JP2005233512A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce pressure loss and prevent the deterioration with lapse of time, of heat transfer performance caused by accumulation of dust, frost formation and the like. <P>SOLUTION: In this heat exchanger wherein a flat fin 11 is mounted on a heat transfer pipe 10 in which a refrigerant is passed, a wing part 12 gradually narrowed toward an upstream side, is formed on the upstream side of the heat transfer pipe 10 of the flat fin 11, and the heat exchange is performed between the air flowing along the flat fin 11 and the refrigerant in such a state that the longitudinal vortex is generated in the air passing through the wing part 12, the wing part 12 has a first wing constitution part 12a gradually narrowed with a first reduction rate, and a second wing constitution part 12b gradually narrowed at an upstream side of the first wing constitution part 12a, with a second reduction rate different from the first reduction rate. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a heat exchanger, for example, a fin-and-tube heat exchanger applied to a vending machine, a showcase, and the like.

  As shown in FIG. 14 and FIG. 15, conventionally, a plurality of flat plate fins 1 arranged in parallel at a predetermined interval and a heat transfer tube 2 that passes through the flat plate fin 1 and in which a refrigerant circulates are provided. There is known a so-called fin-and-tube heat exchanger in which heat is exchanged between the air and the refrigerant.

  In this fin-and-tube heat exchanger, in order to improve heat exchange performance, there are various types of flat plate fins 1 in which minute cuts 3 called so-called louvers are formed between the heat transfer tubes 2 and 2. It has been proposed (see Patent Document 1 and Patent Document 2).

JP-A-11-281279 JP 2001-141383 A

  By the way, the flat plate fin 1 formed with such a cut and raised 3 has high efficiency, but turbulent air on the surface of the cut and raised 3 increases the frictional resistance and increases the pressure loss. is there. In addition, heat transfer performance may deteriorate over time due to dust accumulation and frost formation.

  In view of the above circumstances, an object of the present invention is to provide a heat exchanger that has little pressure loss and suppresses deterioration with time of heat transfer performance due to dust accumulation and frost formation.

  In order to achieve the above object, a heat exchanger according to claim 1 of the present invention is provided with a flat fin on a heat transfer tube through which a refrigerant passes, and upstream of a portion of the flat fin on the upstream side of the heat transfer tube. Heat exchange that forms a wing that gradually narrows toward the side, and exchanges heat between the air flowing along the plate fins and the refrigerant in a state where longitudinal vortices are generated in the air passing through the wing The wing portion includes a first wing component that gradually narrows at a first reduction rate, and a second reduction that differs from the first reduction rate upstream of the first wing component. It has the 2nd wing | blade structure part which becomes gradually narrow at a rate, It is characterized by the above-mentioned.

  A heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect, wherein the first reduction rate is higher than the second reduction rate in the aspect in which the first reduction rate is larger than the second reduction rate. A two-wing component is configured.

  In the heat exchanger according to claim 3 of the present invention, a flat fin is provided on the heat transfer tube through which the refrigerant passes, and the width of the flat fin is gradually narrowed toward the upstream side in the upstream side of the heat transfer tube. A heat exchanger that exchanges heat between the air flowing along the flat fins and the refrigerant in a state where a vertical vortex is generated in the air passing through the wing, An auxiliary vane portion that gradually narrows toward the upstream side and generates a vertical vortex at a position different from the blade portion is provided between the heat transfer tube and the heat transfer tube.

  Further, the heat exchanger according to claim 4 of the present invention is characterized in that, in the above-described claim 3, the auxiliary wing portion has at least a top portion located on the upstream side in the formation region of the wing portion. To do.

  The heat exchanger according to claim 5 of the present invention is characterized in that, in the above-described claim 3, the auxiliary wing portion is formed by cutting up the formation region of the wing portion.

  A heat exchanger according to claim 6 of the present invention is characterized in that, in the above-described claim 3, the auxiliary blade portion is formed in a mode having an angle of attack different from that of the blade portion.

  A heat exchanger according to a seventh aspect of the present invention is the heat exchanger according to the third aspect, wherein the wing portion is formed by cutting and raising the flat plate fin on one surface side, while the flat plate fin is on the other surface side. The auxiliary wing portion is formed by cutting and raising.

  In the heat exchanger according to claim 8 of the present invention, a flat fin is provided on the heat transfer tube through which the refrigerant passes, and the width of the flat fin is gradually narrowed toward the upstream side in the upstream side of the heat transfer tube. A heat exchanger for exchanging heat between the air flowing along the plate fins and the refrigerant in a state in which a vertical vortex is generated in the air passing through the wing portion. The wing portion is formed in such a manner that a blade leading edge facing the air flowing along the fin is continuous with the surface of the flat plate fin.

  A heat exchanger according to a ninth aspect of the present invention is the heat exchanger according to the eighth aspect, wherein the flat plate fin bulges to one surface side with the downstream side edge close to the heat transfer tube as an open end. Thus, a wing portion having two guide surfaces inclined with respect to the flat plate fin is formed.

  A heat exchanger according to a tenth aspect of the present invention is the heat exchanger according to the first, third, or eighth aspect described above, wherein the air flowing along the flat plate fins is caused to flow downstream from the blade portion on the downstream side of the heat transfer tube. A small wing portion for attracting the region is formed.

  According to the heat exchangers of the first and second aspects of the present invention, the flat fins are provided in the heat transfer tubes through which the refrigerant passes, and the plate fins are gradually moved upstream toward the upstream side of the heat transfer tubes. A narrow wing is formed, and heat exchange is performed between the air flowing along the plate fins and the refrigerant in a state where longitudinal vortices are generated in the air passing through the wing. The temperature boundary layer on the surface of the flat fin is thinned by the spiral vortex generated on the surface of the flat fin, and the heat transfer effect can be promoted. Moreover, since the wing | blade part for generating a vertical vortex can keep pressure loss small, without interrupting the flow of air, it becomes possible to suppress generation | occurrence | production of dust accumulation and frost formation. Further, as the wing part, a first wing component that gradually narrows at the first reduction rate, and a gradual width at a second reduction rate that is different from the first reduction rate on the upstream side of the first wing component. Since what has the 2nd wing | blade structure part which becomes narrow is applied, a vertical vortex will generate | occur | produce in a mutually different area | region from each wing | blade structure part, and the effect mentioned above becomes still more remarkable.

  Moreover, according to the heat exchanger which concerns on Claims 3-7 of this invention, while providing a flat plate fin in the heat exchanger tube which a refrigerant | coolant passes through an inside, it directs upstream in the site | part used as the upstream side of a heat exchanger tube in a flat plate fin. In this way, a wing part that gradually becomes narrower is formed, and heat exchange is performed between the air flowing along the flat plate fin and the refrigerant in a state where a longitudinal vortex is generated in the air passing through the wing part. The temperature boundary layer on the surface of the flat plate fin is thinned by the spiral vortex generated on the surface of the flat plate fin, and the heat transfer effect can be promoted. Moreover, since the wing | blade part for generating a vertical vortex can keep pressure loss small, without interrupting the flow of air, it becomes possible to suppress generation | occurrence | production of dust accumulation and frost formation. Furthermore, since an auxiliary wing portion is provided between the wing portion and the heat transfer tube, the width gradually decreases toward the upstream side, and a vertical vortex is generated at a position different from the wing portion. Longitudinal vortices are generated, and the above-described effects become more remarkable.

  According to the heat exchanger according to claims 8 and 9 of the present invention, a flat fin is provided on the heat transfer tube through which the refrigerant passes, and the upstream portion of the flat fin is located upstream of the heat transfer tube. In this way, a wing part that gradually becomes narrower is formed, and heat exchange is performed between the air flowing along the flat plate fin and the refrigerant in a state where a longitudinal vortex is generated in the air passing through the wing part. The temperature boundary layer on the surface of the flat plate fin is thinned by the spiral vortex generated on the surface of the flat plate fin, and the heat transfer effect can be promoted. Moreover, since the wing | blade part for generating a vertical vortex can keep pressure loss small, without interrupting the flow of air, it becomes possible to suppress generation | occurrence | production of dust accumulation and frost formation. In particular, since the blade leading edge that faces the air flowing along the flat fins is formed to be continuous with the surface of the flat fins, the resistance to the air flow should be further reduced. Can do.

  Further, according to the heat exchanger according to claim 10 of the present invention, the small blade portion for drawing the air flowing along the flat plate fin to the downstream side region of the heat transfer tube is formed in a portion downstream of the blade portion. Therefore, it becomes possible to reduce the dead water region at the downstream side of the heat transfer tube.

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

(Embodiment 1)
1 and 2 show a heat exchanger according to Embodiment 1 of the present invention. The heat exchanger exemplified here is used, for example, as an evaporator or a condenser of a refrigerator applied to a vending machine or a showcase, and similarly to the one shown in FIGS. 14 and 15, the heat transfer tube 10. This is called a fin and tube type in which a plurality of flat plate fins 11 are provided.

  The heat transfer tube 10 is, for example, a copper cylindrical tube, and is configured so that a refrigerant circulates therein. The heat transfer tubes 10 are arranged in a zigzag pattern in three rows in an evaporator or a condenser by being appropriately bent.

  The flat fins 11 are formed in a rectangular flat plate shape using a thin steel plate. These flat fins 11 are provided in such a manner that they are parallel to each other with a predetermined distance between them and the heat transfer tube 10 passes therethrough. The heat transfer tube 10 and the flat fin 11 are in close contact with each other over the entire circumference. In the conventional heat exchanger, it is general to punch the steel plate having a thickness of 0.5 mm or less to constitute the flat fin 11, but in the first embodiment, it has a thickness of 0.3 mm. A flat plate fin 11 is formed by punching a steel plate. The surface of the flat fin 11 is preferably subjected to a hydrophilic treatment as appropriate, such as a bamate treatment or a water-repellent coating.

  These flat fins 11 are formed with a plurality of wing parts 12 on one edge. The wing parts 12 are formed in a flat plate shape by raising the flat plate fins 11 so as to have the same size, the same shape, and the same angle of attack α1, and each of them has the first wing component part 12a and the first wing part 12a. 2 wing component 12b. The first wing component 12a is configured to gradually narrow in an isosceles triangle shape with a relatively large reduction rate (hereinafter referred to as "first reduction rate") toward one edge of the flat plate fin 11. It is the part which did. The second blade component 12b continues from the portion located on the one edge side that is the narrowest in the first blade component 12a to the first blade component 12a and is smaller than the first reduction rate. This is a portion configured to gradually narrow in an isosceles triangle shape at a rate (hereinafter referred to as “second reduction rate”). Each blade 12 has a vertical line (hereinafter referred to as “blade center line C”) extending from the center of the heat transfer tube 10 toward one edge of the plate fin 11 to determine the apex angle of the second blade component 12b. It passes through and is disposed at a position where the blade center line C is a symmetrical axis.

  In the heat exchanger configured as described above, for example, a blower fan (not shown) is arranged on one edge side of the flat fin 11, and the refrigerant is passed through the heat transfer tube 10 and the blower fan (not shown). When air is blown from one edge of the flat fin 11, the air flowing along the flat fin 11 and the refrigerant passing through the heat transfer tube 10 exchange heat through the flat fin 11 and the heat transfer tube 10. Thus, heat can be absorbed in the evaporator, while heat can be dissipated in the condenser.

  At this time, according to this heat exchanger, when the air flowing along the flat plate fins 11 passes through the two inclined blade leading edges 12bb of the second blade component 12b, a pair of longitudinal vortices (hereinafter referred to as “secondary vortex”). The vertical vortex S12 ") and a pair of vertical vortices (hereinafter referred to as" first vertical vortex S11 ") when passing through the two inclined blade leading edges 12aa of the first blade component 12a. More specifically, the second vertical vortex S12 generated by the second blade component 12b is generated so as to rotate from the portion close to the blade center line C to the outside of the blade 12, and the second vortex S12 generated by the first blade component 12a. The 1 vertical vortex S11 is generated so as to rotate inward from the blade center line C to the inside of the wing portion 12 from a portion separated from the second vertical vortex S12.

  The second vertical vortex S12 and the first vertical vortex S11 act so as to blow air down on the surface of the flat fin 11, respectively, and the temperature boundary layer on the surface becomes thin, so that the heat transfer effect can be promoted. Thus, the heat transfer performance of the heat exchanger can be improved. Further, the second vertical vortex S12 and the first vertical vortex S11 reaching the heat transfer tube 10 become strong and strong by interfering with the horseshoe vortex H generated at the root portion of the heat transfer tube 10, and thus the heat transfer tube As a result, the temperature boundary layer around the heat transfer tube 10 can be reduced, and the dead water region on the downstream side can be suppressed to promote the heat transfer effect. In addition, the wing portion 12 for generating the second vertical vortex S12 and the first vertical vortex S11 can keep the pressure loss small without interrupting the air flow. Occurrence can be suppressed. When the surface of the flat fin 11 is subjected to a hydrophilic process such as a bamate process or a water-repellent coating, frosting will not occur even if moisture containing air collides with the wing part 12. .

  Further, as the wing part 12, a first wing component 12a that gradually narrows at the first reduction rate, and a second reduction rate that is different from the first reduction rate on the upstream side of the first wing component 12a. Therefore, the vertical vortices S11 and S12 are generated in different regions from the respective blade constituent portions 12a and 12b. This effect becomes more prominent.

  In the first embodiment described above, the reduction rate for narrowing the second blade component 12b is set to be smaller than that of the first blade component 12a, but the second blade component 12b and the first blade configuration are set. It is sufficient if the width reduction rate is different from that of the portion 12a. For example, even if the reduction rate is set in the opposite manner, the same effect can be expected.

  Moreover, in Embodiment 1 mentioned above, although the wing | blade part 12 is comprised by raising the flat plate fin 11, it seems to comprise the wing | blade part 12 in the aspect protruded from the fin front edge 11a of the flat plate fin 11. FIG. Anyway.

(Embodiment 2)
3 and 4 show a heat exchanger according to Embodiment 2 of the present invention. Similarly to the first embodiment, the heat exchanger exemplified here is used as an evaporator or a condenser of a refrigerator applied to, for example, a vending machine or a showcase. The first embodiment is a flat fin. Only the form is different.

  That is, in the heat exchanger of the second embodiment, the first winglet portion 14 or the second winglet portion 15 that is paired with each other is formed in a portion of the flat plate fin 11 that is downstream of the wing portion 12. More specifically, the first winglet portion 14 and the second winglet portion 15 are formed by cutting up a portion that is obliquely rearward of each heat transfer tube 10 when the flat fin 11 is viewed from one edge. It is. Each of the small wing portions 14 and 15 is configured in a triangular shape so that the height gradually decreases toward one edge portion of the flat plate fin 11.

  The first winglet portion 14 and the second winglet portion 15 that form a pair extend from the center of the heat transfer tube 10 toward one edge of the plate fin 11 (hereinafter referred to as “blade centerline C”). With respect to the right and left. Among these, the first small wing portion 14 is inclined and arranged with an inclination angle β1 so that the distance between the first wing portion 14 gradually decreases toward one edge of the flat plate fin 11. The second small wing portion 15 is inclined with an inclination angle β2 so that the distance between the second wing portion 15 gradually increases toward one edge of the flat fin 11.

  Other configurations are the same as those of the first embodiment, and the same reference numerals are given and detailed descriptions thereof are omitted.

  In the heat exchanger configured as described above, for example, a blower fan (not shown) is arranged on one edge side of the flat fin 11, and the refrigerant is passed through the heat transfer tube 10 and the blower fan (not shown). When air is blown from one edge of the flat fin 11, the air flowing along the flat fin 11 and the refrigerant passing through the heat transfer tube 10 exchange heat through the flat fin 11 and the heat transfer tube 10. Thus, heat can be absorbed in the evaporator, while heat can be dissipated in the condenser.

  At this time, according to this heat exchanger, when the air flowing along the flat plate fins 11 passes through the two inclined blade leading edges 12bb of the second blade component 12b, a pair of longitudinal vortices (hereinafter referred to as “secondary vortex”). The vertical vortex S12 ") and a pair of vertical vortices (hereinafter referred to as" first vertical vortex S11 ") when passing through the two inclined blade leading edges 12aa of the first blade component 12a. More specifically, the second vertical vortex S12 generated by the second blade component 12b is generated so as to rotate from the portion close to the blade center line C to the outside of the blade 12, and the second vortex S12 generated by the first blade component 12a. The 1 vertical vortex S11 is generated so as to rotate inward from the blade center line C to the inside of the wing portion 12 from a portion separated from the second vertical vortex S12.

  The second vertical vortex S12 and the first vertical vortex S11 act so as to blow air down on the surface of the flat fin 11, respectively, and the temperature boundary layer on the surface becomes thin, so that the heat transfer effect can be promoted. Thus, the heat transfer performance of the heat exchanger can be improved. Further, the second vertical vortex S12 and the first vertical vortex S11 reaching the heat transfer tube 10 become strong and strong by interfering with the horseshoe vortex H generated at the root portion of the heat transfer tube 10, and thus the heat transfer tube As a result, the temperature boundary layer around the heat transfer tube 10 can be reduced, and the dead water region on the downstream side can be suppressed to promote the heat transfer effect. In addition, the wing portion 12 for generating the second vertical vortex S12 and the first vertical vortex S11 can keep the pressure loss small without interrupting the air flow. Occurrence can be suppressed. Similarly to the first embodiment, if the surface of the flat fin 11 is subjected to a hydrophilic process such as a bomate process or a water-repellent coating, it will adhere even if moisture containing air collides with the wing 12. No frosting.

  Further, as the wing part 12, a first wing component 12a that gradually narrows at the first reduction rate, and a second reduction rate that is different from the first reduction rate on the upstream side of the first wing component 12a. Therefore, the vertical vortices S11 and S12 are generated in different regions from the respective blade constituent portions 12a and 12b. This effect becomes more prominent.

  Still further, according to the above heat exchanger, the first winglet portion 14 and the second winglet are formed by raising a portion that is obliquely rearward of each heat transfer tube 10 when the flat fin 11 is viewed from one edge. Since the portion 15 is formed, the air flowing along the flat plate fins 11 is attracted to the downstream region of the heat transfer tube 10. More specifically, in the first winglet portion 14, a strong swirl component deflected toward the tip side of the first winglet portion 14 is generated in the air traversing the first winglet portion 14. 10 will be drawn to the downstream area. Further, in the second small blade portion 15, the deflection component and the swirl component of the passing air are synchronized, and are drawn to the downstream region of the heat transfer tube 10. As a result, in combination with the effects of the second vertical vortex S12, the first vertical vortex S11, and the horseshoe vortex H described above, the temperature boundary layer around the heat transfer tube 10 can be thinned and the downstream dead water region can be suppressed. Thus, the heat transfer effect can be further promoted.

  In the second embodiment described above, the first winglet portion 14 and the second winglet portion 15 having different inclination angles are formed, but it is not always necessary to form two types of winglet portions. It is sufficient to form one of the small wings.

(Embodiment 3)
5-7 shows the principal part of the heat exchanger which is Embodiment 3 of this invention. Similarly to the first embodiment, the heat exchanger exemplified here is used as an evaporator or a condenser of a refrigerator applied to, for example, a vending machine or a showcase. The first embodiment is a flat fin. Only the form is different.

  That is, in the heat exchanger according to the third embodiment, a plurality of blade portions 22 are formed on one edge portion of the flat plate fin 21, and the auxiliary blade portions 23 are formed in the formation regions of the respective blade portions 22. I have to.

  The wing portion 22 is formed in a flat plate shape by cutting the flat plate fin 21 to one surface side so as to have the same size, the same shape, and the same angle of attack α2. It forms an isosceles triangle shape that becomes gradually narrower toward the edge of. Each blade 22 has a perpendicular (hereinafter referred to as “blade center line C”) extending from the center of the heat transfer tube 10 toward one edge of the flat plate fin 21 passing through the apex angle of the blade 22. And this blade center line C is arrange | positioned in the position used as a left-right symmetric axis.

  The auxiliary wing portion 23 is configured to have a flat plate shape by cutting the flat plate fin 21 to the other surface side so as to have the same size, the same shape, and the same angle of attack α3. It forms an isosceles triangle that gradually narrows toward one edge. Each auxiliary wing portion 23 has a similar shape with the same apex angle as the wing portion 22, and is disposed at a position where the wing center line C passes through the apex angle in such a manner that the wing center line C is a bilaterally symmetrical axis. It is. The broken line that cuts the auxiliary wing 23 is at the same position as the broken line that cut and raised the wing 22.

  In addition, about the structure similar to Embodiment 1, the same code | symbol is attached | subjected and each detailed description is abbreviate | omitted.

  In the heat exchanger configured as described above, for example, a blower fan (not shown) is disposed on one edge side of the flat fin 21 to allow the refrigerant to pass through the heat transfer tube 10 and to send a blower fan (not shown). When air is blown from one edge of the flat fin 21, the air flowing along the flat fin 21 and the refrigerant passing through the heat transfer tube 10 exchange heat through the flat fin 21 and the heat transfer tube 10. Thus, heat can be absorbed in the evaporator, while heat can be dissipated in the condenser.

  At that time, according to this heat exchanger, when the air flowing along the flat plate fin 21 passes through the two blade leading edges 22a inclined by the blade portion 22, a pair of vertical vortices S21 are formed. A pair of longitudinal vortices S22 are formed when the two blade leading edges 23a are inclined. More specifically, the vertical vortex S21 generated by the wing portion 22 is generated so as to rotate inward from the portion separated from the blade center line C, and the vertical vortex S22 generated by the auxiliary wing portion 23 is generated by the wing portion 22. It is generated so as to rotate inward of the auxiliary wing part 23 from a portion closer to the blade center line C than the vertical vortex S21.

  The vertical vortex S21 caused by the wing portion 22 acts so as to blow down air on one surface of the flat plate fin 21, and the vertical vortex S22 caused by the auxiliary wing portion 23 blows air down on the other surface of the flat plate fin 21. Since the temperature boundary layer on each surface becomes thin, the heat transfer effect can be promoted, and the heat transfer performance of the heat exchanger can be improved. In addition, the longitudinal vortices S21 and S22 that reach the heat transfer tube 10 become strong and strong by interfering with the horseshoe vortex H generated at the root of the heat transfer tube 10, and therefore also on the downstream side of the heat transfer tube 10. As a result, the temperature boundary layer around the heat transfer tube 10 can be thinned, and the downstream dead water region can be suppressed to promote the heat transfer effect. In addition, the wing part 22 and the auxiliary wing part 23 for generating the vertical vortices S21 and S22 can keep the pressure loss small without interrupting the air flow, so that dust accumulation and frost formation occur. Can be suppressed. Similarly to the first embodiment, if the surface of the flat fin 21 is subjected to a hydrophilic process such as a bomate process or a water-repellent coating, it will adhere even if moisture containing air collides with the wing 22. No frosting.

  Further, since the auxiliary wing portion 23 is provided between the wing portion 22 provided on the flat plate fin 21 and the heat transfer tube 10, the vertical vortex S 22 caused by the auxiliary wing portion 23 is added to the vertical vortex S 21 caused by the wing portion 22. It occurs in different areas, and the above-described effect becomes more remarkable.

  In the third embodiment described above, the auxiliary wing portion 23 is formed in the formation region of the wing portion 22, so that no additional space is required to provide the auxiliary wing portion 23, and the heat exchanger is large-sized. However, it is not always necessary to provide the auxiliary wing portion 23 in the formation region of the wing portion 22, and only a part of the auxiliary wing portion 23, for example, at least the top located on the upstream side of the wing portion 23 You may comprise so that it may be located in the formation area of the part 22. FIG.

  Further, in Embodiment 3 described above, the auxiliary wing part 23 is formed by cutting and raising in a direction different from the wing part 22, but the auxiliary wing part 23 is provided on the same surface side as the wing part 22. Also good. In this case, the wing portion 22 does not necessarily have the angle of attack α2.

  In the above-described third embodiment, the wing portion 22 is configured by cutting and raising the flat plate fin 21. However, the wing portion 22 is configured to protrude from the fin leading edge 21 a of the flat plate fin 21. Anyway.

(Embodiment 4)
8 and 9 show the main part of the heat exchanger according to Embodiment 4 of the present invention. Similarly to the third embodiment, the heat exchanger exemplified here is used as an evaporator or a condenser of a refrigerator applied to, for example, a vending machine or a showcase. The third embodiment is a flat fin. Only the form is different.

  That is, in the heat exchanger of the fourth embodiment, the first winglet portion 24 or the second winglet portion 25 that is paired is formed in a portion of the flat plate fin 21 that is downstream of the wing portion 22. More specifically, the first winglet portion 24 and the second winglet portion 25 are formed by cutting up a portion that is obliquely rearward of each heat transfer tube 10 when the flat fin 21 is viewed from one edge. It is. Each of the small wing portions 24 and 25 is configured in a triangular shape so that the height gradually decreases toward one edge of the flat plate fin 21.

  The first winglet portion 24 and the second winglet portion 25 that form a pair extend from the center of the heat transfer tube 10 toward one edge of the flat plate fin 21 (hereinafter referred to as “blade centerline C”). With respect to the right and left. Among these, the first winglet portion 24 is inclined with an inclination angle β3 so that the distance between the first winglet portion 24 gradually decreases toward one edge of the flat plate fin 21. The second small wing portion 25 is inclined with an inclination angle β4 so that the distance between the second wing portion 25 gradually increases toward one edge of the flat plate fin 21.

  Other configurations are the same as those of the third embodiment, and the same reference numerals are given and detailed descriptions thereof are omitted.

  In the heat exchanger configured as described above, for example, a blower fan (not shown) is disposed on one edge side of the flat fin 21 to allow the refrigerant to pass through the heat transfer tube 10 and to send a blower fan (not shown). When air is blown from one edge of the flat fin 21, the air flowing along the flat fin 21 and the refrigerant passing through the heat transfer tube 10 exchange heat through the flat fin 21 and the heat transfer tube 10. Thus, heat can be absorbed in the evaporator, while heat can be dissipated in the condenser.

  At that time, according to this heat exchanger, when the air flowing along the flat plate fin 21 passes through the two blade leading edges 22a inclined by the blade portion 22, a pair of vertical vortices S21 are formed. A pair of longitudinal vortices S22 are formed when the two blade leading edges 23a are inclined. More specifically, the vertical vortex S21 generated by the wing portion 22 is generated so as to rotate inward from the portion separated from the blade center line C, and the vertical vortex S22 generated by the auxiliary wing portion 23 is generated by the wing portion 22. It is generated so as to rotate inward of the auxiliary wing part 23 from a portion closer to the blade center line C than the vertical vortex S21.

  The vertical vortex S21 caused by the wing portion 22 acts so as to blow down air on one surface of the flat plate fin 21, and the vertical vortex S22 caused by the auxiliary wing portion 23 blows air down on the other surface of the flat plate fin 21. Since the temperature boundary layer on each surface becomes thin, the heat transfer effect can be promoted, and the heat transfer performance of the heat exchanger can be improved. In addition, the longitudinal vortices S21 and S22 that reach the heat transfer tube 10 become strong and strong by interfering with the horseshoe vortex H generated at the root of the heat transfer tube 10, and therefore also on the downstream side of the heat transfer tube 10. As a result, the temperature boundary layer around the heat transfer tube 10 can be thinned, and the downstream dead water region can be suppressed to promote the heat transfer effect. In addition, the wing part 22 and the auxiliary wing part 23 for generating the vertical vortices S21 and S22 can keep the pressure loss small without interrupting the air flow, so that dust accumulation and frost formation occur. Can be suppressed. Similarly to the first embodiment, if the surface of the flat fin 21 is subjected to a hydrophilic process such as a bomate process or a water-repellent coating, it will adhere even if moisture containing air collides with the wing 22. No frosting.

  Further, since the auxiliary wing portion 23 is provided between the wing portion 22 provided on the flat plate fin 21 and the heat transfer tube 10, the vertical vortex S 22 caused by the auxiliary wing portion 23 is added to the vertical vortex S 21 caused by the wing portion 22. It occurs in different areas, and the above-described effect becomes more remarkable.

  Still further, according to the above heat exchanger, the first winglet portion 24 and the second winglet are formed by raising a portion that is obliquely rearward of each heat transfer tube 10 when the flat fin 21 is viewed from one edge. Since the portion 25 is formed, the air flowing along the flat plate fins 21 is attracted to the downstream region of the heat transfer tube 10. More specifically, in the first winglet portion 24, a strong swirling component deflected toward the tip end side of the first winglet portion 24 is generated in the air traversing the first winglet portion 24, so that the air flowing along the flat fins 21 is transferred to the heat transfer tube. 10 will be drawn to the downstream area. Further, in the second small blade portion 25, the deflection component and the swirl component of the passing air are synchronized and attracted to the downstream region of the heat transfer tube 10. As a result, in combination with the effects of the vertical vortex S21, the vertical vortex S22, and the horseshoe vortex H described above, the temperature boundary layer around the heat transfer tube 10 can be thinned, and the dead water region on the downstream side is suppressed to reduce the heat transfer effect. Can be further promoted.

  In the fourth embodiment described above, the first winglet portion 24 and the second winglet portion 25 having different inclination angles are formed, but it is not always necessary to form two types of winglet portions. It is sufficient to form one of the small wings.

(Embodiment 5)
10 and 11 show the main part of the heat exchanger according to the fifth embodiment of the present invention. Similarly to the first embodiment, the heat exchanger exemplified here is used as an evaporator or a condenser of a refrigerator applied to, for example, a vending machine or a showcase. The first embodiment is a flat fin 31. Only the form of the wing part 32 provided on the wing is different.

  That is, in the heat exchanger of the fifth embodiment, the blade portion 32 is formed in such a manner that the blade leading edge portion 32 a facing the air flowing along the flat plate fin 31 is continuous with the surface of the flat plate fin 31. More specifically, one of the flat fins 31 is extended from the center of the heat transfer tube 10 by causing the flat fins 31 to bulge toward one surface side with the downstream edge 32b close to the heat transfer tube 10 being an open end. A triangular pyramid-shaped wing portion 32 having two guide surfaces 32c inclined with respect to the flat plate fin 31 is formed with a perpendicular line (hereinafter referred to as “wing center line C”) extending toward the edge of the plate fin 31 as a ridgeline. Like to do. The guide surfaces 32 c of the wing portions 32 each have a triangular shape that gradually becomes narrower toward one edge of the flat plate fin 31. Each of the wing parts 32 is configured to have the same size, the same shape, and the same angle of attack α4, and has a bilaterally symmetric shape with the wing center line C as the symmetry axis. An isosceles triangular opening is formed in a portion of the blade portion 32 that faces the heat transfer tube 10.

  In addition, about the structure similar to Embodiment 1, the same code | symbol is attached | subjected and each detailed description is abbreviate | omitted.

  In the heat exchanger configured as described above, for example, a blower fan (not shown) is arranged on one edge side of the flat fin 31 to allow the refrigerant to pass through the heat transfer tube 10 and to send a blower fan (not shown). When air is blown from one edge of the flat fin 31, the air flowing along the flat fin 31 and the refrigerant passing through the heat transfer tube 10 exchange heat through the flat fin 31 and the heat transfer tube 10. Thus, heat can be absorbed in the evaporator, while heat can be dissipated in the condenser.

  At this time, according to this heat exchanger, when the air flowing along the flat plate fin 31 passes through the two inclined guide surfaces 32c of the wing 32, the pair of longitudinal vortices rotate outward from the guide surface 32c. S31 is generated.

  The vertical vortex S31 by the wing portion 32 acts to blow down air on one surface of the flat fin 31 and the temperature boundary layer on the surface becomes thin, so that the heat transfer effect can be promoted. It becomes possible to improve the heat transfer performance of the heat exchanger. Further, the vertical vortex S31 reaching the heat transfer tube 10 becomes strong and strong by interfering with the horseshoe-shaped vortex H generated at the base of the heat transfer tube 10, so that the vertical vortex S31 also wraps around the downstream side of the heat transfer tube 10. Thus, the temperature boundary layer around the heat transfer tube 10 can be thinned, and the downstream dead water region can be suppressed to promote the heat transfer effect. Moreover, the wing part 32 for generating the vertical vortex S31 can keep the pressure loss small without interrupting the air flow, and therefore can suppress the accumulation of dust and the formation of frost. Become. In particular, since the blade leading edge portion 32a facing the air flowing along the flat plate fin 31 forms the blade portion 32 in a manner continuous with the surface of the flat plate fin 31, the resistance to the air flow is further reduced. Therefore, it is possible to greatly suppress deterioration with time of heat transfer performance due to dust accumulation, frost formation, and the like. As in the first embodiment, if the surface of the flat fin 31 is subjected to a hydrophilic treatment such as a bomate treatment or a water-repellent coating, it will be attached even if moisture containing air collides with the wing 32. No frosting.

(Embodiment 6)
12 and 13 show the main part of the heat exchanger according to the sixth embodiment of the present invention. Similarly to the fifth embodiment, the heat exchanger exemplified here is used as an evaporator or a condenser of a refrigerator applied to, for example, a vending machine or a showcase. The fifth embodiment is a flat fin. Only the form is different.

  That is, in the heat exchanger according to the sixth embodiment, the first small wing portion 34 or the second small wing portion 35 that is paired with each other is formed in a portion of the flat fin 31 that is downstream of the wing portion 32. More specifically, the first small blade portion 34 and the second small blade portion 35 are formed by cutting up a portion that is obliquely rearward of each heat transfer tube 10 when the flat plate fin 31 is viewed from one edge portion. It is. Each of the small wing portions 34 and 35 is configured in a triangular shape so that the height gradually decreases toward one edge of the flat plate fin 31.

  The first winglet portion 34 and the second winglet portion 35 that form a pair extend from the center of the heat transfer tube 10 toward one edge of the plate fin 31 (hereinafter referred to as “blade centerline C”). With respect to the right and left. Among these, the first small wing portion 34 is inclined with an inclination angle β5 so that the distance between the first wing portion 34 gradually decreases toward one edge of the flat plate fin 31. The second wing portion 35 is inclined with an inclination angle β6 so that the distance between the second wing portions 35 gradually increases toward one edge of the flat plate fin 31.

  Other configurations are the same as those of the fifth embodiment, and the same reference numerals are given and detailed descriptions thereof are omitted.

  In the heat exchanger configured as described above, for example, a blower fan (not shown) is arranged on one edge side of the flat fin 31 to allow the refrigerant to pass through the heat transfer tube 10 and to send a blower fan (not shown). When air is blown from one edge of the flat fin 31, the air flowing along the flat fin 31 and the refrigerant passing through the heat transfer tube 10 exchange heat through the flat fin 31 and the heat transfer tube 10. Thus, heat can be absorbed in the evaporator, while heat can be dissipated in the condenser.

  At this time, according to this heat exchanger, when the air flowing along the flat plate fin 31 passes through the two inclined guide surfaces 32c of the wing 32, the pair of longitudinal vortices rotate outward from the guide surface 32c. S31 is generated.

  The vertical vortex S31 by the wing portion 32 acts to blow down air on one surface of the flat fin 31 and the temperature boundary layer on the surface becomes thin, so that the heat transfer effect can be promoted. It becomes possible to improve the heat transfer performance of the heat exchanger. Further, the vertical vortex S31 reaching the heat transfer tube 10 becomes strong and strong by interfering with the horseshoe-shaped vortex H generated at the base of the heat transfer tube 10, so that the vertical vortex S31 also wraps around the downstream side of the heat transfer tube 10. Thus, the temperature boundary layer around the heat transfer tube 10 can be thinned, and the downstream dead water region can be suppressed to promote the heat transfer effect. Moreover, the wing part 32 for generating the vertical vortex S31 can keep the pressure loss small without interrupting the air flow, and therefore can suppress the accumulation of dust and the formation of frost. Become. In particular, since the blade leading edge portion 32a facing the air flowing along the flat plate fin 31 forms the blade portion 32 in a manner continuous with the surface of the flat plate fin 31, the resistance to the air flow is further reduced. Therefore, it is possible to greatly suppress deterioration with time of heat transfer performance due to dust accumulation, frost formation, and the like. As in the first embodiment, if the surface of the flat fin 31 is subjected to a hydrophilic treatment such as a bomate treatment or a water-repellent coating, it will be attached even if moisture containing air collides with the wing 32. No frosting.

  Still further, according to the heat exchanger, the first wing portion 34 and the second wing blade are formed by cutting up a portion that is obliquely rearward of each heat transfer tube 10 when the flat plate fin 31 is viewed from one edge portion. Since the portion 35 is formed, the air flowing along the flat plate fins 31 is attracted to the downstream region of the heat transfer tube 10. More specifically, in the first winglet portion 34, a strong swirl component deflected toward the tip end side of the first winglet portion 34 is generated in the air traversing the first winglet portion 34, so that the air flowing along the flat fins 31 is transferred to the heat transfer tube. 10 will be drawn to the downstream area. Further, in the second small blade portion 35, the deflection component and the swirl component of the passing air are synchronized, and are drawn to the downstream region of the heat transfer tube 10. As a result, in combination with the effects of the vertical vortex S31 and the horseshoe vortex H described above, the temperature boundary layer around the heat transfer tube 10 can be thinned, and the dead water region on the downstream side is suppressed to further promote the heat transfer effect. Will be able to.

  In the sixth embodiment described above, the first winglet portion 34 and the second winglet portion 35 having different inclination angles are formed, but it is not always necessary to form two types of winglet portions. It is sufficient to form one of the small wings.

It is the top view which showed the principal part of the heat exchanger which is Embodiment 1 of this invention. It is a perspective view which shows the principal part of the heat exchanger shown in FIG. It is the top view which showed the principal part of the heat exchanger which is Embodiment 2 of this invention. It is a perspective view which shows the principal part of the heat exchanger shown in FIG. It is the top view which showed the principal part of the heat exchanger which is Embodiment 3 of this invention. It is a perspective view which shows the principal part of the heat exchanger shown in FIG. It is a side view which shows the principal part of the heat exchanger shown in FIG. It is the top view which showed the principal part of the heat exchanger which is Embodiment 4 of this invention. It is a perspective view which shows the principal part of the heat exchanger shown in FIG. It is the top view which showed the principal part of the heat exchanger which is Embodiment 5 of this invention. It is a perspective view which shows the principal part of the heat exchanger shown in FIG. It is the top view which showed the principal part of the heat exchanger which is Embodiment 6 of this invention. It is a perspective view which shows the principal part of the heat exchanger shown in FIG. It is a perspective view which shows the conventional heat exchanger. It is a top view of the heat exchanger shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Heat exchanger tube 11 Flat fin 11a Fin front edge 12 Wing part 12a 1st blade structure part 12aa Blade front edge 12b 2nd blade structure part 12bb Blade front edge 14 1st small blade part 15 2nd small blade part 21 Flat fin 21a Fin Leading edge 22 Wing part 22a Wing leading edge 23 Auxiliary wing part 23a Wing leading edge 24 First wing part 25 Second wing part 31 Flat fin 32 Wing part 32a Wing front edge part 32b Downstream side edge part 32c Guide surface 34 First 1 small wing part 35 second wing part C blade center line H horseshoe vortex S11 first vertical vortex S12 second vertical vortex S21 vertical vortex S22 vertical vortex S31 vertical vortex α1 angle of attack α2 angle of attack α3 angle of attack α4 angle of attack β1 angle of inclination Angle β2 Tilt angle β3 Tilt angle β4 Tilt angle β5 Tilt angle β6 Tilt angle

Claims (10)

The flat plate fin is provided in the heat transfer tube through which the refrigerant passes, and the blade that gradually narrows toward the upstream side is formed in the plate fin on the upstream side of the heat transfer tube, and the air passing through the blade unit A heat exchanger for exchanging heat between the air flowing along the plate fins and the refrigerant in a state in which a vertical vortex is generated,
The wing portion has a first wing component that gradually narrows at a first reduction rate, and a gradual narrowness at a second reduction rate that is different from the first reduction rate on the upstream side of the first wing component. A heat exchanger characterized by having a second blade constituent part.   2. The heat exchanger according to claim 1, wherein the first blade component and the second blade component are configured in such a manner that the first reduction rate is larger than the second reduction rate. The flat plate fin is provided in the heat transfer tube through which the refrigerant passes, and a blade portion gradually narrowing toward the upstream side is formed in a portion of the flat plate fin on the upstream side of the heat transfer tube, and the air passing through the blade portion A heat exchanger for exchanging heat between the air flowing along the flat plate fins and the refrigerant in a state in which a vertical vortex is generated,
A heat exchanger characterized in that an auxiliary wing portion is provided between the wing portion and the heat transfer tube. The auxiliary wing portion gradually narrows toward the upstream side and generates a vertical vortex at a position different from the wing portion.   4. The heat exchanger according to claim 3, wherein at least a top portion of the auxiliary wing portion located on the upstream side thereof is located in a formation region of the wing portion. 5.   The heat exchanger according to claim 3, wherein the auxiliary wing portion is formed by cutting and raising the inside of the formation region of the wing portion.   The heat exchanger according to claim 3, wherein the auxiliary wing portion is formed in a mode having an angle of attack different from that of the wing portion.   The said wing | blade part is formed by cutting and raising a flat plate fin to one surface side, and the said auxiliary | assistant wing | blade part is formed by cutting and raising a flat plate fin to the other surface side. Heat exchanger. The flat plate fin is provided in the heat transfer tube through which the refrigerant passes, and the blade that gradually narrows toward the upstream side is formed in the plate fin on the upstream side of the heat transfer tube, and the air passing through the blade unit A heat exchanger for exchanging heat between the air flowing along the plate fins and the refrigerant in a state in which a vertical vortex is generated,
A heat exchanger characterized in that the blade portion is formed in such a manner that at least the blade leading edge facing the air flowing along the plate fin is continuous with the surface of the plate fin.   The wing portion having two guide surfaces inclined with respect to the flat plate fin is formed by bulging the flat plate fin to one surface side with the downstream edge close to the heat transfer tube as an open end. The heat exchanger according to claim 8.   The small blade part for drawing the air which flows along a flat fin to the downstream region of a heat exchanger tube was formed in the part which becomes the lower stream side than the blade part. Heat exchanger.

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