KR20090096030A - Return tube and heat exchanger comprising the same - Google Patents

Abstract

A return tube and a heat exchanger including the same are provided to achieve the efficient heat exchange by performing the heat-exchanging between the refrigerant and an external fluid. A return tube(140) comprises a plurality of refrigerant flow paths. At least some of refrigerant flow paths are formed in the shape of an open curve having a preset radius of curvature. Inside them, refrigerant flows. A return tube connects end parts of adjacent tubes. The both ends of each tube pass through a plurality of pins. The return tube is bent in a pressed state.

Description

Return tube and heat exchanger comprising the same

The present invention relates to a heat exchanger, and more particularly to a return tube and a heat exchanger including the same connecting the tube through which the refrigerant flows.

Generally, a heat exchanger is a component constituting a heat exchange cycle. The heat exchanger is used as a condenser or an evaporator to cool a predetermined space by using absorption heat or discharge heat generated during heat exchange between a refrigerant flowing inside and an external fluid. It serves to heat.

Such heat exchangers are largely classified into fin and tube types and microchannel types according to their shapes. The fin-and-tube type heat exchanger includes a plurality of fins and a tube passing through the fins, and the microchannel type heat exchanger includes a flat tube and a fin that is bent a plurality of times and provided between the flat tubes. The fin and tube type heat exchanger and the microchannel type heat exchanger both exchange heat with an external fluid and a refrigerant flowing inside the tube or flat tube, and the fin is inside the tube or flat tube. It serves to increase the heat exchange area between the refrigerant flowing through and the external fluid.

However, such a heat exchanger according to the prior art causes the following problems.

First, in the fin and tube type heat exchanger, the tube is installed through the fin. Therefore, in the case of the fin-and-tube type heat exchanger, even if condensate generated by operating as an evaporator flows down the fin or even if condensate freezes and lands on the outer surface of the tube or fin, it can be easily removed. . However, in the case of the fin-and-tube type heat exchanger, since only one refrigerant flow path is provided inside the tube, there is a disadvantage in that the heat exchange efficiency of the actual refrigerant is low.

On the other hand, in the case of the microchannel type heat exchanger, since a plurality of refrigerant passages are provided in the flat tube, the heat exchange efficiency of the refrigerant is increased as compared with the fin and tube type heat exchanger. However, in the case of the microchannel type heat exchanger, the fins are provided between the flat tubes. Accordingly, there is a fear that the condensate generated by the microchannel type heat exchanger operates as an evaporator substantially freezes in the space between the flat tubes. In addition, the heat exchange efficiency of the refrigerant is substantially lowered by the freezing of the condensate. In the case of the heat exchanger of the microchannel type, the refrigerant is transferred to the flat tube from the other components constituting the heat exchange cycle through a header connected to one end of the flat tube, and is connected to the other end of the flat tube. The heat exchanger passes through the flat tube through the header to transfer the refrigerant to another part of the heat exchange cycle. Therefore, due to the difference in weight according to the phase of the refrigerant, the liquid phase of the refrigerant is concentrated in the lower portion of the header, the gaseous refrigerant is concentrated in the upper portion of the header, the heat exchange efficiency of the substantial heat exchanger can be reduced.

The present invention is to solve the problems of the prior art as described above, an object of the present invention, to provide a heat exchanger and a return tube configured to improve the heat exchange efficiency of the refrigerant.

According to an embodiment of the present invention for achieving the object as described above, the present invention is formed in an open curve shape having at least a predetermined radius of curvature (open curve), a plurality of refrigerant in which the refrigerant flows therein A flow path is provided, and both ends thereof connect ends of the tubes adjacent to each other among the plurality of tubes passing through the plurality of pins.

According to another embodiment of the present invention, the present invention includes a curved portion bent in a radius of curvature of more than half of the distance between the adjacent tube of the plurality of tubes passing through a plurality of fins; A pair of straight portions extending parallel to each other at both ends of the curved portion and connected to one end of the tube adjacent to each other; It includes.

According to another embodiment of the present invention, the present invention is a plurality of fins formed in the shape of a plate of a predetermined length; A plurality of tubes installed through the fins so as to be spaced apart from each other by a predetermined interval, and each having a plurality of refrigerant passages through which the refrigerant flows; And a return tube of any one of claims 1 to 7 connecting one end of the flat tube adjacent to each other. It includes.

According to the present invention, there is an advantage in that heat exchange can be performed more efficiently.

Hereinafter, with reference to the accompanying drawings an embodiment of a heat exchanger according to the present invention will be described in more detail.

1 is a front view showing an embodiment of a heat exchanger according to the present invention, Figure 2 is a cross-sectional view showing a contact portion of the fin and the tube in the embodiment of the present invention, Figure 3 is a connector constituting an embodiment of the present invention 4 is a cross-sectional view showing a contact portion of a tube and a connector in an embodiment of the present invention, Figure 5 is a perspective view showing a return tube constituting an embodiment of the present invention, Figure 6 is a tube in an embodiment of the present invention And sectional view of the return tube contact.

Referring to FIG. 1, the heat exchanger 100 according to the present invention includes a plurality of fins 110 having a flat plate shape, a plurality of tubes 120 installed through the fins 110, and the tubes 120. A plurality of connectors 130 for connecting a portion and the inlet capillary 160, a plurality of return tubes 140 for connecting one end of the tube 120 adjacent to each other, and a portion of the tube 120 and withdrawal cap It includes a header 150 for connecting the filler 170.

More specifically, the pin 110 is formed in a rectangular flat plate shape having a predetermined length. The fin 110 serves to increase an area that substantially exchanges heat with the refrigerant flowing through the tube 120 and the external fluid. The pin 110 is composed of a plurality of spaced apart from each other by a predetermined interval so that both sides thereof face each other surface of the other pin.

The tube 120 is formed long in the longitudinal direction, for example, by extrusion molding. The tube 120 penetrates through the fin 110 to be spaced apart from each other by a predetermined distance in the longitudinal direction of the fin 110. Hereinafter, in FIG. 1, the uppermost tube in the drawing is referred to as a first tube 121, and the remaining tubes positioned below the first tube 121 are second to sixth tubes 122 and 123 ( 124, 125, and 126.

And the tube 120 is formed in a hollow linear shape having a predetermined length. Referring to FIG. 2, a plurality of coolant flow paths 120P through which coolant flows are provided in the tube 120. Inside the tube 120, a partition rib 127 is provided to partition the plurality of refrigerant passages 120P inside the tube 120. Compartment rib 127 of the tube 120 is provided long in the longitudinal direction of the tube 120 to be spaced apart from each other in a direction orthogonal to the longitudinal direction of the tube (120). The compartment rib 127 of the tube 120 is formed to have the same length as the tube 120. Therefore, the refrigerant passage 120P of the tube 120 is provided in the entire interior of the tube 120.

The connector 130 connects a portion of the tube 120 with the incoming capillary 160 that receives the refrigerant from other components constituting the heat exchange cycle. In this embodiment, the connector 130 connects the right end of the drawing and the inlet capillary 160 on the first tube 121 and the fourth tube 124, respectively.

3 and 4, the connector 130 is formed in a hollow linear shape in which one surface is shielded. In addition, the shielded surface of the connector 130 is provided with a refrigerant supply hole (131). The coolant supply hole 131 is connected to the inlet capillary 160 to the inlet zone receiving the coolant. In addition, the first tube 121 or the fourth tube 124 is illustrated inside the connector 130 through one surface of the connector 130 corresponding to the opposite side of the refrigerant supply hole 131. The upper right end is inserted. As described above, the drawing capillary 160 is connected to the refrigerant supply hole 131, and the right end portion of the first tube 121 or the fourth tube 124 is inside the connector 130. By inserting, the refrigerant flowing through the inlet capillary 160 is delivered to the first tube 121 or the fourth tube (124). To this end, a portion of the connector 130 adjacent to the opened side of the connector 130 is formed to have a relatively large cross section compared to the cross section of the tube 120. And the remaining portion of the connector 130 is formed in a shape and size corresponding to the cross section of the tube (120). Meanwhile, the locking protrusions 133 are provided in the connector 130, respectively. The locking protrusion 133 is formed to protrude from an inner surface of the connector 130 spaced apart from the refrigerant supply hole 131 by a predetermined distance. The locking projection 133 is in close contact with the right end portion of the drawing of the first tube 121 or the fourth tube 124 inserted into the connector 130 to the first tube 121 or the fourth. The tube 124 serves to be inserted into the connector 130 only by a predetermined distance. Accordingly, the right end of the first tube 121 or the fourth tube 124 in the state of being inserted into the connector 130, the shielded surface of the connector 130, more specifically, The refrigerant supply hole 131 is spaced apart by a predetermined interval. This is to allow the refrigerant supplied through one of the refrigerant supply holes 131 to be divided into the refrigerant passages 120P of the plurality of first tubes 121 or the fourth tubes 124. Substantially, the locking protrusion 133 may be enlarged with a portion adjacent to the opened one surface of the connector 130 into which the first tube 121 or the fourth tube 124 is inserted. It may be formed by a step.

The return tube 140 connects one end of the tube 120 adjacent to each other to transfer the refrigerant flowing through the refrigerant channel of any one of the tubes 120 to the other refrigerant channel adjacent thereto. do. In the present embodiment, the return tube 140 has a left end on the drawing of the first tube 121 and the second tube 122, and on the drawing of the second tube 122 and the third tube 123. The right end portion, the left end portion in the drawings of the fourth tube 124 and the fifth tube 125 and the right end portion in the drawings of the fifth tube 125 and the sixth tube 126 are respectively connected.

5 and 6, the return tube 140 is bent in an extruded state in the same shape as the tube 120 to form an open curve as a whole. In more detail, the return tube 140 includes one curved portion 141 and two straight portions 143 that are generally formed in a horseshoe shape.

The curved portion 141 has a radius of curvature R exceeding 1/2 of a distance L between the adjacent tubes 120 (substantially the same as the distance between the straight portions 143). Is formed by bending. This is to facilitate molding of the return tube 140 while minimizing the distance L between the adjacent tubes 120. In other words, as the distance L between the adjacent tubes 120 decreases, the number of the tubes 120 in the same heat exchanger 100 increases. Therefore, substantially, it is possible to increase the heat exchange capacity of the heat exchanger (100). However, as the distance L between the tubes 120 adjacent to each other decreases, the radius of curvature R of the return tube 140 connecting one end of the tube 120 adjacent to each other decreases. Banding will be difficult. In this embodiment, the radius of curvature (R) of the curved portion 141 is greater than half of the distance (L) between the tube 120 adjacent to each other, thereby between the adjacent tube 120 Even if the distance is reduced, the molding of the return tube 140, that is, the bending of the return tube 140 is to be made easily. And the cross section of the curved portion 141 is formed in a shape and size substantially corresponding to the cross section of the tube (120).

The straight portions 143 are provided at both ends of the curved portion 141, respectively. One end of the tube 120 adjacent to each other is inserted into the straight portion 143. To this end, the straight portion 143 is formed to have a cross section having a relatively large cross section compared to the tube 120.

In addition, a plurality of refrigerant passages 140P are provided inside the return tube 140. The refrigerant passage 140P of the return tube 140 communicates with the refrigerant passage 120P of the tube 120, respectively. In addition, a compartment rib 145 is provided inside the return tube 140. The compartment rib 145 of the return tube 140 serves to partition the refrigerant passage 140P of the return tube 140. The refrigerant passage 140P and the partition rib 145 of the return tube 140 are provided only inside the return tube 140 substantially corresponding to the curved portion 141.

The header 150 is connected to the left end of the third tube 123 and the sixth tube 126 in the drawings. The refrigerant 150 and the fourth to sixth tubes 124 that exchange heat with an external fluid while flowing the refrigerant passage 120P of the first to third tubes 121, 122, and 123 inside the header 150. The refrigerant exchanged with the external fluid while the refrigerant flow path 120P of the 125 and 126 flows is delivered. The header 150 is connected to the withdrawal capillary 170 for delivering the heat exchanged refrigerant while flowing through the tube 120 to other components constituting the heat exchange cycle.

Meanwhile, the pin 110 and the tube 120, the tube 120 and the connector 130, and the tube 120 and the return tube 140 are respectively fixed by brazing coupling. Referring to FIG. 2, a plurality of stacked pins 110 are coupled to each other in a state in which a brazing filler material 180 is disposed on an outer circumferential surface of the tube 120. The fin 110, the tube 120, and the brazing material 180 bonded as described above are heated to a temperature of about 580 to 612 ° C. Therefore, as the brazing filler material 180 is melted, the fin 110 and the tube 120 are fixed. 4 and 6, in the case of the tube 120 and the connector 130, and the tube 120 and the return tube 140, the outer surface of the tube 120 and the connector 130 are separated from each other. When the brazing filler metal 180 in a sheet form is positioned between the inner surface and the outer surface of the tube 120 and the inner surface of the return tube 140, the brazing filler material 180 is heated to a temperature of approximately 580 to 612 ° C. Is melted to fix the tube 120, the connector 130, and the tube 120 and the return tube 140.

In addition, the heat exchanger 100, that is, the fin 110, the tube 120, the connector 130, and the return tube 140 are coated with a corrosion resistant coating layer and a hydrophilic coating layer. The corrosion resistant film layer and the hydrophilic film layer is formed after the fixing process by brazing coupling of the pin 110, the tube 120, the connector 130, and the return tube 140 described above is completed. This is to prevent the phenomenon that the corrosion resistant film layer and the hydrophilic film layer is damaged by heating to a high temperature for the brazing bond. The coating of the corrosion resistant coating layer and the hydrophilic coating layer is performed after the process of drying the oil inside the tube 120, the connector 130, and the return tube 140 is completed.

Hereinafter, a process in which the refrigerant flows according to an embodiment of the heat exchanger according to the present invention will be described.

First, the refrigerant delivered from other components constituting the heat exchange cycle flows through the inlet capillary 160 and flows into the refrigerant passage 120P of the first tube 121 and the fourth tube 124 through the connector 130. do. For example, when the heat exchanger 100 is operated as a condenser, that is, when the heat exchange cycle is circulated in a cooling mode, the refrigerant compressed in the compressor is a refrigerant passage of the first tube 121 and the fourth tube 124. When the heat exchanger 100 is operated as an evaporator, the refrigerant condensed in another heat exchanger operated as a condenser may be a refrigerant flow path of the first tube 121 and the fourth tube 124. 120P). In addition, the connector 130 connected to the first tube 121 and the fourth tube 124 is divided into the refrigerant passage 120P of the first tube 121 and the fourth tube 124 and supplied. .

The refrigerant flowing through the refrigerant passage 120P of the first tube 121 and the fourth tube 124 is connected to the return tube 140, substantially, to the refrigerant passage 140P of the return tube 140. It is delivered by the second tube 122 and the third tube 123 or the refrigerant flow path 120P of the fifth tube 125 and the sixth tube 126 in order to flow. The refrigerant flowing through the refrigerant passage 120P of the tube 120 exchanges heat with an external fluid. However, in the present embodiment, since the plurality of refrigerant passages 120P are provided inside the tube 120, the refrigerant flowing through the refrigerant passage 120P of the tube 120 exchanges heat with the external fluid more efficiently. You can do it. In addition, the refrigerant flowing through the refrigerant passage 120P of the tube 120 substantially increases heat exchange area with the external fluid by the fin 110, thereby further increasing heat exchange efficiency with the external fluid.

Meanwhile, the refrigerant that exchanges heat with an external fluid while flowing through the refrigerant passage 120P of the tube 120 is delivered to the header 150. And the refrigerant delivered to the header 150 is delivered to the other components constituting the heat exchanger through the withdrawal capillary (170). However, as described above, in the present embodiment, the refrigerant delivered to the heat exchanger 100 through the inlet capillary 160 does not pass through the header as in the prior art, but through the connector 130. It is directly transmitted to the first tube 121 and the fourth tube 124. Therefore, as in the related art, the phenomenon in which the liquid refrigerant is partially concentrated by the gas phase difference due to the phase of the refrigerant inside the header connected to the inlet capillary 160 is prevented.

Within the scope of the basic technical spirit of the present invention as well as many other modifications are possible to those skilled in the art, the scope of the present invention should be interpreted based on the appended claims. .

In the above embodiment, the tube is composed of six tubes, but is not necessarily limited thereto. That is, the tube may be composed of fewer than six or more than.

According to the return tube and the heat exchanger including the same according to the present invention as described above can be expected the following effects.

First, in the present invention, a plurality of tubes provided with a plurality of refrigerant passages and a plurality of pins through which the tubes pass through heat exchange between the refrigerant and the external fluid. Therefore, more efficient heat exchange by the heat exchanger is possible.

In the present invention, the pin and the tube, the tube and the connector and the return tube is fixed at one time by the brazing coupling. Therefore, the heat exchanger can be manufactured more simply.

In the present invention, the return tube is bent to a radius of curvature of more than half of the distance between the tubes. Therefore, since the number of the tubes can be maximized in the heat exchanger of the same size, the heat exchange efficiency of the heat exchanger can be further increased.

In addition, in the present invention, the refrigerant is directly transmitted to the tube by the connector. Therefore, as compared with the case where the refrigerant is transferred to the tube through the conventional header, the phenomenon in which the liquid and gaseous refrigerant is separated and transferred to the tube is prevented, thereby improving heat exchange efficiency by the heat exchanger.

1 is a front view showing an embodiment of a heat exchanger according to the present invention.

Figure 2 is a cross-sectional view showing the contact portion of the pin and the tube in the embodiment of the present invention.

3 is a perspective view showing a connector constituting an embodiment of the present invention.

Figure 4 is a cross-sectional view showing the contact portion of the tube and the connector in the embodiment of the present invention.

5 is a perspective view showing a return tube constituting an embodiment of the present invention.

Figure 6 is a cross-sectional view showing the contact portion of the tube and the return tube in an embodiment of the present invention.

Claims (10)

At least a part of which is formed in an open curve shape having a predetermined radius of curvature and has a plurality of refrigerant passages through which refrigerant flows, and both ends thereof are adjacent to each other among a plurality of tubes passing through the plurality of fins. Return tube for connecting the end of the tube. The method of claim 1, Return tube formed by bending in an extruded state. The method of claim 1, Both ends of the return tube circumscribed to the end of the tube. The method of claim 1, A return tube bent to a radius of curvature of more than one half of the distance between the adjacent tubes. The method of claim 1, Return tube formed in horseshoe (Ω) shape. A curved portion bent at a radius of curvature exceeding one half of a distance between the adjacent tubes among a plurality of tubes passing through a plurality of fins; And A pair of straight portions extending in parallel from each other at both ends of the curved portion and connected to one ends of the tubes adjacent to each other; Return tube comprising a. The method of claim 6, And a longitudinal section orthogonal to the longitudinal direction of the straight portion is at least a longitudinal section orthogonal to the longitudinal direction of the tube. A plurality of pins formed in a plate shape having a predetermined length; A plurality of tubes installed through the fins so as to be spaced apart from each other by a predetermined interval, and each having a plurality of refrigerant passages through which the refrigerant flows; And A return tube of any one of claims 1 to 7 connecting one end of the flat tube adjacent to each other; Heat exchanger comprising a. The method of claim 8, The tube and the return tube, the heat exchanger is fixed by the brazing coupling. The method of claim 9, The heat exchanger is fixed to the tube and the return tube by melting the brazing material provided between the tube and the return tube.

Images