JP2001304719A - Module type multi-channel flat pipe evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a module type multi-channel flat pipe evaporator having an enhanced heat transfer by causing vortex flow by a shape of a fin. SOLUTION: A plurality of flat pipes 26 are connected to communicate with each other between one fluid supply header 12 and another fluid supply header 48. Closing pieces 18, 54 are installed inside of the one fluid supply header 12 and the other fluid supply header 48 so as to allow a fluid to circulate between the header 12 and the other header 48. Curved fins 38 are welded on outer surfaces of the flat pipes 26 so as to dispose a flat part 38a and another flat part 38a opposite to each other. One fin assembly 24 is superposed on another fin assembly 62, and a flow pipe 22 is connected to communicate with the liquid supply header 12 through a connector 20.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an evaporator, and more particularly to a flat tube type modular flat tube having a high heat transfer effect and applicable to various shapes and sizes. It relates to an evaporator.

[0002]

2. Description of the Related Art Generally, a heat exchanger for cooling a fluid or a refrigerant is installed in, for example, an air conditioning system, a bath cooler, a heat pump, a heat pipe, and the like. Such heat exchangers are formed in various shapes to increase the contact area with the outside air, and have a plurality of fins that reduce the thermal resistance in a flow region having a Reynolds number determined by the flow velocity, hydraulic diameter, and gas density. And an evaporator provided with Therefore, in these heat exchangers, the working fluid radiates heat while passing through the condenser and is cooled, but absorbs heat from the outside while passing through the evaporator and cools the outside air.

[0003] In such a flat tube-fin type heat transfer, the heat resistance of the outside air in contact with the fins occupies most of the total heat resistance, and the performance of the fins determines the performance of the heat exchanger. I have. One of the fins widely used in the conventional heat exchanger is a louver fin called an LF fin.

However, in such a conventional louver fin, the air impact angle is limited to 90 degrees, no vortex is generated in the width direction and the axial direction, and at low speed, the boundary layer becomes thick and the duct flow is formed. There is a problem that heat transfer performance is low.

Another type of conventional fin type is an offset strip fin called OSF.
(offset strip fin).

However, since such offset strip fins provide only a one-dimensional sliding effect, there is a problem that the heat transfer effect is also low.

Accordingly, in the field of heat exchangers or evaporators, research and development of flat tube and fin structures capable of providing advantages of louver fins and offset strip fins have been actively conducted.

On the other hand, a condensation phenomenon occurs outside the flat tube evaporator employing the OSF or LF type fin. In addition, there is a problem that the condensed liquid film formed outside the fin and the flat tube becomes thicker with time, and acts as a heat resistance element in heat transfer with the refrigerant. Further, there is a problem that the flow resistance of the external air flowing between the fins and the like is reduced, thereby increasing the flow resistance.

[0009]

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to provide a modular multi-channel flat tube having reduced heat resistance and improved heat transfer performance. It is to provide an evaporator.

Another object of the present invention is to provide a modular multi-channel flat tube evaporator capable of easily removing condensed water generated outside the fin and the flat tube.

It is still another object of the present invention to provide a modular multi-channel flat tube evaporator in which a vortex flow is generated to destroy a boundary layer and improve a heat transfer effect.

It is still another object of the present invention to provide a modular multi-channel flat tube evaporator having all the advantages of LF fins and OSF fins.

Still another object of the present invention is to provide a modular multi-flow device in which the density of fins can be easily adjusted, the fins can be processed in various forms, and the processability or variability is improved. Road flat tube evaporator is provided.

[0014]

In order to achieve the above object, in a modular multi-channel flat tube evaporator for circulating and evaporating or exchanging a fluid, one side communicates with a fluid inlet pipe, A fluid inlet / outlet is formed at regular intervals along the inside, and one fluid supply header provided with a closing piece on the inside, a plurality of fluid supply flat tubes having one end communicating with and fixed to the fluid inlet / outlet, A fin that is bent to face each other and is welded to the flat tube, and one fin assembly including a support frame coupled to both sides of the flat tube and having one end fixed to one fluid supply header. A modular multi-channel flat tube evaporator including an inlet / outlet to which the other side of the flat tube of one fin assembly is communicated and fixed is formed in the length direction, and another fluid supply header provided with a closing piece inside. Container To have.

Another aspect of the present invention is to provide one fluid supply header, one fin assembly and another fluid supply header and / or one flow tube, another fin assembly and another flow tube. One or more corresponding to the fluid supply header, the fin assembly, and the flow tube in a continuous row following the other fluid supply header and another flow tube in a continuous row. The above-mentioned module-type multi-channel flat tube evaporator further includes a fluid supply header, a fin assembly, and a flow tube.

The above objects and other features and advantages of the present invention will be apparent from the following description of preferred embodiments of the present invention with reference to the accompanying drawings.

[0017]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view showing a modular multi-channel flat tube evaporator according to a preferred embodiment of the present invention. In the following description, a basic configuration in which two fin assemblies are connected is described as one embodiment in order to clarify the description. However, those skilled in the art may Is not limited to this. That is, it should be understood that the modular multi-channel flat tube evaporator according to the present invention can be configured by connecting one or more fin assemblies continuously or repeatedly in various directions. . Referring to FIG. 1, which illustrates an assembly of a preferred embodiment according to the present invention, a modular multi-channel flat tube evaporator according to the present invention is shown in the lower part of the drawing, for example, in an automobile or indoor space or In order to cool the air-conditioned space, it includes an inlet pipe 10 into which a fluid or a refrigerant that has passed through an expansion device or a chiller flows. One fluid supply header 12 communicates with the inflow pipe 10. The length or size of one fluid supply header 12 can be set appropriately according to the capacity of the evaporator or the heat exchanger. As shown in FIG. 8A, a plurality of inlets / outlets 14 through which a fluid can enter and exit are formed in one fluid supply header 12.

In particular, as shown in FIG. 3, one of the fluid supply headers 12 has one or more opening pieces 16 for permitting the supply of fluid therein, and one or more opening pieces 16 therein. One or more closure pieces 18 are provided which shut off the supply of fluid and are arranged alternately with said opening pieces 16. Here, as shown in FIG.
Is provided with an opening 16a through which the fluid passes, and a plurality of fixing pieces 16b formed integrally with the opening. Each fixing piece 16b is bent or bent in a suitable direction when installed on the supply header 12, whereby the opening piece 16 is fixed to the supply header 12. In particular, a fusion bonding agent is applied to the opening piece 16. When heat is applied in a state where the fusion bonding agent is fixed to the supply header 12 as described above, the fusion bonding agent is melted and fusion-bonded to each other. The piece 16 is welded to the supply header 12 and installed. Further, as shown in FIG.
Has a disk-shaped disk 18a and a plurality of fixing pieces 18b integrally formed around the disk 18a. Each fixing piece 18b is, of course, bent or bent in a suitable direction when installed on the supply header 12, whereby the closing piece 18 is fixed to the supply header 12. In particular, the closing piece 18 is coated with a welding agent,
As described above, when heat is applied in a state of being fixed to the supply header 12, the fusion agent is melted and welded, so that the respective closing pieces 18 are fused and installed on the supply header 12. is there. On the other hand, one fluid supply header 12
Is connected to one fluid pipe 22 by a connector 20, and serves to transfer a fluid or a refrigerant flowing out of the one fluid supply header 12 to a predetermined position.

As shown in the center of FIG. 1, one side of the fin assembly 24 is fixed to the one fluid supply header 12 in a communication manner. Fin assembly 24
Is an inlet / outlet 1 of the fluid supply header 12
4 is provided with a flat tube 26 for fluid supply which communicates with 4. 7a and 7b and FIG. 1 are attached to the end of the flat tube 26 for supplying fluid.
0a, the first fluid supply header 1
Channel wall 28a and division wall 28 arranged inside
A channel 28 composed of b is formed. Channels 2 are provided at the center and both sides of the flat tube 26 for supplying fluid.
A central condensed water discharge groove 30 and a side condensed water discharge groove 32 are formed integrally with and extend in the longitudinal direction.
The one fluid supply header 12 and the fluid supply flat tube 26 are desirably formed integrally with each other by a fusion welding portion 34 (FIG. 7A). Optionally, it may be desirable to apply a coating 36 on the inside or outside of one fluid supply header 12 (FIG. 7b).

Optionally, the inner surface of the flat tube 26 may be shaped or machined in various forms to increase the contact area with the fluid or refrigerant and improve heat transfer. That is, FIG.
As shown in detail in a partially enlarged sectional view of FIG. 3A, the inner surface of the flat tube 26 is formed with a triangular, quadrangular or ladder-shaped microgroove.

As shown in FIG. 7a, FIG. 7b, FIG. 9a, FIG. 9b or FIG.
Fins 38 are provided on both sides by fusion welding. That is, the fins 38 are arranged between the flat tubes 26. In each fin 38, a plurality of flat portions 38a and curved portions 38b are integrally formed in a continuous bending manner or in a wave shape. A plurality of inclined strips 40 are formed on each flat portion 38a. In particular, the respective strips 40 at the adjacent or opposite flats 38a may be formed so as to pass each other in a folded state (FIG. 10b) or in the same direction as each other (FIG. 10c). Accordingly, it is desirable that the range of the predetermined collision angle (β) between the strips 40 of the adjacent flat portions 38a with respect to the fluid flowing into the strips is set to be −90 degrees to 90 degrees. Each of the curved portions 38b has a central discharge hole 42 communicating with the central condensed water discharge groove 30 formed at the center of the flat tube 26.

Also, as shown in FIGS. 9a and 9b, the flat tube 26 on which the respective fins 38 are installed is shown.
Are formed so as to be inclined at a predetermined cutting angle θ. By processing both ends in an inclined manner in this manner, the pressure of the refrigerant colliding with the inclined surface at the inflow side or the inflow end is increased, so that the inflow into the flat tube 26 is facilitated, and the outflow side is formed. Alternatively, at the outflow end, the refrigerant can easily flow out of the flat tube 26.

As shown in FIG. 1, a support frame 44 shown in FIG. 4 a is provided on both sides of the fin assembly 24 to support the combined body between the flat tube 26 and the fin 38 on both sides. In addition, it serves to support the entire fin assembly 24 itself. In particular, a cap 46 as shown in FIG. 4 b is provided at one end of each support frame 44, and is fixed to one fluid supply header 12 by the cap 46. As a result, the fin assembly 24 is fixedly connected to the fluid supply header 12.

As shown in the upper part of FIG. 1, another fluid supply header 4 is provided on the other side of the fin assembly 24.
8 is installed. The fluid supply header 48 is similar to the one fluid supply header 12 described above and has a symmetrical configuration. That is, the other fluid supply headers 48
The shape and length of the evaporator or heat exchanger can be appropriately set according to the capacity of the evaporator or the heat exchanger, and can be formed in various shapes. In addition, as shown in FIG. 8B, a plurality of inlets / outlets 50 through which a fluid can enter and exit are formed in another fluid supply header 48. In particular, as shown in FIGS. 5 and 6, the other fluid supply header 48 may include one or more aperture pieces 5 that allow the supply of fluid therein.
2 and cut off the supply of fluid inside the
One or more closure pieces 54, which are alternately arranged, are fused and installed. Of course, the fluid supply header 48
The cap 56 provided on the other end of the support frame 44 supporting both sides of one fin assembly 24 is fixed to both ends of the fin assembly 24.

Also, one fluid supply header 1 described above is used.
2 are connectors 2 as schematically shown in FIG.
In addition, it is connected to one flow pipe 22 which communicates with the discharge pipe 60 through the “0”. The other end of one flow tube 22 is connected to another flow tube 5.
Another fin assembly 62 communicating with 8 is formed. This other fin assembly 62 may be similar or identical to one fin assembly 24 described in detail. Of course, the other fin assembly 62 is one fin assembly 24
Can be arbitrarily formed so as to form a flow form of another fluid or refrigerant. On the other hand, the flow of the fluid or the refrigerant is adjusted by the opening piece 52 and the closing piece 54 provided in the respective flow tubes 22 and 58.

In particular, as one of the main features of the present invention,
In addition to the one fin assembly 24 and the other fin assembly 62 described above, one or more and other fin assemblies similar or identical to the fin assembly are described above. An evaporator can be configured by arranging in a line in such a manner. In addition, the fin assembly can be variously modularized in accordance with the installation space or position to provide a modular multi-channel flat tube evaporator having various shapes.

As described above, one fluid supply header 12, one fin assembly 24, another fluid supply header 48, one fluid pipe 22 connected to the fluid supply header 12, and another fin set. The solid 62 and the other flow tubes 58 are assembled to form a basic modular multi-channel flat tube evaporator. At this time, the size of each component can be easily adjusted, and various modularized flow paths can be formed. That is, the fluid or the refrigerant that has flowed through the inflow pipe 10 circulates through one fluid supply header 12, one fin assembly 24, and another fluid supply header 48, and then returns to the fluid supply header again. Evaporation or heat exchange by circulating one flow tube 22, another flow tube 22, 58 and another fin assembly 62 connected between each flow tube connected to the flow tube 12. Is made. Such one fluid supply header 12, one fin assembly 24, another fluid supply header 48, the fluid supply header 1
2, one fin assembly 24, another fluid supply header 4
8. One flow pipe 2 connected to the fluid supply header 12
2. The flow of the fluid or the refrigerant in the other fin assembly 62 and the other flow tube 58 is controlled by one fluid supply header 12, another fluid supply header 48, one flow tube 22 and another flow tube 58. This is performed by the opening piece 52 and the closing piece 54 which are respectively installed so that the fluid or the refrigerant circulates.

Of course, the two fin assemblies 24, 62
If one or more further fin assemblies are assembled in communication with the fin assembly, the flow of fluid or refrigerant in the two fin assemblies described above is continuously repeated in another fin assembly. Done.

For example, as shown in FIG.
In a basic modular multi-channel flat tube evaporator made up of two fin assemblies 24 and 62, one fluid supply header 12, one fin assembly 24 and another fluid supply header 48 are one. One flow train 64 formed by the plurality of flow passage sections A, B, C, and D is formed,
One flow tube 22, another fin assembly 62 and another flow tube 58 form another flow train 66 made up of two flow sections E and F, thereby circulating fluid or refrigerant in the direction of the arrow. It is evaporated or heat exchanged while being heated. In this embodiment, one flow train 64 is illustrated as having four flow passage sections and the other flow train 66 is illustrated as having two flow passage sections. The direction and number of the flow passage sections are set appropriately by appropriately configuring the respective fluid supply headers and the respective flow tubes according to the use, capacity or size of the evaporator or the heat exchanger.

In particular, one major feature of the present invention is that while each fin assembly, fluid supply header and flow tube are configured as described above, fluid or refrigerant is circulated through the fin assembly. As indicated by the shading in FIG. 2, the configuration is such that the steam generating portion or the refrigerant stagnation portion in each of the adjacent flow passage sections of each of the flow trains overlaps or does not overlap. Is what is done.

Hereinafter, the basic structure of each component constituting the modular type multi-channel flat tube evaporator according to the present embodiment and other embodiments will be described in detail.

As shown in FIG. 5, each opening piece 16, 52 has an opening 16a, 52a around which each header 12, 48 and each A plurality of fixing pieces 16b and 52b which are bent and fixed to the flow tubes 22 and 58 are integrally formed. In particular, the surface of each of the opening pieces 16 and 52 is coated with a fusion bonding agent. When heat is applied in the assembled state as described above, the fusion bonding agent is melted and the supply headers 12 and 48 are supplied.
It is fused to Further, as shown in FIG. 6, closing pieces 18 and 54 that can be installed on one fluid supply header 12, another fluid supply header 48, one flow pipe 22 and another flow pipe 58 are disks. Shaped disk 18a,
54a and a plurality of fixing pieces 18b, 54b formed integrally and foldably around the disks 18a, 54a. Here, the surface of each of the closing pieces 18 and 54 is coated with a fusion bonding agent. When heat is applied in the assembled state as described above, the fusion bonding agent is melted and fused to the supply headers 12 and 48. It is desirable to be touched.

On the other hand, as shown in FIGS. 10a to 10e, the OLF fin 38 is formed to have a predetermined length, and the flat portion 38a of the fin 38 is formed obliquely or linearly. A plurality of strips 40 are formed at regular or irregular intervals. The curved portion 38 as described above is interposed between these flat portions 38a.
b is formed. A condensed water discharge hole 42 is formed in the curved portion 38b. Here, as shown in FIG. 10e, the inclination angle γ between both sides of the curved portion 38b may be variable in a range of −60 degrees to 60 degrees. The fins 38 are desirably welded to the flat tube 26, and the flat tubes 26 and the fins 38 are joined to the support frame 44 in a state where they are welded to each other. As described above, when the flat tube 26 and the fin 38 are assembled, the central condensed water discharge groove 30 formed by the flat tube 26 and the central discharge hole 42 formed in the fin 38 communicate with each other, and the actual condensation The water discharge groove can be made sufficiently large. In addition, each flat tube 2
6, channels 28 are formed. Each channel 28 is formed with a channel wall 28a for forming a pattern of the channel 28 and a dividing wall 28b for dividing each channel 28 by a plurality of channel portions. . In this embodiment shown in the drawings, two channels 28, 28 are formed in the flat tube 26, but one or more channels may be formed in the flat tube 26 as necessary. You can also.

If the condensed water discharge groove 30 of the flat tube 26 and the central discharge hole 42 of the fin 38 are too large, and if the central condensed water discharge groove 30 is too large, the flat tube 2
The contact area between the fins 6 and the fins 38 is reduced, so that the heat transfer efficiency of the fins 38 is reduced, and the performance of the entire modular multi-channel flat tube evaporator is reduced. Conversely, the central condensed water discharge groove 30
Is too small, condensed water causes a phenomenon that the central condensed water discharge groove 30 is closed due to an increase in surface tension. Therefore, it is desirable to form the flat tubes 26 and the fins 38 and to mutually weld them together as follows. .

That is, the central discharge hole 42 is formed in the fin 38 into a flattened circular hole shape in consideration of the fusion welding surface between the flat tube 26 and the fin 38, and the discharge hole 42 is formed into a flattened circular hole. Central condensate drain groove 3 formed in pipe 26
It is desirable that the fin 38 be fusion-welded to the flat tube 26 in a state where the fin 38 communicates with the flat tube 26. In this way, a sufficient condensed water discharge port can be formed by communicating the discharge hole 42 and the central condensed water discharge groove 30, while the fusion welding area between the fin 38 and the flat tube 26 is sufficient. And the fin efficiency is not reduced.

In particular, as shown in FIGS. 11a-11g, the strips 40 formed on the fins 38 are subjected to an evaporation phase or a thermal cycle in order to enhance the efficiency of the fins by promoting vortex flow or flow disturbance of the fluid. Depending on the type or application of the switch, the geometric structure can be variously modified to serve as a short-circuit vortex generator.

Although the strip can take various forms, it can be straight as a basic strip shape, and in particular, a plurality of inclined shapes formed at regular intervals and constant inclination angles shown in FIG. 11a. There is a strip 40. In addition, the strip 40 may be formed in a step shape (FIG. 11b), an uneven shape (FIG. 11c), a waveform or a wave shape (FIG. 11d), or the like.

Also, a plurality of holes (FIG. 11e), which connect various shapes such as an ellipse and a polygon, a hole formed discontinuously (FIG. 11f), or a plurality of protrusions (FIG. 11).
g).

Further, as shown in FIG. 12, the strip 40 may be formed in a non-equidistant linear shape or an oblique shape, in addition to the above-described oblique shape in the same interval. . In particular, as shown in FIGS. 13A and 13B, it is preferable that the louver pitch Lp indicating the width between the strip 40 and the unequally-spaced oblique linear strip is increased or decreased as it goes downward. As described above, when the louver pitch Lp is increased or decreased downward, a channel flow is formed instead of a duct flow even at a low air velocity ReLp, and a directional short-circuited flat plate flow is formed. Has been extended,
Further, the contact time with the heat transfer (front row) surface is prolonged, so that heat transfer can be increased.

Next, the operation and effects of the modular multi-channel flat tube evaporator according to the basic embodiment of the present invention will be described in detail.

For example, in an air conditioning system (not shown), a bus, a cooler, a heat pump, a heat pipe, or the like, a fluid or a coolant is supplied to one fluid supply header 12 through an inflow pipe 10 as shown in FIG. The fluid or the refrigerant flowing into the one fluid supply header 12 is divided into a plurality of flat tubes 26 and a plurality of fins 38 forming a part of the fin assembly 24 by the closing piece 18 installed in the fluid supply header 12. Is supplied to another fluid supply header 48 through the flow path section A formed by the above. Thereafter, the fluid is supplied to the opening piece 16 provided on the other fluid supply header 48.
The fluid is supplied to one fluid supply header 12 through a flow path section B formed by a plurality of flat tubes 26 and a plurality of fins 38 which form a part of the fin assembly 24 by the closing piece 18 via the closing piece 18.

In the manner described above, for example, channel section C, another fluid supply header 48, channel section D, connector 20, one flow tube 22, flow section E, another flow tube 58, The fluid is evaporated or heat exchanged while circulating through the flow path section F and one flow tube 22. That is, the fluid flows into the channel 28 of the flat tube 26.
The heat is absorbed or heat is exchanged from the external environment while passing through the fin assembly 24 including the fins 38. In particular, since the heat exchange area between the channel 28 of the fin assembly 24 and the fin 38 is substantially large, heat exchange or evaporation can be performed quickly and effectively.

On the other hand, during the evaporation or heat exchange of the fluid, for example, condensation is generated outside the flat tube 26 and the fins 38 to generate condensed water. And is discharged downward by gravity through a central condensed water discharge groove 30 formed in the flat tube 26 and a central discharge hole 42 formed in the fin 38. Here, the discharge groove 30 of the flat tube 26 and the discharge hole 42 of the fin 38 communicate with each other to form a sufficient and appropriate condensed water discharge groove, so that the contact area between the flat tube 26 and the fin 38 is reduced. This prevents the fin efficiency and the performance of the evaporator from being lowered.

The width W of the flat tube 26 is formed to be slightly longer than the fin 38, and the side condensed water discharge grooves 32 are formed at both ends thereof. It flows toward 26. Thereafter, the fluid flows downward through the side condensed water discharge groove 32 in the same manner as through the central condensed water discharge groove 30 and is discharged. Thus, the condensed water is easily discharged even if the modular multi-channel flat tube evaporator is installed not only vertically but also inclined.

Further, in the module type multi-channel flat tube evaporator according to the present invention, each fin assembly 24, 62 is modularized as in the above-described basic embodiment, or
Alternatively, the capacity can be adjusted as required by modularizing two or more fin assemblies and connecting them to a support frame 44 such as a socket or a coupler.
Further, the evaporator can be modularized with a multi-channel flat tube, so that the degree of freedom in design can be increased according to demand. In addition, by adopting a multi-pass multi-row design, as shown by the shading in FIG.
The heat transfer performance reduction region due to the flow stagnation that can be generated in each of the flow path sections A, B, C, and D is not overlapped with each of the flow path sections E and F of the other flow trains 66, and the evaporation is performed. This can improve the performance by making the temperature distribution of the air flowing outside the vessel uniform. Of course, the connectors 20, 5 that connect the front row, ie one flow row 64, and the rear row, ie another flow row 66,
6, the heat transfer performance in another flow train 66 can be improved because the flat tubes 26 between one flow train 64 and another flow train 66 can be arranged in a staggered manner. It is. Where two or more fin assemblies are arranged in a row as described above or vice versa to form a modular multi-channel flat tube evaporator, correspondingly or optional. Heat transfer can be provided such that a flow train is formed.

Further, each end of the flat tube 26 is shown in FIG.
When the jig 68 shown in FIG. 4 is used to adjust the depth and insert the jig 68, the flow rate of the fluid in each of the fluid supply headers 12 and 48 can be adjusted to obtain a uniform flow distribution. . Also, if both ends of each flat tube 26 are inclined at an appropriate cutting angle of about 30 to 60 degrees, the total pressure of the refrigerant colliding with the inclined surface on the inflow side rises and enters the inside of the flat tube 26. Inflow becomes easier. On the other hand, on the outflow side, outflow inside the flat tube becomes easy. Of course, the flat tube 26 depends on the allowable pressure of the fluid or refrigerant inside the flat tube 26.
By adjusting the ratio between the channel 28 and the fin 38 formed in the above, it is possible to appropriately cope with various types of fluids or refrigerants.

In particular, as shown in FIGS. 11a to 11g, the geometrical shape of the stream 40 formed on the fin 38 may be oblique, stepped, uneven, wavy, perforated, perforated, etc. To improve the efficiency of the fins by promoting heat transfer in the fins as well as promoting the vortex flow and flow disturbance of the fluid.

For reference, in the performance characteristics of the fins 38, the flow structure in the louver arrangement is the air velocity (Re).
Lp (= ρυLp / μ)). At high air velocities (ReLp number), a main flow is formed along the louver angle and a directional short-circuited plate flow (directed interrupted fl
at plate flow) (boundary layer flow) and high heat transfer coefficient. On the other hand, louvers at very low air velocities (ReLp numbers) have only a small effect on the flow structure, and the main flow does not flow in the louver direction, but forms a duct flow between the fin and the heat transfer coefficient. Where it is noticeably lower, this results in axial flow (duct flow) through the fin array, with the low velocity air flow causing the boundary layer growing between adjacent louvers to be thick enough to completely block the flow path. To do that. Accordingly, in the modular multi-channel flat tube evaporator according to the present invention, the collision angle (β) of the fluid is set to −90.
At very low air velocities (ReLp numbers), duct flow is formed by making the louver pitch (louver strip width, Lp) progressively increase or decrease in the downstream direction at degrees to +90 degrees. Instead, a directional short-circuit flat plate flow is formed, the flow length is increased, the contact time with the front row surface is increased, and the heat transfer is increased.

The louver angle affects the heat transfer coefficient only in the transition region between the duct flow region and the boundary layer flow region. At low air velocities, the average flow angle is the air velocity (R
eLp number), and as the air velocity (ReLp) increases, the mean flow angle (mean flow angle) almost approaches the louver angle. However, at a high air velocity (ReLp), the mean flow angle may be affected by the air velocity (ReLp). Disappears. And
The larger the fin pitch, the greater the flow rate of the fluid bypassing the louver, because the hydraulic resistance of the duct flow area is significantly smaller than the hydraulic resistance of the boundary layer flow passing through the louver. When the fin pitch decreases, the hydraulic resistance of the duct increases and most of the flow will flow through the louvers. Therefore, the side surface inclination angle (γ) of the fin can be adjusted in the range of −60 degrees to +60 degrees, and the duct flow can be suppressed by adjusting the density so that flow disturbance can be sufficiently generated even at a low flow velocity. Things.

[0050]

As described above, according to the present invention, the number of fin assemblies and / or their modules can be set appropriately according to the evaporation capacity or heat exchange capacity, so that the overall evaporator is improved. The size can be arbitrarily adjusted, and an effect of obtaining a modular multi-channel flat tube evaporator having an optimal evaporation effect or heat exchange efficiency can be obtained.

Further, not only the mixing promotion by the vortex flow in the flat tube and the fin, the accumulation and removal of the condensed water due to the sliding effect and the scoring phenomenon become easy, but also the flow length is extended even at a low flow rate. This has the advantage of improving the heat transfer efficiency.

Further, since the fin assemblies are arbitrarily selected in a suitable number or are modularized and assembled, the fin assemblies can be assembled or manufactured in a size and capacity suitable for various heat exchangers, so that the exchangeability is improved. Therefore, there is an advantage that the size and the weight can be reduced.

Although the present invention has been described in detail with reference to embodiments, the present invention is not limited to the embodiments, and any person having ordinary knowledge in the technical field to which the present invention belongs may depart from the spirit and spirit of the present invention. Rather, the invention could be modified or changed.

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing a basic overall structure.

FIG. 2 is a diagram showing a flow path modularized by the evaporator of FIG. 1;

FIG. 3 is a partially enlarged sectional view of a fluid supply header of the evaporator of FIG. 1;

FIG. 4a is an inner side view and a sectional view of the support frame of FIG. 1; FIG. 4b is a cross-sectional and half side view of the cap of FIG.

FIG. 5 is a front view and a side view showing the opening piece of FIG. 1;

FIG. 6 is a front view and a side view showing the closing piece of FIG. 1;

FIG. 7a is a partially enlarged cross-sectional view showing in detail a coupling structure between a header and a fin assembly. FIG. 7b is a partially enlarged cross-sectional view showing the coupling structure between the header and the fin assembly in detail.

FIG. 8A is a partially enlarged perspective view showing a structure of a first fluid supply pipe of FIG. 1; FIG. 8B is a partially enlarged perspective view showing the structure of the second fluid supply pipe.

FIG. 9a is a front perspective view showing an assembled state of a flat tube and fins. FIG. 9b is a rear perspective view of the same.

FIG. 10a is a plan view showing the channel structure of the flat tube in detail, and shows the structure inside the channel;
Two embodiments are shown in enlarged cross-sectional views, respectively. FIG. 10b is a partial angle enlarged plan view showing a state before the fin is formed by bending. FIG. 10c is a partially enlarged plan view showing a state before bending and forming a fin according to another embodiment. FIG. 10D is a partial plan view showing a state where the flat tube of FIG. 10A and the fin of FIG. 10B are joined to each other. FIG.
10B is a partial front view in a state where the flat tube of FIG. 10A and the fin of FIG. 10B are mutually joined.

11a to 11g are plan views showing various types of strips formed on the fin of the evaporator according to the present invention.

FIG. 12 is a side view showing another embodiment of the strip.

13a and 13b show a line XIII in FIG.
FIG. 13 is a configuration diagram of an odd-numbered row and an even-numbered strip viewed from the front and rear along XIII, respectively.

FIG. 14 is a perspective view of a jig for adjusting the insertion depth of the flat tube into the header.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Inflow pipe 12, 48 Fluid supply header 14, 50 Outlet 16, 52 Opening piece 18, 54 Closing piece 20, 56 Connector 22, 58 Flow tube 24, 62 Fin assembly 26 Flat tube 38 Fin 40 Stream

Continuing on the front page (72) Inventor Li Deok-ho, Gyeonggi-do, Korea Pyeongtaek-dong, Dokjeong-dong, Sanbon APT103, No. 801 (72) Inventor Li Shun-bu, Korea Special City, Seoul, Yeongcheon-gu, Shin-dong 1st Mokdong APT 1024, 1405 No. 1405 F-term ( Reference) 3L065 FA14 FA19 3L103 AA01 AA06 AA22 AA37 BB38 BB42 CC22 CC28 DD08 DD34 DD36

Claims (23)

[Claims] 1. A modular multi-channel flat tube evaporator for circulating a fluid to evaporate or exchange heat, wherein one side communicates with a fluid inlet pipe 10 and fluid inlets and outlets 14 are formed at regular intervals along a length direction. One fluid supply header 12 having a closing piece 18 provided inside, a plurality of fluid supply flat tubes 26 having one ends communicating with and fixed to the fluid port 14, and a flat portion 38a are bent so as to face each other. Fins 38 that are welded and welded to the flat tube 26
One fin assembly 24 having a support frame coupled to both sides of the flat tube 26 and having one end fixed to the one fluid supply header 12, An inlet / outlet 50 to which the other side of the flat tube 26 is communicated and fixed is formed in the length direction, and another fluid supply header 48 provided with a closing piece 54 on the inside thereof. Flat tube evaporator. 2. Following one fluid supply header 12, one fin assembly 24 and another fluid supply header 48 and / or one flow tube 22, another fin assembly 62 and another flow tube 58. The fluid supply headers 12, 48, the fin assemblies 24, 62 and the fluid The modular multi-channel flat tube evaporator according to claim 1, further comprising one or more additional fluid supply headers, fin assemblies, and flow tubes corresponding to the tubes 22. 3. The opening piece 16 installed on one fluid supply header 12 is symmetrical with the closing piece 54 installed on another fluid supply header 48, and is installed on the one fluid supply header 12. The modular multi-channel flat tube evaporator according to claim 1 or 2, wherein the closed piece (18) is symmetrical with an opening piece (52) provided on the other fluid supply header (48). 4. One or more fluid supply headers 12, one fin assembly 24 and another fluid supply header 48 are provided with one or more plurality of modularized fluid flow paths interconnected for fluid circulation. 3. A flow train comprising A, B, C and D to form one flow train.
5. The modular multi-channel flat tube evaporator according to [1]. 5. The opening pieces 16, 52 are circular opening portions 16.
a, 52a and the fluid supply headers 12, 48, which are formed integrally with the openings 16a, 52a so as to be bendable.
Fixed pieces 16b, 52b, which are welded to the discs 18a, 54a, respectively.
5. The module according to claim 4, further comprising: fixing pieces 18 b, 54 b formed integrally with the discs 18 a, 54 a so as to be bendable and fused to the fluid supply headers 12, 48. Type multi-channel flat tube evaporator. 6. Each end of the flat tube 26 is disposed inside one fluid supply header 12 and another fluid supply header 48, and said flat tube 26 has a channel wall 28a.
And channel 28 composed of channel dividing wall 28b
A modular multi-channel flat tube evaporator according to claim 1 or 2, wherein: 7. The evaporator of claim 6, wherein the inner surface of the flat tube 26 has micro grooves having a triangular or square cross section. 8. A flat tube 26 has a channel 2 at its center.
8. A central condensed water discharge groove formed integrally with the second condensate water, and side condensed water discharge grooves formed on both sides of the central condensed water discharge groove, respectively. 5. The modular multi-channel flat tube evaporator according to [1]. 9. Each of the strips 40 formed on each of the adjacent flat portions 38a of the fins 38 is formed so as to pass each other, and forms a collision angle β with a fluid passing through the fins. 3. The modular multi-channel flat tube evaporator according to 1 or 2. 10. The modular multi-channel flat tube evaporator according to claim 1, wherein the strips 40 formed on adjacent flat portions 38a of the fins 38 are formed in parallel with each other. . 11. The modular multi-channel flat tube evaporator according to claim 9, wherein the collision angle β ranges from −90 degrees to +90 degrees. 12. The respective fluid supply headers 12, 4.
3. The modular multi-channel flat tube evaporator according to claim 1, wherein both ends of each of the flat tubes 26 inserted into the tube 8 are cut so as to be inclined at a cutting angle θ. 4. 13. The modular multi-channel flat tube evaporator according to claim 12, wherein the cutting angle θ is about 30 to 60 degrees. 14. The fin 38 has a central discharge hole 42 formed at the center of the curved portion 38b and communicating with the central condensed water discharge groove 32 formed at the center of the flat tube 26. 3. The modular multi-channel flat tube evaporator according to item 2. 15. One flow tube 22, another fin assembly 62 and another flow tube 58 form another flow train 66 having flow passage sections E and F communicating with one flow train 64. 3. The modular multi-channel flat tube evaporator according to claim 1 or 2, wherein: 16. The flattened module type multi-channel according to claim 1, wherein the curved portions 38b of the fins 38 are bent such that the flat portions 38a adjacent to each other form an inclination angle γ. Tube evaporator. 17. The modular multi-channel flat tube evaporator according to claim 15, wherein the inclination angle γ is in a range of −60 degrees to +60 degrees. 18. The evaporator according to claim 13, wherein the central condensed water discharge hole of the fin is formed as a flat hole. 19. The modular multi-channel flat tube evaporator according to claim 1, wherein the strip is oblique. 20. The strip 40 has a short eddy current (discret).
The modular multi-channel flat tube evaporator according to claim 1 or 2, wherein the evaporator is formed in a stepped shape, an uneven shape, or a corrugated shape so as to generate an e vortex. 21. The modular multi-stream according to claim 1, wherein the strip is formed in a circular, elliptical, rectangular, or polygonal hole shape to generate a short-circuit vortex. Road flat tube evaporator. 22. The modular multi-channel flat tube evaporator according to claim 1, wherein the strip 40 is formed in one of projections having a pattern that generates a short-circuit vortex. 23. The modular multi-channel flat tube evaporator according to claim 19, wherein the intervals between the strips 40 are unequal intervals, and the width between the strips becomes wider or narrower as going downward. vessel.