear refrigerant flow holes that do not correspond to each other in the intermediate portion between the sides.

The other structures are the same as those of the basic example of FIG. 6 and the first modification of FIG.

In the case of such a configuration, the flat heat transfer surface 1
a, 1b At the intermediate portion from the upstream side to the downstream side of the air flow on both sides, condensed water droplets flowing from the upstream side to the downstream side can be collected and discharged by the air flow, and can be discharged from the upstream side of the air flow on both left and right sides. An effective drainage action can be obtained over a wide part reaching the downstream side. As a result, the water splash on the trailing edge B side is more effectively reduced.

(Modification 4) Next, FIG. 11 shows that the width of the drain grooves 3, 3 is reduced to one of the coolant circulation holes 2 while the width of the trailing edge is reduced as in the configuration of Modification 3 of FIG. The second and third non-corresponding refrigerant flow holes from the rear end on the part B side are provided in a similar relationship.

The other structure is the same as that of the basic example of FIG. 6 and the modification 3 of FIG.

In the case of such a configuration, the flat heat transfer surface 1
The condensed water droplets conveyed from the upstream side to the downstream side of the air flow at the downstream side of the air flow on both sides a and 1b can be reliably captured near the downstream rear edge B and drained downward, and the water splash prevention effect can be obtained. Better.

(Fifth Modification) Next, FIG. 12 shows a configuration of the basic example of FIG. 6 described above, wherein the completely same drain groove 3 is further added to the second and third refrigerants from the rear end of the rear edge B side. It is characterized in that it is also provided in the circulation hole portion.

The other structure is the same as that of the basic example shown in FIG.

In the case of such a configuration, the flat heat transfer surface 1
A large amount of condensed water generated on the upstream side of the air on the side a is quickly drained to ensure effective heat transfer performance on the front edge A side, while the air flow on the downstream side of the air flow on the flat heat transfer surface 1b side Condensed water droplets conveyed from the upstream side to the downstream side can be reliably captured near the downstream rear edge B and drained downward, and an effective condensed water discharging action and a water splash preventing action can be realized. .

(Modification 6) Next, FIG. 13 shows the structure of Modification 3 in FIG. Drainage grooves 3 are provided in the same relationship in the second and second non-corresponding refrigerant flow holes on the front edge A side and the rear edge B side as in Modification Example 12 of FIG. It is characterized by having.

The other structure is exactly the same as that of the fifth modification of FIG.

In the case of such a configuration, the same operation and effect as in the case of the fifth modification of FIG. 12 can be obtained.

In this case, although the drainage capacity is reduced by the reduction in the cross-sectional area of the drainage grooves 3, 3, only two refrigerant circulation holes are reduced. Requires less.

(Modification 7) Next, FIG. 14 shows that the width of the drain groove 3 is made as narrow as one of the coolant circulation holes 2 as in the configuration of Modification 1 of FIG. The refrigerant flow holes at the second portion from the front end on the front edge A side on the 1a side and the second refrigerant flow hole portion from the rear end at the rear edge B side, and the refrigerant flow holes at the intermediate portion between them on the flat heat transfer surface 1b Drain similar to the part 3,3
3 is provided.

The other structure is the same as that of the basic example of FIG.

In the case of such a configuration, the flat heat transfer surface 1
While a large amount of condensed water generated on the upstream side of the air flow on the side a is quickly drained to ensure effective heat transfer performance on the front edge A side, air is generated on the downstream side of the flat heat transfer surface 1a on the air flow side. Condensed water droplets conveyed from the upstream side to the downstream side are reliably captured near the downstream rear edge B and drained downward, thereby realizing a water splash prevention effect.

On the other hand, the flat heat transfer surface 1a on the opposite side
The condensed water droplets flowing from the upstream to the downstream can be collected and drained by the air flow at the intermediate portion from the upstream to the downstream of the air flow, and can be discharged to the wide area from the upstream to the downstream of the air flow. An effective drainage action can be obtained throughout. As a result, water splashing at the rear edge B of the flat heat transfer surface 1b is also reduced.

(Modification 8) Next, FIG. 15 shows a combination of the structure of Modification 1 of FIG. 8 and the structure of Modification 4 of FIG.
Similar drain grooves 3, 3, 3, 3 are provided in the refrigerant flow holes which do not correspond to each other on the front edge A side and the rear edge B side.

The rest of the structure is exactly the same as in the above-described basic example 6 and modification 1.

In the case of such a configuration, the flat heat transfer surface 1
On both sides of a and 1b, a large amount of condensed water generated on the upstream side of the air is quickly drained to ensure effective heat transfer performance on the leading edge A side, while the downstream side of the air stream is upstream of the air stream. The condensed water droplets conveyed to the downstream side can be reliably captured near the downstream rear edge B and drained downward, so that both the drainage and the water splash prevention are effectively improved.

(Embodiment 3) FIG. 16 and FIG.
The structure of a flat heat transfer tube portion of an air heat exchanger according to a basic example of Embodiment 3 of the present invention and a modification 1 thereof is shown.

-Basic Example- The flat heat transfer tubes 1, 1...
For example, as shown in FIG. 16, the front edge A side and the rear edge B side end portions which are arranged side by side with a partition wall therebetween in the width direction of the inside are semicircular in cross section, and those between them are rectangular in cross section. Has a multi-hole structure having a plurality of refrigerant flow holes 2, 2,.
Although not shown on the entire inner peripheral surface of each of the coolant circulation holes 2, 2,..., A large number of protrusions having a triangular cross section for increasing the heat transfer area are provided at predetermined pitches as necessary. It is provided in.

As shown in FIG. 48, a plurality of flat heat transfer surfaces 1a and 1b extending in the vertical direction and arranged between the front edge portion A and the rear edge portion B are arranged therebetween. .. Are bent over the substantially entire surface of the corrugated fins 11, 11..., And the refrigerant introduced and distributed from the outside via the upper header 12A is distributed to each of them. The corrugated fins 1 are uniformly flown into the coolant circulation holes 2, 2,.
The heat exchange is efficiently performed between the refrigerant flowing inside and the outside air with a heat transfer area as wide as possible via 1, 11,.

Two flat heat transfer surfaces 1a, 1b, which are surfaces to be brazed to the corrugated fins 11, 11,... Of the flat heat transfer tubes 1, 1,. The third and third refrigerant flow holes that do not correspond to each other are formed in the solid portions 1c, 1c instead of the refrigerant flow holes.
The flat heat transfer tubes 1, 1... c and 1 c are provided in a range where the necessary and sufficient rigidity of the solid portion 1 c can be secured.
It drains half longitudinal or more of depth t ₁ V-shaped cross section of the thickness t of the ... 4,4 is provided.

Therefore, as shown in FIG. 44, for example, almost the entire surface of the flat heat transfer surfaces 1a and 1b except for the front edge A side and the rear edge B side is formed as a brazing surface. When the bent surfaces of the fins 11, 11,... Are brazed, the corrugated fins 11, 11,.
Between the bent surface and the flat heat transfer surfaces 1a and 1b, drainage grooves 4 and 4 having a V-shaped cross section having a necessary and sufficient cross-sectional area are formed, and the water introduction action by the capillary action is provided. The accompanying drainage of condensed water is ensured.

In the configuration of this basic example, as described above, the left and right flat heat transfer surfaces 1a and 1b, which are the brazing surfaces of the flat heat transfer tubes 1, 1. since only refrigerant flow hole portion not corresponding drainage groove 4,4 is not provided, the inner projection 1c, to the extent necessary rigidity of 1c portion is retained, their depth t _1, t ₁ respectively The flat heat transfer tubes 1, 1,... Can be formed sufficiently deep to be about 1/2 or more of the thickness t of the flat heat transfer tubes 1, 1,. , 11... The drain grooves 4 and 4 are not blocked even by the adhesion of the brazing material at the time of brazing.

In addition, each of the drain grooves 4, 4 is provided on both sides of the front edge A side where the temperature difference between the refrigerant and the air is large and the amount of condensed water generated and the amount of frost generated are large. Therefore, it is effective and appropriate for discharging the large amount of generated water.

Therefore, according to the air heat exchanger, the flat heat transfer tubes 1, 1,... And the corrugated fins 11, 11,.
.. Having a high heat exchange performance can be provided.

(Modification 1) Next, FIG. 17 shows the same structure as that of the basic example shown in FIG. It is characterized in that it is provided in the third and third refrigerant flow holes that do not correspond to each other.

The other structure is exactly the same as that of the basic example of FIG.

In the case of such a configuration, the same operation and effect as in the above-described basic example can be obtained in the downstream area of the airflow on the trailing edge B side. Since the grooves 4 can securely catch and catch, water splashing at the downstream rear edge portion B can be effectively suppressed.

(Embodiment 4) FIGS. 18 to 28 show a basic example of Embodiment 4 of the present invention in which a drain groove is provided in a flat heat transfer surface portion except for a brazing surface with a corrugated fin, and various types thereof. 10 shows a structure of a flat heat transfer tube portion of an air heat exchanger according to Modifications 1 to 10.

-Basic Example- The flat heat transfer tubes 1, 1...
For example, as shown in FIG. 18, a multi-hole structure having a plurality of refrigerant flow holes 2, 2... 45, the front edge A side end which is not brazed to the corrugated fins 11, 11,... In the relationship shown in FIG. Only the rear edge B side end is formed to have a semicircular cross section. Although not shown on the entire inner peripheral surface of each of the refrigerant flow holes 2, 2,..., A large number of protrusions having a triangular cross section for increasing the heat transfer area are provided as necessary. The pitch is provided.

As shown in FIG. 48 described above, a plurality of lines extend in the vertical direction and are arranged side by side.
In the state where the corrugated fins 11, 11... Are provided in the heat exchanger in such a relationship as described above, the refrigerant introduced and distributed from the outside via the upper header 12A is supplied to the respective refrigerant circulation holes 2, 2,. ..Efficiently between the refrigerant flowing outside and the outside air with a heat transfer area as large as possible via corrugated fins 11, 11... Perform heat exchange.

A flat heat transfer surface is formed on a solid portion 1d formed at the front edge A side end of the flat heat transfer tubes 1, 1,... Which is not a brazing surface with the corrugated fins 11, 11,. 1a, was opened to about half the front-rear or air flow side of the more depth t ₁ of either one in the surface 1a side of the side of the flat heat transfer tubes 1, 1 ... thickness t of the 1b A drain groove 5 formed of a hook-shaped notch groove is provided.

Then, as shown in FIG. 45, substantially the entire surface of the flat heat transfer surfaces 1a and 1b except for the solid end surface on the front edge A side is brazed as shown in FIG.
When the bent surfaces 1, 11,... Are brazed, regardless of the bent surfaces of the corrugated fins 11, 11,. The V-shaped drain grooves 4 and 4 are formed in the front edge portion A, and the drainage action of condensed water and the like is secured in a state where the reduction of the heat transfer area is reduced as much as possible.

In the configuration of this basic example, any one of the left and right flat heat transfer surfaces 1a and 1b at the front edge A side end which does not become the brazing surface of the flat heat transfer tubes 1, 1. Since the drain groove 5 is provided only on one side of the flat heat transfer surface 1a, there is no need to make the rigidity much a problem, and the depth of the flat heat transfer tube 1, 1,... It can be formed to a depth of about 1/2 or more, and can be formed into a drainage groove having a sufficient amount of drainage, and also drains due to the adhesion of the brazing material at the time of brazing. The groove 5 is not closed.

Therefore, according to the air heat exchanger, the flat heat transfer tubes 1, 1,... And the corrugated fins 11, 11,.
.. Having a high heat exchange performance can be provided.

Further, since the drain groove 5 is provided on the front edge portion A side where the amount of condensed water is generated most and is provided at the front end portion of the front edge portion A avoiding the brazing surface, the drainage groove 5 is generated. Of course, a large amount of condensed water can be effectively drained down, and for example, the corrugated fin 1 shown in FIG.
When the brazing structure of 1, 11,... Is adopted, the brazing area is not restricted, and the corrugated fin 1 is not restricted.
The heat transfer performance in relation to 1, 11,... Is hardly reduced.

(Modification 1) Next, FIG. 19 shows a case where drainage grooves 5 similar to the basic example of FIG.
Flat heat transfer surfaces 1a, 1b provided in the refrigerant flow hole at the rear edge B side end of the flat heat transfer surface 1a, excluding the rear edge B side end
The corrugated fins 11, 11,.
・ ・ It is characterized by brazing.

The other structure is exactly the same as the basic example shown in FIG.

In the case of such a configuration, in addition to the operation of the above-described basic example, the condensed water droplets carried from the upstream side to the downstream side of the air flow at the downstream side of the air flow are reliably captured near the downstream rear edge B. And can be drained down. In addition, it is possible to prevent water splashing backward as much as possible.

(Modification 2) Next, FIG. 20 shows a combination of the structure of the basic example of FIG. 18 and the structure of Modification 1 of FIG. And corrugated fins 11, 11... Are brazed to the flat heat transfer surfaces 1a, 1b except for those ends in the relationship shown in FIG. It is characterized by having done.

The rest of the structure is exactly the same as the basic example of FIG. 18 and the first modification of FIG.

In the case of such a configuration, the same operation and effect as in the basic example of FIG. 18 are performed in the air upstream side portion, and the operation and effect of the basic example in FIG.
The same operation and effect as those of the first modification can be obtained, and both the water discharge performance and the water splash prevention performance are improved.

(Modification 3) Next, FIG. 21 shows the configuration of Modification 2 of FIG. 20 described above, and the front edge A side of the flat heat transfer surface 1a which is a brazing surface when the structure is further changed as shown in FIG. The intermediate portion between the refrigerant flow hole and the rear edge B side is a solid portion 1
c, and the solid portion 1c is provided with a drain groove 3 having a rectangular cross section similar to that of FIG.

The other structure is exactly the same as that of the second modification of FIG.

In the case of such a configuration, the above-described modification 2
In addition to the action described above, the same water discharging action as in the case of FIG. 3 can be obtained at the intermediate portion of the flat heat transfer surface 1a from the upstream side to the downstream side of the air flow, and the scattering of water droplets to the rear is prevented. The effect can also be obtained, and the effect of preventing water splash can be further improved.

(Modification 4) Next, FIG. 22 shows a structure of a modification 2 of FIG.
Each of the refrigerant flow hole portions, which are the second from the front edge A side end and the second from the rear edge B side end, are solid portions 1c, 1c, and the solid portions 1c, 1c are the above-described figures. Drain grooves 3 and 3 similar to those of the fifteenth embodiment are provided.

The other structure is exactly the same as that of the second modification of FIG.

In the case of such a configuration, the flat heat transfer surface 1
The same effect as in the case of Modification 2 of FIG. 20 is obtained in both the upstream and downstream portions of the air flow a in FIG. 20, and the same as in FIG. 15 in the upstream and downstream portions of the flat heat transfer surface 1b in the air flow. The function and effect of can be obtained.

In the case of this configuration, the flat heat transfer surfaces 1a and 1a at the respective ends of the leading edge A and the trailing edge B which are not the brazing surfaces are provided.
Since the drain grooves 5, 5 and the drain grooves 3, 3 are provided corresponding to the flat heat transfer surfaces 1a, 1b on the front edge portion A side and the rear edge portion B side serving as the brazing surface 1b, respectively. Modification 3 of FIG.
As shown in FIG. 7 described above, the corrugated fins 1
The number of portions (circled by broken lines) of the drain grooves 3, 3 of 1, 11,... Is increased, and condensed water from the corrugated fins 11, 11,.

(Modification 5) Next, FIG. 23 shows the configuration of Modification 4 of FIG. 22 described above, and further shows the front edge A side and rear edge of flat heat transfer surface 1a as in Modification 3 of FIG. The refrigerant flow hole portion in the middle portion between the side B and the B side is defined as a solid portion 1c, and a drain groove 3 similar to that of FIG. 3 is provided in the solid portion 1c.

The rest of the configuration is exactly the same as that of the fourth modification of FIG.

In the case of such a configuration, in addition to the operation and effect of the basic example of FIG. 18 and the fourth modification of FIG. 22, the above-described intermediate portion between the air flow upstream side and the downstream side of the flat heat transfer surface 1a is provided. Since the same operation and effect as those of the third modification in FIG. 21 (the operation and effect of FIG. 3) can be obtained, the flat heat transfer surface 1a
The water discharge performance and the water splash prevention performance on both sides 1b and 1b are more effectively improved.

(Modification 6) Next, FIG. 24 shows a structure similar to that of the basic example shown in FIG. 18 except that the shape of the drain groove 5 is changed from a hook shape to a drain groove 6 having a V-shaped cross section. The drainage performance is improved by enhancing the capillary action.

The other structure is exactly the same as the basic example shown in FIG.

In the case of such a configuration, the surrounding water can be introduced by utilizing the capillary action.
The operation and effect of the basic example can be more effectively obtained.

(Variation 7) Next, FIG. 25 shows a modification of the first modification of FIG. 19 in which the shape of the drain groove 5 is changed to a drain groove 6 having a V-shaped cross section in the same manner as that of the sixth modification. The present invention is characterized in that a capillary action is obtained.

The other structure is exactly the same as the first modification of FIG. 19, and the brazing structure of FIG. 46 is employed.

In the case of such a configuration, the trapping rate of water from the upstream side of the air flow is increased by utilizing the capillary action, and the operation and effect of the first modification of FIG. 19 can be more effectively obtained.

(Modification 8) Next, FIG. 26 shows that the shapes of the drain grooves 5, 5 of Modification 2 of FIG. 20 are changed to inclined grooves 7, 7 having a substantially V-shaped cross section inclined toward the outer end. Each end b, b
Is formed as a flat surface, and the opposite surface 1b side corner surface a is formed as a tapered surface through which the air flow easily flows, and the opposite surface 1b is formed.
A drainage groove 3 similar to that of FIG. 3 described above is provided as a solid portion 1c in the refrigerant flow hole portion.

In the case of such a configuration, the flat heat transfer surface 1
a in the upstream and downstream portions of the air flow in FIG.
The same operation and effect as described above can be obtained more effectively by utilizing the capillary action, and the same operation and effect as in the case of FIG. 3 can be obtained at the intermediate portion on the side of the flat heat transfer surface 1b.

Further, the drain grooves 7, 7 are located on the front edge portion A side of the flat heat transfer surface 1a where condensed water is generated most and on the rear edge portion B side where water splash occurs, and are both brazed. Since the condensed water having a large amount of generation can be effectively drained and discharged on the flat heat transfer surface 1a side, the corrugated fin 11, as shown in FIG. .. Can be adopted, so that the brazing area serving as a heat transfer region is not restricted, and the corrugated fins 11, 11,...
・ It is not necessary to reduce the heat transfer performance in relation to the above.

In this configuration, the drain groove 3 is also provided on the flat heat transfer surface 1b, which is the other brazing surface, so that the drain grooves 7, 7 are provided only on one flat heat transfer surface 1a. , The portions of the corrugated fins 11, 11,..., Which are in contact with the drain grooves 3, 3, of the bent surface are increased, and condensed water is more smoothly discharged from the corrugated fins 11, 11,. Will be able to do that.

(Modification 9) Next, FIG. 27 shows drain grooves 7, 7 composed of inclined grooves having the configuration of Modification 8 of FIG. 26, which are formed on the front edge A side and on the rear edge B side. To reverse the opening direction and the inclination direction, while the front edges A of the flat heat transfer surfaces 1a and 1b
Drain grooves 8, 8 of the same shape are provided in the same relationship in the refrigerant flow hole portions that do not correspond to each other in the intermediate portion between the side and the rear edge portion B side.

In the case of such a configuration, the flat heat transfer surface 1
It is possible to obtain an effective drainage action from the airflow upstream side to the midstream side on both surfaces a and 1b, and an effective drainage action and a water splash prevention action from the midstream side to the downstream side of the flat heat transfer surface 1b. .

Further, in the case of this configuration, drain grooves 8, 8 with a capillary action are provided in the middle portions of the flat heat transfer surfaces 1a, 1b on the left and right sides, which are the brazing surfaces, respectively.
Also, when the corrugated fins 11, 11,... Are brazed as shown in FIG.
7, the corrugated fins 11, 11,..., As shown in FIG.
・ Parts in contact with the drain grooves 8, 8 (circles indicated by broken lines)
Increases, and corrugated fins 11, 11
・ ・ Condensed water can be discharged from the part.

(Modification 10) Next, FIG.
In a configuration like the ninth modification of the first embodiment, the shape of the drain grooves 9, 9 opened to the side of the flat heat transfer surface 1b is V-shaped in cross section so as to obtain the capillary phenomenon, while the end portion 2 is formed. The two corners are formed as a curved surface d and a tapered surface c that allow the air flow to flow more easily and are continuous with the flat heat transfer surface 1a and the flat heat transfer surface 1b, respectively, and the front edges of the flat heat transfer surfaces 1a and 1b. Drain grooves 3 and 3 similar to those shown in FIG. 10 are provided at positions that do not correspond to each other between the A side and the intermediate portion on the rear edge B side.

In the case of such a structure, the flat heat transfer surface 1
An effective drainage action can be obtained in the entire area from the air upstream side on the a-side intermediate portion and the flat heat transfer surface 1b side to the downstream side, and the water splash prevention effect on the flat heat transfer surface 1b side is also improved.

Also in this configuration, since the drain grooves 8 are provided on both the flat heat transfer surfaces 1a and 1b, which are the brazing surfaces, the drain grooves are provided only on the one flat heat transfer surface 1a. 8
Compared with the case where the corrugated fins are provided.
··· The portion of the bent surface that contacts the drain grooves 8, 8 increases, and condensed water can be more smoothly discharged from the corrugated fins 11, 11,....

(Embodiment 5) FIGS.
In the configuration of various flat heat transfer tubes of the air heat exchanger according to Embodiment 4 in FIG.
Flat heat transfer surfaces 1a, 1b at the front edge A side end or the rear edge B side end, or both the front edge A side and the rear edge B side both ends of the flat heat transfer tube 1 provided with 6, 7, or 9 are provided. 1b, for example, in FIG.
As shown in FIGS. 46, 47, 47, the corrugated fins 11, 11,... Are not brazed to each other but protrude from between the fins. 1, the corrugated fins 11,
11 becomes narrower, which is not preferable from the viewpoint of expanding the heat transfer area.

Therefore, in the case of each of the flat heat transfer tubes 1 of FIGS. 18 to 28, as in the brazing structure of FIG. 44 described above, the distance from the front edge portion A to the rear edge portion B of the flat heat transfer tube 1 is increased. Corrugated fins 11, 1 are provided on the entire flat heat transfer surfaces 1a, 1b.
Of course, it is also possible to braze 1,..., And in this case, the same condensed water discharging action as in the above case can be obtained.

(Other Embodiments and Modifications) A: Shape of Drain In the above-described first and second embodiments and their modifications, the basic shape of the drain 3 is as shown in FIG. 29, for example. A rectangular cross section was adopted.

In the case of this shape, there is a merit that the cross-sectional area is large and a large amount of condensed water can be discharged in the case of the same width and the same depth.

However, on the other hand, the condensed water generated widely around the flat heat transfer surfaces 1a and 1b is efficiently removed from the drain groove 3 at the predetermined position.
It's not always enough in terms of introducing it inside.

Therefore, it is conceivable that the cross-sectional shape of the drain groove 3 is modified into various shapes as shown in FIGS.

(1) In the case of FIG. 30 Since the cross section is an isosceles triangular shape, a capillary phenomenon occurs and water easily enters.

(2) In the case of FIG. 31 There is a spherical bulge 3a at the center of the drain groove 3, and the gap between the surrounding V-grooves 3e is gradually narrowed.
Capillary phenomenon is more likely to occur.

(3) In the case of FIG. 32 As compared with the case of a V-shaped groove having an isosceles triangular cross-section as shown in FIG. 30, the opening itself becomes wider and the slope on one side becomes longer, while the groove on the bottom is formed. Since the interval is small, water easily enters and a capillary phenomenon is more likely to occur.

(4) In the case of FIG. 33 Since the cross section is semicircular, the capillary phenomenon is more likely to occur than in the case of a rectangular cross section.

(5) In the case of FIG. 34 Since the cross section is elliptical, the capillary phenomenon is more likely to occur than in the case of a semicircular cross section.

(6) In the case of FIG. 35 Since the groove 3c has a trapezoidal cross section, a capillary phenomenon is more likely to occur than in the case of an elliptical cross section.

(7) In the case of FIG. 36 Since the drain groove 3 having a trapezoidal cross section is divided into two sets of trapezoidal grooves 3c, 3c by a projection 3b having a triangular cross section, the trapezoidal cross section shown in FIG. The capillary phenomenon is more likely to occur than in the case of the narrow groove.

(8) In the case of FIG. 37 The drain groove 3 having a trapezoidal cross section is divided into two sets of V-shaped grooves 3d, 3d by a projection 3b having a triangular cross section. In addition, capillary action is more likely to occur.

(9) In the case of FIG. 38 The drainage groove 3 having a rectangular cross section is divided into a plurality of V-shaped grooves 3d, 3d, 3d by protrusions 3b, 3b having a triangular cross section. Capillary action is more likely to occur than in the case.

(10) In the case of FIG. 39 The drainage groove 3 having a trapezoidal cross section is divided into a plurality of grooves 3d, 3d, 3d having a V-shaped cross section by protrusions 3b, 3b having a triangular cross section. Capillary action is more likely to occur than in the case.

(11) In the case of FIG. 40 A drain groove 3 having a rectangular cross section has a triangular cross section on the bottom side.
A plurality of protrusions 3b, 3b form a plurality of V-shaped grooves 3d,
Since it is divided into 3d and 3d, it is possible to discharge a larger amount of water than in the case of FIG.

(12) In the case of FIG. 41 A drain groove 3 having a trapezoidal cross section has a triangular cross section on the bottom side.
A plurality of protrusions 3b, 3b form a plurality of V-shaped grooves 3d,
Since it is divided into 3d and 3d, it is possible to discharge a large amount of water while obtaining a more effective capillary phenomenon than in the case of FIG.

(13) In the case of FIG. 42 The drain groove 3 having a rectangular cross section is divided into a plurality of grooves by a plurality of spherical projections 3a, 3a, 3a on the bottom side. Even the capillary phenomenon tends to occur.

(14) In the case of FIG. 43 The bottom of the drain groove 3 having a rectangular cross section is formed of a plurality of semicircular bottom surfaces 3.
Since it is divided into f, 3f, and 3f, the capillary phenomenon is more likely to occur than in the case of only a rectangular section.

It is needless to say that these various drainage groove shapes (1) to (14) can be adopted as needed in the above-described third and fourth embodiments.

B: Regarding Surface Treatment of Outer Peripheral Surface of Flat Heat Transfer Tube 1 and Corrugated Fin 11 Various treatment forms are conceivable. For example, the outer peripheral surfaces of the corrugated fins 11, 11. A method is employed in which the drainage grooves are each subjected to a hydrophilic treatment to increase the water introduction power and improve the drainage performance.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to a basic example of an air heat exchanger according to Embodiment 1 of the present invention.

FIG. 2 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a first modification of the embodiment.

FIG. 3 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a second modification of the embodiment.

FIG. 4 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a third modification of the embodiment.

FIG. 5 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a modification 4 of the embodiment.

FIG. 6 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to a basic example of an air heat exchanger according to Embodiment 2 of the present invention.

FIG. 7 is a front view showing a structure of a main part of an air heat exchanger employing the heat transfer tube according to the basic example of the embodiment.

FIG. 8 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a first modification of the embodiment.

FIG. 9 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a second modification of the embodiment.

FIG. 10 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a third modification of the embodiment.

FIG. 11 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to Modification 4 of the embodiment.

FIG. 12 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a fifth modification of the embodiment.

FIG. 13 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to Modification 6 of the embodiment.

FIG. 14 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a modification 7 of the embodiment.

FIG. 15 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a modification 8 of the embodiment.

FIG. 16 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to a basic example of an air heat exchanger according to Embodiment 3 of the present invention.

FIG. 17 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a first modification of the embodiment.

FIG. 18 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to a basic example of an air heat exchanger according to Embodiment 4 of the present invention.

FIG. 19 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a first modification of the embodiment.

FIG. 20 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a second modification of the embodiment.

FIG. 21 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a third modification of the embodiment.

FIG. 22 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to Modification 4 of the embodiment.

FIG. 23 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a fifth modification of the embodiment.

FIG. 24 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to Modification 6 of the embodiment.

FIG. 25 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to Modification 7 of the embodiment.

FIG. 26 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a modification 8 of the embodiment.

FIG. 27 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to a ninth modification of the embodiment.

FIG. 28 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube according to Modification 10 of the embodiment.

FIG. 29 is an enlarged sectional view of Structural Example 1 showing a sectional structure example of a drainage groove common to the first and second embodiments.

FIG. 30 is an enlarged sectional view of Structural Example 2 showing an example of a sectional structure of a drainage groove common to the first and second embodiments.

FIG. 31 is an enlarged cross-sectional view of Structural Example 3 showing a cross-sectional structural example of a drain groove common to the first and second embodiments.

FIG. 32 is an enlarged sectional view of Structural Example 4 showing an example of a sectional structure of a drain groove common to the first and second embodiments.

FIG. 33 is an enlarged cross-sectional view of Structural Example 5 showing a cross-sectional structure example of a drain groove common to the first and second embodiments.

FIG. 34 is an enlarged cross-sectional view of Structural Example 6 showing a cross-sectional structure example of a drain groove common to the first and second embodiments.

FIG. 35 is an enlarged sectional view of Structural Example 7 showing an example of a sectional structure of a drainage groove common to the first and second embodiments.

FIG. 36 is an enlarged cross-sectional view of Structural Example 8 showing a cross-sectional structural example of a drain groove common to the first and second embodiments.

FIG. 37 is an enlarged sectional view of Structural Example 9 showing a sectional structure example of a drainage groove common to the first and second embodiments.

FIG. 38 is an enlarged sectional view of Structural Example 10 showing a sectional structure example of a drainage groove common to the first and second embodiments.

FIG. 39 is an enlarged sectional view of Structural Example 11 showing a sectional structure example of a drainage groove common to the first and second embodiments.

FIG. 40 is an enlarged sectional view of Structural Example 12 showing a sectional structure example of a drainage groove common to the first and second embodiments.

FIG. 41 is an enlarged sectional view of Structural Example 13 showing an example of a sectional structure of a drain groove common to the first and second embodiments.

FIG. 42 is an enlarged sectional view of Structural Example 14 showing a sectional structure example of a drain groove common to the first and second embodiments.

FIG. 43 is an enlarged cross-sectional view of Structural Example 15 showing a cross-sectional structure example of a drain groove common to the first and second embodiments.

FIG. 44 is a horizontal cross-sectional view (hatching omitted) showing a first layout structure example of a flat heat transfer tube portion and a corrugated fin of the air heat exchanger according to each embodiment of the present invention.

FIG. 45 is a cross-sectional view (hatching omitted) showing a second layout structure example of the flat heat transfer tube portion and the corrugated fin of the air heat exchanger according to each embodiment of the present invention.

FIG. 46 is a cross-sectional view (hatching omitted) showing a third layout structure example of the flat heat transfer tube portion and the corrugated fin of the air heat exchanger according to the embodiment of the present invention.

FIG. 47 is a cross-sectional view (hatching omitted) showing a fourth layout structure example of the flat heat transfer tube portion and the corrugated fin of the air heat exchanger according to the embodiment of the present invention.

FIG. 48 is a perspective view showing the overall structure of an air heat exchanger according to a conventional example.

FIG. 49 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to a general example of the conventional example.

FIG. 50 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to Modification 1 of the conventional example.

FIG. 51 is a cross-sectional view (hatching omitted) showing a structure of a flat heat transfer tube portion according to Modification 2 of the conventional example.

[Explanation of symbols]

1 is a flat heat transfer tube, 2 is a coolant circulation hole, 3, 4, 5, 6,
Reference numerals 7 and 8 denote drain grooves, and reference numeral 10 denotes an air heat exchanger.

Claims (4)

[Claims] 1. A plurality of refrigerant flow holes (2), (2) therein.
Flat heat transfer tubes (1), (1)
.. Are provided, a plurality of the flat heat transfer tubes (1), (1)... Are extended in the vertical direction, and a plurality of the flat heat transfer tubes (1), (1). Corrugated fins (1
In the air heat exchanger in which 1), (11)... Are brazed and installed, the corrugated fins (11), (11)... Of the flat heat transfer tubes (1), (1). The flat heat transfer tubes (1), (1),... Are provided on one of the left and right flat heat transfer surfaces (1a) and (1b), which are brazing surfaces.
An air heat exchanger provided with a drain groove (3) having a depth of at least about 1/2 of the thickness of the air heat exchanger. 2. A plurality of refrigerant flow holes (2), (2) therein.
Flat heat transfer tubes (1), (1)
···, the plurality of flat heat transfer tubes (1), (1) ··· extend in the vertical direction and are arranged side by side, and between the plurality of flat heat transfer tubes (1) · (1) ··· Corrugated fins (1
In the air heat exchanger in which 1), (11)... Are brazed and installed, the corrugated fins (11), (11)... Of the flat heat transfer tubes (1), (1). The flat heat transfer tubes (1), (2) are located at positions where the left and right flat heat transfer surfaces (1a) and (1b), which are
(1) An air heat exchanger provided with drain grooves (3), (3) having a depth of at least about 1/2 of the thickness of (1). 3. A plurality of refrigerant flow holes (2), (2) therein.
Flat heat transfer tubes (1), (1)
···, the plurality of flat heat transfer tubes (1), (1) ··· extend in the vertical direction and are arranged side by side, and between the plurality of flat heat transfer tubes (1) · (1) ··· Corrugated fins (1
In the air heat exchanger in which 1), (11)... Are brazed and installed, the corrugated fins (11), (11)... Of the flat heat transfer tubes (1), (1). The flat heat transfer tubes (1), (1),...
An air heat exchanger provided with a drain groove (3) having a depth of at least about 1/2 of the thickness of the air heat exchanger. 4. A plurality of refrigerant flow holes (2), (2) therein.
Flat heat transfer tubes (1), (1)
.. Are provided, a plurality of the flat heat transfer tubes (1), (1)... Are extended in the vertical direction, and a plurality of the flat heat transfer tubes (1), (1). Corrugated fins (1
In the air heat exchanger in which 1), (11)... Are brazed and installed, the corrugated fins (11), (11)... Of the flat heat transfer tubes (1), (1). The flat heat transfer tubes (1), (2) are located at positions that do not correspond to each other on the left and right flat heat transfer surfaces (1a) and (1b) except for the brazing surfaces.
(1) An air heat exchanger provided with a drain groove (3) having a depth of at least about 1/2 of the thickness of (1).