JP2009127896A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger improved in heat transfer efficiency. <P>SOLUTION: In this heat exchanger which includes a plurality of flat tubes 1 arranged in parallel with each other to circulate a liquid inside thereof, and a plurality of cylindrical fins 4 disposed between the plurality of flat tubes 1, and in which spiral portions 7 are formed on the cylindrical fins 4 so that a gas is circulated in a state of generating swirling flow between the plurality of flat tubes 1 to exchange heat with the liquid in the flat tubes 1, an array of the cylindrical fins 4 is constituted by arranging the cylindrical fins 4 along a plane 2 of the flat tubes 1, and the arrays of the cylindrical fins 4 are stacked in several stages in such a state that an area of an opening 5 surrounded by outer peripheral faces 8 of the plurality of cylindrical fins 4 is reduced. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a heat exchanger such as a radiator.

  Generally, a radiator heat exchanger disposed in a vehicle is disposed between a plurality of flat tubes 1 that are arranged in parallel and in which coolant flows, and a plurality of flat tubes 1 as shown in FIG. And corrugated fins 3 that are in contact with the flat surfaces 2 of the flat tubes 1 on both sides, and when cooling the high-temperature coolant flowing down from the engine, a space in which the corrugated fins 3 are arranged for the wind from the running and cooling fans The high-temperature coolant is cooled via the corrugated fins 3 and the flat tubes 1.

  Moreover, in the example of the heat exchanger of the radiator using the corrugated fin 3, there is one that improves heat transfer efficiency by about 1.4 times by providing a louver on the corrugated fin 3 so as to increase the heat radiation area.

Furthermore, in another example of the heat exchanger of the radiator, a plurality of flat tubes that are arranged in parallel and in which the coolant flows, and pin fins that are arranged between the flat tubes and are in contact with the flat surfaces of the flat tubes on both sides. And a wire fin, and similarly, a high-temperature coolant is cooled by a wind from a running or cooling fan through a flat tube, a pin fin, and a wire fin (for example, Patent Documents 1 to 3). 3).
JP 62-242794 A JP-A-7-159073 JP 2007-3115 A

  However, in recent years, there has been a tendency for the load on the engine to increase due to stricter vehicle exhaust gas regulations, so there is a strong demand to improve heat transfer efficiency so as to improve the cooling performance of the radiator. Moreover, when the louver was provided in the corrugated fin 3, there existed a problem that a pressure loss increased and heat transfer efficiency could not be improved suitably.

  This invention is made | formed in view of the above-mentioned situation, and it aims at providing the heat exchanger which improves heat transfer efficiency.

  The present invention includes a plurality of flat tubes arranged in parallel and through which liquid flows, and a plurality of cylindrical fins arranged between the plurality of flat tubes, and forming a spiral portion in the cylindrical fins. A heat exchanger that allows gas to circulate between a plurality of flat tubes to exchange heat with the liquid in the flat tubes, with cylindrical fins aligned along the plane of the flat tubes The arrangement of the fins and the arrangement of the cylindrical fins are stacked in a plurality of stages so as to reduce the area of the opening surrounded by the outer peripheral surfaces of the plurality of cylindrical fins.

  In addition, the present invention includes a plurality of flat tubes arranged in parallel and through which a liquid flows, and a plurality of cylindrical fins arranged between the plurality of flat tubes, and a spiral portion is formed in the cylindrical fin. Thus, a heat exchanger that can exchange heat with the liquid in the flat tube by circulating a gas so as to generate a swirling flow between the plurality of flat tubes, the cylindrical fins being arranged along the plane of the flat tube The arrangement of the cylindrical fins is arranged side by side, the arrangement of the cylindrical fins is stacked in a plurality of stages, and a gap member is provided in the opening surrounded by the outer peripheral surface of the plurality of cylindrical fins.

  Thus, since the area of the opening surrounded by the outer peripheral surfaces of the plurality of cylindrical fins is reduced in this way, the flow velocity inside the cylindrical fins is increased, and the gas is guided to the inner periphery of the cylindrical fins. The spiral portion of the surface gives a swirl flow to the gas, and as a result, the heat transfer efficiency can be improved. Further, the heat transfer efficiency can be improved as compared with the laminar cooling by the corrugated fin, and the pressure loss can be reduced and the heat transfer efficiency can be improved as compared with the corrugated fin with the louver.

  Moreover, in this invention, you may provide a clearance member in the opening enclosed by the outer peripheral surface of a some cylindrical fin, and the flat surface of a flat tube, If it does in this way, the outer peripheral surface of a some cylindrical fin, and a flat tube As a result, the flow area inside the cylindrical fin is further increased and the gas is guided to the inside of the cylindrical fin to give a swirling flow to the gas by the spiral portion of the inner peripheral surface. In particular, the heat transfer efficiency can be further improved.

  According to the heat exchanger of the present invention described above, the flow velocity inside the cylindrical fin is increased and a spiral flow is given to the gas by the spiral portion, so that various excellent effects such as improvement in heat transfer efficiency can be obtained. Can play.

  Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 and FIG. 2 show a first example of an embodiment for carrying out the present invention. The heat exchanger of the radiator of the first example is arranged in parallel, and a plurality of coolants (liquids) are circulated therein. A flat tube 1 and a plurality of cylindrical fins 4 disposed between the plurality of flat tubes 1 are provided.

  Each of the plurality of cylindrical fins 4 is formed of a cylindrical body having the same diameter, and a plurality of cylindrical fins 4 are arranged in contact with each other along the flat surface 2 of the flat tube 1 to form an array in one row. The cylindrical fins 4 are arranged in two stages along the width direction between the flat tubes 1 (direction perpendicular to the flat surface 2 of the flat tubes 1), and one row of the cylindrical fins 4 is the flat surface 2 of one flat tube 1. The cylindrical fins 4 in the other row are arranged so as to contact the plane 2 of the other flat tube 1.

  Further, as shown in FIGS. 1 and 3, the second-stage arrangement of the cylindrical fins 4 is the arrangement direction (the radial direction of the cylindrical fins 4 and the extending direction of the flat surface 2 of the flat tube 1) with respect to the first-stage arrangement. ), The distance of the radius of the cylindrical fins 4 is shifted so that two cylindrical fins 4 on the first stage side are in contact with one cylindrical fin 4, and the outer peripheral surfaces of the plurality of cylindrical fins 4 The area of the opening 5 surrounded by is reduced. Here, the second-stage arrangement of the cylindrical fins 4 is arranged in the arrangement direction (the radial direction of the cylindrical fins 4 and the extending direction of the flat surface 2 of the flat tube 1) with respect to the first-stage arrangement as shown in FIG. When it is arranged at the same position and one cylindrical fin 4 is in contact with one cylindrical fin 4, the area of the opening 5a surrounded by the outer peripheral surfaces of the plurality of cylindrical fins 4 is as follows. The area of the opening 5 shown in the first example of implementation of the present invention needs to be at least smaller than the area of the opening 5a.

  Further, the inner peripheral surface 6 of the cylindrical fin 4 is provided with a spiral portion 7 formed at a predetermined lead pitch along the extending direction (axial direction) of the cylindrical fin 4 as shown in FIG. Here, the spiral portion 7 is preferably a spiral convex body formed by convex portions.

  Hereinafter, the operation of the first example of the embodiment of the present invention will be described.

  When the high-temperature coolant flowing down from the engine or the like is cooled by the heat exchanger of the radiator, the high-temperature coolant is allowed to flow through the flat tube 1 and at the same time, wind (gas) is cylindrical between the flat tubes 1. It distribute | circulates so that the extension direction of the fin 4 may be met.

  Next, by reducing the area of the opening 5 surrounded by the outer peripheral surfaces 8 of the plurality of cylindrical fins 4, the flow velocity of the internal space of the cylindrical fins 4 is increased and the wind flows down, and the inner peripheral surface 6 of the cylindrical fins 4. The spiral portion 7 imparts a swirl flow to the wind, activates the wind flow, reduces the wind boundary layer on the surface of the heat transfer surface of the cylindrical fin 4, and extends the wind flow distance to flow down.

  Thus, the swirling wind exchanges heat with the coolant via the cylindrical fins 4 and the flat tubes 1 to cool the high-temperature coolant.

  Here, as shown in FIG. 5, when the area of the opening 5 on the outer peripheral surface 8 side is reduced by the arrangement and stacking (oblique stacking) of the cylindrical fins 4 (FIG. 3), the arrangement of the cylindrical fins 4 and When the area of the opening 5 on the outer peripheral surface 8 side is large by stacking (vertical stacking) (FIG. 4), the heat transfer coefficient is compared. In the case of oblique stacking (FIG. 3), the case of vertical stacking ( Compared with FIG. 4), the heat transfer coefficient was improved by about 15%, and the effect of reducing the area of the opening 5 was clear.

  Thus, according to this, the openings 5 having a small area surrounded by the outer peripheral surfaces 8 of the plurality of cylindrical fins 4 are reduced by the arrangement and the stacked state of the plurality of cylindrical fins 4. While increasing the flow velocity, the wind (gas) is guided to the inside of the cylindrical fin 4, and the swirl flow is given to the wind (gas) by the spiral portion 7 of the inner peripheral surface 6, and as a result, the heat transfer efficiency can be improved. . Further, the heat transfer efficiency can be improved as compared with the laminar cooling by the corrugated fin, and the pressure loss can be reduced and the heat transfer efficiency can be improved as compared with the corrugated fin with the louver. Furthermore, since heat transfer efficiency is improved, a heat exchanger such as a radiator can be reduced in size.

  The second embodiment of the present invention will be described below with reference to the drawings.

  6 and 7 show a second example of the embodiment of the present invention. The heat exchanger of the radiator of the second example is arranged in parallel and a plurality of coolants (liquids) are circulated therein. A flat tube 1 and a plurality of cylindrical fins 9 disposed between the plurality of flat tubes 1 are provided.

  Each of the plurality of cylindrical fins 9 is configured by a cylindrical body having the same diameter, and a plurality of cylindrical fins 9 are arranged in contact with each other along the flat surface 2 of the flat tube 1 to form a one-row arrangement. The cylindrical fins 9 are arranged in two stages along the width direction between the flat tubes 1 (direction perpendicular to the flat surface 2 of the flat tubes 1), and one row of the cylindrical fins 9 is the flat surface 2 of one flat tube 1. The cylindrical fins 9 in the other rows are arranged so as to contact the flat surface 2 of the other flat tube 1.

  Further, as shown in FIG. 6, the second stage arrangement of the cylindrical fins 9 is along the arrangement direction (the radial direction of the cylindrical fins 9 and the extending direction of the flat surface 2 of the flat tube 1) with respect to the first stage arrangement. Thus, two cylindrical fins 9 on the first stage are in contact with one cylindrical fin 9 so that the distance corresponding to the radius of the cylindrical fin 9 is shifted. Here, as shown in FIG. 7, the second-stage arrangement of the cylindrical fins 9 is in the arrangement direction (the radial direction of the cylindrical fins 9 and the extending direction of the flat surface 2 of the flat tube 1) with respect to the first-stage arrangement. They may be arranged at the same position so that one cylindrical fin 9 is in contact with one cylindrical fin 9.

  As shown in FIGS. 6 and 7, the openings 11 and 12 surrounded by the outer peripheral surface 10 of the plurality of cylindrical fins 9 are provided with gap members 13 and 14 to reduce the area of the openings 11 and 12. The opening 15 surrounded by the outer peripheral surface 10 of the plurality of cylindrical fins 9 and the flat surface 2 of the flat tube 1 is provided with a gap member 16 so as to reduce the area of the opening 15. Here, the gap members 13, 14, and 16 are preferably brazed of a metal material or the like that can be brazed. However, if the gaps 11, 12, and 15 can be closed, they correspond to the shapes of the respective openings 11, 12, and 15. A closing plate may be used. In addition, it is desirable that the gap members 13, 14, 16 close all the openings 11, 12, 15 to completely reduce the area of the openings 11, 12, 15, but the arrangement of the cylindrical fins 9 and the flat tubes 1 is preferable. Alternatively, some of the areas of the openings 11, 12, 15 may be reduced by closing a part of the openings 11, 12, 15 by a wind flow or the like.

  Furthermore, the inner peripheral surface 17 of the cylindrical fin 9 is provided with a spiral portion 7 (see FIG. 2) formed at a predetermined lead pitch along the extending direction (axial direction) of the cylindrical fin 9. Here, the spiral portion 7 is preferably a spiral convex body formed by convex portions.

  Hereinafter, the operation of the second example of the embodiment of the present invention will be described.

  When the high-temperature coolant flowing down from the engine or the like is cooled by the heat exchanger of the radiator, the high-temperature coolant is allowed to flow through the flat tubes 1 at the same time as in the first example. The wind (gas) is circulated along the extending direction of the cylindrical fin 9.

  Next, by reducing the area of the openings 11, 12, 15 surrounded by the outer peripheral surfaces 10 of the plurality of cylindrical fins 9 by the gap members 13, 14, 16, the flow velocity in the internal space of the cylindrical fins 9 is increased and wind is increased. The wind is swirled by the spiral portion 7 of the inner peripheral surface 17 of the cylindrical fin 9, and the wind flow is activated to reduce the wind boundary layer on the surface of the heat transfer surface of the cylindrical fin 9, and Extend the distance that the circulates and let it flow down.

  Thus, the swirling wind exchanges heat with the coolant via the cylindrical fins 9 and the flat tubes 1 to cool the high-temperature coolant.

  Here, as shown in FIG. 8, when the area of the openings 11 and 12 on the outer peripheral side is reduced using the gap members 13 and 16 (FIG. 6), the outer periphery without applying the gap members 13 and 16 is used. When the area of the openings 11 and 12 on the side is large (FIG. 3) in terms of thermal efficiency, the gap members 13 and 16 are not applied when the gap members 13 and 16 are used (there is a gap member, FIG. 6). Compared to the case (no gap member, FIG. 3), the thermal efficiency was improved by about 10%, and the effect of reducing the area of the openings 11 and 12 was apparent.

  Thus, since the openings 11 and 12 having a small area surrounded by the outer peripheral surfaces 10 of the plurality of cylindrical fins 9 are reduced by the arrangement of the gap members 13 and 14, the flow velocity inside the cylindrical fins 9 is reduced. At the same time, the wind (gas) is guided to the inside of the cylindrical fin 9 to give a swirl flow to the wind (gas) by the spiral portion 7 (see FIG. 2) of the inner peripheral surface 17, and as a result, the heat transfer efficiency is improved. be able to. Further, the heat transfer efficiency can be improved as compared with the laminar cooling by the corrugated fin, and the pressure loss can be reduced and the heat transfer efficiency can be improved as compared with the corrugated fin with the louver. Furthermore, since heat transfer efficiency is improved, a heat exchanger such as a radiator can be reduced in size.

  Further, in the second example of the embodiment of the present invention, when the gap member 16 is provided in the opening 15 surrounded by the outer peripheral surface 10 of the plurality of cylindrical fins 9 and the flat surface 2 of the flat tube 1, the plurality of cylindrical fins 9. The opening 15 having a small area surrounded by the outer peripheral surface 10 and the flat surface 2 of the flat tube 1 is reduced, so that the flow velocity inside the cylindrical fin 9 is further increased and gas is guided to the inside of the cylindrical fin 9. A spiral flow is given to the gas by the spiral portion 7 of the peripheral surface 17, and as a result, the heat transfer efficiency can be further improved.

  Note that the heat exchanger of the present invention is not limited to the above-described embodiments. The gas may not only cool a high-temperature liquid, but the gas may raise the temperature of a low-temperature liquid, Of course, the exchanger is not limited to a radiator, and may be applied to devices other than the vehicle. In addition, various changes may be made without departing from the scope of the present invention.

It is a perspective view which shows the 1st example of the form which implements this invention. It is an enlarged view which shows the spiral part of a cylindrical fin. It is a first example of the embodiment for carrying out the present invention, and is a front view showing a configuration in which an array of cylindrical fins is stacked in two stages and one row of cylindrical fins is shifted from another row. It is a comparative example compared with the 1st example of the form which carries out the present invention, and is a front view showing the composition which laminated the arrangement of the cylindrical fin in two steps, and arranged one row of the cylindrical fin in the same state as the other row. . It is the graph which compared the case where the area of an opening was reduced (diagonal lamination) and the case where the area of an opening was large (vertical lamination) by heat transfer rate. It is a 2nd example of embodiment which implements this invention, Comprising: It is a front view which shows the structure which laminated | stacked the arrangement | sequence of a cylindrical fin in two steps, and shifted and arrange | positioned one row of cylindrical fins with respect to the other row. It is a front view which shows the structure of the 2nd example of embodiment which implements this invention, Comprising: The arrangement | sequence of a cylindrical fin is laminated | stacked on two steps, and the structure which has arrange | positioned one row of a cylindrical fin in the same state as another row. It is the graph which compared the case where the area of an opening is reduced (with a gap member) and the case where the area of an opening is large (without a gap member) by thermal efficiency. It is a perspective view which shows the structure of the conventional heat exchanger.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Flat tube 2 Plane 4 Cylindrical fin 5 Opening 7 Spiral part 8 Outer peripheral surface 9 Cylindrical fin 10 Outer peripheral surface 11 Opening 12 Opening 13 Gap member 14 Gap member 15 Opening 16 Gap member

Claims (3)

  A plurality of flat tubes arranged in parallel and through which liquid flows; and a plurality of cylindrical fins arranged between the plurality of flat tubes, and forming a spiral portion in the cylindrical fins, thereby forming a plurality of flat tubes. A heat exchanger that allows gas to flow between tubes to exchange heat with the liquid in the flat tube, and arranges the cylindrical fins by arranging the cylindrical fins along the plane of the flat tube. A heat exchanger characterized in that the arrangement of the cylindrical fins is stacked in a plurality of stages so as to reduce the area of the opening surrounded by the outer peripheral surfaces of the plurality of cylindrical fins.   A plurality of flat tubes arranged in parallel and through which liquid flows; and a plurality of cylindrical fins arranged between the plurality of flat tubes, and forming a spiral portion in the cylindrical fins, thereby forming a plurality of flat tubes. A heat exchanger that allows gas to flow between tubes to exchange heat with the liquid in the flat tube, and arranges the cylindrical fins by arranging the cylindrical fins along the plane of the flat tube. A heat exchanger comprising: a plurality of stages of cylindrical fins arranged in layers, and a gap member provided in an opening surrounded by the outer peripheral surfaces of the plurality of cylindrical fins.   The heat exchanger according to claim 2, wherein a gap member is provided in an opening surrounded by an outer peripheral surface of the plurality of cylindrical fins and a flat surface of the flat tube.

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