JP5589860B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger, and is suitable for use in, for example, a heat exchanger for vehicle air conditioning (refrigerant radiator, refrigerant evaporator, heater core for heating) and the like.

  A typical example of a conventional heat exchanger is a flat tube formed in a flat cross section through which a fluid such as water or refrigerant flows, and a fin joined to a flat portion (flat surface) formed of a flat surface of the flat tube. Thus, a heat exchange core part is configured.

  By the way, the air flowing outside the tube is different in temperature difference between the fluid flowing in the tube between the air flowing near the outer wall surface of the tube and the air flowing away from the outer wall surface of the tube, and there is a temperature boundary layer on the air side. Arise. As a result, as the distance from the outer wall surface of the tube increases, the temperature difference between the air flowing outside the tube and the fluid flowing in the tube increases, resulting in a problem that heat transfer performance decreases.

  On the other hand, for example, in Patent Document 1, in order to disturb the air flowing along the outer wall surface of the tube, the outer wall surface of the tube is provided with a protrusion (outer protrusion portion) that protrudes outward, thereby The temperature distribution of the air flowing on the wall surface is made uniform to suppress the deterioration of the heat transfer performance on the air side.

  Moreover, in patent document 1, in order to disturb the fluid which flows through the inside of a tube, the temperature distribution of the fluid which flows through the inside of a tube is made uniform by providing the protrusion (inside protrusion part) which protrudes inside on the inner wall surface of a tube. The reduction of the heat transfer performance on the fluid side is suppressed. In Patent Document 1, the inner protrusions are equally provided on the inner wall surface of the tube corresponding to the outer protrusions (see FIGS. 1 and 5 of Patent Document 1).

JP 05-340686 A

  However, as in Patent Document 1, when the inner protrusions are provided corresponding to the outer wall surface of the tube, the pressure loss of the fluid increases due to the plurality of inner protrusions, which leads to a decrease in the flow rate flowing through the heat exchanger. There is a problem that it becomes difficult to exhibit the performance.

  In view of the above points, an object of the present invention is to reduce pressure loss of a fluid flowing in a tube while suppressing a decrease in heat transfer performance in a heat exchanger.

To achieve the above object, according to the invention of claim 1, having a cross-sectional flat shape, a plurality of tubes (1) through which fluid flows therein, is bonded to the flat surface of the tube (1) (10) more a heat exchanger and a fin (2) to increase the heat exchange area of the air flowing around the tube (1), the tube (1) is projecting outwardly from the flat surface (10) Te And the plurality of inner projections (12) projecting inward from the flat surface (10), and the number of inner projections (12) is the number of outer projections (11). rather less than, the inner projections (12), compared inner surface of the portion outside projections of the tube (1) (11) is formed, is disposed so as to face in the thickness direction of the tube (1), The tube (1) has a pair of flat surfaces (10). One flat surface (10) of two flat surfaces (10) having a pair of flat surfaces (10) is provided with an outer protrusion (11), but an inner protrusion (12) It is not provided, and the other flat surface (10) is provided with the inner protrusion (12) but not with the outer protrusion (11) .

  According to this, since the plurality of outer protrusions (11) and the plurality of inner protrusions (12) are provided on the flat surface (10) of the tube (1), the air flowing around the tube (1) is disturbed. At the same time, the fluid flowing in the tube (1) can be disturbed.

  In addition, since the number of the inner protrusions (12) is smaller than the number of the outer protrusions (11), the inner protrusions (12) are provided corresponding to the outer protrusions (11) as in the prior art. Compared with the structure to provide, the pressure loss of the fluid which flows through the inside of the tube (1) by the inner protrusion (12) can be reduced.

  Therefore, it is possible to reduce the pressure loss of the fluid flowing in the tube (1) while suppressing the deterioration of the heat transfer performance in the heat exchanger.

  Specifically, as in the invention according to claim 2, in the heat exchanger according to claim 1, the interval between the inner protrusions (12) arranged in the flow direction of the fluid flowing in the tube (1). Can be made wider than the interval between the outer protrusions (11) arranged in the flow direction of the fluid flowing in the tube (1).

  In the invention according to claim 3, in the heat exchanger according to claim 1 or 2, the interval between the inner protrusions (12) arranged in the flow direction of the fluid flowing in the tube (1) is plural. It is characterized in that it is at least twice the dimension in the flow direction of the fluid flowing in the tube (1) in the inner protrusion (12).

  According to this, the pressure loss of the fluid flowing through the tube (1) due to the inner protrusion (12) can be sufficiently reduced.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a front view of the heater core which concerns on 1st Embodiment. It is a perspective view which shows the principal part of the heater core which concerns on 1st Embodiment. It is explanatory drawing explaining the flow of the engine cooling water which flows through the inside of a tube. It is a front enlarged view which shows the principal part of the heater core which concerns on 1st Embodiment. It is AA sectional drawing of FIG. It is explanatory drawing explaining the arrangement | positioning form of the outer side projection part and inner side projection part which concern on 1st Embodiment. It is a graph which shows the relationship between the space | interval of the inner side protrusion parts adjacent to the fluid flow direction of engine cooling water, and the vorticity of the engine cooling water which flows through the inside of a tube. It is a graph which shows the relationship between the space | interval of the inner side protrusion parts adjacent to the fluid flow direction of engine cooling water, and the pressure loss in a tube. It is explanatory drawing explaining the space | interval of the inner side protrusion parts 12 adjacent in the fluid flow direction of engine cooling water. It is explanatory drawing explaining the arrangement | positioning form of the outer side projection part and inner side projection part which concern on 2nd Embodiment. It is explanatory drawing explaining the arrangement | positioning form of the outer side projection part and inner side projection part which concern on 3rd Embodiment. It is explanatory drawing explaining the modification of the shape of an outer side protrusion part and an inner side protrusion part. It is a perspective view which shows the principal part of the heater core which concerns on other embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
1st Embodiment of this invention is described based on FIGS. In the present embodiment, the heat exchanger according to the present invention is applied to a heater core that is a heat exchanger for heating of a vehicle air conditioner, and FIG. 1 is a front view of the heater core according to the present embodiment. FIG. 2 is a perspective view showing a main part of the heater core according to the present embodiment.

  The heater core is a heat exchanger for heating that heats the air that is blown into the vehicle interior by exchanging heat between the engine cooling water (hot water) that is warmed by the heat generated by the engine of the vehicle and the air that is blown into the vehicle interior. The heater core is supplied with engine cooling water by a water pump (not shown) provided in an engine cooling water circuit (not shown), and a blower fan (not shown) arranged on the vehicle rear side with respect to the heater core. ) To supply air.

  As shown in FIG. 1, the heater core heat-transfers a plurality of tubes 1 through which engine coolant (fluid) flows, and air that is joined to the outer surface of the tubes 1 and blows into the vehicle interior (air that flows around the tubes). A heat exchanging core portion including fins 2 and the like that increase the area (heat exchanging area) and promote heat exchange between engine coolant and air is provided. Moreover, the side plate which extends in the direction orthogonal to the longitudinal direction of the tube 1 (the left and right direction on the paper surface) at both ends in the longitudinal direction of the tube 1 and communicates with each tube 1 and a side plate that serves as a reinforcing member for the heat exchange core portion (Insert) 4 etc. are provided.

  In this embodiment, the tube 1, the fin 2, the header tank 3, and the side plate 4 are all made of metal (for example, aluminum alloy), and these members 1 to 4 are joined by brazing.

  As shown in FIG. 2, the tube 1 of the present embodiment is a tube having a flat cross section in which an engine cooling water passage (fluid passage) is formed inside (in the tube), and the major axis direction of the cross section is the air flow direction. It is joined to the header tank 3 so as to match.

  The tube 1 has a pair of flat surfaces 10 formed of flat surfaces extending along the air flow direction. And the fin 2 is joined to the outer surface of the flat surface 10 of the tube 1 by brazing. The fin 2 is a corrugated fin formed in a wave shape so as to have a flat plate portion 2a having a plate surface and a curved portion 2b curved so as to connect adjacent flat plate portions 2a. The curved portion 2 b of the fin 2 is brazed to the flat surface 10 of the tube 1.

  A plurality of armor window-like louvers 2c are formed on the flat plate portion 2a of the fin 2 as protrusions that protrude so as to intersect the air flow direction. Specifically, the plurality of louvers 2c are formed by cutting and raising a part of the flat plate portion 2a. The air flowing on the edge of the louver 2c is collided to increase the heat transfer coefficient with the air by the tip effect.

  Here, in order to avoid poor connection between the flat surface 10 of the tube 1 and the like, the positions of both end portions of the louver 2c are separated from the flat surface 10 of the tube 1 and the curved portion 2b which is a bonding site. Therefore, the fin 2 has a cut-and-raised portion 2d where the louver 2c is provided, and a portion other than the cut-and-raised portion 2d, that is, between both ends of the louver 2c in the fin 2 and the flat surface 10 of the tube 1. There is a non-cut portion 2e which is a portion where the louver 2c is not formed.

  Of the pair of flat surfaces 10 in the tube 1, one flat surface 10 (the flat surface on the near side in FIG. 2) has a hemispherical shape that protrudes toward the outside through which air flows on the outer surface (outer wall surface). A plurality of outer protrusions 11 are formed. The outer protrusion 11 functions as a resistor that disturbs the flow of air that passes through the uncut portion 2 e of the fin 2. In addition, the inner surface of the site | part in which the outer side projection part 11 in one flat surface 10 was formed is dented toward the outer side.

  Further, of the pair of flat surfaces 10 in the tube 1, the other flat surface 10 (the flat surface on the back side in FIG. 2) protrudes toward the inner surface (inner wall surface) toward the inner side where the engine coolant flows. A plurality of hemispherical inner protrusions 12 are formed. The inner protrusion 12 functions as a resistor that disturbs the flow of engine cooling water flowing inside the tube 1. In addition, the outer surface of the site | part in which the inner side projection part 12 in the other flat surface 10 was formed is dented toward the inner side.

  In the present embodiment, the protruding shapes such as the diameter and the protruding height of the protruding portions 11 and 12 are the same in the outer protruding portion 11 and the inner protruding portion 12, respectively.

  FIG. 3 is an explanatory diagram for explaining the flow of engine cooling water flowing in the tube 1. As shown in FIG. 3, the temperature difference between the engine coolant and the inner surface of the flat surface 10 of the tube 1 increases. The engine coolant having such a temperature distribution is disturbed by collision of the engine coolant flowing along the inner surface of the tube 1 with the inner protrusion 12, and the engine coolant flowing along the inner surface of the tube 1 The temperature distribution is reduced by replacing the engine coolant flowing away from the inner surface. For this reason, in the structure which provides the inner side projection part 12 in the inner surface of the flat surface 10 of the tube 1, the improvement of the heat transfer performance by the side of engine cooling water can be aimed at.

  However, in the configuration in which the inner protrusion 12 is provided on the inner surface of the flat surface 10 of the tube 1, there is a trade-off that the pressure loss ΔP of engine cooling water in the tube 1 is increased.

  Therefore, in this embodiment, the number of the inner protrusions 12 on the flat surface 10 of the tube 1 is made smaller than the number of the plurality of outer protrusions 11, thereby suppressing the increase in the pressure loss ΔP of the engine cooling water. Yes.

  A specific arrangement form of the protrusions 11 and 12 will be described with reference to FIGS. FIG. 4 is an enlarged front view showing the main part of the heater core, and FIG. 5 is a cross-sectional view taken along the line AA of FIG. FIG. 6 is an explanatory diagram for explaining the arrangement of the outer protrusions 11 and the inner protrusions 12, in which FIG. 6 (a) shows a perspective view of the tube 1, and FIG. 6 (b) shows (a). B shows a view in the direction of arrow B, and (c) shows a view in the direction of arrow C in (a).

  As shown in FIG. 4, the plurality of outer protrusions 11 are sandwiched between adjacent curved portions 2 b in the fin 2 in the fluid flow direction of the engine coolant flowing in the tube 1 (the direction orthogonal to the air flow direction). As shown in FIG.

  Here, the outer protrusion 11 is formed such that the protrusion height H in the direction orthogonal to the flat surface 10 is equal to or greater than the non-cut portion length L of the non-cut portion 2e. Specifically, the ratio (H / L) of the protrusion height H of the outer protrusion 11 to the non-cut portion length L is within a range where the heat transfer performance of the heater core can be sufficiently improved (for example, 1. 0 to 3.5).

  On the other hand, the plurality of inner protrusions 12 are arranged at equal intervals in the fluid flow direction of the engine coolant flowing in the tube 1 (the direction orthogonal to the air flow direction). The plurality of inner protrusions 12 of the present embodiment are arranged such that the interval P2 between the adjacent inner protrusions 12 is wider than the interval P1 between the adjacent outer protrusions in the fluid flow direction of the engine coolant. ing.

  Further, as shown in FIG. 5, the plurality of outer protrusions 11 are arranged in a line at equal intervals in the air flow direction of the air flowing outside the tube 1. On the other hand, the plurality of inner protrusions 12 are arranged in a line at equal intervals in the air flow direction of the air flowing outside the tube 1 corresponding to the plurality of outer protrusions 11.

  For example, when 16 outer protrusions 11 are provided on one flat surface 10 of the tube 1 and eight inner protrusions 12 are provided on the other flat surface 10, as shown in FIG. A configuration in which four outer projections 11 are arranged in a lattice pattern on the surface 10 along the fluid flow direction and the air flow direction, and the inner projections 12 are arranged at a distance from the outer projections 11 in the fluid flow direction. To do.

  Here, the space | interval of the inner side protrusion parts 12 adjacent in the fluid flow direction of engine cooling water is demonstrated based on FIGS. FIG. 7 is a chart showing the relationship between the distance between the inner protrusions adjacent to each other in the direction of fluid flow of the engine coolant and the vorticity of the engine coolant flowing in the tube 1, and FIG. 6 is a chart showing a relationship between an interval between inner protrusions adjacent in the flow direction and a pressure loss ΔP in the tube 1. Moreover, FIG. 9 is explanatory drawing explaining the space | interval of the inner side projection parts adjacent in the fluid flow direction of engine cooling water.

  As shown in FIG. 7, the distance P2 between the inner protrusions 12 adjacent to each other in the fluid flow direction of the engine cooling water is in a range up to twice the dimension of the inner protrusion 12 in the flow direction of the fluid flowing in the tube 1 (P2). In <2d), the vorticity of the engine cooling water is maintained substantially constant. In the present embodiment, the dimension in the flow direction of the fluid flowing in the tube 1 in the inner protrusion 12 corresponds to the inner diameter d of the inner protrusion 12.

  Further, as shown in FIG. 8, the inner protrusions are within a range (P2 <2d) in which the interval P2 between the inner protrusions 12 adjacent to each other in the fluid flow direction of the engine coolant is up to twice the inner diameter d of the inner protrusion 12. As the distance between the portions 12 decreases, the pressure loss in the tube 1 increases rapidly.

  Thus, when the interval P2 between the inner protrusions 12 adjacent to each other in the fluid flow direction of the engine cooling water is set to a range up to twice the inner diameter d of the inner protrusion 12, the interval between the inner protrusions 12 is reduced. However, there is no difference in the disturbance effect of the engine cooling water, and the pressure loss ΔP in the tube 1 increases.

  On the other hand, as shown in FIG. 7, in the range (P2 ≧ 2d) in which the interval P2 between the inner protrusions 12 adjacent to each other in the fluid flow direction of the engine cooling water is more than twice the inner diameter d of the inner protrusion 12. As the distance between the protrusions 12 increases, the vorticity gradually decreases.

  Further, as shown in FIG. 8, the tube 1 is within a range in which the interval between the inner protrusions 12 adjacent to each other in the fluid flow direction of the engine coolant is at least twice the inner diameter d of the inner protrusion 12 (P2 ≧ 2d). The internal pressure loss gradually decreases as the distance P2 between the inner protrusions 12 increases.

  As described above, when the interval P2 between the inner protrusions 12 adjacent to each other in the fluid flow direction of the engine cooling water is set to be twice or more the inner diameter d of the inner protrusion 12, the interval P2 between the inner protrusions 12 is enlarged. However, the pressure loss ΔP in the tube 1 can be sufficiently reduced while obtaining the disturbance effect of the engine cooling water.

  For this reason, in this embodiment, as shown in FIG. 9, the interval P2 between the inner projections 12 adjacent to each other in the fluid flow direction of the engine cooling water is set to an interval more than twice the inner diameter d of the inner projection 12. doing.

  According to the heater core of the present embodiment described above, by providing the plurality of outer protrusions 11 on one flat surface 10 of the tube 1, the air flowing around the tube 1 is disturbed, and the air side of the tube 1 is Heat transfer performance can be improved.

  Further, by providing a plurality of inner protrusions 12 on the other flat surface 10 of the tube 1, engine cooling water flowing in the tube 1 is disturbed, and the heat transfer performance on the engine cooling water side in the tube 1 is improved. be able to.

  In addition, since the number of the inner protrusions 12 is smaller than the number of the outer protrusions 11, the inner protrusions 12 can be compared with the structure in which the inner protrusions 12 are provided corresponding to the outer protrusions 11. The pressure loss of engine cooling water flowing in the tube 1 can be reduced.

  Therefore, according to the configuration of the present embodiment, it is possible to reduce the pressure loss of the fluid flowing in the tube 1 while suppressing the deterioration of the heat transfer performance in the heater core.

  In the present embodiment, the interval P2 between the inner projections 12 adjacent to each other in the fluid flow direction of the engine cooling water is set to be an interval more than twice the inner diameter d of the inner projection 12, so the engine by the inner projection 12 While obtaining the disturbance effect of the cooling water, the pressure loss ΔP in the tube 1 can be sufficiently reduced.

  In addition, in this embodiment, since the protrusion height H of the some outer side protrusion part 11 provided in the flat surface 10 of the tube 1 is made into the non-cut part length L or more, the non-cut part 2e in which the louver 2c is not provided. Ventilation resistance of the air flowing through can be increased. As a result, the wind speed, air volume, etc. of the air flowing through the non-cut portion 2e where the louver 2c is not provided on the fin surface are reduced, and the wind speed, air volume, etc. of the air flowing through the cut-and-raised portion 2d provided with the louver 2c are increased. Can be made. Thereby, the effect of improving the heat transfer performance of the heat exchanger can be sufficiently obtained.

  Moreover, in this embodiment, since the protrusion height H of the outer side protrusion part 11 is set to the appropriate range of 1.0-3.5, the heat transfer performance improvement effect is caused without causing deterioration of heat transfer efficiency. Can be sufficiently obtained.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 10 is an explanatory diagram for explaining the arrangement of the outer protrusions 11 and the inner protrusions 12 according to the present embodiment. FIG. 10A shows a perspective view of the tube 1, and FIG. The arrow D figure in (a) is shown, (c) has shown the arrow E figure in (a).

  The heater core of the present embodiment is different from the first embodiment in the arrangement of the outer protrusions 11 and the inner protrusions 12 in the tube 1. In the present embodiment, description of the same or equivalent parts as in the first embodiment will be omitted or simplified.

  In the present embodiment, the plurality of inner protrusions 12 are arranged in a line at equal intervals with an interval wider than the interval between adjacent outer protrusions 11 in the air flow direction of the air flowing outside the tube 1. Also in the flow direction of the engine coolant, they are arranged in a line at equal intervals with an interval wider than the interval between adjacent outer projections 11.

  For example, when 16 outer protrusions 11 are provided on one flat surface 10 of the tube 1 and eight inner protrusions 12 are provided on the other flat surface 10, as shown in FIG. On the surface 10, four outer protrusions 11 are arranged in a lattice pattern along the fluid flow direction and the air flow direction. Then, a plurality of inner protrusions 12 are arranged in two along the fluid flow direction and the air flow direction, and the rows formed by the plurality of inner protrusions 12 in the fluid flow direction and the air flow direction are arranged at a half pitch for each row. Staggered and arranged alternately.

  Thus, also in the form which arrange | positions the several inner side protrusion part 12 in zigzag form, there can exist an effect similar to 1st Embodiment.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG. FIG. 11 is an explanatory diagram for explaining the arrangement of the outer protrusions 11 and the inner protrusions 12 according to this embodiment. FIG. 11A shows a perspective view of the tube 1 and FIG. The F arrow figure in (a) is shown, (c) has shown the G arrow figure in (a).

  The heater core of this embodiment is different from the first and second embodiments in the arrangement of the outer protrusions 11 and the inner protrusions 12 in the tube 1. In the present embodiment, description of the same or equivalent parts as in the first and second embodiments will be omitted or simplified.

  In the present embodiment, the plurality of outer protrusions 11 are disposed on the entire flat surface 10 of the tube 1, whereas the plurality of inner protrusions 12 are disposed on only a part of the entire flat surface 10 of the tube 1. It is configured to do.

  For example, as shown in FIG. 11, the inner protrusion 12 is arranged on the inlet side (upstream side) of the engine cooling water and is not arranged on the outlet side (downstream side) of the engine cooling water. In addition, the space | interval P2 of the inner side protrusion parts 12 of this embodiment is made into the same space | interval as the space | interval P1 of the adjacent outer side protrusion parts 11. FIG.

  In this way, the plurality of inner projections 12 are not arranged over the entire flat surface 10 of the tube 1 but are arranged so as to be partially biased so that the number of inner projections 12 is larger than the number of outer projections 11. The pressure loss ΔP in the tube 1 can be sufficiently reduced.

  In particular, in the configuration in which the inner protrusion 12 is disposed on the inlet side of the engine cooling water as in the present embodiment, the engine cooling water is disturbed on the inlet side of the engine cooling water in the tube 1. Compared with the case where the inner protrusion 12 is disposed on the side (downstream side), it is possible to suppress a decrease in heat transfer performance on the engine coolant side in the tube 1.

(Other embodiments)
As mentioned above, although embodiment of this invention was described, this invention is not limited to this, Unless it deviates from the range described in each claim, it is not limited to the wording of each claim, and those skilled in the art Improvements based on the knowledge that a person skilled in the art normally has can be added as appropriate to the extent that they can be easily replaced. For example, various modifications are possible as follows.

  (1) In each of the above-described embodiments, the arrangement form of the outer projections 11 in the tube 1 is configured to be arranged over the entire flat surface 10 of the tube 1, but the number of inner projections 12 is the number of outer projections 11. As long as the arrangement form is smaller, the arrangement form of the outer protrusions 11 may be arranged on a part of the flat surface 10 of the tube 1.

  (2) In each of the above-described embodiments, the example in which each of the outer protrusion 11 and the inner protrusion 12 is formed of a hemispherical protrusion has been described, but the present invention is not limited to this. For example, as shown in FIG. 12, each of the outer protrusion 11 and the inner protrusion 12 may be a semi-ellipsoidal protrusion having a long diameter along the air flow direction. FIG. 12 is an explanatory diagram for explaining a modification of the shape of each of the outer protrusion 11 and the inner protrusion 12.

  (3) In each of the above-described embodiments, the outer protrusion 11 is formed by raising a part of the flat surface 10 from the inner side where the engine cooling water flows toward the outer side where the air flows. However, the present invention is not limited to this. . For example, the outer protrusion 11 may be configured separately from the tube 1 and may be provided by being joined to the outer wall surface of the flat surface 10 of the tube 1.

  Similarly, although the inner protrusion 12 is formed by raising a part of the flat surface 10 from the outside where the air flows to the inside where the engine coolant flows, it is not limited to this. For example, the inner protrusion 12 may be configured separately from the tube 1 and may be provided by being joined to the inner wall surface of the flat surface 10 of the tube 1.

  Thus, when it is set as the structure which makes the tube 1, the outer side protrusion part 11, and the inner side protrusion part 12 into a different body, what is necessary is just to join the outer side protrusion part 11 and the inner side protrusion part 12 to the existing tube 1, and processing the tube 1 itself. Therefore, the productivity of the heat exchanger can be improved.

  (4) In each of the above-described embodiments, the configuration in which the fin 2 of the heat exchanger is a corrugated fin formed on the wave is exemplified, but the present invention is not limited to this. For example, as shown in FIG. It is good also as a plate fin shape | molded by flat form.

  (5) In each above-mentioned embodiment, although the projection part of the fin 2 is comprised by the armor window-like louver 2c formed by raising a part of the flat plate part 2a of the fin 2, it is not limited to this. . The protrusions of the fins 2 may be constituted by, for example, band-shaped offsets formed by bending the fin flat plate portions 2a, pins arranged in a staggered manner on the fin flat plate portions 2a, or the like.

  (6) In the above-described embodiments, the tube 1 and the fin 2 are joined by brazing. However, the present invention is not limited to this. For example, the tube 1 and the fin 2 are expanded by expanding the tube 1. It may be mechanically coupled.

  (7) In each of the above-described embodiments, the present invention is applied to the heater core of the vehicle air conditioner. However, the present invention is not limited to the heater core, and for example, the present invention is applied to a radiator, an evaporator (evaporator), a condenser (condenser), and the like. Can be applied. Moreover, this invention is applicable not only to the heat exchanger for vehicle air conditioners but to the heat exchanger of other apparatuses.

1 Tube 2 Fin 10 Flat Surface 11 Outer Projection 12 Inner Projection

Claims (3)

Heat exchange area between a plurality of tubes (1) having a flat cross-sectional shape and fluid flowing therein and air flowing around the tubes (1) joined to the flat surfaces (10) of the tubes (1) A heat exchanger with fins (2) for increasing
The tube (1) includes a plurality of outer protrusions (11) protruding outward from the flat surface (10) and a plurality of inner protrusions (12) protruding inward from the flat surface (10). ) has the inner protrusion in the number of (12) rather less than the number of the outer projections (11),
The inner protrusion (12) is disposed so as to face the inner surface of the tube (1) where the outer protrusion (11) is formed, in the thickness direction of the tube (1).
The tube (1) has two flat surfaces (10) such that the flat surfaces (10) form a pair,
One flat surface (10) of the pair of flat surfaces (10) is provided with the outer protrusion (11) but not with the inner protrusion (12). The flat surface (10) is provided with the inner protrusion (12) but is not provided with the outer protrusion (11) .   The interval between the inner protrusions (12) aligned in the flow direction of the fluid flowing in the tube (1) is the same between the outer protrusions (11) aligned in the flow direction of the fluid flowing in the tube (1). The heat exchanger according to claim 1, wherein the heat exchanger is wider than the interval.   The interval between the inner protrusions (12) arranged in the flow direction of the fluid flowing in the tube (1) is the flow direction of the fluid flowing in the tube (1) in the plurality of inner protrusions (12). The heat exchanger according to claim 1 or 2, wherein the heat exchanger is at least twice the size.

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