KR20010019880A - Heat exchanger - Google Patents

Abstract

PURPOSE: A heat exchanger is provided to reduce loss of wind pressure while improving heat transferring efficiency according to length of an air channel. CONSTITUTION: A heat exchanger comprises heat transfer tubes(10) separately formed while having plural refrigerant passages; headers connecting the heat transfer tubes while being arranged on both ends of the heat transfer tubes; and a heat transfer fin(30) with plural variable portions(33) varying a flowing sectional area of air by being depressed from one surface and protruded from the other surface. Herein, a flowing sectional area of air is varied while mixing air in an expanded area. Therefore, heat transfer efficiency of the air passage is improved. Moreover, loss of wind pressure is reduced by not using an inclined louver.

Description

Heat exchanger {HEAT EXCHANGER}

The present invention relates to a heat exchanger, and more particularly, to a heat exchanger that can not only reduce the wind pressure loss, but also increase the heat transfer effect.

1 is a schematic perspective view of a conventional heat exchanger, and FIG. 2 is an enlarged cross-sectional view taken along line II-II of the heat exchanger of FIG. 1. As shown in these figures, the heat exchanger is erected on both ends of the plurality of plate-shaped heat transfer tubes 101 and the heat transfer tubes 101 which are spaced apart in parallel to each other in the transverse direction with respect to the air flow direction. Headers 103a and 103b made of hollow bodies for mutually communicating 101 and a plurality of heat transfer fins arranged to contact the plate surface of the heat transfer tube 101 to enlarge the heat transfer area to promote heat transfer of the heat transfer tube 101. Have 105.

The heat transfer tube 101 is formed of a metal member having a rectangular cross-sectional shape, and a plurality of refrigerant passages (not shown) are formed inside and spaced apart in parallel to each other. The heat transfer tubes 101 are spaced apart from each other horizontally with respect to the flow direction of air, and both ends thereof are coupled to the hollow headers 103a and 103b so that the refrigerant flow paths formed therein communicate with each other.

The heat transfer fins 105 are spaced apart to be parallel to each other at a predetermined air passage interval along the longitudinal direction of the heat transfer tube 101, and each plate surface is disposed with a predetermined inclination angle with respect to the air flow direction to provide air flow. A plurality of louvers 107 for guiding are formed.

By the way, in such a conventional heat exchanger, a wind pressure loss becomes large by the louver arrange | positioned inclined to the flow direction of air. Accordingly, there is a problem in that the power consumption is relatively increased because a blower fan that promotes the heat transfer effect of the heat exchanger is required because it is disposed on one side of the heat exchanger and blows toward the heat exchanger.

In addition, since the flow path of air formed by these heating fins is formed almost linearly, relatively no air is uniformly contacted with the heating fins. That is, some of the air in the flow path passes through the flow path in a state that is hardly in contact with the heating fins, so there is a problem that the heat transfer efficiency is relatively low.

Accordingly, an object of the present invention is to provide a heat exchanger which can reduce wind pressure loss and can improve heat transfer efficiency with respect to an air flow path length.

1 is a schematic perspective view of a conventional heat exchanger,

2 is an enlarged cross-sectional view taken along line II-II of the heat exchanger of FIG.

3 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention;

4 is an enlarged perspective view illustrating main parts of the heat transfer fin region of FIG. 3;

5 is a cross-sectional view taken along the line VV of FIG. 4;

FIG. 6 is a partially enlarged view of an expanded state of the heat transfer fin of FIG. 3;

7 is an enlarged cross-sectional view taken along the line VII-VII of FIG. 6.

Explanation of symbols on the main parts of the drawings

10: heat transfer tube 23a, 23b: header

25: refrigerant inlet 27: refrigerant outlet

30: heating fin 31: heating fin

33: variable part 35: connection part

According to the present invention, there is provided a plate-shaped heat transfer tube having a plurality of refrigerant passages formed in parallel with each other therebetween and horizontally spaced apart in the traveling direction of the air; A header disposed at both ends of the heat transfer tube to communicate with the heat transfer tube; Spaced apart from each other along the longitudinal direction of the heat transfer tube so that the air can pass through, characterized in that it comprises a heat transfer fin having a plurality of variable parts recessed from one side surface and protruding to the other side surface to vary the flow cross-sectional area of the air Is achieved by a heat exchanger.

Here, the heat transfer fins are preferably arranged so that the variable parts are symmetrical with respect to the center line of the air flow path formed between the other heat transfer fins adjacent to each other along the longitudinal direction of the heat transfer tube.

In addition, it is effective to configure the variable part to have an arc shape when projecting.

Hereinafter, with reference to the accompanying drawings will be described in detail with respect to the present invention.

3 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention, and FIG. 4 is an enlarged perspective view of main parts of the heat transfer fin region of FIG. 3. As shown in these figures, the heat exchanger has a plurality of heat transfer tubes 10 having a flat plate shape and spaced apart from each other in parallel to each other in a flow direction of air, and are disposed at both ends of the heat transfer tubes 10. The headers 23a and 23b communicating with each other 10 and the heat-transfer fins 30 having a wave shape are arranged along the longitudinal direction of the heat-transfer tube 10 so as to be in contact with at least one plate surface of the heat-transfer tube 10.

The headers 23a and 23b are formed by a plurality of hollow members, and a partition member 24 partitioning the inside is formed to form a plurality of refrigerant accommodating spaces along the longitudinal direction. The upper support member 17 and the lower support member 19 are coupled to the upper and lower regions of the headers 23a and 23b, respectively, to support the heat transfer fins 30, and the upper and lower portions of one header 23a. A coolant inlet 25 and a coolant outlet 27 for entering and exiting the coolant are respectively formed in the region.

The heat transfer tube 10 has a substantially rectangular parallelepiped shape, and a plurality of refrigerant passages 11a, 11b, and 11c are partitioned in parallel with each other. Both ends of each heat transfer tube 10 are coupled to each other to communicate with the headers 23a and 23b, so that the flow path of the coolant has a substantially zigzag shape from the coolant inlet 25 to the coolant outlet 27.

The heat transfer fins 30 are adjacent to each other at the top and bottom of the heat transfer fins 31 and a plurality of heat transfer fins 31 disposed to be spaced apart from each other such that air flow paths are formed along the length direction of the heat transfer tube 10. It has a connection portion 35 for connecting the heat transfer fin portion 31 is curved.

5 is an enlarged cross-sectional view taken along line V-V of the heating fin of FIG. 4, FIG. 6 is a partially enlarged view of a developed state of the heating fin of FIG. 3, and FIG. It is an enlarged cross-sectional view. As shown in these figures, each heat-transfer fin portion 31 is recessed from one plate surface and protrudes with respect to the other plate surface and extends along the longitudinal direction of the headers 23a and 23b to have a substantially partial cylindrical shape. 33 is formed. The variable parts 33 are spaced apart in parallel with each other at a predetermined distance S along the air flow direction, and are symmetrical with respect to the center line of the variable parts 33 and the air flow path of the adjacent other heat-transfer fins 31. By being arranged in, the flow cross-sectional area of the air passage is enlarged or reduced.

Referring to the manufacturing process of the heat transfer fin 30 schematically, first, a thin plate-like heat transfer member such as aluminum is partitioned along the longitudinal direction so that the heat transfer fin 31 and the connection portion 33 can be formed. In the present embodiment, for convenience of description, the width of the heat transfer member is regarded as being equal to the width of the heat transfer fin 30. Next, the variable part 33 is shape | molded so that it may have a predetermined | prescribed pitch in the heat transfer fin part 31 except the connection part 33 of each division section partitioned by the partition line 41. As shown in FIG. The shaping of the variable portion 33 includes a female mold (not shown) having a semi-circular depression-shaped surface corresponding to the variable portion 33, and a depression-shaped surface having a molding surface protruding to correspond to the variable portion 33. It is made by a mold (not shown) for forming the variable portion 33 by pressing the heat transfer member with the molding space of the variable portion 33 in between.

Here, the variable portion 33 is formed to have a circular cross-sectional shape, the radius (R) is to be formed in the range of approximately 0.1 to 0.5mm. The length L of the variable part 33 is 60-90% of the total length which added the length L of the heat transfer fin part 31 to the length of the connection part 33 formed in the upper end and the lower end of the heat transfer fin part 31, respectively. It is to have a length range of, it is effective that the interval (S) between the center of each variable portion 33 has a range of 0.2 to 4mm.

When the molding of the variable part 33 is completed, bending is performed using a bending machine or the like not shown so that the connection part 35 of an arc is formed around the partition line 41. At this time, the bending operation is carried out so that the variable portion 33 is symmetrical with respect to the center line of the air flow path formed between the adjacent heat transfer fins 31. That is, the protruding side of the variable part 33 is bent so as to be mutually adjacent to the protruding side of another adjacent variable part 33, and the recessed side is bent so as to be disposed adjacent to each other with the depressed side of the other variable part 33. Between the heat transfer fins 31 where bending is completed, the variable sections 33 increase and decrease the sections E1 and E2 in which the flow width is increased compared to the pitch P of the heat transfer fins 31, D1, D2) are alternately formed along the flow direction of air alternately. Here, E1 (D1) represents the section in which the flow width is increased (decreased) by the recessed side of the variable portion 33, and E2 (D2) the flow width is increased (decreased) by the protruding side of the variable portion 33. ) Means the interval.

By this configuration, the refrigerant flowing into the header 23a through the refrigerant inlet 25 flows to the opposite header 23b through the plurality of heat transfer tubes 10 communicating with each other. The refrigerant flowing to the opposite header 23b flows again to the refrigerant outlet side header 23a through the heat transfer tube 10, and is repeatedly discharged through the refrigerant outlet 27 by repeating this process.

At this time, the air blown by a blower fan (not shown) is introduced into the air flow path formed between the heat transfer fins 31, and the introduced air flows along the air flow path whose flow cross-sectional area is expanded and contracted. It is in contact with the heat exchanger. That is, some of the air introduced into the air flow path is in contact with the heat transfer fins 30, and the air not contacted with the heat transfer fins 30 is expanded through the expansion section E1, E2 by the flow section. ), It creates a turbulent flow and intermixes with the heated air, causing heat exchange. The mixed air again undergoes heat exchange while passing through the reduction sections D1 and D2, and passes through the air flow path while repeating mixing and heat exchange in the expansion sections E1 and E2.

In the above-described and illustrated embodiments, the variable parts arranged at predetermined intervals along the flow direction of air have been described to have a semicircular shape, but they may be configured to have a circular arc cross-sectional shape, and may have a triangular, square or elliptical cross section. It may be configured to have a shape.

In addition, in the above-described and illustrated embodiments, the heat transfer fins are configured so as to have a continuous wave shape with heat transfer fin portions arranged parallel to each other along the longitudinal direction of the heat transfer tube and a connection portion connecting the heat transfer fin portions. Of course, it is possible to form a heat transfer fin individually by a separate plate-like member and configured to be spaced apart in parallel to each other along the longitudinal direction of the heat transfer tube.

In addition, although each of the heating fins is configured to have a wave shape connected to each other by a connecting portion curved upward or downward, it may be configured to have a square wave shape so that the heat transfer tube and the heat transfer fins are in surface contact.

As described above, according to the present invention, the heat transfer efficiency for the unit length of the air flow path by forming an air flow path so that the flow cross-sectional area of the air is expanded and contracted alternately, and the air is mixed with each other in the expanded area Heat exchangers are provided to maximize the

In addition, according to the present invention, a heat exchanger capable of significantly reducing the loss of wind pressure is provided as compared to a conventional heat exchanger which changes an air flow path by forming an inclined louver or the like in the air flow direction.

In addition, when the heat exchanger according to the present invention is adopted, since the loss of wind pressure is small, it is possible to reduce the power consumption of the blower fan installed adjacent to the heat exchanger and blowing toward the heat exchanger.

Claims (3)

A plate-shaped heat transfer tube having a plurality of refrigerant passages formed in parallel with each other and arranged to be spaced apart from each other in a traveling direction of air; A header disposed at both ends of the heat transfer tube to communicate with the heat transfer tube; Spaced apart from each other along the longitudinal direction of the heat transfer tube so that the air can pass through, characterized in that it comprises a heat transfer fin having a plurality of variable parts recessed from one side surface and protruding to the other side surface to vary the flow cross-sectional area of the air Heat exchanger. The method of claim 1, The heat exchanger fins are arranged so that the variable parts are symmetrical with respect to the center line of the air flow path formed between the other heat transfer fins adjacent to each other along the longitudinal direction of the heat transfer tube. The method according to claim 1 or 2, The variable portion heat exchanger, characterized in that having a circular arc shape in planar projection.