JP2008202896A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger improved in efficiency in heat exchange, by preventing a residence of condensation water. <P>SOLUTION: This heat exchanger has: a cylindrical refrigerant inflow side header pipe 1; a refrigerant outflow side header pipe 2; and a plurality of heat transfer tubes 3 inserted and connected between the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2. The heat transfer tubes 3 are formed with a projection part 8 arranged in a zigzag shape in the wind flowing direction on its surface. Thus, since the condensation water smoothly flows down downward by going along the projection part 8, residence of the condensation water is prevented. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat exchanger provided with a plurality of heat transfer tubes between a header tube on the refrigerant inflow side and a header tube on the refrigerant outflow side.

  Conventionally, as a heat exchanger constituting a refrigeration cycle such as a refrigerator or an air conditioner, as shown in Patent Document 1, a header pipe on a refrigerant inflow side and a refrigerant outflow side arranged so that the pipe axis directions are parallel to each other And a plurality of heat transfer tubes arranged in a direction orthogonal to the two header tubes, both ends of each heat transfer tube are inserted and connected in a row to the header tube, and the refrigerant passes through the heat transfer tubes And a refrigerant flow path that is finely divided into a plurality of parts is formed.

On the other hand, as what improved heat exchange efficiency rather than the heat exchanger shown in patent document 1, what bent the heat exchanger tube and made it meander, and provided the convex part along the direction of a wind flow on the surface. This is disclosed in Patent Document 2.
Japanese Patent No. 3133897 JP 2006-284123 A

  However, in order to improve the efficiency of heat exchange, if a convex part is provided along the flow direction of the wind, when the heat exchanger is used as an evaporator, condensed water stays in the convex part. There is a problem that the dew condensation water staying on the leeward side in the flowing direction flies. In addition, when a heat exchanger is used as an evaporator outdoors in winter, there is a problem that the number of times of defrosting operation is increased because the condensed water staying on the convex portion freezes.

  Then, in view of the above, an object of the present invention is to provide a heat exchanger that prevents the accumulation of condensed water and improves the efficiency of heat exchange.

  In order to achieve the above object, in the present invention, a refrigerant inflow side header pipe and a refrigerant outflow side header pipe, which are arranged so that the pipe axis directions are parallel, are arranged in a direction perpendicular to the two header pipes. A plurality of flat heat transfer tubes through which the refrigerant passes, and the heat transfer tubes are arranged in a row at intervals so that air passes along the tube axis direction of the header tube, Each heat transfer tube protrudes to the adjacent heat transfer tube side, and a convex portion is formed along the tube axis direction of the heat transfer tube, and the convex portion is arranged at a position shifted from the convex portion facing each other. And

  A convex part protrudes toward the adjacent heat exchanger tube. At this time, the positions of the convex portions facing each other are shifted from each other. Thereby, compared with the case where the heat exchanger tube which provided the convex part in the position which faces is arranged in parallel, the distance of an adjacent heat exchanger tube and a heat exchanger tube can be narrowed. Therefore, even if the width | variety of the whole heat exchanger is the same, the direction of the heat exchanger tube which has arrange | positioned in the position which mutually shifted the convex parts can be arrange | positioned more. Therefore, the area of contact with the wind increases as a whole, and the efficiency of heat exchange can be improved. Moreover, it becomes difficult for dew condensation water to stay on a convex part, and it can flow smoothly below.

  The convex portion is preferably formed continuously in the tube axis direction of the heat transfer tube. According to this configuration, since the convex portion is formed from one end side to the other end side of the heat transfer tube, the condensed water attached to the convex portion flows smoothly downward along the convex portion. Therefore, since dew condensation water does not stay on a convex part, even if it uses a heat exchanger in the place where ambient temperature is low, for example, the outdoor of a winter season etc., frost formation can be controlled. Therefore, the heat exchanger can reduce the number of defrosting operations. Moreover, since dew condensation water does not stay, it does not fly toward the leeward by the wind flowing between the heat transfer tubes.

  When the convex portions are located at opposite positions, the gap through which the wind flows becomes narrow at the convex portions, so that the change in the width in the wind flow direction becomes severe. For this reason, the wind stays at the portion where the air passage becomes narrow, that is, the convex portion, and the flow is inhibited. Therefore, it is preferable to arrange the convex portions facing each other in a staggered manner along the direction in which the wind flows. With this configuration, the width in the wind flow direction can always be set to an interval that does not impede the wind flow, that is, a substantially constant interval. Thereby, since a wind flows smoothly, without staying in a convex part, the efficiency of heat exchange can be improved.

  A header pipe on the refrigerant inflow side and a header pipe on the refrigerant outflow side arranged so that the pipe axis directions are parallel, and a plurality of flat shapes arranged in a direction orthogonal to the two header pipes and through which the refrigerant passes. The heat transfer tubes are arranged in a line at intervals along the tube axis direction of the header tube so as to allow wind to pass, and the heat transfer tubes have at least one end in the direction in which the wind passes. A fin-like convex portion is formed which protrudes in the direction in which wind passes through the portion and extends along the tube axis direction of the heat transfer tube.

  Since the convex part protrudes along the direction in which the wind flows, the wind does not disturb the flow by the convex part. Therefore, for example, compared with the case where the convex portion protrudes in a direction orthogonal to the air flow direction, the area where the wind hits the convex portion is narrowed, and therefore noise generated by hitting the convex portion can be suppressed. Moreover, it becomes difficult for dew condensation water to stay on a convex part, and it can flow smoothly below.

  The convex portion is preferably formed continuously in the tube axis direction of the heat transfer tube. According to this configuration, since the wind flows along the convex portion, the area hit by the convex portion protruding perpendicularly to the direction of the wind flow becomes larger. Therefore, the efficiency of heat exchange can be improved. Moreover, since the convex part is formed from the one end side of a heat exchanger tube to the other end side, the dew condensation water adhering to a convex part flows along the convex part smoothly toward the downward direction. Therefore, since dew condensation water does not stay on a convex part, even if it uses a heat exchanger in the place where ambient temperature is low, for example, the outdoor of a winter season etc., frost formation can be controlled. Therefore, the heat exchanger can reduce the number of defrosting operations. Moreover, since dew condensation water does not stay, it does not fly toward the leeward by the wind flowing between the heat transfer tubes.

  The convex portion is characterized in that the cross section is formed in a wave shape in order to increase the contact area with the wind. With this configuration, the distance that the wind flows along the convex portion is increased, so that the efficiency of heat exchange is improved.

  The heat transfer tubes are inserted and connected to the respective header tubes, and the convex portions are arranged close to the end portions of the heat transfer tubes so that the end portions of the heat transfer tubes can be inserted into the two header tubes with a predetermined length. It is preferable to form.

  The heat transfer tube removes the convex portion from the end portion on the insertion side to the inserted portion according to the length inserted into each header tube. When the heat transfer tube is inserted, the convex portion from which the end portion has been removed is caught by the insertion opening formed in both header tubes and becomes a stopper. Thereby, the heat transfer tube can be inserted into the header tube by a predetermined length. Further, since the convex portion is removed from the surface of the heat transfer tube inserted into the header tube, the size of the insertion port of the header tube into which the heat transfer tube is inserted may be formed to the size of the main body portion of the heat transfer tube, The insertion port can be easily formed.

  As described above, in the present invention, since the convex portion that is continuous along the tube axis direction of the heat transfer tube is provided, the condensed water does not accumulate in the convex portion and flows smoothly downward. Moreover, since each convex part is arrange | positioned in the position shifted | deviated between the convex parts which face each other, the space | interval of adjacent heat exchanger tubes can be narrowed, it becomes possible to arrange | position more heat exchanger tubes, and heat exchange. Efficiency can be improved.

  Moreover, since the convex part protrudes along the flow direction of the wind, the flow of the wind is not hindered. For this reason, since the area where the wind hits the convex portion is reduced, noise can be made quieter than in the case where the convex portion is protruded in a direction perpendicular to the flow direction of the wind.

[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. The heat exchanger of this invention is used for the heat exchanger (evaporator, condenser) which comprises refrigeration cycles, such as an air conditioner and a refrigerator. As shown in FIG. 1, the heat exchanger includes a refrigerant inflow side header pipe 1 and a refrigerant outflow side header pipe 2 formed of a cylindrical hollow body with the longitudinal direction horizontal, and a refrigerant inflow side header pipe 1. Are inserted and connected in the vertical direction between the refrigerant outlet header pipe 2 and the refrigerant outlet header pipe 2 so that the wind passes in a direction perpendicular to the longitudinal direction of the refrigerant inlet header pipe 1 and the refrigerant outlet header pipe 2 in a row. And a plurality of heat transfer tubes 3 arranged.

  Note that the refrigerant flow may be reversed in the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2 during cooling and heating. That is, the refrigerant flows in from the refrigerant outflow side header pipe 2, passes through the heat transfer pipe 3, and flows out from the refrigerant inflow side header pipe 1. In this embodiment, in order to make the explanation easy to understand, the inflow header is configured to be on the upper side when functioning as a condenser, and the header provided at the upper portion is provided at the refrigerant inflow side header pipe 1 and the lower portion. The header will be described as the refrigerant outflow side header pipe 2.

  As shown in FIG. 2, the refrigerant inflow header pipe 1 and the refrigerant outflow header pipe 2 are aluminum pipes formed by rolling an aluminum plate member into a cylindrical shape and seam welding the joint surfaces. The refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2 are arranged such that the pipe axes thereof are parallel to each other, the refrigerant inflow side header pipe 1 is arranged at the upper end side, and the refrigerant outflow side header pipe 2 is arranged at the lower end side. One end side of each of the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2 is closed, and the refrigerant inflow / outflow pipe 4 is connected to the other end side by brazing, screw fitting or the like. The inner diameters of the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2 are such that the end of a flat heat transfer pipe 3 described later is inserted into the refrigerant inflow side header pipe 1, the refrigerant outflow side header pipe 2, and the heat transfer pipe 3. The size in which the refrigerant can circulate between them, specifically, the width of the heat transfer tube 3 (the direction in which the wind flows) is formed larger.

  On the surfaces of the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2, an insertion port 6 into which the heat transfer pipe 3 is inserted is formed. The insertion ports 6 are formed in a line along the tube axis direction of both header tubes 1 and 2. The heat transfer tubes 3 are connected by being inserted into the insertion port 6. The insertion port 6 is brazed after the heat transfer tube 3 is inserted in order to prevent the occurrence of refrigerant leakage.

  As shown in FIG. 3, the heat transfer tube 3 is a flat aluminum tube formed by extrusion, and a plurality of flow passages 7 communicating from one end to the other end are formed therein. A refrigerant flows through each flow passage 7.

  On the surface of the heat transfer tube 3, a plurality of convex portions 8 having a semicircular cross section projecting toward the adjacent heat transfer tube 3 side are formed. By making the cross section of the convex portion 8 a semicircular shape, even if the convex portion 8 is formed so as to protrude in a direction orthogonal to the air flow direction, it is possible to make it difficult to inhibit the flow of wind.

  Each convex portion 8 is formed continuously from one end side to the other end side of the heat transfer tube 3 along the tube axis direction of the heat transfer tube 3. As shown in FIG. 3, the convex portions 8 are arranged in a staggered manner along the direction in which the wind flows. Thereby, for example, as shown in FIG. 4, when the plurality of heat transfer tubes 3 are arranged in parallel, the convex portions 8 facing each other are displaced from each other. Specifically, the convex portion 8 is arranged such that the convex portion D is located between the convex portion A and the convex portion B, and the convex portion E is located between the convex portion B and the convex portion C.

  According to the said structure, compared with the case where the heat exchanger tube 10 in which the convex part 9 which faces each other was arrange | positioned in the same position as shown in FIG. 5 was arranged in parallel, the space | interval between heat exchanger tubes 3 can be narrowed. Therefore, even if the width h of the heat exchanger is the same, more heat transfer tubes 3 can be provided than when the heat transfer tubes 10 having the convex portions 9 facing each other arranged at the same position are arranged in parallel. Further, since the wind passes between the heat transfer tubes 3 in a zigzag manner, the contact efficiency with the heat transfer tubes 3 is improved, and the efficiency of the heat exchange effect is improved.

  Further, the convex portion 8 is formed up to the vicinity of the end portion of the heat transfer tube 3. Specifically, when the end portion of the heat transfer tube 3 is inserted into the refrigerant inflow side header tube 1 and the refrigerant outflow side header tube 2, the end portion is placed inside the refrigerant inflow side header tube 1 and the refrigerant outflow side header tube 2. The convex portion 8 is cut and polished from the surface of the heat transfer tube 3 so as to reach the circulating refrigerant. As a result, when inserted into the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2, the end surface of the convex portion 8 cut and polished on the end portion side of the heat transfer tube 3 is hooked on the insertion port 6 and becomes a stopper. Therefore, the heat transfer pipe 3 can be inserted into the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2 by a predetermined length.

  Further, the convex portion 8 near the end of the heat transfer tube 3 is cut and polished from the surface of the heat transfer tube 3 so that the end of the heat transfer tube 3 is inserted into the refrigerant inflow side header tube 1 and the refrigerant outflow side header tube 2. At this time, the convex portion 8 is not inserted into the refrigerant inflow side header pipe 1 and the refrigerant outflow side header pipe 2. Therefore, since the insertion port 6 should just form the insertion port 6 in the magnitude | size of the main-body part of the heat exchanger tube 3, ie, a flat shape, formation of the insertion port 6 becomes easy.

[Second Embodiment]
Next, a second embodiment will be described with reference to FIGS.

  The heat exchanger of 2nd Embodiment differs in the position in which the convex part 12 of the heat exchanger tube 11 is formed compared with 1st Embodiment. Specifically, the convex portion 12 is formed in a fin shape in the side surface side of the flat heat transfer tube 11 along the tube axis direction of the heat transfer tube 11. Other configurations are the same as the configuration of the heat exchanger of the first embodiment.

  According to the said structure, since the convex part 12 protrudes in the direction where a wind flows, the area which a wind and the heat exchanger tube 11 contact increases, Therefore The efficiency of heat exchange can be improved.

  By the way, in order to expand the contact area between the wind and the heat transfer tube 3, a method of increasing the width of the heat transfer tube 13 is also conceivable. However, it is the same as the width of the heat transfer tube 11 when a fin-like convex portion is attached to the heat transfer tube 11. When the width of the heat transfer tube 13 is widened so as to be wide, the diameters of the refrigerant inflow side header tube 1 and the refrigerant outflow side header tube 2 into which the heat transfer tube 13 is inserted are shown in FIG. It is necessary to change the diameter of the header pipe shown in FIG. However, when the convex portion 12 is provided on the side surface of the heat transfer tube 11 so as to protrude in the wind flow direction as in the present invention, the convex portion 12 in the vicinity of the end portion of the heat transfer tube 11 is disposed on the surface of the heat transfer tube 11. Is cut and polished so that the convex portion 12 of the heat transfer tube 13 is not inserted into the refrigerant inflow side header tube 1 and the refrigerant outflow side header tube 2, so that the refrigerant inflow side header tube 1 and the refrigerant outflow are inserted. As the diameter of the side header pipe 2, the diameter of the header pipe shown in FIG. 8A can be used. Furthermore, the insertion port 6 can be easily formed.

  Moreover, the convex part 12 protrudes along the direction through which a wind flows. Therefore, it is possible to prevent wind noise generated when the wind passes through the convex portion 12 as compared with the case where the wind projects in a direction orthogonal to the wind flow direction.

  In addition, this invention is not limited to the said embodiment, Of course, many corrections and changes can be added to the said embodiment within the scope of the present invention. For example, the convex portion is not limited to a semicircular cross section, and may be a quadrangular shape or a triangular shape.

  Since the convex portion is formed continuously from one end side of the heat transfer tube to the other end side along the tube axis direction of the heat transfer tube, the flow passage formed in the heat transfer tube is formed so as to pass inside the convex portion. May be. In this way, the thickness of the convex portion becomes thinner than when no flow passage is provided inside the convex portion, so that the heat exchange efficiency can be improved.

  In the present invention, the convex portion is formed continuously from one end of the heat transfer tube to the other end, but is not particularly limited thereto. You may divide | segment a continuous convex part into plurality. Specifically, a part of the convex portion is cut or cut to be divided into a plurality at predetermined intervals. In this case, the flow path formed in the heat transfer tube is not formed inside the convex portion. Thereby, since the area which a heat exchanger tube contacts with a wind increases, heat exchange efficiency can further improve.

  A plurality of hemispherical convex portions may be provided. In this case, it is necessary to prevent the convex portions facing each other from overlapping each other. Instead of the hemispherical convex shape, the convex shape may be a square shape or a triangular shape.

  As the heat transfer tube, it is preferable to use a heat transfer tube formed so that the surface facing the adjacent heat transfer tube is flat when the heat transfer tubes are arranged in a line, but the facing surface such as an oval shape or an elliptical shape is used. A shape with some swelling may be sufficient.

  When the convex portion is projected along the wind flow direction, the convex portion 14 may be formed in a wave shape in cross section as shown in FIG. According to this structure, even if the width | variety of the heat exchanger tube 15 whole is the same, the area which a wind contacts can be increased. In addition, in this case, since the wind flows along the wave-shaped convex portion 14, the flow of the wind is hardly hindered. Therefore, the efficiency of heat exchange can be improved while suppressing noise.

The whole front view of the heat exchanger concerning a 1st embodiment of the present invention. 1 is a schematic perspective view of a heat exchanger according to a first embodiment. 1 is a schematic perspective view of a heat transfer tube according to a first embodiment. Plan sectional drawing when arranging a plurality of heat transfer tubes according to the first embodiment in parallel Plan sectional drawing of arrangement of other heat exchanger tubes for comparison with the arrangement of heat exchanger tubes shown in FIG. Schematic perspective view of a heat exchanger according to the second embodiment Plan sectional drawing when arranging a plurality of heat transfer tubes according to the second embodiment in parallel It is front sectional drawing of the heat exchanger tube which concerns on 2nd Embodiment, (a) is the heat exchanger tube and header tube of this invention, (b) is a figure which shows the heat exchanger tube and header tube which extended the width | variety of the longitudinal surface. Plan sectional view when multiple heat transfer tubes with convex portions of other shapes are arranged in parallel

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigerant inflow side header pipe 2 Refrigerant outflow side header pipe 3 Heat transfer pipe 4 Refrigerant inflow / outlet pipe 6 Insertion port 7 Flow path 8 Convex part 9 Convex part 10 Heat transfer pipe 11 Heat transfer pipe 12 Convex part 13 Heat transfer pipe 14 Convex part 15 Heat transfer pipe

Claims (7)

A header pipe on the refrigerant inflow side and a header pipe on the refrigerant outflow side arranged so that the pipe axis directions are parallel, and a plurality of flat shapes arranged in a direction orthogonal to the two header pipes and through which the refrigerant passes. With heat transfer tubes,
The heat transfer tubes are arranged in a row at intervals so that wind passes along the tube axis direction of the header tube,
Each of the heat transfer tubes protrudes toward the adjacent heat transfer tube, and a convex portion is formed along the tube axis direction of the heat transfer tube,
The said convex part is arrange | positioned in the position which shifted | deviated from the convex part which each faces, The heat exchanger characterized by the above-mentioned. The heat exchanger according to claim 1, wherein the convex portion is formed continuously in the tube axis direction of the heat transfer tube. The heat exchanger according to claim 1, wherein the convex portions facing each other are arranged in a staggered manner in a direction in which the wind passes. A header pipe on the refrigerant inflow side and a header pipe on the refrigerant outflow side arranged so that the pipe axis directions are parallel, and a plurality of flat shapes arranged in a direction orthogonal to the two header pipes and through which the refrigerant passes. With heat transfer tubes,
The heat transfer tubes are arranged in a row at intervals so that wind passes along the tube axis direction of the header tube,
The heat exchanger is characterized in that a fin-like convex portion is formed along the tube axis direction of the heat transfer tube so as to protrude in at least one end portion in the direction in which the wind passes. The heat exchanger according to claim 4, wherein the convex portion is formed continuously in the tube axis direction of the heat transfer tube. 6. The heat exchanger according to claim 4, wherein the convex portion is formed in a wave shape in order to increase a contact area with the wind. The heat transfer tube is inserted and connected to the insertion port formed in each header tube,
The convex portion is formed so as to be close to the end portion of the heat transfer tube so that the end portion of the heat transfer tube can be inserted into the two header tubes with a predetermined length. The heat exchanger in any one of.

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