JPH06331290A - Heat exchanger for air conditioner and its manufacture - Google Patents

Abstract

PURPOSE:To improve heat exchanging efficiency by a method wherein a heat transfer pipe and a fine wire fin are combined by means of melted and solidified substance of a metallic coat which is plated on a surface of either one of the heat transfer pipe and the fine wire fin. CONSTITUTION:A heat transfer pipe 11 is preparatorily applied with a plating treatment in a non-electrolytic Ni plating solution to form a metallic coat 13 of nickel on an outer peripheral surface of the heat transfer pipe 11. Next, a plurality of the extremely fine heat transfer pipes 11 which are applied with the plating treatment are arranged in a line with a space between them, then thin wire fins 12a and 12b made of copper wire are knitted into them to fix the heat transfer pipe 11 temporarily, and finally heated in a vacuum atmospheric soldering furnace. Then, the Ni-plated coat 13 melts down and gathers at a contacting part with the fine wire fins 12a and 12b by its surface tension, its wetness and the like to form a fillet. As the fine wire fins 12a and 12b and the heat transfer pipe 11 are combined with each other by the plating material which has been melted and solidified, a thermal contact can be realized without fail. Accordingly, a heat transfer between the heat transfer pipe 11 and the fine wire fins 12a and 12b can be promoted, and thereby heat exchanging efficiency can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump type air conditioner, a heat exchanger for air conditioners used for refrigerating or refrigerating machines and the like.

[0002]

2. Description of the Related Art FIG. 31 is an external view showing a conventional heat exchanger disclosed in, for example, the Japan Society of Mechanical Engineers, Vol. 56, No. 530, issued in October 1990. In the figure, 1 is a heat transfer tube through which a heat exchange fluid such as a refrigerant flows, 2a and 2b are fine wire fins, and the fine wire fins 2a and 2b are woven alternately on the front side and the back side of the heat transfer tube 1 and the fine wire fins 2a and 2b are provided. Is in close contact with the heat transfer tube 1. In this heat exchanger, the thin wire fins 2a, 2b are alternately woven into the heat transfer tube 1 to ensure thermal contact between the thin wire fins 2a, 2b and the heat transfer tube 1, and at the same time, for the heat transfer tube 1 and the thin wire fin 2
Positioning and fixing of a and 2b are performed. As the heat transfer tube 1, for example, an ultrafine pipe having an outer diameter of 1 to 2 mm and an inner diameter of 0.7 to 1.7 mm is used, and wires are used as the thin wire fins 2a and 2b. In addition, 3 has shown the direction where an air flow flows (it calls an "air flow direction").

Next, the operation will be described. In this heat exchanger, as shown in the enlarged view of the flow of air in FIG. 32, the air flows along the airflow direction 3 so as to sew through the gaps between the thin wire fins 2a and 2b. In the meantime, heat is exchanged between the air and the heat transfer tube 1 and the thin wire fins 2a and 2b.

When, for example, cold water is flowed through the heat transfer tube 1 of such a heat exchanger, or when a low-temperature refrigerant is evaporated inside the heat transfer tube 1, the passing air is cooled, whereby cooling can be performed. . At this time, when the air near the surfaces of the heat transfer tube 1 and the thin wire fins 2a, 2b is cooled to a temperature below the dew point temperature, dew condensation occurs on the surfaces of the heat transfer tube 1 and the thin wire fins 2a, 2b, and the condensed water is the surface of the heat transfer tube 1. And thin wire fins 2a, 2b
Drain along the surface of.

[0005]

Since the conventional heat exchanger is constructed as described above, there is a problem that there is a limit to the improvement of the heat exchange efficiency due to the following reasons, for example.

That is, the conventional heat exchanger has a thin wire fin 2
Since only a and 2b are in contact with the heat transfer tube 1, the thermal resistance of this contact portion is large and the heat exchange efficiency of the entire heat exchanger is low. To deal with this, it is conceivable to join the fine wire fin and the heat transfer tube with powdered Ni brazing material or solder material. In such a case, however, the brazing material fills this part due to the narrow gap between the fine wire fins. As a result, defects tend to occur, so that there is a limit to improving heat exchange efficiency.

Further, the capacity Q of the heat exchanger is expressed by "Q = K × A ×" where K is the heat transfer rate, A is the heat transfer area, and ΔT is the temperature difference between the air and the medium flowing in the heat transfer tube 1. ΔT ”, the conventional heat exchanger has a structure in which the thin wire fins 2a and 2b are alternately woven into the heat transfer tube 1. Therefore, it is difficult to increase the heat transfer area A per front surface area. Moreover, since it is difficult to increase the turbulence of the flow to increase the heat transfer rate K, it is impossible to expect an increase in the factors contributing to the increase in the amount of heat exchange, and there is a limit in improving the heat exchange efficiency.

When dew condensation water is generated on the heat transfer tube 1 or the thin wire fins 2a and 2b, the dew condensation water is held between the thin wire fins 2a and 2b to cause clogging, and the air does not sufficiently pass therethrough. There is also a problem that the air volume decreases due to the loss, and eventually the heat exchange efficiency decreases.

The present invention has been made to solve the above problems, and an object thereof is to obtain an air conditioning heat exchanger capable of improving the heat exchange efficiency, and further suitable for this device. It is an object of the present invention to provide a manufacturing method.

[0010]

According to a first aspect of the present invention, there is provided a heat exchanger for air conditioning, wherein a heat transfer tube and a fine wire fin are formed by melting and solidifying a metal film plated on either surface of the heat transfer tube and the fine wire fin. Are joined together.

The heat exchanger for air conditioning according to the invention of claim 2 is
The thin wire fin is wound around the outer circumference of the heat transfer tube, and the heat transfer tube and the thin wire fin are joined by a melted and solidified body of a metal coating plated on either surface of the heat transfer tube or the thin wire fin.

A heat exchanger for air conditioning according to the invention of claim 3 is
In a case where a wire mesh composed of thin wire fins is arranged in contact with the heat transfer tube on each of the front surface and the rear surface of the heat transfer tubes arranged in a line, the molten solidified body of the metal coating plated on either surface of the heat transfer tube or the wire mesh, A heat transfer tube and a wire mesh are joined together.

The heat exchanger for air conditioning according to the invention of claim 4 is
By alternately passing the wire mesh consisting of thin wire fins through the rows of heat transfer tubes arranged in a row, the wire mesh is brought into contact with the heat transfer tube, and the heat transfer tube is formed by melting and solidifying a metal film plated on either surface of the heat transfer tube or the wire mesh. And wire mesh are joined together.

According to a fifth aspect of the present invention, there is provided an air conditioning heat exchanger manufacturing method, wherein a metal coating is formed on at least one of an outer peripheral surface of a heat transfer tube and an outer peripheral surface of a thin wire fin in advance, and then the heat transfer tube and the thin wire are formed. The fins are combined and heated in the combined state to the melting temperature of the metal coating, thereby melting a part of the metal coating and joining the heat transfer tube and the thin wire fin.

In the method for manufacturing an air conditioning heat exchanger according to the sixth aspect of the present invention, the type of plating is Ni plating.

In the method of manufacturing the heat exchanger for air conditioning according to the invention of claim 7, the type of plating is solder plating.

The air conditioner heat exchanger according to the invention of claim 8 is
A plurality of heat transfer tubes are arranged at intervals, and rod fins are obliquely inserted from the front in the air flow direction of one adjacent heat transfer tube toward the rear in the air flow direction of the other heat transfer tube, and the rod fins are brought into contact with each heat transfer tube. By alternately changing the inserting directions of the rod-shaped fins adjacent to each other in the axial direction of the heat transfer tube, a large number of rod-shaped fins are attached in contact with all the heat transfer tubes.

A heat exchanger for air conditioning according to a ninth aspect of the invention is
Another heat transfer tube is inserted into a gap formed by rod-shaped fins with different insertion directions.

In the heat exchanger for air conditioning according to the tenth aspect of the present invention, rod-shaped fins are arranged so as to form a rhombic lattice, and a plurality of the fins are stacked and a heat transfer tube serving as a refrigerant passage is inserted into the openings of these lattices. However, the grid and heat transfer tubes are in close contact.

In the heat exchanger for air conditioning according to the invention of claim 11, a U-shaped or H-shaped fin is provided in the heat transfer tube, and the heat transfer tube is sandwiched between the U-shaped recess or one of the H-shaped recesses. A plurality of these fins are attached at intervals in the axial direction of the heat transfer tube, and the directions of adjacent fins are alternately changed.

In the heat exchanger for air conditioning according to the twelfth aspect of the present invention, the heat transfer tube is inserted into the annular fin, the inside of the annular portion is attached so as to contact the surface of the heat transfer tube, and the annular fin is attached to the heat transfer tube. A plurality of them are attached at intervals along the axial direction of.

In the heat exchanger for air conditioning according to the thirteenth aspect of the present invention, the interval between the heat transfer tubes is fixed by inserting a rod or a tube into the overlapping portion of the annular fins, and the endmost heat transfer tube is laterally moved. The tension is applied to the ring-shaped fin by pulling the rod to the tube or tube and the heat transfer tube is brought into close contact with the ring-shaped fin.

In the heat exchanger for air conditioning according to the fourteenth aspect of the present invention, the heat transfer tube is sandwiched by a pair of wire fins, and the ends of both wire fins are twisted together to generate tension in the wire fins. Thus, the wire-shaped fins are attached so as to be in contact with the heat transfer tube.

In the heat exchanger for air conditioning according to the fifteenth aspect of the present invention, the ends of the U-shaped or H-shaped fins are directed downward from the horizontal plane.

A heat exchanger for air conditioning according to a sixteenth aspect of the present invention is the heat exchanger for air conditioning according to any one of the eighth to fifteenth aspects, wherein the fins and the heat transfer tubes are made of materials having different contact angles. is there.

In the heat exchanger for air conditioning according to the seventeenth aspect of the invention, instead of using different materials, the fins and the heat transfer tubes are surface-treated with materials having different contact angles.

In the heat exchanger for air conditioning according to the eighteenth aspect of the present invention, a plurality of support rods are arranged on the upstream side and the downstream side of the row of the heat transfer tubes in the air flow direction by being shifted by a half pitch from the heat transfer tubes, respectively.
Alternately knit the heat transfer tube and the upstream side support rod with thin wire fins,
Alternately weaving the heat transfer tubes and the downstream side support rods with another thin wire fin, and alternating the thin wire fins woven into the upstream side support rods and the thin wire fins woven into the downstream side support rods in the axial direction of the heat transfer tube. It was placed in.

In the heat exchanger for air conditioning according to a nineteenth aspect of the present invention, the support rod is replaced with a heat transfer tube having a tube diameter the same as or different from that of the heat transfer tube.

According to a twentieth aspect of the present invention, there is provided an air conditioner heat exchanger in which a header communicating with an end of the heat transfer tube is arranged in the same plane as the heat transfer tube, and the support rod is fixed to the header. is there.

In the heat exchanger for air conditioning according to the twenty-first aspect of the present invention, another heat transfer tube is arranged on the upstream side and the downstream side of the heat transfer tube in the central row in the air flow direction by a half pitch offset from the heat transfer tubes in the central row. , The heat transfer tubes in the central row and the heat transfer tubes in the upstream row are alternately woven with thin wire fins, and the heat transfer tubes in the center row and the heat transfer tubes in the downstream row are alternately woven with another thin wire fin, and the heat transfer tubes in the upstream row , The thin wire fins woven with the heat transfer tubes in the downstream row are alternately arranged in the axial direction of the heat transfer tubes, and the heat transfer tubes in the center row and the heat transfer tubes in the upstream row are further arranged. Also, a plurality of support rods extending in a direction orthogonal to the heat transfer tubes are inserted between the heat transfer tubes in the central row and the heat transfer tubes in the downstream row at an appropriate pitch.

In the heat exchanger for air conditioning according to the twenty-second aspect of the present invention, when the thin wire fins are alternately woven on the front side and the back side of the heat transfer tube, one or more heat transfer tubes are woven for any thin wire fin. It is a thing.

The heat exchanger for air conditioning according to the invention of claim 23 is the heat exchanger for air conditioning according to claims 18-22.
The heat transfer tube is a flat tube.

An air conditioning heat exchanger according to a twenty-fourth aspect of the present invention is the air conditioning heat exchanger according to any one of the eighteenth to twenty-third aspects.
The thin wire fin is brought into close contact with the heat transfer tube by applying tension.

An air conditioning heat exchanger according to a twenty-fifth aspect of the present invention is the air conditioning heat exchanger according to any one of the eighteenth to twenty-fourth aspects.
The heat transfer tube is made of a soft material, and the surface of the heat transfer tube is deformed in a concavo-convex shape by the tension applied to the fine wire fin so as to be in close contact with the fine wire fin.

An air conditioning heat exchanger according to a twenty-sixth aspect of the present invention is the air conditioning heat exchanger according to any of the eighteenth to twenty-third aspects.
A depression corresponding to the thin wire fin is formed on the surface of the heat transfer tube.

The heat exchanger for air conditioning according to the invention of claim 27 is the heat exchanger for air conditioning according to claims 18 to 26,
The whole is curved in a wave shape.

An air conditioning heat exchanger according to a twenty-eighth aspect of the present invention is the air conditioning heat exchanger according to any of the eighteenth to twenty-sixth aspects.
The whole is curved in a semicircle.

In the heat exchanger for air conditioning according to a twenty-ninth aspect of the present invention, the plate fin tube type heat exchanger is arranged in the first row in the air flow direction, and the fine wire fin braided heat exchanger is arranged in the second row. is there.

In the heat exchanger for air conditioning according to the thirtieth aspect of the present invention, the corrugated fin tube type heat exchanger is arranged in the first row in the air flow direction and the thin wire fin braided heat exchanger is arranged in the second row. is there.

In the heat exchanger for air conditioning according to the invention of claim 31, the plate fin tube type heat exchanger is arranged in the first row in the air flow direction, and the heat exchanger for air conditioning in any of claims 18 to 26 is arranged in the second row. It was placed in.

In the heat exchanger for air conditioning according to the invention of claim 32, the corrugated fin tube type heat exchanger is arranged in the first row in the air flow direction, and the heat exchanger for air conditioning in any one of claims 18 to 26 is arranged in the second row. It was placed in.

[0042]

In the heat exchanger for air conditioning according to the first aspect of the present invention, the heat transfer tube and the thin wire fin are joined by the molten solidified body of the plated metal coating, so that the thermal resistance of the heat transfer tube and the thin wire fin is reduced. The heat transfer efficiency is improved and the heat exchange efficiency is improved.

In the heat exchanger for air conditioning according to the second aspect of the present invention, in the type in which the fine wire fins are woven into the heat transfer tube, the heat transfer tube and the fine wire fins are joined by the molten solidified body of the plated metal coating. The thermal resistance of the heat transfer tube and the thin wire fins is reduced, the heat transfer efficiency is improved, and the heat exchange efficiency is improved.

In the heat exchanger for air conditioning according to the third aspect of the present invention, the wire net consisting of fine wire fins is arranged on the front and rear surfaces of the heat transfer tube, and the heat transfer tube and the fine wire fin are formed by the molten solidified body of the plated metal film. Since the above is joined, the thermal resistance of the heat transfer tube and the thin wire fin is reduced, the heat transfer efficiency is improved, the heat exchange efficiency is improved, and it can be manufactured at low cost.

In the heat exchanger for air conditioning according to the fourth aspect of the present invention, since the wire mesh is alternately passed through the front side and the back side of the heat transfer tube, the heat exchange efficiency is improved even with one wire mesh.

In the method of manufacturing the heat exchanger for air conditioning according to the fifth aspect of the present invention, since the thickness of the metal coating can be controlled by the plating time, the excess joining material does not fill the space between the thin wire fins and the joining is performed accurately. it can. Therefore, the thermal resistance of the heat transfer tube and the thin wire fin can be reduced, and the heat exchange efficiency can be improved.

In the heat exchanger for air conditioning according to the sixth aspect of the invention, since the type of plating is Ni plating, it is suitable for joining materials according to it.

In the heat exchanger for air conditioning according to the seventh aspect of the invention, the type of plating is solder plating, so that it is suitable for joining materials according to it.

In the heat exchanger for air conditioning according to the eighth aspect of the present invention, the rod-shaped fins are alternately inserted into the heat transfer tubes. Therefore, when air is passed through the heat exchanger, vortices are emitted from the fins to disturb the flow. There is an action of inducing, and an effect of promoting heat transfer can be obtained. Furthermore, since the length of the fins can be set freely, the fin area can be increased and the required heat transfer area can be easily obtained.

In the heat exchanger for air conditioning according to the ninth aspect of the present invention, since the heat transfer pipe is further inserted, the heat transfer performance is further improved by improving the fin efficiency.

The heat exchanger for air conditioning according to the tenth aspect of the invention has the same heat transfer promoting effect as that of the eighth aspect of the invention and is easy to manufacture.

In the heat exchanger for air conditioning of the eleventh aspect of the present invention, since U-shaped or H-shaped fins are attached to the heat transfer tubes, there is an effect of promoting heat transfer as in the heat exchanger of the preceding claim, and the fin Since the dimensions can be set freely, the required heat transfer area can be easily obtained.

Since the heat exchanger for air conditioning according to the twelfth aspect of the invention is provided with the annular fins, it has the same effect of promoting heat transfer as the heat exchanger, and the size of the annular ring is changed. , The heat transfer area can be set freely.

In the heat exchanger for air conditioning according to the thirteenth aspect of the invention, since the heat transfer tube is inserted in the overlapping portion of the annular fins, the heat transfer area can be increased without impairing the effect of promoting heat transfer. . Furthermore, since tension is applied to the thin wire fins by pulling the heat transfer tube, it is possible to improve thermal contact between the heat transfer tube and the fins and to fix the pitch of the heat transfer tube.

In the heat exchanger for air conditioning of the fourteenth aspect of the invention, since the wire-shaped fins are attached to the heat transfer tube, not only the effect of promoting heat transfer by the wire-shaped fins can be obtained, but also the length of the wire-shaped fins can be adjusted. The required heat transfer area can be obtained by the above.

In the heat exchanger for air conditioning according to the fifteenth aspect of the invention, not only the effect of promoting heat transfer but also the end of the fin faces downward from the horizontal plane, so that the condensed water easily drops and the wind caused by the condensed water is generated. The blockage of the passage is relieved, and the effect of promoting heat transfer can be maintained.

In the heat exchanger for air conditioning according to the sixteenth aspect of the present invention, since the thin wire fins and the heat transfer tubes are made of materials having different contact angles, water droplets are attracted to the portion having a small contact angle, and water is condensed. Is also easy to drain. Due to this effect, water drops are less likely to be held between the fins, and heat transfer performance is maintained even when water is condensed.

In the heat exchanger for air conditioning according to the seventeenth aspect of the present invention, since the thin wire fins and the heat transfer tubes are subjected to surface treatment with different contact angles, water droplets are less likely to be retained between the fins, as in the preceding paragraph. The heat transfer performance is maintained even when water is condensed.

In the heat exchanger for air conditioning of the eighteenth aspect of the present invention, since the thin wire fins are woven into the support rod, the crossing angle of the thin wire fins when viewed in a cross section orthogonal to the heat transfer tube becomes large. Therefore, it becomes difficult for the liquid droplets to be retained, clogging is less likely to occur even when the heat exchanger surface is used in a wet state, and a decrease in heat exchange amount due to a decrease in air volume is suppressed.

In the heat exchanger for air conditioning according to the nineteenth aspect of the invention, since a new heat transfer tube is provided as a support rod, the fin efficiency of the thin wire fins is improved and heat transfer is promoted.

In the heat exchanger for air conditioning of claim 20, the working fluid is distributed to the heat transfer tubes by the header. Also,
Since the support rod is fixed to the header, it is possible to have sufficient strength against the tension of the thin wire fin.

In the heat exchanger for air conditioning according to the twenty-first aspect of the invention, since the new heat transfer tube and the support rod are provided, the crossing angle of the thin wire fins when viewed in a cross section orthogonal to the heat transfer tube becomes large, and droplets are formed. It becomes difficult to retain the heat exchanger, and even if it is used while the surface of the heat exchanger is wet, it is less likely to be clogged, and a decrease in the heat exchange amount due to a decrease in the air volume is suppressed. Further, the heat transfer tube pitch can be fixed by the support rods, and the structure becomes strong.

In the air conditioner heat exchanger according to the twenty-second aspect of the present invention, since the fine wire fins are appropriately woven, the number of crosses of the fine wire fins in the cross section orthogonal to the heat transfer tube is reduced, and thus the fine wire fins are retained. The amount of droplets to be reduced decreases, and even when used with the heat exchanger surface wet, clogging is less likely to occur,
A decrease in heat exchange amount due to a decrease in air volume is suppressed.

In the heat exchanger for air conditioning of the twenty-third aspect of the present invention, since the flat tube is used as the heat transfer tube, the contact angle between the heat transfer tube and the braided thin wire becomes large. Therefore, it becomes difficult for the liquid droplets to be retained, clogging is less likely to occur even when the heat exchanger surface is used in a wet state, and a decrease in heat exchange amount due to a decrease in air volume is suppressed.

In the heat exchanger for air conditioning according to the twenty-fourth aspect of the invention, since the fine wire fins are tensioned, the heat transfer tube and the fine wire fins are in close contact with each other, and the thermal resistance due to contact is reduced.

In the heat exchanger for air conditioning according to the twenty-fifth aspect of the present invention, a soft material is used for the heat transfer tube, and tension is applied to the thin wire fins to cause unevenness in the surface of the heat transfer tube to cause the heat transfer tube and the thin wire to separate. Since they are in close contact with each other, the thermal resistance between the heat transfer tube and the thin wire is reduced, and heat transfer in the tube is promoted.

In the air conditioner heat exchanger of the twenty-sixth aspect of the present invention, since the tube having the depression is used as the heat transfer tube, the thin wire fins can be easily fixed to the heat transfer tube, and the contact between the heat transfer tube and the thin wire is facilitated. The thermal resistance due to

In the air conditioner heat exchanger of the twenty-seventh aspect of the present invention, since the heat transfer surface is formed in a corrugated shape, the heat transfer area per front surface area becomes large.

In the air conditioner heat exchanger according to the twenty-eighth aspect of the invention, since the heat transfer surface is formed in a semicircular shape, the heat transfer area per front surface area becomes large.

In the heat exchanger for air conditioning according to the twenty-ninth aspect of the invention, the plate fin tube type heat exchanger and the fine wire fin braided type heat exchanger are arranged in two rows, so the heat transfer area per front surface area is The heat exchanger can be made larger than the two rows. When used under the condition that water in the air is condensed, the condensation is mainly performed on the plate in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed. .

In the heat exchanger for air conditioning according to the thirtieth aspect of the invention, since the corrugated fin tube type heat exchanger and the thin wire fin woven type heat exchanger are arranged in two rows, the heat transfer area per front surface area is The heat exchanger can be made larger than the two rows. Further, when used under the condition that water in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed.

The heat exchanger for air conditioning in the invention of claim 31 is a plate fin tube type heat exchanger.
Since the heat exchangers for air conditioning described in No. 26 are arranged in two rows, the heat transfer area per front surface area can be made larger than that of the latter heat exchanger arranged in two rows. Further, when used under the condition that water in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed.

The heat exchanger for air conditioning in the invention of claim 32 is a corrugated fin tube type heat exchanger.
Since the heat exchangers for air conditioning described in Nos. 26 to 26 are arranged in two rows, the heat transfer area per front surface area can be made larger than that of the latter heat exchanger arranged in two rows. Further, when used under the condition that water in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed.

[0074]

【Example】

Example 1. An embodiment of the present invention will be described below with reference to the drawings. 1 is a sectional view showing an air conditioning heat exchanger and a method for manufacturing the same according to a first embodiment of the present invention. In the figure, 1
Reference numeral 1 is an ultra-fine heat transfer tube made of a copper material. First, the manufacturing method will be explained. This heat transfer tube 11 shown in (a) is pre-electroless Ni plated (nickel: 87-93%, phosphorus: 4-
12%, other 1%) solution is plated at 90 ° C. to form a nickel metal coating 13 on the outer peripheral surface of the heat transfer tube 11 as shown in FIG. The film thickness at this time is controlled to about 1 to 10 μm depending on the plating time. Next, the plated ultra-fine heat transfer tubes 11 are arranged in a line at intervals, and as shown in (c), the thin wire fins 12a and 12b made of, for example, copper wires are formed by the same method as the conventional method (see FIG. 31). Braid and temporarily fix the heat transfer tube 11. This is placed in a brazing furnace in a vacuum (about 10 ⁻³ Torr) atmosphere and heated at 950 ° C. for 30 minutes. Then,
As shown in (d), the Ni-plated coating 13 is melted by the heat treatment, and is gathered at the contact portions with the thin wire fins 12a and 12b due to surface tension, wettability, etc. to form a fillet. When the heat treatment is completed, the Ni-plated film 13 is solidified in this state, and the thin fins 1 are attached to the heat transfer tube 11.
2a and 12b are fixed, and a heat exchanger as a product is obtained.

Next, the operation will be described. The operation of heat exchange is the same as that of the conventional heat exchanger, but since the fine wire fins 12a and 12b and the heat transfer tube 11 are joined with each other by the molten and solidified plating material, a reliable thermal contact can be obtained. Further, since the thickness of the metal coating material 13 formed by plating can be freely controlled by the plating time, precise joining is possible, and the remaining joining material is the fine wire fins 12a, 1a.
There is no inconvenience of blocking the space between 2b and increasing the air passage resistance. Therefore, the heat transfer tube 11 and the thin wire fin 12
The heat transfer enhancing effects of a and 12b are obtained, and as a result, the heat exchange efficiency is improved.

Example 2. FIG. 2 is a cross-sectional view showing another example of the method for manufacturing the heat exchanger described above. In the first embodiment, the heat transfer tube 11 was plated with Ni, but in this second embodiment, the thin wire fins 12a and 12b shown in FIG. Fin 12
1 to 10 μm on the surface of a, 12b as shown in (b)
A nickel coating 13 having a certain degree is formed. After that, as shown in (c), the thin wire fins 12a, 12 for the heat transfer tube 11 are
Weave b, and perform the same heat treatment as above,
As shown in (d), the Ni-plated coating 13 is melted,
When the heating is completed, the plating material is solidified and the thin wire fins 12a and 12b are fixed to the heat transfer tube 11. Heat transfer tube 1
If the Ni plating is applied to the No. 1 side, the Ni plating may wrap around the inner surface of the tube, but N is applied to the thin wire fins 12a and 12b.
If i-plating is applied, there is no need to worry.

Example 3. In Examples 1 and 2, the metal coating 1
Although nickel plating was used to form No. 3, solder plating has the same effect. FIG. 3 shows a manufacturing method for solder plating. Since the joining temperature (heat treatment temperature) is high in nickel plating, this method cannot be adopted, but in the case of solder plating, the joining temperature is low, so this method can be adopted. That is, in this method, first, as shown in (a), molten solder (Pb: 40%, S
n: 60%) In the tank 100, for example, a heat transfer tube 11 made of copper material
Alternatively, one of the thin fins 12a and 12b of copper material is dipped and pulled up. In the illustrated example, the thin wire fins 12a, 12
b is continuously passed through the solder bath 100 while being drawn from the wire coil 102 by the roller 101.

In this state, about 10 μm as shown in (b)
Fine wire fins 12a, 1 covered with a coating 13 having a film thickness of about 1
2b is obtained. Next, as shown in (c), the heat transfer tube 1
1 thin wire fins 12a, 12b solder-plated on the outer circumference
Is braided in the same manner as in the conventional method, and the heat transfer tube 11 is fixed (when the heat transfer tube 11 is plated, the same method is braided). Next, flux is applied to the contact portions between the thin wire fins 12a and 12b and the heat transfer tube 11, and the flux is put in an atmospheric pressure furnace (otherwise, it can be heated by a hot plate or the like). Heat for about a minute. The heat treatment melts the coating 13 of the solder plating, and the solder gathers at the contact portions between the thin wire fins 12a and 12b and the heat transfer tube 11 due to surface tension, wettability, etc. to form a fillet. When the heat treatment is completed, the solder-plated coating 13 is solidified in this state, and a heat exchanger having an integral structure as shown in (d) is obtained. Maximum temperature of the joint when using the heat exchanger is 100 ° C
Since it is as follows, joining by solder plating can sufficiently withstand.
In this case, the joining temperature can be lowered as compared with Ni-plated joining, so that the joining process time can be shortened and the manufacturing advantage is great.

Example 4. In Examples 1 to 3, the thin wire fins 12a and 12b were woven into the row of the heat transfer tubes 11. However, this structure requires an automatic machine for weaving,
There is a drawback that it takes time to weave. Therefore, in the heat exchanger of the fourth embodiment, as shown in FIG.
The upper surface and the lower surface of the row of the heat transfer tubes 11 arranged at intervals in one row, that is, on the upstream side and the downstream side in the direction of the air flow,
As shown in (a), the upper wire net 15a and the lower wire net 15b are positioned and arranged so that the openings are staggered. Each of these wire nets 15a and 15b is formed by assembling wires as fine wire fins in a grid pattern. At this time, (b)
As shown in FIG. 5, the surface of the heat transfer tube 11 is preliminarily subjected to electroless Ni plating in another step, and the surface of the heat transfer tube 11 is coated with nickel to form a coating film 13. Place these in a brazing furnace in a vacuum atmosphere as described above, and
Heat at 50 ° C for 30 minutes. The Ni-plated coating 13 is melted by the heat treatment, and is gathered at the contact portions between the upper and lower metal nets 15a and 15b and the heat transfer tube 11 due to surface tension, wettability, etc. to form a fillet. Then, by finishing heating and cooling, the coating film 1 in which the metal nets 15a and 15b are solidified on the upper and lower surfaces of the heat transfer tube 11 as shown in (c)
Joined by 3 to obtain an integral heat exchanger.

Next, the operation will be described. In this heat exchanger, the air forcedly sent by a fan (not shown) hits the upper surface of the heat transfer tube 11 and the upper wire net 15a, flows through the gap between the upper wire nets 15a, and the air flows into the lower wire net 15b. At this time, since the flow direction is changed, a vortex is generated, and this vortex crushes the temperature (velocity) boundary layer generated around the heat transfer tube 11 to improve the heat transfer coefficient. A heat exchange fluid such as a refrigerant flows through the heat transfer tube 11 and exchanges heat with the turbulent air. Thus, according to this configuration,
The same effect as that of the conventional heat exchanger can be obtained, and since there is no step of weaving the fine wire fins in the heat transfer tube 11 and only a general wire mesh is used, the manufacturing time can be shortened.

Example 5. In Example 4, wire meshes were arranged above and below the heat transfer tubes 11, but in this Example 5, as shown in FIG. 5, one wire mesh 16 was alternately passed through the rows of the heat transfer tubes 11 and then joined. ing. Explaining the manufacturing method, first,
As shown in (a) and (b), the heat transfer tube 11 is preliminarily subjected to electroless Ni plating in another step to form a nickel coating 13 on the outer peripheral surface of the heat transfer tube 11. The film thickness at this time is controlled to about 1 to 10 μm depending on the plating time. Next, the plated heat transfer tubes 11 are arranged at a predetermined pitch as shown in (c) and fixed with a jig (not shown) or the like to form a pipe row. Then, the wire mesh 16 made of a copper material is passed through the pipe row alternately in front and back (zigzag) to make contact with the heat transfer tube 11. In this state, it is placed in a brazing furnace in a vacuum atmosphere, heated at 950 ° C. for 30 minutes, and then cooled to obtain the heat exchanger shown in (d).

Next, the operation will be described. In this heat exchanger, the generation of the above-mentioned vortices is reduced and the effect of crushing the temperature (velocity) boundary layer by the vortices is reduced, but since the wire mesh 16 is wound and brought into contact with the heat transfer pipes 11, the heat transfer is ensured. Of the metal net 16 acting as a fin is improved, and the heat efficiency of the heat exchanger is improved. In addition, the effect of the vortex is reduced with the heat exchanger alone having this configuration, but when this heat exchanger is combined with 2 rows and 3 rows without a gap, the effect of the vortex can also be expected, so that the heat exchange capacity of the conventional product can be expected. And can be used as a comparable one.

In the fourth and fifth embodiments described above, N is provided on the heat transfer tube 11 side.
i plating was applied, but for the wire nets 15a, 15b, 16
Alternatively, even if both are plated with Ni, the same effect can be obtained. In addition to Ni plating, the same effect can be obtained by applying solder plating as shown in FIG. Further, in Examples 1 to 5, a copper material having high thermal conductivity was used as the material of the heat transfer tube 11, and the fine wire fins 12a and 12b and the wire mesh 15a,
A copper material was also used as the material of 15b and 16, but stainless steel or other materials may be used as long as inexpensive plating such as Ni plating or solder plating is possible.

Example 6. 6 is a sectional view showing a sixth embodiment of the present invention, in which 11 is a heat transfer tube, 22a,
22b is a rod-shaped fin. Here, the arrow 3 shows the airflow direction. A plurality of heat transfer tubes 11 are arranged in a line at equal intervals, and the rod-shaped fins 22a and 22b are attached thereto. At that time, of the pair of adjacent heat transfer tubes 11 and 11, from the front of the left heat transfer tube 11 The rod-shaped fin 22a is inserted toward the rear of the heat transfer tube 11 on the right side, and these adjacent heat transfer tubes 1
Attach so that it touches 1, 11. On the rod-shaped fin 22a attached in this way, another rod-shaped fin 22b is placed next time from the front of the right-side heat transfer pipe 11 to the left-side heat transfer pipe 1.
1 to the rear of the heat transfer tubes 1 adjacent to each other
Attach so that it touches 1, 11. In this way, rod-shaped fins 22a and 22b are alternately stacked between the heat transfer tubes 11 to form a heat exchanger.

Next, the operation will be described. In this heat exchanger, air flows as shown by arrow 3. Looking at a part, at a certain place, the air passes through the rod-shaped fins 22a and flows so as to sew a gap with the rod-shaped fins 22b. When the airflow passes through the rod-shaped fins 22a, vortices are generated behind the rod-shaped fins 22a, and the vortices collide with the rod-shaped fins 22b and the heat transfer tubes 11 which are located behind them. At that time, there is an effect of disturbing the boundary layer between the rod-shaped fins 22b and the heat transfer tube 11, and the heat transfer is improved in that part.
The rod fins 22a and 22b located behind the heat transfer tube 11 also have the same effect.
The heat transfer is promoted because the vortex generated when passing through the heat transfer tube 11 repeats the action of disturbing the boundary layer of the heat transfer surface located rearward (downstream) thereof.

Example 7. 7 is a sectional view showing Embodiment 7 of the present invention. The heat exchanger of this Example 7 is the same as that of Example 6.
Another heat transfer tube 21 is inserted into the gap (opening) formed by the rod-shaped fins 22a, 22b of the heat exchanger of No. 2 and brought into contact with the rod-shaped fins 22a, 22b.

Next, the operation will be described. In this heat exchanger, heat exchange is efficiently performed according to the same principle as that of the heat exchanger of the sixth embodiment. In this case, since another heat transfer tube 21 is inserted in the gap between the rod-shaped fins 22a and 22b, the temperature of the rod-shaped fins 22a and 22b is equal to the heat transfer tubes 11 and 22.
As the temperature approaches 1, the fin efficiency increases and the temperature difference from the air flow increases. Therefore, the amount of heat exchange increases.

In the seventh embodiment, the rod-shaped fins 22a, 2a, 2
Although the heat transfer tubes 21 are inserted into all the gaps formed by 2b, it goes without saying that the heat transfer tubes 11 may be inserted at any positions depending on the capacity of the heat exchanger. Further, the diameter of the inserted heat transfer tube 21 can be set to be equal to or smaller than that of the heat transfer tube 11 depending on the capacity and size of the heat exchanger.

Example 8. 8 is a sectional view of Embodiment 8 of the present invention. Although the external appearance shown is the same as that of the embodiment of FIG. 6, in this embodiment, a plurality of rod-shaped fins 22a are arranged parallel to each other in an oblique direction with respect to the airflow direction, and are arranged adjacent to the rod-shaped fins 22a. A plurality of rod-shaped fins 22b are arranged parallel to each other in the diagonal direction opposite to the above, thereby forming a grid 22 having rhombic openings, and stacking a plurality of the grids 22 with a refrigerant flow path at the openings of these grids 22. The heat transfer tube 11 is inserted, and the rod-shaped fins 22a and 22b forming each side of the lattice 22 are brought into close contact with the heat transfer tube 11.

Example 9. 9 is an external view showing Embodiment 9 of the present invention, in which 24 is a U-shaped fin. In this heat exchanger, the U-shaped fins 24 are stacked in the axial direction of the heat transfer tube 11 and attached. The U-shaped fins 24 have alternating directions. Note that an H-shaped fin may be used instead of the U-shaped fin.

Next, the operation will be described. In this heat exchanger, heat exchange is efficiently performed according to the same principle as that of the sixth embodiment. In this case, since the fins are attached to the heat transfer tube 11 in a U shape or an H shape, the heat transfer tube 11 is bent as shown in FIG. 10 so that the entire heat exchanger has the same shape as that of the sixth embodiment. Heat transfer tube 11
It has a degree of freedom that allows various heat exchanger shapes to be formed by bending. In addition, the amount of heat exchange can be adjusted by adjusting the length of the U-shaped fin 24.

Example 10. FIG. 11 is a first embodiment of the present invention.
It is a side view showing 0, 11 is a heat transfer tube, 3
Is an air flow direction, and 25 is an annular fin. This heat exchanger is formed by penetrating a plurality of annular fins 25 through the heat transfer tube 11 and stacking them, and is attached so that the annular fins 25 are in contact with the heat transfer tube 11. As a method of attachment, tension may be applied to the annular fin 25 to contact the heat transfer tube 11 as shown in FIG. 12, or may be welded by soldering or the like.

Next, the operation will be described. In this heat exchanger, a vortex is generated from a portion of the annular fin 25 in the air flow inflow direction, and the vortex is generated by the heat transfer tube 11 and the annular fin 25.
By colliding with other parts of the air flow, turbulence is added to the boundary layer of the part, and the heat transfer coefficient is improved by updating the boundary layer, that is, vortices are generated to disturb the main flow of the air flow. The heat transfer is promoted not only by giving it, but also by making it collide with the heat transfer surface and using it again.

Example 11. FIG. 13 is a first embodiment of the present invention.
1 is a cross-sectional view showing 1; 11 is a heat transfer tube; 25 is an annular fin; and 26 is a rod or tube inserted to determine the distance between the heat transfer tubes 11. 26 may be the heat transfer tube 11 or may have a diameter different from that of the heat transfer tube 11. In this heat exchanger, a plurality of heat transfer tubes 11 are arranged in parallel, and annular fins 25 attached to adjacent heat transfer tubes 11 are used.
So that the annular fins 25 attached to the other overlap
All heat transfer tubes 11 are arranged. Then, a rod or a tube 26 is inserted into the gap (opening) in the overlapping portion, and the endmost heat transfer tube 11 is pulled laterally, so that the annular fin 25
The rod or tube 26 and the heat transfer tube 11 are brought into contact with the annular fin 25 by applying a tension to. When tension is applied from the left and right in this way, the contact between the annular fin 25 and the heat transfer tube 11 and the rod or tube 26 is improved, and not only the contact heat resistance at the time of heat transfer can be reduced but also the heat transfer tube 11 The pitch can be determined and it is easy to manufacture. The operation of this embodiment is the same as that of the heat exchanger of the tenth embodiment.

Example 12. FIG. 14 is a first embodiment of the present invention.
2 is an external view showing 2, wherein 11 is a heat transfer tube and 27 is a pair of wire fins. This heat exchanger is configured by disposing a pair of wire-shaped fins 27 on both sides of the heat transfer tube 11 and twisting the ends of the wire-shaped fins 27 together. This heat exchanger has a structure similar to that of the tenth embodiment. In this case, if the tension at the time of twisting is adjusted, the heat transfer tube 11 and the wire-shaped fin 27 can be adjusted.
The contact thermal resistance of is reduced. Regarding the operation of this embodiment,
This is the same as the heat exchanger of the tenth embodiment, and if the length of the wire-shaped fins 27 is made appropriate, the required heat transfer area can be obtained.

Example 13 FIG. 15 is a first embodiment of the present invention.
It is sectional drawing which shows 3. This heat exchanger changes the posture of the heat exchanger of the ninth embodiment shown in FIG.
The ends of the U-shaped fins 24 are located below the horizontal plane 28.

Next, the operation will be described. In this heat exchanger, when the air flow passes through the heat exchanger, the U-shaped fins 2
When the temperature of 4 is lower than the dew point temperature of the air flow, the water vapor in the air flow is condensed and water drops are generated on the U-shaped fins 24. Since the ends of the U-shaped fins 24 are below the horizontal plane,
Water droplets travel along the surface of the U-shaped fins 24 and gather at the ends,
Gravity makes it easy to fall. In this case, by tilting the entire heat exchanger, not only the structure in which the ends of the U-shaped fins 24 are lower than the horizontal plane 28, but only the ends of the U-shaped fins 24 are bent and the U-shaped fins 24 are bent. You may make it the edge part of this face a vertical direction.
The same applies to the H-shaped instead of the U-shaped.

Example 14. In the heat exchanger of the fourteenth embodiment, for example, the heat transfer tube 11 and the fins 12a and 12b of the heat exchanger of the sixth embodiment of FIG. 6 are made of materials having different contact angles. When the heat exchanger is operated under the condition that water drops are generated on the fins as described in the thirteenth embodiment, the heat exchanger tube 11 is made of a material having a contact angle smaller than the contact angles of the fins 12a and 12b. Then, the heat transfer tube 1
1 is more hydrophilic than the fins 12a and 12b, and the water droplets are attracted and concentrated on the heat transfer tube 11, the weight of the water droplet increases, and the water is drained through the heat transfer tube 11. Also,
On the contrary, the contact angle of the fins 12a and 12b is the heat transfer tube 1
When made of a material that has a contact angle smaller than 1,
The fins 12a and 12b become more hydrophilic than the heat transfer tube 11, and water droplets concentrate on the fins 12a and 12b. When the weight of the water drops increases and the water drops easily, or when the velocity of the airflow is high, the airflow facilitates the blow-off, which facilitates drainage. As a result, it is possible to suppress an increase in pressure loss due to the attachment of water droplets, and also to prevent the mechanism of heat transfer promotion from being lost due to water droplets, so that the heat transfer performance can be maintained. In addition, Examples 7-1
Even if this is applied to the heat exchanger of No. 3, the same effect can be obtained.

Example 15. The structure and operation of the fifteenth embodiment are exactly the same as those of the heat exchanger described in the fourteenth embodiment, but the contact angle between the fin and the heat transfer tube is made different by the surface treatment. For example, the fins may be subjected to a water repellent treatment and the heat transfer tubes may be subjected to a hydrophilic treatment, and vice versa. This facilitates drainage and eliminates the harmful effects of water droplets, so that the performance of the heat exchanger is maintained as in the fourteenth embodiment.

Example 16. 16 shows a first embodiment of the present invention.
6 is a sectional view of FIG. In the figure, reference numeral 11 denotes a plurality of heat transfer tubes arranged vertically at regular intervals, and a working fluid (for example, a refrigerant) in the tubes flows inside. 32a and 32b are fine wire fins for weaving. Reference numeral 33 denotes a support rod, which is arranged in the direction orthogonal to the flow direction 3 of the air flow with the same interval as the heat transfer pipe 11 and shifted by a half pitch.
It is arranged so that it is pinched from the front and back. And
The support rods 33 and the heat transfer tubes 11 on the upstream side of the air flow are alternately woven with the thin wire fins 32a, and the support rods 33 and the heat transfer tubes 11 on the downstream side of the air flow are alternately woven with the other thin wire fins 32b. , 32b are staggered.

Next, the operation will be described. In this heat exchanger, air cannot flow straight through the core portion of the heat exchanger and flows so as to sew through the gaps between the braided fine wire fins 32a and 32b, the support rod 33, and the heat transfer tube 11, and at that time, minute vortices are generated. To do. The generated vortices are not simply flowed down, but the thin wire fins 32b on the downstream side, the support rods 33, the heat transfer tube 1
Taken at 1 to generate flow turbulence. as a result,
Heat transfer is promoted and the heat exchanger surface shows a high heat transfer coefficient.
Further, since the support rod 33 is provided, the heat transfer tube 11
The crossing angle between the thin wire fins 32a and 32b as viewed in a cross section orthogonal to is increased. Therefore, even if it is used under the condition that the moisture in the air is condensed, it becomes difficult for the droplets to be retained,
Less likely to cause clogging. Therefore, there is an advantage that the reduction of the heat exchange amount due to the reduction of the air volume is suppressed.

Example 17 FIG. 17 is a first embodiment of the present invention.
7 is a sectional view of FIG. In the heat exchanger of this embodiment, another heat transfer tube 31 is used instead of the support rod 33 of the 16th embodiment. In this heat exchanger, as a result, the heat transfer tubes 11, 31, 31 are arranged in three rows and the rows are displaced by half a pitch, so that the heat transfer tubes are arranged in a staggered manner.
In this heat exchanger, heat exchange is efficiently performed as in the sixteenth embodiment. At that time, instead of the support rod, another heat transfer tube 31
, The fin efficiency of the thin wire fins 32a and 32b is increased, and heat transfer is further promoted. The diameter of the heat transfer tube 31 may be the same as or different from the diameter of the heat transfer tube 11.

Example 18. FIG. 18 shows a first embodiment of the present invention.
8 is a side view of FIG. In the figure, 11 is a heat transfer tube, 32a,
32b is a thin wire fin, 33 is a support rod, and 34 is a header. The heat exchanger of this embodiment is the same as the heat exchanger of the 16th embodiment except that a header 34 is provided. Each end of the heat transfer tubes 11 communicates with a header 34 extending in the arrangement direction of the heat transfer tubes 11, and each heat transfer tube 11 receives the distribution of the working fluid from the header 34 or joins the working fluid to the header 34. The support bar 33 is fixed to the outer surface of the header 34 by means such as brazing, and receives strong support. Therefore, sufficient strength against the tension of the thin wire fins 32a and 32b can be provided. In addition, although the circular pipe is used for the header 34 in the present embodiment, the present invention is not limited to this. Further, the fixing position of the support rod 33 to the header 44 is not limited to the side surface. In this heat exchanger, heat exchange is efficiently performed as in the sixteenth embodiment.

Example 19. FIG. 19 shows the first embodiment of the present invention.
9 is a sectional view of FIG. The heat exchanger of this embodiment is the same as that of the first embodiment.
Of the heat transfer tubes 11, 31, 31 arranged in three rows of the heat exchanger 7 of FIG. 7, the heat transfer tubes 11 in the central row and the heat transfer tubes 3 in the rows on both sides thereof
Support rods 35 and 35 extending in a direction orthogonal to the heat transfer tubes 11 and 31 are provided between the support rods 1 and 31. The support rods 35 are inserted at an appropriate pitch in the axial direction of the heat transfer tube 11. In this heat exchanger, heat exchange is efficiently performed as in the sixteenth embodiment. In addition, the heat transfer tube 1 is supported by the support rod 35.
Since 1 and 31 are positioned and fixed, manufacturing is facilitated and the pitch of the heat transfer tubes 11 and 31 can be fixed, and the structure is strong.

Example 20. FIG. 20 shows a second embodiment of the present invention.
FIG. Reference numeral 11 is a plurality of heat transfer tubes arranged in parallel at regular intervals, and 42 is a fine wire fin for weaving. The fine wire fins 42 are alternately woven on the front side and the back side of the heat transfer tube 11, but the fine wire fins 42 at any stage
Is woven by skipping the heat transfer tubes 11 in one row or several rows. In this heat exchanger, the fine wire fins 42 at appropriate stages are knitted in one row or several rows in a row, so that the droplets are not easily held, and it is used under the condition that water in the air is condensed. Also, there is an advantage that clogging is less likely to occur and a decrease in heat exchange amount due to a decrease in air volume is suppressed. Other than that, the heat exchange is efficiently performed on the principle similar to that of the sixteenth embodiment and the like.

Example 21. FIG. 21 shows a second embodiment of the present invention.
2 is a sectional view of FIG. The heat exchanger of this embodiment is the same as that of the first embodiment.
The flat tube 51 is used instead of the heat transfer tube 11 of the heat exchanger 6 of FIG. The flat tubes 51 are arranged with their major axis directions aligned with the air flow direction. In this heat exchanger,
Similar to No. 6, clogging does not easily occur even when used under the condition that water in the air is condensed. In particular, since the flat tube 51 is used, the contact angle with the braided fine wire fins becomes large, and it becomes difficult for the liquid droplets to be held and clogging does not occur. Also,
The pressure loss of the air flow is reduced, and the decrease in heat exchange due to the decrease in air volume is suppressed. An elliptic tube may be used as the flat tube 51. Of course, the heat transfer tube made of a flat tube may be replaced with the heat transfer tube 11 of Examples 17 to 20.

Example 22. 22 shows a second embodiment of the present invention.
It is sectional drawing of FIG. The heat exchanger of this embodiment is the same as that of the first embodiment.
The thin wire fins 32a, 32b are pulled by pulling the ends of the thin wire fins 32a, 32b in the heat exchanger 6 of FIG.
Tension is applied to the heat transfer tube 11 and the support rod 33.
And the thin wire fins 32a and 32b are in close contact with each other. This is also applicable to the heat exchangers of Examples 17 to 20.

Example 23. 23 shows a second embodiment of the present invention.
3 is a sectional view of FIG. In the heat exchanger of this embodiment, a heat transfer tube 61 made of a soft material is used as the heat transfer tube of the heat exchanger of the sixteenth embodiment. Fine wire fins 32a, 3
When 2b is braided into the heat transfer tube 61 with tension, the heat transfer tube 61 is deformed in an uneven shape due to the adhesion force of the thin wire fins 32a and 32b, and the degree of adhesion is increased. Therefore, the thermal resistance due to contact is reduced, and the heat transfer is promoted by the unevenness generated in the tube. 4 is the flow direction of the working fluid in the pipe. This technique can also be applied to the heat exchangers of Examples 17-22.

Example 24. FIG. 24 shows a second embodiment of the present invention.
4 is a sectional view of FIG. In the figure, numeral 71 indicates a depression 7 on the outer peripheral surface.
Heat transfer tubes 1a are attached, and 32a and 32b are fine wire fins for weaving. When the fine wire fins 32a and 32b are woven into the heat transfer tube 71, the fine wire fins 32a and 32b are
The heat transfer tube 71 is fitted and fixed in a recess 71a provided on the surface of the heat transfer tube 71, and the contact thermal resistance with the heat transfer tube 71 is reduced. Also,
The thin wire fins 32a and 32b are easily fixed, which facilitates manufacturing. There is also an advantage that the pitch of the thin wire fins can be easily changed by changing the pitch of the depressions. This technique can also be applied to the heat exchangers of Examples 17-22.

Example 25. FIG. 25 shows a second embodiment of the present invention.
5 is a sectional view of FIG. The heat exchanger of this example is the same as that of Example 16.
The entire heat exchanger is bent to form a heat transfer surface in a wavy shape. In the heat exchanger of this embodiment, the heat transfer area per front surface area can be made large, and the heat exchange efficiency can be improved. The same effect can be expected even when the heat exchangers of Examples 17 to 24 are bent into a corrugated shape.

Example 26. FIG. 26 shows a second embodiment of the present invention.
6 is a sectional view of FIG. The heat exchanger of this example is the same as that of Example 16.
The heat exchanger of (1) is curved as a whole to form a heat transfer surface in a semicircular shape. In the heat exchanger of this embodiment, the heat transfer area per front surface area can be made large, and the heat exchange efficiency can be improved. Further, the semicircular shape can be changed according to the direction of the air flow and the wind force characteristics of the fan as shown by the arrow in the figure. The same effect can be expected even if the heat exchangers of Examples 17 to 24 are curved in a semicircular shape.

Example 27. FIG. 27 shows the second embodiment of the present invention.
7 is a perspective view of FIG. Reference numeral 81 is a thin-wire fin braided heat exchanger, 82 is a plate fin tube heat exchanger,
These are closely arranged facing each other. The former has a structure in which fine wire fins 12a and 12b are alternately woven on the front side and the back side of a plurality of heat transfer tubes 11 arranged in a line at regular intervals, and the fine wire fins 12a and 12b are in close contact with each other. The latter is composed of the heat transfer tube 11 and a plurality of plate-shaped fins 82a inserted into the heat transfer tube 11 at regular intervals. What is important here is the plate fin tube type heat exchanger 82 on the upstream side in the air flow direction 3, that is, in the first row.
Is arranged, and the thin-line fin braided heat exchanger 81 is arranged on the downstream side, that is, in the second row.

Next, the operation will be described. The air enters the plate fin tube heat exchanger 82 in the first row and takes full advantage of the leading edge effect to obtain a high heat transfer coefficient. In the second row where the flow has developed, the heat transfer tube 11 and the braided fine wire fins 12a, 1 are provided.
The heat transfer coefficient is improved by the effect of the vortex generated between 2b.
The result is a heat exchanger with a high average heat transfer coefficient.

Even when used under the condition that water in the air is condensed, the condensation is mainly generated in the plate-shaped fins 82a of the first row.
Let it be done above, the second row thin wire fin braided heat exchanger 8
The clogging caused by dew condensation at 1 is suppressed. In this way, by using the plate fin tube heat exchanger 82 having a large heat transfer area per front surface area together, the heat transfer area of the entire heat exchanger is made larger than that of arranging the thin wire fin braided heat exchanger 81 in two rows. can do.

Example 28. FIG. 28 shows the second embodiment of the present invention.
9 is a perspective view of FIG. Reference numeral 81 is a thin-wire fin braided heat exchanger, and 83 is a corrugated fin tube heat exchanger, which are closely arranged to face each other. The latter is
The flat heat transfer tube 83a is provided with corrugated fins 83b. What is important here is that the corrugated fin tube heat exchanger 83 is located on the upstream side of the air flow direction 3, that is, in the first row.
Is arranged, and the thin-line fin braided heat exchanger 81 is arranged on the downstream side, that is, in the second row. The function and effect are similar to those of the twenty-seventh embodiment.

Example 29. FIG. 29 shows the second embodiment of the present invention.
9 is a sectional view of FIG. In the heat exchanger of this embodiment, the plate fin tube heat exchanger 82 and the heat exchanger of embodiment 16 are closely arranged to face each other, and the former is positioned upstream in the air flow direction and the latter is positioned downstream. It is a thing. As the effect, the heat exchanger of Example 16 is arranged in the second row,
The efficiency can be expected to be higher than that of the heat exchanger of Example 27.

Example 30. FIG. 30 shows a third embodiment of the present invention.
It is sectional drawing of 0. In the heat exchanger of this embodiment, the corrugated fin tube heat exchanger 83 and the heat exchanger of embodiment 16 are closely arranged to face each other, and the former is arranged on the upstream side in the air flow direction.
The latter is located on the downstream side. As the effect, the heat exchanger of Example 16 is arranged in the second row,
The efficiency can be expected to be higher than that of the heat exchanger of Example 28.

[0118]

As described above, according to the first aspect of the present invention, since the heat transfer tube and the thin wire fin are joined by the molten and solidified body of the plated metal coating, the heat transfer tube and the thin wire fin are thermally coupled. The resistance is reduced, the heat transfer efficiency is improved, and the heat exchange efficiency is improved.

According to the second aspect of the invention, in the type in which the thin wire fin is woven into the heat transfer tube, the heat transfer tube and the thin wire fin are joined by the molten solidified body of the plated metal coating. There is an effect that the thermal resistance of the heat pipe and the thin wire fin is reduced, the heat transfer efficiency is improved, and the heat exchange efficiency is improved.

According to the third aspect of the present invention, the wire mesh composed of thin wire fins is arranged on the front surface and the rear surface of the heat transfer tube.
Since the heat transfer tube and the thin wire fin are configured to be joined by the molten solidified body of the plated metal film, the thermal resistance of the heat transfer tube and the thin wire fin is reduced, the heat transfer efficiency is improved, and the heat exchange efficiency is improved. In addition, there is an effect that it can be manufactured at low cost.

According to the fourth aspect of the invention, since the wire mesh is alternately passed through the front side and the back side of the heat transfer tube, there is an effect that the heat exchange efficiency is improved even with one wire mesh.

According to the invention of claim 5, a metal coating is formed on at least one of the outer peripheral surface of the heat transfer tube and the outer peripheral surface of the fine wire fin in advance, and then the heat transfer tube and the fine wire fin are combined and combined. By heating up to the melting temperature of the metal coating with, the part of the metal coating is melted and the heat transfer tube and the thin wire fin are joined, so the thickness of the metal coating can be controlled by the plating time. It is possible to prevent the excess joining material from filling the space between the thin wire fins, and it is possible to perform precise joining.
Therefore, there is an effect that the thermal resistance of the heat transfer tube and the thin wire fin can be reduced and the heat exchange efficiency can be improved.

According to the invention of claim 6, since Ni plating is applied, in addition to the effect of the invention of claim 5,
There is an effect that it is suitable for joining materials according to it.

According to the invention of claim 7, since it is configured to perform solder plating, in addition to the effect of the invention of claim 5,
There is an effect that it is suitable for joining materials according to it.

According to the eighth aspect of the present invention, since the rod-shaped fins are alternately inserted into the heat transfer tube, when air is passed through the heat exchanger, air is sewn in the gap between the thin wire fins and the heat transfer tube. As described above, it is possible to flow the fluid while accelerating it and discharging the vortex, inducing turbulence of the flow, improving heat transfer promotion, and improving heat exchange efficiency. Furthermore, since the length of the fin can be freely set, there is an effect that the fin area can be increased and the required heat transfer area can be easily obtained.

According to the invention of claim 9, since the heat transfer tube is further inserted, the heat transfer performance is further improved by improving the fin efficiency and the like, compared with the invention of claim 8.
There is an effect that the heat exchange efficiency is improved.

According to the tenth aspect of the present invention, the rod-shaped fins are arranged so as to form a rhombic lattice, a plurality of the fins are stacked, and the heat transfer tubes serving as the refrigerant flow passages are inserted into the openings of these lattices.
Since the grid and the heat transfer tube are configured to be in close contact with each other, the heat exchange efficiency can be improved as in the invention of claim 8 and
The effect is that it is easy to manufacture.

According to the eleventh aspect of the invention, since the U-shaped or H-shaped fins are attached to the heat transfer tube, the heat exchange efficiency can be improved and the fins can be improved as in the eighth aspect. Since the dimensions can be freely set, there is an effect that a necessary heat transfer area can be easily obtained.

According to the twelfth aspect of the invention, since the ring-shaped fins are provided, the heat exchange efficiency can be improved and the dimension of the ring can be changed similarly to the eighth aspect of the invention. This has the effect that the heat transfer area can be set freely.

According to the thirteenth aspect of the present invention, the heat transfer tube is inserted in the overlapping portion of the annular fins.
The heat transfer area can be increased without impairing the effect of heat transfer promotion, and heat exchange efficiency can be improved. Furthermore, since tension is applied to the thin wire fins by pulling the heat transfer tubes, it is possible to improve the thermal contact between the heat transfer tubes and the fins and to fix the pitch of the heat transfer tubes.

According to the fourteenth aspect of the present invention, since the wire-shaped fins are attached to the heat transfer tube, not only can the heat exchange efficiency be improved by the wire-shaped fins as in the case of the eighth aspect. By adjusting the length of the wire fin, it is possible to obtain a necessary heat transfer area.

According to the fifteenth aspect of the invention, since the end portions of the fins face downward from the horizontal plane, in addition to the effect of the eighth aspect of the invention, the condensed water easily drops, and the condensed water blocks the air passage. Is alleviated, the effect of promoting heat transfer can be maintained, and as a result, the heat exchange efficiency is improved.

According to the sixteenth aspect of the invention, since the thin wire fins and the heat transfer tubes are formed of materials having different contact angles, drainage is easy even if water is condensed, and water droplets are used between the fins. Is less likely to be retained, heat transfer performance is maintained even when water is condensed, and as a result, heat exchange efficiency is improved.

According to the seventeenth aspect of the invention, since the fine wire fins and the heat transfer tubes are configured to be subjected to surface treatments having different contact angles, water droplets are less likely to be retained between the fins as in the preceding paragraph, and the heat transfer is reduced. The thermal performance is maintained even when water is condensed, and as a result, the heat exchange efficiency is improved.

According to the eighteenth aspect of the present invention, since the fine wire fins are knitted into the support rod arranged at a position distant from the heat transfer tube, the crossing angle between the fine wire fins becomes large, and the droplets are difficult to be held. Thus, even if the heat exchanger is used while the surface is wet, it is less likely to be clogged, the decrease in the heat exchange amount due to the decrease in the air flow is controlled, and as a result, the heat exchange efficiency is improved.

According to the nineteenth aspect of the present invention, since the new heat transfer tube is provided as the support rod, the fin efficiency of the thin wire fin is improved, the heat transfer is promoted, and the heat exchange efficiency is improved. There is.

According to the twentieth aspect of the invention, since the support rod is fixed to the header, in addition to the effect of the eighteenth aspect of the invention, sufficient strength against the tension of the thin wire fins can be provided. effective.

According to the twenty-first aspect of the invention, since the new heat transfer tube and the support rod are provided, the crossing angle of the thin wire fins becomes large, and it becomes difficult to hold the liquid droplets, and the heat exchanger surface Even when used in a wet state, clogging is unlikely to occur, and a decrease in heat exchange amount due to a decrease in air volume is suppressed, and as a result, heat exchange efficiency is improved. Further, there is an effect that the heat transfer tube pitch can be fixed by the support rod and the structure becomes strong.

According to the twenty-second aspect of the present invention, since the fine wire fins are appropriately woven, the number of crossings between the fine wire fins is reduced, and hence the amount of droplets retained is reduced, and Even if the exchanger surface is used in a wet state, it is unlikely to be clogged, the decrease in the heat exchange amount due to the decrease in the air volume is suppressed, and as a result, the heat exchange efficiency is improved.

According to the twenty-third aspect of the present invention, since the flat tube is used as the heat transfer tube, the contact angle between the heat transfer tube and the braided fine wire fin becomes large, and it becomes difficult to hold the liquid droplets, and heat exchange is performed. Even if the vessel surface is used in a wet state, clogging is unlikely to occur, and a reduction in heat exchange rate due to a reduction in air volume is suppressed, and as a result, heat exchange efficiency is improved.

According to the twenty-fourth aspect of the present invention, since the thin wire fin is configured to be tensioned, the heat transfer tube and the thin wire fin are brought into close contact with each other to reduce the thermal resistance due to the contact, and as a result, the heat exchange efficiency is improved. effective.

According to the twenty-fifth aspect of the present invention, a soft material is used for the heat transfer tube, and tension is applied to the thin wire fins to cause unevenness on the surface of the heat transfer tube so that the heat transfer tube and the thin wire are brought into close contact with each other. Since it is configured, the thermal resistance between the heat transfer tube and the thin wire is reduced, and the heat transfer in the tube is promoted, and as a result, the heat exchange efficiency is improved.

According to the twenty-sixth aspect of the present invention, since the tube having the depression is used as the heat transfer tube, the thin wire fins can be easily fixed to the heat transfer tube, and the heat generated by the contact between the heat transfer tube and the thin wire can be improved. The resistance is reduced, and as a result, the heat exchange efficiency is improved.

According to the twenty-seventh aspect of the present invention, since the heat transfer surface is formed in a corrugated shape, the heat transfer area per front surface area is increased, and as a result, the heat exchange efficiency is improved. .

According to the twenty-eighth aspect of the invention, since the heat transfer surface is formed in a semicircular shape, the heat transfer area per front surface area is increased, and as a result, the heat exchange efficiency is improved. .

According to the twenty-ninth aspect of the invention, since the plate fin tube type heat exchanger and the fine wire fin braided type heat exchanger are arranged in two rows, the heat transfer area per front surface area is The heat exchanger can be made larger than the two rows. Also, when used under conditions where water in the air will condense, condensation can be performed mainly on the plate in the first row, and clogging due to condensation in the heat exchanger in the second row can be suppressed. The effect of suppressing a decrease in the amount of heat exchange due to a decrease in the amount of air flow and, as a result, improving the heat exchange efficiency is obtained.

According to the twenty-ninth aspect of the invention, since the corrugated fin tube type heat exchanger and the thin wire fin woven type heat exchanger are arranged in two rows, the heat transfer area per front surface area is The heat exchanger can be made larger than the two rows. Further, when used under the condition that the moisture in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed. There is an effect that a decrease in heat exchange amount due to a decrease in air volume is suppressed, and as a result, heat exchange efficiency is improved.

According to the thirtieth aspect of the present invention, the plate fin tube heat exchanger and the fine wire fin braided heat exchanger are arranged in two rows. Therefore, the heat transfer area per front surface area is the same as that of the latter. It is possible to make the exchanger larger than a two-row exchanger. Further, when used under the condition that the moisture in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed. There is an effect that a decrease in heat exchange amount due to a decrease in air volume is suppressed, and as a result, heat exchange efficiency is improved.

According to the thirty-first aspect of the invention, since the plate fin tube type heat exchanger and the air conditioning heat exchangers of the eighteenth to twenty-sixth aspects are arranged in two rows, heat transfer per front surface area The area can be larger than the latter two-column heat exchanger. Further, when used under the condition that the moisture in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed. There is an effect that a decrease in heat exchange amount due to a decrease in air volume is suppressed, and as a result, heat exchange efficiency is improved.

According to the invention of claim 32, since the corrugated fin tube type heat exchanger and the heat exchangers for air conditioning according to claims 18 to 26 are arranged in two rows, heat transfer per front surface area The area can be larger than the latter two-column heat exchanger. Further, when used under the condition that the moisture in the air is condensed, the condensation is mainly performed on the corrugated fins in the first row, and the clogging due to the condensation in the heat exchanger in the second row can be suppressed. There is an effect that a decrease in heat exchange amount due to a decrease in air volume is suppressed, and as a result, heat exchange efficiency is improved.

[Brief description of drawings]

FIG. 1 is a diagram showing a heat exchanger for air conditioning and a method for manufacturing the same according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a method for manufacturing an air conditioning heat exchanger according to a second embodiment of the present invention.

FIG. 3 is a cross-sectional view showing a method for manufacturing an air conditioning heat exchanger according to a third embodiment of the present invention.

FIG. 4 is a diagram showing an air conditioning heat exchanger and a method for manufacturing the same according to a fourth embodiment of the present invention.

FIG. 5 is a diagram showing a heat exchanger for air conditioning and a method for manufacturing the same according to a fifth embodiment of the present invention.

FIG. 6 is a sectional view showing an air conditioning heat exchanger according to a sixth embodiment of the present invention.

FIG. 7 is a sectional view showing an air conditioning heat exchanger according to a seventh embodiment of the present invention.

FIG. 8 is a sectional view showing an air conditioning heat exchanger according to an eighth embodiment of the present invention.

FIG. 9 is a perspective view showing an air conditioning heat exchanger according to a ninth embodiment of the present invention.

FIG. 10 is a perspective view showing an application example of the ninth embodiment.

FIG. 11 is a perspective view showing an air conditioning heat exchanger according to a tenth embodiment of the present invention.

FIG. 12 is a view of the air conditioning heat exchanger of Example 10 viewed from above.

FIG. 13 is a perspective view showing an air conditioning heat exchanger according to an eleventh embodiment of the present invention.

FIG. 14 is a perspective view showing an air conditioning heat exchanger according to a twelfth embodiment of the present invention.

FIG. 15 is a sectional view showing an air conditioning heat exchanger according to a thirteenth embodiment of the present invention.

FIG. 16 is a sectional view showing an air conditioning heat exchanger according to a sixteenth embodiment of the present invention.

FIG. 17 is a sectional view showing an air conditioning heat exchanger according to a seventeenth embodiment of the present invention.

FIG. 18 is a side view showing an air conditioning heat exchanger according to an eighteenth embodiment of the present invention.

FIG. 19 is a sectional view showing an air conditioning heat exchanger according to a nineteenth embodiment of the present invention.

FIG. 20 is a perspective view showing an air conditioning heat exchanger according to a twentieth embodiment of the present invention.

FIG. 21 is a sectional view showing an air conditioning heat exchanger according to a twenty-first embodiment of the present invention.

FIG. 22 is a cross-sectional view of essential parts showing an air conditioning heat exchanger according to Embodiment 22 of the present invention.

FIG. 23 is a cross-sectional view of essential parts showing a heat exchanger for air conditioning according to Embodiment 23 of the present invention.

FIG. 24 is a sectional view showing an air conditioning heat exchanger according to Embodiment 24 of the present invention.

FIG. 25 is a sectional view showing an air conditioning heat exchanger according to a twenty-fifth embodiment of the present invention.

FIG. 26 is a perspective view showing a heat exchanger for air conditioning according to Embodiment 26 of the present invention.

FIG. 27 is a perspective view showing an air conditioning heat exchanger according to Embodiment 27 of the present invention.

FIG. 28 is a perspective view showing a heat exchanger for air conditioning according to Embodiment 28 of the present invention.

FIG. 29 is a sectional view showing an air conditioning heat exchanger according to embodiment 29 of the present invention.

FIG. 30 is a sectional view showing an air conditioning heat exchanger according to a thirtieth embodiment of the present invention.

FIG. 31 is a perspective view of a conventional air conditioning heat exchanger.

FIG. 32 is an enlarged view of a main part showing a state where air flows in a conventional air conditioning heat exchanger.

[Explanation of symbols]

 3 Airflow direction 11,21,31 Heat transfer tube 12a, 12b, 32a, 32b, 42 Fine wire fin 13 Metal coating 15a, 15b, 16 Wire mesh 22a, 22b Rod-shaped fin 24 U-shaped fin 25 Circular fin 26 Rod or tube 27 Wire-shaped Fins 33, 35 Support rod 34 Header 51 Flat tube 71 Heat transfer tube 71a Depression 81 Fine wire fin braided heat exchanger 82 Plate fin tube type heat exchanger 83 Corrugated fin tube type heat exchanger 85 Heat exchanger

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[Procedure amendment]

[Submission date] November 25, 1993

[Procedure Amendment 1]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 31

[Correction method] Change

[Correction content]

[Procedure Amendment 2]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 32

[Correction method] Change

[Correction content]

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0001

[Correction method] Change

[Correction content]

[0001]

BACKGROUND OF THE INVENTION The present invention relates to, for example, a heat pump.
The present invention relates to an air conditioning heat exchanger used in a type air conditioner .

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0004

[Correction method] Change

[Correction content]

When, for example, cold water is flowed through the heat transfer tube 1 of such a heat exchanger, or when a low-temperature refrigerant is evaporated inside the heat transfer tube 1, the passing air is cooled, whereby cooling can be performed. . At this time, if the air near the surfaces of the heat transfer tube 1 and the thin wire fins 2a, 2b is cooled to a temperature below the dew point temperature, dew condensation will form on the surfaces of the heat transfer tube 1 and the thin wire fins 2a, 2b.
Occurs .

[Procedure Amendment 5]

[Document name to be amended] Statement

[Name of item to be corrected] 0131

[Correction method] Change

[Correction content]

According to the fourteenth aspect of the present invention, since the wire-shaped fin is attached to the heat transfer tube, the heat exchange efficiency can be improved by the wire-shaped fin as in the case of the eighth aspect. Not only that, but there is an effect that a necessary heat transfer area can be obtained by adjusting the length of the wire fin.

[Procedure correction 6]

[Document name to be amended] Statement

[Name of item to be corrected] 0133

[Correction method] Change

[Correction content]

[0133] According to the invention of claim 16, and then, is formed by materials having different contact angles a fine wire fins and the heat transfer tube, even moisture condenses be easily drained, water droplets between full fin Is less likely to be retained, heat transfer performance is maintained even when water is condensed, and as a result, heat exchange efficiency is improved.

[Procedure Amendment 7]

[Document name to be amended] Statement

[Name of item to be corrected] Fig. 13

[Correction method] Change

[Correction content]

FIG. 13 is a sectional view showing an air conditioning heat exchanger according to Embodiment 11 of the present invention.

Front Page Continuation (72) Inventor Takayuki Yoshida 3-18-1 Oga, Shizuoka City, Air-Conditioning Engineering Management Center, Mitsubishi Electric Corporation (72) Inventor Tomomasa Takeshita 3--18-1, Oka, Shizuoka City Air Conditioning Company In Engineering Center (72) Inventor Yoichi Kumori 8-1-1 Tsukaguchihonmachi, Amagasaki City Mitsubishi Electric Corporation Production Technology Laboratory (72) Inventor Kuraki Kitazaki 8-1-1 Tsukaguchihonmachi, Amagasaki Mitsubishi Electric Production Technology Laboratory Co., Ltd.

Claims (32)

[Claims] 1. A heat exchanger for air conditioning, in which a thin wire fin is arranged in contact with the outer periphery of a heat transfer tube through which a refrigerant flows,
A heat exchanger for air conditioning, characterized in that the heat transfer tube and the thin wire fin are joined by a melted and solidified body of a metal coating plated on either surface of the heat transfer tube or the thin wire fin. 2. A heat exchanger for air conditioning in which a plurality of heat transfer tubes in which a refrigerant flows are arranged at intervals, and thin wire fins are wound around the outer circumference of these heat transfer tubes, wherein either the heat transfer tube or the thin wire fins is wound. A heat exchanger for air conditioning, wherein the heat transfer tube and the thin wire fins are joined by a melted and solidified body of a metal coating plated on the surface of the. 3. A heat transfer tube in which a plurality of tubes are arranged in a line at intervals and a refrigerant flows therein, a wire mesh arranged on the front and rear surfaces of the heat transfer tubes arranged in a line, and the heat transfer tube and the wire mesh. An air-conditioning heat exchanger for joining the heat transfer tube and a wire net, which is formed by melting and solidifying by heating and cooling on one surface of the metal film, and joining the heat transfer tube and the wire mesh. 4. A heat transfer tube in which a plurality of tubes are arranged in a row at intervals and a refrigerant flows therein, a wire mesh alternately passed through the rows of the heat transfer tubes, and a surface of either the heat transfer tube or the wire mesh. An air-conditioning heat exchanger for joining the heat transfer tube and a wire net, which is formed by melting and solidifying the metal coating by being plated on and heat-cooled. 5. A method for manufacturing an air-conditioning heat exchanger in which a thin wire fin is placed in contact with the outer periphery of a heat transfer tube through which a refrigerant flows inside, and at least one of an outer peripheral surface of the heat transfer tube and an outer peripheral surface of the thin wire fin is prepared in advance. After forming a metal coating by crab plating, a heat transfer tube and a thin wire fin are combined, and by heating to the melting temperature of the metal coating in the combined state, a part of the metal coating is melted to form the heat transfer tube and the thin wire. A method for manufacturing an air-conditioning heat exchanger, characterized by joining fins. 6. The method for manufacturing an air conditioner heat exchanger according to claim 5, wherein the plating is Ni plating. 7. The method for manufacturing an air conditioning heat exchanger according to claim 5, wherein the plating is solder plating. 8. A plurality of heat transfer tubes through which a refrigerant passes are arranged at intervals, and rod fins are inserted obliquely from the front in the air flow direction of one adjacent heat transfer tube to the rear in the air flow direction of the other heat transfer tube, The rod-shaped fins are brought into contact with each heat transfer tube, and the insertion directions of the rod-shaped fins adjacent to each other in the axial direction of the heat transfer tube are alternately changed, so that a large number of rod-shaped fins are attached to all the heat transfer tubes in contact with each other. A heat exchanger for air conditioning. 9. A plurality of heat transfer tubes through which a refrigerant flows are arranged at intervals, and rod fins are inserted obliquely from the front of one adjacent heat transfer tube in the air flow direction to the rear of the other heat transfer tube in the air flow direction, By bringing the rod-shaped fins into contact with each heat transfer tube and alternately changing the inserting direction of the rod-shaped fins adjacent to each other in the axial direction of the heat-transfer tubes, a large number of rod-shaped fins are brought into contact with all the heat-transfer tubes to be attached, and further adjacent heat-transfer tubes are attached. An air-conditioning heat exchanger, characterized in that another heat transfer tube is inserted in a gap formed by rod-shaped fins having different insertion directions between the heat pipes while being in contact with the rod-shaped fins. 10. A plurality of rod-shaped fins are arranged in parallel in a direction oblique to the air flow direction, and a plurality of rod-shaped fins are arranged in parallel in the opposite diagonal direction so as to be adjacent to the rod-shaped fins. Line up, create a grid with diamond-shaped openings, stack a plurality of grids, insert heat transfer tubes that serve as coolant channels into the openings of these grids, and insert rod-shaped fins and heat transfer tubes that form each side of the grid. A heat exchanger for air conditioning characterized by being closely attached. 11. A U-shaped or H-shaped fin is attached to a heat transfer tube through which the refrigerant flows so that the heat transfer tube is sandwiched between the U-shaped recess or one of the H-shaped recesses.
In addition, a heat exchanger for air conditioning, characterized in that a plurality of these fins are attached at intervals in the axial direction of the heat transfer tube, and the directions of adjacent ones are alternately changed. 12. A heat transfer tube is inserted into an annular fin having a hole in the center, the inside of the annular part of the fin is attached so as to contact the surface of the heat transfer tube, and the annular fin is arranged in the axial direction of the heat transfer tube. A heat exchanger for air conditioning, characterized in that a plurality of heat exchangers are mounted along the space. 13. A plurality of heat transfer tubes are arranged in parallel, and all the heat transfer tubes are arranged so that the annular fins attached to one of the pair of heat transfer tubes and the annular fin attached to the other of the heat transfer tubes overlap each other. Is placed, and a rod or tube is inserted into the gap between the overlapping portions, and tension is applied to the circular fin by pulling the heat transfer tube at the end sideways. The heat exchanger for air conditioning according to claim 12, wherein the heat exchanger is brought into contact with the annular fin. 14. A heat transfer tube is sandwiched between a pair of wire fins, and the ends of both wire fins are twisted together to generate tension in the wire fin, thereby contacting the wire fin to the heat transfer tube. A heat exchanger for air conditioning, characterized by being attached to. 15. The air conditioner heat exchanger according to claim 11, wherein the ends of the U-shaped or H-shaped fins face downward from the horizontal plane. 16. The fin and the heat transfer tube are made of materials having different contact angles from each other.
The heat exchanger for air conditioning according to the item. 17. The air conditioner heat exchanger according to claim 8, wherein the fins and the heat transfer tubes are surface-treated with materials having different contact angles. 18. A plurality of heat transfer tubes are arranged in a row at regular intervals in a direction orthogonal to the air flow direction, and the heat transfer tubes are shifted by a half pitch on the upstream side and the air flow direction downstream side of the row of the heat transfer tubes, respectively. A plurality of support rods are arranged at regular intervals, the heat transfer tube and the upstream side support rod are alternately woven with thin wire fins, the heat transfer tube and the downstream side support rod are alternately woven with another thin wire fin, and the upstream side support bar is provided. A heat exchanger for air conditioning, characterized in that fine wire fins braided to each other and fine wire fins braided to a downstream side support rod are arranged alternately in the axial direction of the heat transfer tube. 19. The heat exchanger for air conditioning according to claim 18, wherein the support rod is replaced with a heat transfer tube having the same or different tube diameter as the heat transfer tube. 20. The heat exchange for air conditioning according to claim 18, wherein a header communicating with an end of the heat transfer tube is arranged in the same plane as the heat transfer tube, and the support rod is fixed to the header. vessel. 21. When a plurality of heat transfer tubes are arranged in a row at a constant interval in a direction orthogonal to the air flow direction and the heat transfer tubes are a central row, the central row is provided on the upstream side and the downstream side in the air flow direction, respectively. A plurality of heat transfer tubes are arranged at the above-mentioned constant intervals with a half pitch offset from the heat transfer tubes of the central row, and the heat transfer tubes of the central row and the heat transfer tubes of the upstream side are alternately woven with thin wire fins, and another thin wire fin is used for the central row. Of the heat transfer tubes and the heat transfer tubes in the downstream row are alternately woven, and the thin wire fins woven into the heat transfer tubes in the upstream row and the thin wire fins woven into the heat transfer tubes in the downstream row are arranged in the axial direction of the heat transfer tubes. And arranged alternately between the heat transfer tubes in the central row and the heat transfer tubes in the upstream row and between the heat transfer tubes in the center row and the heat transfer tubes in the downstream row in the direction orthogonal to these heat transfer tubes. Characterized by inserting multiple support rods at an appropriate pitch A heat exchanger for air conditioning. 22. In an air-conditioning heat exchanger in which fine wire fins are alternately woven on the front side and the back side of a plurality of heat transfer tubes arranged in a line at regular intervals, and the fine wire fins are in close contact with each other, An air-conditioning heat exchanger, characterized in that one or more heat transfer tubes are woven by skipping. 23. The heat exchanger for air conditioning according to claim 18, wherein the heat transfer tube is a flat tube. 24. The heat exchanger for air conditioning according to claim 18, wherein the thin wire fin is brought into close contact with the heat transfer tube by applying tension. 25. The heat transfer tube is made of a soft material, and is brought into close contact with the fine wire fin by forming a concave-convex deformation on the surface by the tension applied to the fine wire fin. The heat exchanger for air conditioning according to any one of 18 to 24. 26. A recess corresponding to a thin wire fin is formed on a surface of the heat transfer tube.
23. The heat exchanger for air conditioning according to claim 23. 27. The heat exchanger for air conditioning according to claim 18, wherein the whole is curved in a corrugated shape. 28. The heat exchanger for air conditioning according to claim 18, wherein the whole is curved in a semicircular shape. 29. A plate fin tube type heat exchanger consisting of a heat transfer tube and a plurality of plate-shaped fins inserted into the heat transfer tube at regular intervals is arranged in a first row in the air flow direction and arranged in a row at regular intervals. A heat exchanger for air conditioning, characterized in that a thin-wire fin-braided heat exchanger in which thin-wire fins are alternately woven on the front and back sides of a plurality of heat transfer tubes, and the thin-wire fins are in close contact with each other is arranged in the second row. . 30. A corrugated fin tube type heat exchanger is arranged in a first row in the air flow direction, and fine wire fins are alternately woven on the front side and the back side of a plurality of heat transfer tubes arranged in a row at regular intervals, and the fine wire fins are A heat exchanger for air conditioning, characterized in that thin-wire fin-braided heat exchangers that are in close contact with each other are arranged in the second row. 31. A plate fin tube type heat exchanger consisting of a heat transfer tube and a plurality of plate-shaped fins inserted into the heat transfer tube at regular intervals is arranged in the first row in the air flow direction, and the heat exchanger for air conditioning is provided. The heat exchanger for air conditioning according to any one of claims 18 to 26, wherein the heat exchanger is arranged in a second row. 32. The corrugated fin tube type heat exchanger is arranged in the first row in the air flow direction, and the air conditioning heat exchanger is arranged in the second row. Air conditioner heat exchanger.