KR20030067409A - Heat exchanger - Google Patents

Abstract

PURPOSE: A heat exchanger is provided to decrease drop in pressure and improve evaporating performance. CONSTITUTION: Outside cut protrusions(111,111') and middle cut protrusions(112,112') of an air current inflow side cut protrusion group are divided into two split bodies, respectively, and an inside cut protrusion(113) is formed as a single body. First rising parts(111a,111a',112a,112a') of the outside cut protrusions and the middle cut protrusions are parallel with air current(l). Second rising parts(111b,111b'112b,112b') of the outside cut protrusions and the middle cut protrusions are parallel with a tangent of heat transfer tubes(102). Outside cut protrusions(116,116') of an air current outflow side cut protrusion group are divided into two split bodies to be symmetrical with the outside cut protrusions of the air current inflow side cut protrusion group with respect to a center-line(C-C) of the heat transfer tubes. First rising parts(116a,116a') of the outside cut protrusions are parallel with the air current while second rising parts(116b,116b') are parallel with the tangent of the heat transfer tubes. Middle cut protrusions(115,115') are divided into two split bodies to be asymmetrical with the middle cut protrusions of the air current inflow side cut protrusion group. Both rising parts(115a,115a',115b,115b') of the middle cut protrusions are parallel with the tangent of the heat transfer tubes. An inside cut protrusion(114) is formed as a single body. Both rising parts(114a,114b) of the inside cut protrusion are parallel with the air current.

Description

Heat exchanger {HEAT EXCHANGER}

The present invention relates to a heat exchanger, and more particularly, by differently configuring the cutting protrusion structure of the inflow side and the outflow side of the wind blowing on the basis of the center line of the heat pipe to improve the evaporation performance while reducing the pressure drop. A heat exchanger that can be.

In general, since the interior space of a building is contaminated by internal factors such as occupants' breath, it is necessary to periodically supply fresh air from the outside.

In addition, in hot summer or cold winter, the room should be cooled and heated to an appropriate temperature, and the proper humidity is maintained to be suitable for people's activities.

To this end, most buildings are equipped with air conditioners.

A typical air conditioner is an air conditioner that cools a room by using a phenomenon of absorbing heat when surrounding liquid evaporates.

The air conditioner consists of a compressor for compressing the refrigerant into a gas of high temperature / high pressure, a condenser for liquefying the compressed high temperature / high pressure refrigerant, and a heat exchanger for evaporating the refrigerant expanded by the expansion valve. The cooled air is forcedly blown into the room where cooling is required by the blowing fan in the blower assembly.

This type of heat exchanger is composed of heat transfer tubes such as copper and fins connected to each other by U bends, and the air flowing between the fluid and the fins passing through the heat transfer tubes is cooled by heat exchange with the refrigerant. Have

In heat exchangers, miniaturization and high performance have recently been required, but problems of deterioration of heat transfer performance and generation of noise are accompanied.

Accordingly, there have been attempts to improve heat transfer performance and reduce noise while achieving miniaturization and high performance of heat exchangers.

Korean Patent No. 1991-3071, filed on October 28, 1988 and registered on May 17, 1991, discloses a heat exchanger to improve heat transfer performance while simultaneously reducing noise.

The fin shape of the heat exchanger disclosed in this patent has a structure as shown in FIG.

That is, the heat transfer pipe 2 is inserted into the pin collar 12, which is burried at a predetermined interval on the plate-shaped pin 1, and the wind flows in the direction of the arrow (A).

The fin 1 has three rows on the inflow side of the wind flow A between two heat transfer tubes 2 adjacent in the short direction, three rows on the outflow side where the wind blows, and a total of six rows. It has a cutting protrusion group which consists of cutting protrusion pieces.

Among the six rows of cutting projection pieces, the cutting projection pieces in the most upstream and downstream streams of the air stream are each composed of two cutting projection pieces 14 and 24 separated by the central divided flat portion 3a, and the cutting projections in different rows. Each piece consists of one cutting protrusion piece 4, respectively.

The openings 8, 18, and 28 of the six rows of cutting projection pieces are perpendicular to the air flow direction l. In addition, the granular portions 5, 6, 15, and 25 on the heat transfer pipe 2 side of each of the cutting projection pieces 4, 14, and 24 are tangent to the heat transfer pipe 2 (m). The inclination angle is set in a direction substantially along a line extending in parallel with the cross-section), and the granular portions 16 and 26 on the central portion of the two cutting protrusion pieces 14 and 24 respectively at the upstream end or the downstream end of the air stream are formed into the granular part ( Parallel to 15 and 25, respectively, the cutting projection pieces 14 and 24 are formed in parallel quadrilateral shapes.

Each of the six rows of cutting projection pieces has the intermediate flat portion 3b interposed therebetween, and the cutting projections are alternately formed on the surface side and the rear surface side of the pin 1.

According to the above configuration, the effect of improving the heat transfer rate between the air and the fin surface can be expected to increase the heat exchange efficiency, but noise is still generated and there is a limit to the improvement of the evaporation performance.

The present invention for solving the above problems is configured heat exchanger to improve the evaporation performance while reducing the pressure drop by configuring the cutting protrusion structure of the inflow side and the blowing side of the wind blowing on the basis of the center line of the heat transfer pipe The purpose is to provide a flag.

1 is a plan view showing the fin shape of a conventional heat exchanger,

Figure 2 is a plan view showing the fin shape of the heat exchanger according to the present invention.

♣ Explanation of symbols for main part of drawing ♣

100: fin 102: heat transfer pipe

111, 111 '; 116, 116 ': outer cutting protrusion

112, 112 '; 115, 115': Middle cutting protrusion

113, 114: inner cutting protrusion 100a: split flat portion

100b: Middle flat part 118: Opening

The heat exchanger of the present invention for achieving the above object is arranged in parallel at a predetermined interval, a plurality of flat fins through which air flows therebetween, and a heat transfer tube inserted at right angles to each of the flat fins and passing the fluid therein A plurality of airflow inlet side cutting protrusion groups and airflow outflow side cutting protrusion groups are disposed between the two heat transfer tubes with respect to the center line of the heat of the heat transfer tube, between the two heat transfer tubes. A central flat portion located on the center line of the heat transfer tube is formed therebetween, and each cutting protrusion composed of a granular portion protruding from the fin surface at both ends and a cross-linking portion between the two granular portions has a front side and a rear surface side with respect to the fin surface. Alternately protruding from each other, an intermediate flat portion is formed between the cutting protrusions, and each of the cutting protrusions uses the intermediate flat portion. In the heat exchanger disposed in parallel adjacent to each other, the outer cutting protrusion and the middle cutting protrusion of the cutting protrusion group on the inlet side of the air flow is formed of two divided bodies, the inner cutting protrusion is formed of a single body, the double outer cutting protrusion and the middle The first granular portion of the cutting projection is parallel to the airflow direction and the second granular portion is parallel to the tangent of the heat transfer pipe; The outer cutting protrusion of the cutting protrusion group on the outflow side of the air flow is formed into two divisions symmetrically with the outer cutting protrusion on the inflow side of the heat transfer tube with respect to the center line of the heat transfer pipe, and the first granular portion is parallel to the airflow direction and the second granular portion is Parallel to the tangential direction of the heat transfer pipe, the intermediate cutting protrusion is formed in two segments asymmetrically with the intermediate cutting protrusion of the air flow inlet side with respect to the center line of the heat transfer pipe, and both granular portions are similar to the second granular portion of the outer cutting protrusion. It is parallel to the tangential direction of the heat transfer pipe, the inner cutting protrusion is formed in a single body, characterized in that both granular portion is parallel to the air flow direction.

Hereinafter, a heat exchanger according to a preferred embodiment of the present invention will be described in detail with reference to the accompanying FIG. 2.

2 is a plan view showing the fin shape of the heat exchanger according to the present invention.

The fin shape of the heat exchanger according to the present invention has a structure as shown.

That is, the heat transfer tube 102 is inserted into the flat plate-shaped pin 100 at a predetermined interval, and the wind flows in the direction of the arrow A to exchange heat with the refrigerant.

That is, the plurality of flat fins 100 are arranged in parallel at regular intervals, and the plurality of heat transfer tubes 102 through which fluid flows are inserted at right angles to the flat fins 100.

In the flat fin 100 of the present invention, between the two heat pipes 102, a total of six rows of cutting protrusions are formed on each of the inflow side of the air flow A and the outflow side of the wind. .

Here, the inflow side is based on the center line (C) of the heat pipe 102, the air flow (A) refers to the blowing side (lower in the drawing), the outlet side is based on the center line (C) of the heat pipe 102 rows. , It refers to the side (upward in the drawing) where the airflow A is blowing out.

Between the airflow inlet side cutting protrusion group 111, 111 '; 112, 112'; 113 and the airflow outlet side cutting protrusion group 114; 115, 115 '; 116, 116' on the center line of the heat exchanger tube 102 The central flat portion 100a is located.

Each cutting protrusion (for example, 113; 114 in the center) is a bridge between the granular portions 113a, 113b; 114a, 114b, which protrude from the fin surface at both ends, and the two granular portions 113a, 113b; 114a, 114b. It is composed.

Further, each of the cutting protrusions is formed by alternately protruding the surface side and the rear side with respect to the pin surface or by protruding both in the surface side and the rear side.

That is, the first row cutting projections 111 and 111 ', the third row cutting projections 113 and the fifth row cutting projections 115 and 115' are formed on the surface side of the pin surface in order from the lower end thereof. In addition to the second row cutting protrusions 112 and 112 ', the fourth row cutting projections 114 and the sixth row cutting projections 116 and 116' are formed.

Intermediate flat portions 100b are formed between the cutting projections, and the six rows of cutting projections are arranged adjacently in parallel with the intermediate flat portions 100b interposed therebetween.

Looking in more detail the configuration of the air flow inlet side cutting protrusion group (111, 111 '; 112, 112'; 113), the inner cutting protrusion 113 is located close to the center line (CC) of the heat transfer pipe 102, the most front The outer cutting protrusions 111 and 111 'positioned at the inflow side of the air stream, and the intermediate cutting protrusions 112 and 112' positioned between the inner cutting protrusion 113 and the outer cutting protrusions 111 and 111 '. have.

Among them, the outer cutting protrusions 111 and 111 'and the intermediate cutting protrusions 112 and 112' are formed of two divided bodies, the inner cutting protrusion 113 is formed of a single body, and the double outer cutting protrusions 111 and 111 '. ') And the first granular portions 111a, 111a'; 112a, 112a 'of the intermediate cutting protrusions 112, 112' are parallel to the airflow direction l and the second granular portions 111b, 111b '; 112b, 112b. ') Is formed parallel to the tangential direction of the heat transfer pipe (102).

In addition, in view of the configuration of the outflow side cutting protrusion group 114; 115, 115 '; 116, 116', the inner cutting protrusion 114 located close to the center line CC of the heat transfer pipe 102, and the air flow at the rearmost portion. The outer cutting protrusions 116 and 116 'positioned on the outflow side and the intermediate cutting protrusions 115 and 115' positioned between the inner cutting protrusion 114 and the outer cutting protrusions 116 and 116 '.

Among them, the outer cutting protrusions 116 and 116 'are formed in two segments while being symmetrical with the outer cutting protrusions 111 and 111' of the air flow inlet side with respect to the center line CC of the heat transfer pipe 102. The first granular portions 116a and 116a 'are formed parallel to the air flow direction l and the second granular portions 116b and 116b' are formed parallel to the tangential direction of the heat transfer pipe 102.

In addition, the intermediate cutting protrusions 115 and 115 'and the inner cutting protrusion 114 are formed in a single body, respectively, and both of the granular portions 115a, 115a', 115b, and 115b 'of the intermediate cutting protrusions 115 and 115' are formed. Similarly to the second granular portions 116b and 116b 'of the outer cutting protrusions 116 and 116', both of the granular portions 114a and 114b of the inner cutting protrusion 114 are parallel to the tangential direction of the heat transfer pipe 102. It is formed parallel to the air flow direction (l).

In addition, in order to reduce the dead zone of the heat transfer pipe 102, which leads to a decrease in the heat transfer rate and an increase in the pressure loss, in the present invention, both outer cutting protrusions 111 and 111 ' The gap between the first granular portions 111a and 111a 'is formed to be larger than the gap between the first granular portions 112a and 112a' of both intermediate cutting protrusions 112 and 112 ', thereby forming both outer cutting protrusions 111 and 111 ') and the second granular portions 111b, 111b'; 112b, 112b 'of the intermediate cutting protrusions 112, 112' are arranged closer to each other than the conventional heat pipe 102 at a distance.

Similarly, the interval between the first granular portions 116a, 116a 'of the both outer cutting projections 116, 116' on the airflow outlet side is equal to the first granular portion 115a, of the intermediate cutting projections 115, 115 '. It is formed larger than the interval between 115a '), so that the second granular portions 116b, 116b'; 115b, 115b 'of the both outer cutting projections 116, 116' and the intermediate cutting projections 115, 115 'are transferred to the heat transfer pipe ( 102 are arranged in close proximity at approximately the same distance.

At the same time, the first granular portion 116a 'of the at least one shear protrusion 116' of the outer shear protrusions 116 and 116 'is formed of at least one shear protrusion of the intermediate shear protrusions 115 and 115'. And the first granular portion 115a 'of 115' are arranged side by side in the airflow direction l.

At this time, the intermediate cutting protrusions 112 and 112 'of the airflow inlet side and the intermediate cutting protrusions 115 and 115' of the airflow outlet side are arranged symmetrically in a diagonal direction with respect to the center line CC of the heat transfer pipe 102. There are features of the invention.

Next, a structure in which heat transfer tubes are arranged in two rows in a fin-like structure having the above-described configuration will be described.

As shown, the fin 100 is divided into an upstream row portion of the structure as described above and a downstream row portion of the structure as described above with respect to the center, with respect to the airflow mainstream direction l in each row portion. The heat transfer tubes 102 and 102 'are fitted in the perpendicular direction.

These heat transfer tubes 102 and 102 'are arranged so that the upstream row and the downstream row do not overlap in the airflow direction A. As shown in FIG.

On the other hand, the upstream column and the downstream column each have a phase difference equal to the phase difference between the heat transfer tubes 102 and 102 with respect to the center lines C-C and C1-C1 of the heat transfer tube, and have the same arrangement structure.

That is, the shear projection groups in the upstream row arranged on the basis of the center line CC of the heat transfer pipe 102 and the shear projection groups in the downstream row arranged on the basis of the center line C1-C1 of the heat transfer pipe 102 'are combined with each other. 102 and 102 'have the same arrangement shape at equal intervals.

According to the present invention described above, three rows of cutting protrusions are arranged on the inflow side and the outflow side of the wind, based on the center line of the heat transfer pipe, but the inner cutting protrusions of the inflow side and the outflow side are single bodies. Furnace, the outer cutting protrusion is composed of a separate body divided into two, in the case of the intermediate cutting protrusion disposed between the inner cutting protrusion and the outer cutting protrusion, the inlet side is divided into two, the outlet side is composed of a single body, thereby reducing the pressure drop. It can reduce the noise can be expected, there is an advantage to improve the evaporation performance by increasing the heat transfer rate between the air and the fin surface.

Claims (4)

A plurality of flat fins arranged in parallel at regular intervals and in which air flows therebetween, and a plurality of heat transfer tubes inserted at right angles to each of the flat fins and passing fluid therein are provided at right angles to the passage direction of the airflow. Between the two heat pipes, the airflow inlet side cutting protrusion group and the airflow outlet side cutting protrusion group are disposed with respect to the centerline of the heat of the heat transfer tube, and between these two cutting protrusion groups, the central flat located on the centerline of the heat transfer tube. An additional portion is formed, and each cutting protrusion composed of a granular portion protruding from the fin surface at both ends and a cross-linking portion between the two granular portions is formed by alternately protruding the surface side and the rear surface side with respect to the pin surface, and between the cutting protrusions. An intermediate flat portion is formed, and each of the cutting protrusions is disposed in a heat exchanger disposed adjacently in parallel with the intermediate flat portion therebetween. hurry, The outer cutting protrusions 111 and 111 'and the middle cutting protrusions 112 and 112' of the cutting protrusion group on the inflow side of the air flow are formed of two divided bodies, and the inner cutting protrusion 113 is formed of a single body, and the double outer side thereof. The first and second granular portions 111a and 111a 'and 112a and 112a' of the cutting protrusions 111 and 111 'and the intermediate cutting protrusions 112 and 112' are parallel to the airflow direction l and the second granular portions 111b and 111b '; 112b and 112b' are parallel to the tangential direction of the heat pipe 102; The outer cutting protrusions 116 and 116 'of the cutting protrusion group on the airflow outlet side are symmetrical with the outer cutting protrusions 111 and 111' on the airflow inlet side with respect to the center line C of the heat transfer pipe 102. The first granular portions 116a and 116a 'are parallel to the air flow direction l and the second granular portions 116b and 116b' are parallel to the tangential direction of the heat transfer pipe 102, and the intermediate cutting protrusions 115 and 115 'are formed in two segments asymmetrically with the intermediate cutting protrusions 112 and 112' at the air flow inlet side with respect to the center line CC of the heat transfer pipe 102, and both granular portions 115a, 115a ', 115b and 115b' are parallel to the tangential direction of the heat transfer pipe 102 similarly to the second granular portions 116b and 116b 'of the outer cutting protrusions 116 and 116', and the inner cutting protrusion 114 is A heat exchanger, characterized in that formed in one piece, wherein both of the granular portions 114a and 114b are parallel to the airflow direction l. The method of claim 1, The interval between the first granular portions 111a and 111a 'of the both outer cutting projections 111 and 111' on the inflow side of the airflow is the first granular portions 112a and 112a of the intermediate cutting projections 112 and 112 '. By forming a larger than the interval between '), the second granular portion (111b, 111b'; 112b, 112b ') of the both outer cutting projections (111, 111') and the intermediate cutting projections (112, 112 ') is transferred to the heat pipe (102). Are placed close to each other at approximately the same distance as The first granular portion 111a of the at least one shear protrusion 111 of the outer shear protrusions 111 and 111 'is the first of the at least one shear protrusion 112 of the intermediate shear protrusions 112 and 112'. Heat exchanger, characterized in that arranged in parallel with the granular portion (112a) in the air flow direction (ℓ). The method of claim 1, The interval between the first granular portions 116a and 116a 'of the both outer cutting projections 116 and 116' on the airflow outlet side is the first granular portion 115a and 115a of the intermediate cutting projections 115 and 115 '. By forming a larger than the interval between '), the second granular portion (116b, 116b'; 115b, 115b ') of the both outer cutting projections (116, 116') and the intermediate cutting projections (115, 115 ') is transferred to the heat pipe 102 Are placed close to each other at approximately the same distance as The first granular portion 116a 'of the at least one shear protrusion 116' of the outer shear protrusions 116, 116 'is at least one shear protrusion 115' of the intermediate shear protrusions 115, 115 '. Heat exchanger, characterized in that arranged in parallel with the first granular portion (115a ') of the air flow direction (l). The method of claim 2 or 3, The intermediate cutting protrusions 112 and 112 'of the airflow inlet side and the intermediate cutting protrusions 115 and 115' of the airflow outlet side are symmetrically disposed in a diagonal direction with respect to the center line CC of the heat transfer pipe 102. Heat exchanger made.