JP4775429B2 - Finned tube heat exchanger - Google Patents

Description

  The present invention is used in air conditioners such as room air conditioners, packaged air conditioners, and car air conditioners, heat pump water heaters, refrigerators, freezers, and the like, and gas such as air flowing between a plurality of stacked flat fins. The present invention relates to a finned tube heat exchanger that transfers heat to and from a fluid such as water or refrigerant flowing in a heat transfer tube.

In general, a fin-and-tube heat exchanger composed of a large number of laminated flat plate-shaped heat transfer fins and heat transfer tubes is stacked in parallel at a constant pitch as shown in FIG. A large number of flat fins 101 through which a gas W such as air flows, and heat transfer tubes 104 inserted into these fins 101 at a predetermined pitch substantially at right angles and through which a fluid R such as water or refrigerant flows The heat transfer tube 104 is tightly joined to a cylindrical fin collar 102 that rises perpendicularly to the outer periphery of the through hole of the fin 101. Further, the fin 101 has a triangular delta wing in which a slit forming portion 103 is provided with two side cuts as shown in FIGS. 14, 15, 16, and 17 to cut one side as a basic line. Cut and raised pieces 111 and 112 are provided. Then, the cut and raised pieces 111 and 112 of the conventional heat exchanger are gradually narrowed from the base portion toward the tip portion as shown in FIGS.
Is formed by cutting and raising from the flat fin. This vertical vortex improves the heat transfer coefficient (see, for example, Patent Document 1).

Also, guide fins that are inclined with respect to the flow direction of the air flow are provided so that the air flow near the heat transfer tube is guided to the rear side of the heat transfer tube in the flow direction, and both the heat transfer promotion effect and drainage are compatible. It has been proposed (see, for example, Patent Document 2).
Japanese Patent Laid-Open No. 2005-207688 JP 2007-010279 A

  However, in the finned tube heat exchanger described in Patent Document 1, although the heat transfer coefficient is improved by the longitudinal vortex S generated in the wake of the cut and raised pieces 111 and 112, the heat transfer from the heat transfer tube 104 is performed approximately in a radial manner. In the meantime, the heat conduction in the step direction (vertical direction) of the fins 101 is cut off by the cut and raised pieces 111 and 112, and there is a problem that a region that does not contribute to heat transfer is generated and heat transfer performance is deteriorated.

  Similarly, even in the fin-tube heat exchanger described in Patent Document 2, the heat conduction of the heat transfer fin is blocked by the guide fin, and a region that does not contribute to heat transfer is generated, thereby reducing the heat transfer performance. There was a problem.

  The present invention has been made in view of such a problem of the prior art, and is provided with a notch in the heat transfer fin, and the heat transfer fin portion on the windward side where the gas of the notch flows is raised. The fin tube type heat exchanger has improved heat transfer performance by forming a peak portion having an opening formed on the leeward side by the cut so that the heat conduction of the heat transfer fin is not interrupted. The purpose is to provide.

  In order to achieve the above object, a finned tube heat exchanger according to the present invention includes a plurality of heat transfer fins stacked substantially in parallel at a predetermined interval, and substantially orthogonal to the planar direction of the heat transfer fins. A plurality of heat transfer tubes penetrating through the heat transfer fins in a direction, and extending substantially in a direction substantially perpendicular to the plane direction of the heat transfer fins around the through holes of the heat transfer fins through which the heat transfer tubes pass. A cylindrical fin collar is formed, and the heat transfer tube is inserted into the through hole in close contact with the fin collar, and a gas flowing in a plane direction of the heat transfer fin and a thermal refrigerant flowing inside the heat transfer tube Heat exchange is performed between them.

Then, the heat transfer fin is provided with a cut only in a step direction that is substantially perpendicular to the flow direction of the gas, and the heat transfer fin portion on the windward side where the gas of the cut flows is raised to the leeward side. A crest having an opening formed by the notch is provided, and the crest is not formed at a position passing through the center of the heat transfer tube and intersecting a straight line parallel to the gas flow direction .

  Since the finned tube heat exchanger according to the present invention is configured as described above, when the gas flows along the mountain portion having the opening on the leeward side and passes through the opening on the leeward side, the vertical vortex From there, the temperature boundary layer on the surface of the heat transfer fin on the leeward side was disturbed to improve the heat transfer rate, promote heat transfer, and launched a triangular piece called Delta Wing with a similar effect As in the case of a triangle, the heat conduction of the heat transfer fins is interrupted by a triangular piece and a region that does not contribute to heat transfer is generated and heat transfer performance is not deteriorated. Therefore, the entire heat transfer fin surface can contribute to heat transfer, and excellent heat transfer performance can be obtained.

In the first invention, the heat transfer fin is cut only in the step direction which is substantially perpendicular to the gas flow direction, and the heat transfer fin portion on the windward side where the cut gas flows is raised, and cut into the leeward side. Since the peak portion is formed at a position that passes through the center of the heat transfer tube and intersects with a straight line parallel to the flow direction of the gas, the gas is not in the peak portion. A vertical vortex is generated when it flows along and then passes through the opening on the leeward side, from which it disturbs the temperature boundary layer on the surface of the heat transfer fins on the leeward side to improve heat transfer, thereby promoting heat transfer At the same time, the heat transfer fins can be thermally conducted through the ridges, so that the heat transfer performance is not reduced by generating a region that does not contribute to heat transfer by blocking the heat conduction. The entire surface contributes to heat transfer and has excellent heat transfer performance It is possible to obtain.

In addition, gas flows between the raised heat transfer fins between the raised heat transfer fins on the opposite side of the mountain, so that the gas is mixed between the heat transfer fins and the heat transfer performance is improved. Can do. Furthermore, Ru can improve heat transfer performance by leading effect of the temperature boundary layer at the leeward side of the cut.

In the second invention, since the shape of the opening is substantially triangular, the peak portion having the substantially triangular opening on the leeward side is called a delta wing that generates a vertical vortex in the wake and promotes heat transfer. Two rising triangles face each other and are connected to each other by the ridge of the ridge line from the summit to the foot of the mountain. After the gas flows along the slope of the mountain, the leeward opening is opened. When passing, a vertical vortex is generated in the same manner as the delta wing, and the heat transfer can be promoted by disturbing the temperature boundary layer on the leeward side to improve the heat transfer coefficient. On the other hand, unlike the delta wing, the heat conduction fins continue in the step direction without causing heat transfer performance to be reduced by blocking the heat conduction in the step direction of the heat transfer fins and generating a region that does not contribute to heat transfer. Therefore, the entire heat transfer fin surface can contribute to heat transfer, and excellent heat transfer performance can be obtained.

  In addition, gas flows between the raised heat transfer fins between the raised heat transfer fins on the opposite side of the mountain, so that the gas is mixed between the heat transfer fins and the heat transfer performance is improved. Can do. Furthermore, on the leeward side of the cut, the heat transfer performance can be improved by the leading edge effect of the temperature boundary layer.

In the third invention, since the shape of the opening is substantially trapezoidal, the mountain portion having the substantially trapezoidal opening on the leeward side is called a delta wing that promotes heat transfer by generating a vertical vortex in the wake. Two of the rising triangles are on both sides of the slope and are connected by a flat ridge from the summit to the foot of the mountain. After the gas flows along the slope of the mountain, When passing through the opening, a vertical vortex is generated in the same manner as the delta wing, and the heat transfer rate can be enhanced by disturbing the temperature boundary layer on the leeward side and improving the heat transfer coefficient. On the other hand, unlike the delta wing, the heat conduction fins continue in the step direction without causing heat transfer performance to be reduced by blocking the heat conduction in the step direction of the heat transfer fins and generating a region that does not contribute to heat transfer. Therefore, the entire heat transfer fin surface can contribute to heat transfer, and excellent heat transfer performance can be obtained. In addition, since the two slopes are connected to the flat ridge at a gentle angle, the process of raising the mountain portion is easy.

In addition, gas flows between the raised heat transfer fins between the raised heat transfer fins on the opposite side of the mountain, so that the gas is mixed between the heat transfer fins and the heat transfer performance is improved. Can do. Furthermore, on the leeward side of the cut, the heat transfer performance can be improved by the leading edge effect of the temperature boundary layer.

In the fourth aspect of the present invention, the shape of the opening is substantially arcuate, so that the mountain part having the substantially arcuate opening on the leeward side is a delta wing that generates a vertical vortex in the wake and promotes heat transfer. The rising triangle pieces called curved surfaces face each other and are connected so that they touch each other at the ridge of the ridge line from the summit to the foot of the mountain, and the gas flowed along the slope of the mountain Later, when passing through the opening on the leeward side, a vertical vortex is generated in the same manner as the delta wing, and heat transfer can be promoted by disturbing the temperature boundary layer on the leeward side to improve the heat transfer coefficient. . On the other hand, unlike the delta wing, the heat transfer fins are continuous and do not contribute to heat transfer by blocking the heat conduction in the step direction of the heat transfer fins, so that the heat transfer performance is not degraded, and the ridges are continuous. Therefore, the entire surface of the heat transfer fin can contribute to heat transfer, and excellent heat transfer performance can be obtained. Moreover, since the peak portion is raised with an arc cross section, it is easy to process.

  In addition, gas flows between the raised heat transfer fins between the raised heat transfer fins on the opposite side of the mountain, so that the gas is mixed between the heat transfer fins and the heat transfer performance is improved. Can do. Furthermore, on the leeward side of the cut, the heat transfer performance can be improved by the leading edge effect of the temperature boundary layer.

In the fifth aspect of the present invention, a plurality of crests having openings on the leeward side are formed, and the cuts of the crests formed on the leeward side from the tangent line connecting the upwind sides of the fin collars adjacent in the step direction are defined as the width of the heat transfer fins. Since it is shifted in the direction, the heat transfer performance improvement effect due to the ridges with the opening on the leeward side can be increased almost in proportion to the number formed, and the heat exchanger greatly promotes heat transfer In addition, the strength against the external force applied to the windward front edge of the heat transfer fin can be maintained.

A sixth invention is a peak portion having an opening on the leeward side several forms, since the windward side of the tangent line connecting the upwind side of the fin collar adjacent stage direction so as not to form a cut pile portion In addition, the heat transfer performance improvement effect by the mountain portion having the leeward side opening can be increased substantially in proportion to the number formed, and the heat exchanger can greatly promote heat transfer , The intensity | strength with respect to the external force to the windward front edge of a heat-transfer fin can be maintained .

In the seventh aspect of the present invention, a plurality of ridges having openings on the leeward side are formed, and the number of ridges is increased as the distance from the straight line connecting the fin collars or heat transfer tube adjacent in the step direction increases. Even in heat transfer fins in areas far from the straight line connecting the fin collars or heat transfer tube centers adjacent to each other in the step direction where the amount of heat due to the heat conduction of the fins is small, the openings on the leeward side are formed more than the heat transfer fins in the near area. The effect of improving the heat transfer coefficient due to the peaks is great, and the heat transfer performance of the entire heat transfer fin can be increased.

In the eighth aspect of the present invention, a plurality of peaks having openings on the leeward side are formed, and the number of peaks is greater on the leeward side where the gas flows than on the windward side. When used as a heat exchanger, when the outside air temperature becomes low, such as when heating operation, frost adheres to the heat transfer fin surface, but after some of the moisture in the air adheres to the heat transfer fin surface as frost on the windward side, Since the air with reduced moisture flows to the leeward side, the frost adhering to the heat transfer fin surface on the leeward side is dispersed and reduced, and the growth of frost can be suppressed even if there are many peaks having openings on the leeward side. . Thereby, the time until the heat transfer fins are blocked with frost can be kept long, and the heat transfer performance of the heat transfer fins as a whole can be improved.

In the ninth aspect of the present invention, a plurality of ridges having openings on the leeward side are formed, and the number of ridges increases as the distance from the nearest fin collar or heat transfer tube increases. As the distance increases, the heat exchanger is used as an outdoor heat exchanger for room air conditioners. The blockage between the heat transfer fins due to frost can be suppressed.

  In the tenth aspect of the invention, the peak portion having the opening on the leeward side is not formed on or near a straight line connecting the centers of the fin collars or the heat transfer tubes adjacent in the step direction. When the exchanger is used as an evaporator, even if a large amount of condensed water adheres to the heat transfer tubes and fin collars, it does not stay and drops quickly and is drained, and the ventilation resistance does not increase abnormally.

  In an eleventh aspect of the present invention, the heat transfer fin is provided with a notch obtained by cutting one side of the quadrilateral and three sides are cut, and the left side is bent along the basic line as a basic line and is raised substantially vertically to the heat transfer fin surface. Since the raised piece is formed and the raised piece is higher than the height of the fin collar so as to define a predetermined interval when the heat transfer fins are laminated, the height of the normal fin collar As in the case of restricting the fin pitch, the thickness is reduced, the tip is cracked, and the height is uneven. However, there is a limit to the height that can be processed, so unlike the case where the fin pitch that can be regulated cannot be made too rough, the fin pitch is regulated by a rising piece that can process the height higher than the fin collar. Ri, it is possible to roughen the fin pitch. As a result, the heat transfer performance of the heat transfer fins is excellent, and in order to exhibit equivalent performance, it is possible to cope with the case where the fin pitch can be coarsened, and there is a possibility of operating under conditions where frost is formed on the heat transfer fin surface When used as an evaporator, even if frost adheres to the surface of the heat transfer fins, by roughening the fin pitch, the time until the heat transfer fins are blocked by frost can be lengthened, and the airflow resistance is drastically increased. The increase can be suppressed.

  In the twelfth invention, the plane of the rising piece forms an angle of 30 degrees or less with the main flow direction in which the gas flows, that is, the direction parallel to the heat transfer fin and perpendicular to the windward leading edge of the heat transfer fin, In addition, even when used as an evaporator, condensed water does not stay on the rising piece, and even if it adheres, it drops quickly, drains, and the ventilation resistance increases abnormally. There is no.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

  The finned tube heat exchanger according to the present invention penetrates through heat transfer fins in a direction perpendicular to the plane direction of the plurality of heat transfer fins, and the heat transfer fins stacked substantially in parallel at a predetermined interval. And a plurality of heat transfer tubes. A heat medium such as a refrigerant passes through the inside of each heat transfer tube and exchanges heat with a gas (generally air) flowing in the plane direction of the heat transfer fins between the heat transfer fins.

(Embodiment 1)
A first embodiment of the present invention will be described with reference to FIGS. 1 to 3 are the first shape of the first embodiment, FIG. 4 is the second shape of the first embodiment, and FIG. 5 is the third shape of the first embodiment.

  First, the 1st shape of Embodiment 1 is demonstrated according to FIGS. 1-3. FIG. 1 is a front view of a heat transfer fin having a first shape, FIG. 2 is a bottom view thereof, and FIG. 3 is an enlarged perspective view of a main part of the heat transfer fin having a first shape. FIG. 1 shows one of the plurality of heat transfer fins 10, and FIG. 2 penetrates the four heat transfer fins 10 and the heat transfer fins 10 among the plurality of stacked heat transfer fins 10. One of the plurality of heat transfer tubes 12 is shown.

As shown in FIGS. 1 and 2, each heat transfer fin 10 is formed with a plurality of through holes 10 a (only two through holes are shown in FIG. 1) through which the heat transfer tubes 12 pass. Each through hole 10
Around a, a substantially cylindrical fin collar 11 extending in a plane direction of the heat transfer fin 10 or a direction substantially orthogonal to the flow direction of the airflow 1 is formed. For example, the diameter of each heat transfer tube 12 is increased. Thus, the heat transfer tube 12 is inserted into the through hole 11 a in a state of being in close contact with the fin collar 11. Note that all the fin collars 11 extend from the heat transfer fins 10 in the same direction and have substantially the same height.

  Here, the diameter expansion of the heat transfer tube 12 will be described in detail. When the heat exchanger is manufactured, the heat transfer fins 10 are stacked and the heat transfer tubes 12 are inserted into the fin collar 11, but the workability is improved. The inner diameter of the fin collar 11 at the time of fin pressing is processed to be slightly larger than the outer diameter of the heat transfer tube 12. However, after the heat transfer tube 12 is inserted into the fin collar 11, the heat transfer tube 12 is expanded in diameter using a hydraulic pressure or by a mechanical method, and the heat transfer tube 12 and the fin collar 11 are brought into close contact with each other to perform heat transfer performance. Has improved.

  1 to 3, the heat transfer fin 10 is provided with a cut 13 only in the step direction of the heat exchanger that is substantially perpendicular to the flow direction of the airflow 1, and the heat transfer on the windward side where the gas in the cut 13 flows. The fin portion is raised on the front side (the front side in FIG. 1, the upper side in FIG. 2), and a peak portion 15 having a substantially triangular opening 14 formed by the cut 13 on the leeward side is formed. A plurality of ridges 15 having leeward openings 14 are formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent in the step direction.

  In addition, the peak part 15 is not limited to be formed to be raised on the front side, and may be formed to be raised on the back side, or may be a mixture of a front-side uplift and a back-side uplift.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  Cuts 13 are provided in the heat transfer fins 10 in a step direction that is substantially perpendicular to the gas flow direction, and the heat transfer fins on the windward side of the airflow 1 of the cuts 13 are raised to form openings formed by the cuts 13 on the leeward side. Since the peak portion 15 having the portion 14 is formed, the gas flows along the peak portion 15 and then a vertical vortex is generated when passing through the opening portion 14 on the leeward side, from which the surface of the heat transfer fin 10 surface on the leeward side is generated. Heat transfer is promoted by disturbing the temperature boundary layer and improving the heat transfer coefficient. At the same time, the heat transfer fin 10 is continuous in the step direction so that the heat conduction fin 10 is continuously cut in the step direction so that the heat conduction in the step direction of the heat transfer fin 10 is cut off and the region that does not contribute to heat transfer does not occur. Since the peak portion 15 can be moved by heat conduction, the entire surface of the heat transfer fin 10 can contribute to heat transfer, and excellent heat transfer performance can be obtained.

  Moreover, since gas flows out between the heat-transfer fins 10 raised from the heat-transfer fins 10 on the opposite side where the ridges are raised, the gas is mixed between the front and back surfaces of the heat-transfer fins 10. Can be improved. Furthermore, on the leeward side of the notch 13, the heat transfer performance can be improved by the leading edge effect of the temperature boundary layer.

  In addition, since the direction of the notch 13 is a step direction that is substantially perpendicular to the flow direction of the air flow 1, the vertical vortex is effective when the gas flows along the mountain portion 15 and then passes through the opening 14 on the leeward side. Heat transfer can be greatly promoted by disturbing the temperature boundary layer on the surface of the heat transfer fin 10 on the leeward side and improving the heat transfer coefficient. In addition, it is considered that the heat of the heat transfer tube 12 is transferred in a radial direction from the heat transfer tube 12 to the heat transfer fins 10, and then the heat transfer fins 10 are elongated and thus conduct heat in the step direction. Therefore, the notch 13 formed in the step direction which is substantially perpendicular to the flow direction of the airflow 1 is in a direction along the direction of heat conduction of the heat transfer fin 10, and the heat conduction in the step direction of the heat transfer fin 10 is cut off. Thus, a region that does not contribute to heat transfer does not occur.

In addition, since the shape of the opening 14 is a substantially triangular shape, the substantially triangular opening 14 on the leeward side.
The mountain portion 15 having a ridge is formed by connecting two rising triangular pieces called delta wings that generate a vertical vortex in the wake to promote heat transfer, and is connected by a ridge 16 on the ridge line that leads from the mountain top 16a to the mountain foot 16b. It has a form like this. As a result, when the gas flows along the slopes 17a and 17b of the mountain portion 15 and passes through the opening 14 on the leeward side, a vertical vortex is generated in the same manner as the delta wing, and the temperature boundary layer on the leeward side is generated therefrom. Heat transfer can be promoted by disturbing and improving the heat transfer coefficient. On the other hand, unlike the delta wing, the heat conduction fin 10 is in the direction of the heat without causing the heat conduction performance to deteriorate by generating a region that does not contribute to heat transfer by blocking the heat conduction in the direction of the heat conduction fin 10. Since the ridges 15 that are continuous to each other can be moved by heat conduction, the entire surface of the heat transfer fin 10 can contribute to heat transfer, and excellent heat transfer performance can be obtained.

  In addition, since a plurality of ridges 15 having the leeward side opening 14 are formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent in the step direction, the number of the ridges 15 forming the heat transfer performance improvement effect. Thus, the heat exchanger can be greatly increased in heat transfer.

  Further, the peak portion 15 having the leeward opening 14 is not formed on or near the straight line 18 connecting the centers of the fin collars 11 or the heat transfer tubes 12 adjacent in the step direction. Thereby, when the heat exchanger is used as an evaporator, the condensed water adhering to the heat transfer tubes 12 and the fin collars 11 is quickly dropped without staying in the heat transfer fins 10 and drained, and the ventilation resistance is reduced. It does not increase abnormally. As shown in FIG. 1, it is best not to form the peak portion 15 on and near the straight line 18 connecting the centers of the fin collar 11 or the heat transfer tube 12, but considering the momentum of the condensed water dropping, etc. For example, in the range of the heat transfer fins 10 between the two fin collars 11 adjacent to each other in the step direction, the upper half should not be formed near the straight line 18. Moreover, even if the mountain portion 15 is slightly hung on the lower position of the fin collar 11, the drainage performance is not greatly deteriorated.

  Next, the second shape of the first embodiment will be described with reference to FIG. FIG. 4 is an enlarged perspective view of a main part of the heat transfer fin having the second shape.

  In the second shape of the first embodiment, the heat transfer fin 10 is provided with a notch 23 in the step direction that is substantially perpendicular to the flow direction of the airflow 1, and the heat transfer fin portion on the windward side where the gas in the notch 23 flows is provided. A peak 25 having a substantially trapezoidal opening 24 formed by a cut 23 on the leeward side is formed on the leeward side, except that the ridgeline increases and the shape of the opening 24 becomes a substantially trapezoid. The configuration is the same as the first shape of the first embodiment.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  The ridge portion 25 having the substantially trapezoidal opening 24 on the leeward side has two rising triangular pieces called delta wings that generate a vertical vortex in the wake and promote heat transfer, and have both sides 27a and 27b of the slope, It is shaped like a flat ridge 26 connected from the summit to the foot of the mountain, and the gas flows along the slopes 27a and 27b of the mountain 25 and then passes through the opening 24 on the leeward side to form a delta. Like the wing, a vertical vortex is generated, and the heat boundary can be improved by disturbing the temperature boundary layer on the leeward side. On the other hand, unlike the delta wing, the heat conduction fin 10 continues in the step direction without generating a region that does not contribute to heat transfer by blocking the heat conduction in the step direction of the heat transfer fin 10. Since the ridge portion 25 is thermally conductive, the entire surface of the heat transfer fin 10 can contribute to heat transfer, and excellent heat transfer performance can be obtained.

Moreover, since gas flows out between the heat-transfer fins 10 raised from the heat-transfer fins 10 on the opposite side where the ridges are raised, the gas is mixed between the front and back surfaces of the heat-transfer fins 10. Can be improved. Furthermore, on the leeward side of the cut, the heat transfer performance can be improved by the leading edge effect of the temperature boundary layer.

  Further, since the two inclined surfaces 27a and 27b are connected to the flat ridge 26 at a gentle angle, the processing for raising the mountain portion 25 is easy.

  The operation and action of the configuration similar to the first shape of the first embodiment except that the opening 24 is substantially trapezoidal is the same as that of the first shape of the first embodiment. Omit.

  Next, the third shape of the first embodiment will be described with reference to FIG. FIG. 5 is an enlarged perspective view of a main part of the third shape heat transfer fin.

  In the third shape of the first embodiment, the heat transfer fin 10 is provided with a stepwise cut 23 that is substantially perpendicular to the flow direction of the air flow 1, and the heat transfer fin portion on the windward side where the gas of the cut 33 flows is provided. A mountain portion 35 having a substantially arc-shaped opening 34 formed by a notch 33 is formed on the leeward side by being raised, but the configuration other than that the shape of the opening 34 is substantially arc-shaped is implemented. This is the same as the first shape of form 1.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  Since the crest 35 having the substantially arc-shaped opening 34 on the leeward side has a substantially arc-shaped opening, the crest 35 having the substantially arc-shaped opening 34 on the leeward side is in the wake. A form in which two rising triangular pieces called delta wings that generate longitudinal vortices and promote heat transfer are curved and face each other, and are connected so that they are in contact with the ridge 36 of the ridge line that leads from the top 36a to the top 36b. After the gas flows along the slope of the mountain portion 35 and passes through the opening 34 on the leeward side, a vertical vortex is generated in the same manner as the delta wing, and from this, the temperature boundary layer on the leeward side is disturbed. Heat transfer can be promoted by improving the heat transfer coefficient. On the other hand, unlike the delta wing, the heat conduction fin 10 continues in the step direction without generating a region that does not contribute to heat transfer by blocking the heat conduction in the step direction of the heat transfer fin 10. Since the ridge portion 35 is thermally conductive, the entire surface of the heat transfer fin 10 can contribute to heat transfer, and excellent heat transfer performance can be obtained.

  Moreover, since gas flows out between the heat-transfer fins 10 raised from the heat-transfer fins 10 on the opposite side where the ridges are raised, the gas is mixed between the front and back surfaces of the heat-transfer fins 10. Can be improved. Furthermore, on the leeward side of the cut, the heat transfer performance can be improved by the leading edge effect of the temperature boundary layer.

  Further, since the mountain portion 35 is raised with an arc cross section, it is easy to process.

  The operation and action of the configuration similar to the first shape of the first embodiment except that the opening 34 is substantially arc-shaped is the same as that of the first shape of the first embodiment. Omit.

  As mentioned above, although the shape of three types of peak parts was demonstrated in this Embodiment 1, a different magnitude | size may be mixed in each shape. Furthermore, different shapes and sizes may be mixed.

(Embodiment 2)
A second embodiment of the present invention will be described with reference to FIGS. 6 (a) and 6 (b). FIG. 6A is a front view of the heat transfer fin having the shape of the second embodiment, and FIG. 6B is a bottom view thereof. FIG. 6A shows one of the plurality of heat transfer fins 10, and FIG. 6B shows four heat transfer fins 10 among the plurality of stacked heat transfer fins 10, and the heat transfer fins 10. One of the heat transfer tubes 12 penetrating the heat fin 10 is shown.

  6 (a) and 6 (b), as in the first embodiment, a peak 45a having an opening 44a on the leeward side, a peak 45b having an opening 44b on the leeward side, and an opening on the leeward side. A plurality of crests 45c having 44c are respectively formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent in the step direction. And the peak parts 45a, 45b, 45c are formed so that it distances from the straight line 18a which connects the center of the fin collar 11 or the heat exchanger tube 12 adjacent to a step direction. In addition, the reference | standard which shows the position of the peak parts 45a, 45b, 45c is made into the approximate gravity center position of each of the triangles of the hole formed on the plane of the heat transfer fin 10 by forming the peak parts 45a, 45b, 45c, The distance from the straight line 18a is a distance obtained by drawing a perpendicular line.

  Specifically, for example, in FIG. 6A, two peak portions 45a that are closest to the straight line 18a and are actually arranged so as to overlap with the straight line 18a are formed between the fin collars 11, and then the straight line. Three crests 45 b close to 18 a are formed between the fin collars 11, and four crests 45 c farthest from the straight line 18 a are formed between the fin collars 11.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In addition, since the operation | movement by the structure similar to Embodiment 1 and an effect | action are the same as Embodiment 1, description is omitted.

  The heat transfer fin 10 in the region far from the straight line 18a connecting the centers of the fin collars 11 or the heat transfer tubes 12 adjacent to each other in the step direction has heat transfer due to heat conduction compared to the heat transfer fin 10 in the region near the straight line 18a. Decreases as the distance increases. In this Embodiment 2, since the mountain parts 45a, 45b, 45c were formed so that it distanced from the straight line 18a, the heat transfer fin 10 of the area | region far from the straight line 18a has a heat transfer coefficient rather than the heat transfer fin 10 of the near area | region. The improvement effect becomes larger. Thereby, the heat-transfer performance of the heat-transfer fin 10 whole can be made high, and a heat exchange capability can be improved.

  Next, the intensity | strength of the heat-transfer fin 10 when the peak part 45c is formed is demonstrated. In FIG. 6A, the four cuts in the peak portion 45c are arranged on a straight line, and are formed further on the windward side than the tangential line 18b on the windward side connecting the fin collars 11 adjacent in the step direction. For example, specifically showing the dimensions of the heat transfer fin 10 and the peak portion 45c in FIG. 6A, the step dimension H which is the distance between the fin collars 11 is 21 mm, and the cut dimension L is 3 mm. Since four crests 45c are formed, the total cut dimension L is 12 mm, which is approximately 57% of the step dimension H21 mm. In such a case, when an external force is applied to the windward front edge 10a of the heat transfer fin 10, there is a possibility that the cut will be easily broken or fall down. In particular, when used in an outdoor unit of an air conditioner, an external force is easily applied because the windward front edge 10a constitutes an outer shell, and even when two rows are aligned and bent into an L shape, the external force Further, the tension due to the distortion of the fin collar 11 at the bent portion is easily applied.

  Therefore, as shown in FIGS. 7A and 7B, every other cut portion is shifted in the width direction of the heat transfer fin 10 (for example, S = 1 mm) and arranged on two straight lines. Like that. Thus, if it forms so that each of the incision dimension L arrange | positioned on two straight lines may be 50% or less of the step dimension H, the intensity | strength of the heat-transfer fin 10 will improve and the windward front edge 10a will be improved. When an external force is applied to the wire or a tension is applied when it is bent and formed, it can be prevented from being easily folded or overturned. Thus, even if the peak part 45c is shifted, it is only one group as the peak part 45c, and for each peak part 45a, 45b, 45c, a shift of 2 mm or less may be regarded as one group.

  In addition, about the intensity | strength of the heat-transfer fin 10 demonstrated here, the number and shape of the peak part of the leeward side are not limited from the tangent line 18b on the leeward side which connects the fin collar 11 adjacent to a step direction.

(Embodiment 3)
A third embodiment of the present invention will be described with reference to FIGS. 8 is a front view of the heat transfer fin having the shape of the third embodiment, and FIG. 9 is a bottom view thereof. FIG. 8 shows one of the plurality of heat transfer fins 10, and FIG. 9 shows four heat transfer fins 10 out of the plurality of stacked heat transfer fins 10 and the heat transfer fins 10. One of the plurality of heat transfer tubes 12 is shown.

  8 to 9, as in the first embodiment, the peak portion 55a having the opening portion 54a on the leeward side, the peak portion 55b having the opening portion 54b on the leeward side, and the peak portion 55c having the opening portion 54c on the leeward side. Are formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent to each other in the step direction. And the mountain parts 55a, 55b, 55c are formed more on the leeward side where the gas flows than on the leeward side.

  Specifically, in FIG. 8, for example, two peak portions 55a arranged on the windward side are formed between the fin collars 11, and then the peak portions 55b arranged on the windward side are fin collars. Three crests 55 c are formed between the fin collars 11 and three are formed between the fin collars 11. The cut portion of the peak portion 55a arranged on the most windward side is not formed on the windward side from the windward tangent line 18b connecting the fin collars 11 adjacent in the step direction.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In addition, since the operation | movement by the structure similar to Embodiment 1 and an effect | action are the same as Embodiment 1, description is omitted.

  When the heat exchanger is used as an outdoor heat exchanger of a room air conditioner, frost adheres to the surface of the heat transfer fin 10 when the outside air temperature becomes low during heating operation. The air containing moisture flows to the leeward side after most of the moisture in the air is attached to the leeward heat transfer fin 10 surface as frost on the windward side, so that the frost adhering to the leeward heat transfer fin 10 surface is generated. Less. In the third embodiment, the ridges 55a, 55b, 55c are formed so that the leeward side where the gas flows is larger than the leeward side, so the number of the ridges 55a arranged on the most leeward side is the largest. The frost formation is relatively suppressed even on the windward side under the condition that the frost is formed on the heat transfer fin 10 surface. Then, a large number of ridges 55b arranged on the leeward side and ridges 55c arranged on the most leeward side are formed in order, so that the surface of the heat transfer fin 10 is reached. It is possible to suppress the frost from being dispersed and the frost from growing intensively on the windward side. Thereby, the time until the heat transfer fins 10 are blocked with frost can be kept long, and the heat transfer performance of the entire heat transfer fins can be improved.

  Further, since the cut portion of the peak portion 55a arranged on the most windward side is formed on the leeward side with respect to the tangent line 18b, the strength against the external force to the windward front edge 10a of the heat transfer fin 10 can be maintained. .

(Embodiment 4)
A fourth embodiment of the present invention will be described with reference to FIGS. FIG. 10 is a front view of a heat transfer fin having the shape of the fourth embodiment, and FIG. 11 is a bottom view thereof. FIG. 10 shows one of the plurality of heat transfer fins 10, and FIG. 11 passes through the four heat transfer fins 10 and the heat transfer fins 10 among the plurality of stacked heat transfer fins 10. One of the plurality of heat transfer tubes 12 is shown.

10 to 11, similarly to the first embodiment, a peak 65a having an opening 64a on the leeward side, a peak 65b having an opening 64b on the leeward side, and a peak having an opening 64c on the leeward side. A plurality of 65c is formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent in the step direction. And the mountain | heap part 65a, 65b, 65c is formed more as it leaves | separates from the nearest fin collar 11 or the heat exchanger tube 12. As shown in FIG.

  Specifically, for example, in FIG. 10, two peak portions 65 a closest to the fin collar 11 are arranged between the fin collars 11, and then the peak portions 65 b closest to the fin collar 11 are between the fin collars 11. Three ridges 65 c that are the farthest from the fin collar 11 are arranged between the fin collars 11. The cut portion of the peak portion 65b arranged on the most windward side is not formed on the windward side from the windward tangent line 18b connecting the fin collars 11 adjacent in the step direction.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In addition, since the operation | movement by the structure similar to Embodiment 1 and an effect | action are the same as Embodiment 1, description is omitted.

  Since the peak portions 65a, 65b, 65c arranged on the heat transfer fin 10 increase as the distance from the nearest fin collar 11 or heat transfer tube 12 increases, the heat transfer due to heat conduction decreases as the distance from the heat transfer tube increases. Therefore, by forming more peaks as far away from the heat transfer tube 12, when the heat exchanger is used as an outdoor heat exchanger of a room air conditioner and the outside air temperature is low during heating operation, The amount of frost adhering to the surface of the heat fin can be suppressed, and blockage between the heat transfer fins due to frost can be suppressed.

  Further, since the cut portion of the peak portion 65b arranged on the most windward side is formed on the leeward side with respect to the tangent line 18b, the strength against the external force applied to the windward front edge 10a of the heat transfer fin 10 can be maintained. .

(Embodiment 5)
A fifth embodiment of the present invention will be described with reference to FIGS. FIG. 12 is a front view of a heat transfer fin having the shape of the fifth embodiment, and FIG. 12 is a bottom view thereof. FIG. 12 shows one of the plurality of heat transfer fins 10, and FIG. 12 passes through the four heat transfer fins 10 and the heat transfer fins 10 among the plurality of stacked heat transfer fins 10. One of the plurality of heat transfer tubes 12 is shown. 12 to 13, similarly to the first embodiment, a plurality of ridges 75 having openings 74 on the leeward side are formed on the surface of the heat transfer fin 10 between the fin collars 11 adjacent to each other in the step direction. .

  Then, the heat transfer fin 10 is provided with a notch 80 in which one side of the quadrilateral is left and three sides are cut, and the remaining one side is bent at the basic line 81 as a basic line 81 and is raised substantially perpendicular to the surface of the heat transfer fin 10. A rising piece 82 is formed. The rising piece 82 is configured to be higher than the height of the fin collar 11 so as to define a predetermined interval when the heat transfer fins 10 are stacked, that is, a fin pitch.

  Further, the plane of the rising piece 82 forms an angle of 30 degrees or less with a main flow direction in which the gas flows, that is, a direction parallel to the heat transfer fin 10 and perpendicular to the windward leading edge 10a of the heat transfer fin 10, and It is formed so as not to be horizontal.

  About the heat exchanger comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In addition, since the operation | movement by the structure similar to Embodiment 1 and an effect | action are the same as Embodiment 1, description is omitted.

Usually, the fin pitch is regulated by the height of the fin collar 11. However, since the fin collar 11 is formed by pressing ironing, the thickness of the fin collar 11 may be reduced, leading to problems such as cracking of the tip and uneven height. There is a limit to the height that can be achieved. Therefore, the fin pitch cannot be made too rough with the fin collar 11.

  In the fifth embodiment, the heat transfer fin 10 is provided with a notch 80 in which one side of the quadrilateral is left and three sides are cut, and the remaining one side is bent at the basic line 81 as a basic line 81 so as to be approximately on the surface of the heat transfer fin 10. A rising piece 82 that is vertically raised is formed, and the rising piece 82 is higher than the height of the fin collar 11 so as to define a predetermined interval when the heat transfer fins 10 are stacked, that is, a fin pitch. Therefore, even in the case of fin pitch roughness that cannot be regulated by the height of the normal fin collar 11, the fin pitch can be regulated. Thereby, the heat transfer performance of the heat transfer fin 10 is excellent, and it is possible to deal with the case where the fin pitch can be roughened to exhibit the equivalent performance. Moreover, when using as an evaporator which may be frosted on the surface of the heat-transfer fin 10, even if frost adheres to the surface of the heat-transfer fin 10, it heat-fins 10 with frost by roughening a fin pitch. The time until the gap is closed can be lengthened, and a rapid increase in ventilation resistance can be suppressed.

  Further, the plane of the rising piece 82 forms an angle of 30 degrees or less with the main flow direction in which the gas flows, that is, the direction parallel to the heat transfer fin 10 and perpendicular to the windward leading edge of the heat transfer fin 10. If it is formed so that it does not become, even if it is used as an evaporator, even if condensed water adheres to the rising piece, it will drop quickly without stagnation and drain, and the ventilation resistance will not increase abnormally.

  6A, FIG. 7A, FIG. 8, FIG. 10 and FIG. 12 showing the second to fifth embodiments, the opening portions 44, 54, 64 of the mountain portions 45, 55, 65, 75 are provided. Although the shape of 74 is a substantially triangular shape, a similar effect can be obtained if it is a substantially trapezoidal shape or a substantially arc shape.

  Further, in the case of a two-row heat exchanger, in consideration of performance and frost formation characteristics, the second embodiment is a leeward row, and the third, fourth, or fifth embodiment is an upwind row. Even if it is used, the same effect can be obtained.

  Further, in FIG. 1 showing the first embodiment and FIGS. 6A, 7A, 8, 10, and 12 showing the second to fifth embodiments, the fin collar 11 is provided near the leeward side. Since the ridge portion guides the airflow to the wake of the heat transfer tube 12 and reduces the dead water area that does not contribute to heat transfer, the heat transfer performance can be improved.

  The finned tube heat exchanger according to the present invention is provided with a notch in a heat transfer fin, and a heat transfer fin portion on the windward side of the notch is raised to form a peak portion having an opening formed on the leeward side by the notch. As a result, a vertical vortex is generated when the gas flows along a mountain portion having an opening on the leeward side, disturbing the temperature boundary layer behind the air flow, improving the heat transfer rate, and promoting heat transfer. At the same time, the heat transfer fins can get over the ridges that are continuous in the step direction and conduct heat, and the entire surface of the heat transfer fins can contribute to heat transfer, so that excellent heat transfer performance can be obtained. It is useful as a heat exchanger used in a conditioner, a heat pump type hot water heater, a refrigerator, a freezer and the like.

Front view of first shape heat transfer fin of embodiment 1 of the present invention The bottom view of the 1st shape heat-transfer fin of Embodiment 1 of the present invention The expanded perspective view of the principal part of the heat transfer fin of the 1st shape of Embodiment 1 of this invention The expanded perspective view of the principal part of the 2nd shape heat-transfer fin of Embodiment 1 of this invention The expanded perspective view of the principal part of the heat-transfer fin of the 3rd shape of Embodiment 1 of this invention (A) Front view of first shape heat transfer fin of embodiment 2 of the present invention (b) Bottom view (A) Front view of second shape heat transfer fin of embodiment 2 of the present invention (b) Bottom view Front view of heat transfer fin according to Embodiment 3 of the present invention The bottom view of the heat-transfer fin of Embodiment 3 of this invention Front view of heat transfer fin according to embodiment 4 of the present invention The bottom view of the heat-transfer fin of Embodiment 4 of this invention Front view of heat transfer fin according to embodiment 5 of the present invention The bottom view of the heat-transfer fin of Embodiment 5 of the present invention Front view of conventional heat transfer fin Bottom view of conventional heat transfer fin Enlarged perspective view of main part of conventional heat transfer fin An enlarged perspective view of another main part of the heat transfer fin of the conventional example Perspective view of finned tube heat exchanger

DESCRIPTION OF SYMBOLS 10 Heat transfer fin 10a Windward front edge part of heat transfer fin 11 Fin collar 11a Through-hole 12 Heat transfer tube 13, 23, 33 Cut 14, 24, 34, 44a-44c, 54a-54c for forming a mountain part, 64a-64c, 74 Mountain leeward opening 15, 25, 35, 45a-45c, 55a-55c, 65a-65c, 75 Mountain ridge with leeward opening 16a, 36a Mountain ridge summit 16b, 36b Mountain ridges 16, 26, 36 Mountain ridges 17a, 17b, 27a, 27b Mountain slopes 18, 18a Straight line 18b connecting the centers of fin collars 11 or heat transfer tubes 12 adjacent to each other in the step direction Windward tangent line connecting fin collars 11 adjacent to each other in the step direction 80 Notch for forming the rising piece 81 Basic line for folding the rising piece 82 Launch piece

Claims (12)

A plurality of heat transfer fins stacked substantially in parallel at a predetermined interval; and a plurality of heat transfer tubes penetrating the heat transfer fins in a direction substantially perpendicular to the plane direction of the heat transfer fins, A substantially cylindrical fin collar extending in a direction substantially orthogonal to the planar direction of the heat transfer fin is formed around the through hole of the heat transfer fin passing therethrough, and the heat transfer tube is in close contact with the fin collar The fin tube type heat exchanger is configured to perform heat exchange between the gas flowing in the planar direction of the heat transfer fin and the thermal refrigerant flowing inside the heat transfer tube.
The heat transfer fin is provided with a cut only in a step direction that is substantially perpendicular to the flow direction of the gas, and the heat transfer fin portion on the windward side where the gas flows in the cut is raised so that the cut is made on the leeward side. A fin tube type heat exchange characterized in that it does not form the peak portion at a position crossing a straight line passing through the center of the heat transfer tube and parallel to the gas flow direction. vessel. The fin tube type heat exchanger according to claim 1, wherein the opening has a substantially triangular shape. The fin tube type heat exchanger according to claim 1, wherein the shape of the opening is substantially trapezoidal. The fin tube type heat exchanger according to claim 1, wherein the opening has a substantially arc shape. A plurality of the crests having the opening on the leeward side are formed, and the notch of the crest formed on the leeward side from a tangent line connecting the upwind side of the fin collar adjacent in the step direction is defined as the width of the heat transfer fin. The finned tube heat exchanger according to any one of claims 1 to 4, wherein the finned tube heat exchanger is arranged in a shifted direction. A plurality of the crests having the opening on the leeward side are formed, and the cuts in the crests are not formed on the leeward side from a tangent line connecting the upwind sides of the fin collars adjacent in the step direction. Item 5. The finned tube heat exchanger according to any one of Items 1 to 4. A plurality of the crests having the opening on the leeward side are formed, and the number of crests is increased as the distance from the straight line connecting the fin collars adjacent to each other in the step direction or the center of the heat transfer tube is increased. The finned-tube heat exchanger according to any one of claims 1 to 4. 5. A plurality of the crests having the opening on the leeward side are formed, and the number of crests is greater on the leeward side where the gas flows than on the leeward side. The finned tube heat exchanger according to item 1. The fin tube according to claim 8, wherein a plurality of the crests having the opening on the leeward side are formed, and the number of crests is increased as the distance from the nearest fin collar or the heat transfer tube increases. Mold heat exchanger. The ridge portion having the opening portion on the leeward side is not formed on or near a straight line connecting the centers of the fin collars or the heat transfer tubes adjacent in the step direction. The described finned tube heat exchanger. The heat transfer fin is provided with a notch obtained by cutting one side of the quadrilateral while leaving one side of the quadrilateral as a basic line, and is bent at the basic line to rise up substantially perpendicularly to the heat transfer fin surface. 11. The structure according to claim 1, wherein a predetermined interval when the heat transfer fins are stacked is defined such that the rising pieces are higher than a height of the fin collar. A finned tube heat exchanger according to claim 1. The plane of the rising piece forms an angle of 30 degrees or less with the main flow direction in which the gas flows, that is, the direction parallel to the heat transfer fin and perpendicular to the windward leading edge of the heat transfer fin, and is not horizontal. It formed, The finned tube type heat exchanger of Claim 11 characterized by the above-mentioned.