JP2011190966A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger, capable of suppressing deflection of an effluent external fluid from a direction orthogonal to a tube arrangement surface. <P>SOLUTION: The heat exchanger is configured as follows. When a pitch Fp of a planar portion 41 is 1 mm≤Fp≤2.5 mm, a louver inclination angle La is 25°≤La≤40°, and a louver pitch Lp is 0.7 mm≤Lp≤1.2 mm, a predetermined length Lf of a flat portion 44 is set to 25% or less of the length in air circulating direction AA of the planar portion 41 of a fin 40, and the relation of Lf≥(2Lp-1.4)(1.33La<SP>3</SP>-300La<SP>2</SP>+17,100La)/10<SP>5</SP>-5Lp+4.9+(2Lp-1.4)ä0.1085(2Fp-2.9)<SP>2</SP>+0.32(2Fp-2.9)} is satisfied. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heat exchanger in which louvers are formed on fins disposed between tubes.

  Conventionally, heat exchange has been formed by obliquely cutting and raising a louver to promote heat exchange on a fin, with multiple tubes arranged in parallel at intervals and fins arranged between the tubes A container is known (for example, refer to Patent Document 1).

Japanese Patent Laid-Open No. 10-231724

  However, in the above-described conventional heat exchanger, when the external fluid that has passed between the tubes flows out of the heat exchanger, it is deflected in a direction that is inclined with respect to the direction orthogonal to the tube arrangement surface, for example, the external fluid is discharged. Is used as a heat medium, there is a problem in that the external fluid flowing out from the heat exchanger may be unevenly distributed to cause problems such as deterioration in temperature control characteristics.

  The inventors of the present invention have conducted intensive studies including experiments and simulations on this problem, and among the louvers formed in the fins, the louvers cut and raised in the same direction formed in the most downstream portion of the external fluid flow direction. However, it has been found that the external fluid is deflected, and if the flat portion is appropriately provided on the downstream side of the louver, it is possible to suppress the deflection of the flowing-out external fluid.

  The external fluid flowing between the tubes along the fins flows along the louver inclined from one surface side of the fins to the other surface side by the action of the louver formed on the fins, and in a direction perpendicular to the tube arrangement surface. It is flowing with an inclination. Therefore, if a flat portion having a predetermined length is appropriately provided in the flow direction of the external fluid downstream from the louver, the flow of the external fluid deflected by the louver is rectified and the external fluid is orthogonal to the tube arrangement surface. It was found that it can be discharged from the heat exchanger.

  This invention is made | formed in view of the said point, and it aims at providing the heat exchanger which can suppress deflection | deviation of the external fluid which flows out.

In order to achieve the above object, in the invention described in claim 1,
A plurality of tubes (30) through which the first fluid flows are arranged in parallel,
A heat exchanger provided between adjacent tubes (30) with heat exchange promoting means (40) for promoting heat exchange between the first fluid and the second fluid flowing outside the tube (30),
The heat exchange promoting means (40)
A base (41) extending in a flat plate shape in the flow direction (AA) of the second fluid;
A louver part (43) protruding from the base part (41) in a direction intersecting the flow direction (AA) of the second fluid;
It is provided on the most downstream side in the flow direction of the second fluid of the base portion (41), rectifies the second fluid, and blows out toward the direction along the flow direction (AA) on the downstream side from the base portion (41). It has the flat part (44) extended in the distribution direction (AA) of the 2nd fluid, It is characterized by the above-mentioned.

  According to this, the flow direction of the second fluid disturbed by the louver (43) is rectified by the flat portion (44) extending in the flow direction (AA) of the second fluid downstream from the louver (43), and the second The fluid can flow out of the heat exchanger in a direction along the flow direction (AA), that is, in a direction perpendicular to the arrangement surface of the tubes (30). In this way, it is possible to suppress the deflection of the second fluid that is the external fluid that flows out.

In the invention according to claim 2,
The heat exchange promoting means (40) is thermally connected to the tube (30) so that the base (41) is arranged in parallel with the extending direction (BB) of the tube (30) at a base pitch Fp that is a predetermined interval. Fins (40),
The flat portion (44) has a predetermined length Lf in the flow direction (AA) of the second fluid,
The louver part (43) is provided upstream of the second fluid circulation direction (AA) of the flat part (44), and is inclined at a predetermined inclination angle La with respect to the second fluid circulation direction (AA). A plurality of louvers (43) cut and raised in the same direction and parallel to the flow direction (AA) of the second fluid at a predetermined louver pitch Lp,
The flat portion (44) and the formation region of the plurality of louvers (43) are adjacent to each other,
The base pitch Fp is 1 mm ≦ Fp ≦ 2.5 mm, the louver inclination angle La is 25 ° ≦ La ≦ 40 °, the louver pitch Lp is 0.7 mm ≦ Lp ≦ 1.2 mm,
The predetermined length Lf of the flat portion (44) is
And not more than 25% of the length of the flow direction (AA) of the second fluid of the fin (40),
Lf ≧ (2Lp−1.4) (1.33La ³ −300La ² + 17100La) / 10 ⁵ −5Lp + 4.9 + (2Lp−1.4) {0.1085 (2Fp−2.9) ² +0.32 (2Fp -2.9)}
It is characterized by satisfying the relationship.

  According to this, the base portion on which the louver is formed in the fin (40), with the predetermined length Lf of the flat portion (44) being 25% or less of the length of the fin (40) in the flow direction (AA) of the second fluid. (41) The flow direction of the second fluid that has flow-deflected along the louver (43) is rectified by the flat portion (44) on the downstream side of the louver (43) while ensuring heat exchange performance by securing the region. Then, the second fluid can flow out of the heat exchanger in a direction perpendicular to the arrangement surface of the tubes (30). In this way, it is possible to suppress the deflection of the second fluid that is the external fluid that flows out.

  Further, as in the invention described in claim 3, the present invention is also applicable to a heat exchanger in which the base pitch Fp is 1 mm ≦ Fp ≦ 2 mm, the heat transfer area of the fin (40) is secured, and the heat exchange performance is improved. Is effective to apply.

  Further, the invention according to claim 4 is characterized in that the fin (40) has a corrugated shape. According to this, since it is easy to arrange the base (41) in the extending direction of the tube (30) with the base pitch Fp, the manufacturing process of the heat exchanger can be simplified.

  The invention according to claim 5 is a cooling heat exchanger that cools the second fluid by transferring heat from the second fluid to the first fluid, and is downstream of the flow direction (AA) of the second fluid. On the side, there are a heating inlet (8) for guiding the second fluid to the heating means (5) and a bypass inlet (9) for guiding the second fluid to bypass the heating means (5). 30) is arranged side by side in the extending direction (BB).

  According to this, the flow direction of the second fluid, which flows along the louver (43) and is deflected in the direction in which the heating inlet (8) and the bypass inlet (9) are aligned, is located downstream of the louver (43). The flow is rectified by the flat portion (44), and the second fluid can flow out of the heat exchanger in a direction perpendicular to the arrangement surface of the tubes (30). Therefore, it is possible to facilitate the control of distributing the second fluid cooled by the heat exchanger to the heating inlet (8) and the bypass inlet (9).

  In addition, the code | symbol in the parenthesis attached | subjected to each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a mimetic diagram showing roughly composition of a vehicle air conditioner provided with evaporator 4 which is a heat exchanger in one embodiment to which the present invention is applied. 2 is a perspective view showing a schematic configuration of an evaporator 4. FIG. It is the III-III sectional view taken on the line of FIG. 3 is an enlarged cross-sectional view of a main part of a fin 40 of an evaporator 4. FIG. It is a graph for demonstrating how to obtain | require flat part length Lf from which the deflection angle of the outflow air flow from the core part 20 becomes 0 degree in a flow analysis. It is a graph which shows the minimum value of Lf from which the deflection angle of an outflow air flow becomes 0 degree by setting the flat part length Lf as a vertical axis | shaft with the louver inclination angle La as a horizontal axis. It is a graph which shows the minimum value of Lf from which the deflection angle of an outflow air flow is set to 0 degree by setting louver pitch Lp as a horizontal axis and flat part length Lf as a vertical axis | shaft. It is a graph which shows the minimum value of Lf from which the deflection angle of an outflow air flow becomes 0 degree by setting the flat part length Lf as a vertical axis | shaft by fin pitch Fp and a vertical axis | shaft. (A), (b) is a schematic block diagram explaining the air distribution state of a vehicle air conditioner provided with the evaporator 904 in a comparative example.

  Embodiments to which the present invention is applied will be described below with reference to the drawings.

  FIG. 1 is a schematic configuration diagram schematically showing the configuration of a vehicle air conditioner including an evaporator 4 that is a heat exchanger in an embodiment to which the present invention is applied. 2 is a perspective view showing a schematic configuration of the evaporator 4, FIG. 3 is a sectional view taken along the line III-III of FIG. 2, and FIG. 4 shows fins 40 corresponding to heat exchange promoting means of the evaporator 4. FIG.

  As shown in FIG. 1, a blower 3 driven by a blower motor 2 that generates an air flow in the ventilation duct 1 is disposed in the ventilation duct 1 for sending air into the vehicle interior. Here, the blower motor 2 and the blower 3 constitute a blower. In the downstream part of the blower 3, an evaporator 4 that is a cooling heat exchanger is disposed so as to cross the entire air passage in the ventilation duct 1, and the evaporator 4 cools the air flow blown out by the blower 3. It has become.

  The evaporator 4 constitutes a refrigeration cycle together with a compressor, a condenser, a decompression means, etc. (not shown), and the evaporator 4 evaporates liquid phase refrigerant in the refrigeration cycle after being discharged from the compressor, condensed and decompressed. It is a refrigerant evaporator.

Further, on the downstream side of the evaporator 4, a heater core 5 that is a heat exchanger for heating is provided at a predetermined interval. The heater core 5 is disposed so as to cross about half of the air passage in the ventilation duct 1, and reheats the cold air that has passed through the evaporator 4.

In the air passage in the ventilation duct 1, a bypass passage 6 is formed above the heater core 5 to bypass the heater core 5 and through which air (cold air) flows. Further, an air mix door (air volume ratio) that adjusts the air volume ratio between the cold air reheated by the heater core 5 and the cold air that bypasses the heater core 5 through the bypass passage 6 is provided between the evaporator 4 and the heater core 5. Adjustment means) 7 is arranged.

  The evaporator 4 is a cooling heat exchanger that cools air by transferring heat from air, which is an external fluid (corresponding to a second fluid), to a refrigerant, which is an internal fluid (corresponding to a first fluid). On the downstream side in the direction, a first opening 8 that is a heating inlet that guides the air that has flowed out of the evaporator 4 to the heater core 5 that is a heating means, and a second opening that is a bypass inlet that bypasses and leads to the passage 6. Part 9 is lined up. The air mix door 7 adjusts the air flow rate ratio between the cold air reheated by the heater core 5 and the cold air that bypasses the heater core 5 through the bypass passage 6 by adjusting the opening ratio between the openings 8 and 9. It is like that.

  In the most downstream portion of the ventilation duct 1, a face opening, a foot opening, a defroster opening, and the like (not shown) are provided, and blowing mode switching means for switching a blowing mode from these openings is provided. The air-conditioning air whose temperature is adjusted by mixing the warm air heated by the heater core 5 and the cold air passing through the bypass passage 6 passes through at least one of the openings according to the blowing mode set by the blowing mode switching means. It comes to blow out indoors. Further, an inside / outside air switching door 11 is disposed on the upstream side of the blower 3. The inside / outside air switching door 11 is configured to change the ratio between the outside air introduction port 12 and the inside air introduction port 13 to switch the ratio of the inside air and the outside air to be introduced into the ventilation duct 1.

  As shown in FIG. 2, the evaporator 4 includes a core part 20 that is a heat exchange part, and a pair of header tanks 60 provided above and below the core part 20.

  The core part 20 is comprised from the tube 30, the fin 40, and the side plate 50, and these members are formed with the aluminum material or aluminum alloy material which is excellent in corrosion resistance etc. Corrugated fins 40 formed into a corrugated shape from thin strips and tubes 30 having a flat cross section are alternately arranged in the left-right direction, and the outermost fins 40 on the left and right sides are further reinforced outwardly. A side plate 50 as a member is provided.

  Ends in the vertical longitudinal direction (vertical extending direction, BB direction in FIG. 2) of each tube 30 are fitted into a tube hole provided in the header tank 60, and the tube 30, the fin 40, the side plate 50, and the header The tank 60 is integrally brazed. When the refrigerant, which is an internal fluid, flows through the tube 30 in the direction BB in the figure, the outside of the tube 30 exchanges heat with the air flowing in the direction AA in the figure, thereby cooling the air.

  As shown in FIG. 2, the fins 40 are corrugated fins, and are formed so as to be substantially parallel to the air flow direction (AA direction in FIG. 2, the front and back direction in FIG. 2) (along the air flow direction). It has a plurality of flat plate portions (corresponding to a flat plate portion and a base portion) 41 and is formed in a wave shape by connecting the adjacent flat portions 41 with a curved portion 42.

  In other words, the fin 40 has a corrugated shape as a whole in which peaks and troughs are alternately continuous, a valley is formed between adjacent peaks, and further between the peaks and valleys. A flat surface portion 41 is formed and connects the peak portion and the valley portion. The peaks and valleys are the curved portions 42.

  As shown in FIG. 3, a plurality of louvers 43 (corresponding to louver portions) are arranged in parallel at predetermined intervals in the air flow direction (direction AA in FIG. 3). As shown in FIG. 3, for example, a group of louvers 43 that are inclined in the same direction are formed in one plane portion 41 in four areas, and the louver 43 is inclined in the adjacent louver 43 formation areas. Is reversed.

  In each louver 43 formation region, the louvers 43 except for those located at both ends are so-called double-cut louvers in which both end portions in the air flow direction AA are cut and raised to the opposite sides across the plane portion 41, respectively. Only the louvers 43 located at both ends in the direction AA are so-called one-side louvers in which only one side end is cut and raised.

  As shown in FIG. 3, louvers 43 are similarly formed on the plurality of plane portions 41 arranged in parallel with the tube extending direction BB at the fin pitch (corresponding to the base pitch) Fp, and the core portion 20 of the evaporator 4 is formed. The air that has flowed in from the upstream surface (see FIG. 2) flows, for example, as shown by the dashed arrows in FIG. 3, and flows out from the downstream surface.

  4 shows an enlarged cross section near the downstream end (near the right end in FIG. 3) of the flat portion 41 of the fin 40. As shown in FIG. As shown in FIG. 4, a flat portion 44 in which a louver is not formed at the most downstream portion in the air flow direction AA of the flat portion 41 further toward the downstream side of the air flow direction AA from the downstream end of the flat portion 41. It is provided to extend. Further, on the upstream side of the air flow direction AA of the flat portion 44, a plurality of louvers 43 cut and raised in the same direction at the same inclination angle La and the louver pitch Lp with respect to the air flow direction AA are arranged in parallel with the air flow direction AA. ing. The plurality of louvers 43 is a group of louvers 43 located on the most downstream side in the air flow direction AA among the louvers 43 inclined in the same direction as described above. Therefore, as shown in FIG. 4, the flat portion 44 and the formation region of the plurality of louvers 43 are adjacent to each other.

  As indicated by broken line arrows in FIG. 3, the air flowing between the tubes 30 of the core portion 20 flows from one surface side of the flat portion 41 to the other along the louver 43 provided to improve the heat exchange characteristics. Passes to the surface side. Therefore, the flow direction of the air passing between the louvers 43 shown in FIG. 4 is the air flow direction AA in which the flat portion 41 extends, that is, the direction orthogonal to the downstream side surface of the core portion 20 (the arrangement surface of the tubes 30 arranged in parallel (In a direction orthogonal to the direction) is inclined upward (deflected).

  The air immediately after passing between the louvers 43 due to the action of the plurality of louvers 43 inclined in the same direction located on the most downstream side in the air flow direction AA causes the louvers 43 to be perpendicular to the direction perpendicular to the downstream side surface of the core portion 20. Tilt in the tilt direction. On the other hand, the present inventors provide the louver 43 in order to improve the heat exchange characteristics if the air flow direction is rectified before the air passing between the louvers 43 reaches the downstream side surface of the core portion 20. Even so, attention has been paid to the fact that the flow direction of the air flowing out of the core portion 20 can be the direction perpendicular to the downstream side surface of the core portion 20.

  Therefore, a flat portion 44 is provided on the downstream side of the plurality of louvers 43 inclined in the same direction located at the most downstream side in the air flow direction AA, and the inclination angle La and the louver pitch Lp of the louvers 43 which are factors related to the direction of air flow. The relationship between the fin pitch Fp and the length Lf of the flat portion 44 is intensively simulated and experimented, and the length Lf of the flat portion 44 in the air flow direction AA is set to a predetermined length that satisfies the relationship shown below. For example, it has been found that the flow direction of the air flowing out from the core portion 20 can be a direction perpendicular to the downstream side surface of the core portion 20.

When the fin pitch Fp is 1 mm ≦ Fp ≦ 2.5 mm, the louver inclination angle La is 25 ° ≦ La ≦ 40 °, and the louver pitch Lp is 0.7 mm ≦ Lp ≦ 1.2 mm, the flat portion The length Lf of 44 is 25% or less of the length W of the fin 40 in the air flow direction AA (that is, the sum of the lengths of the flat portion 41 and the flat portion 44) W, and the following formula (1)
Lf ≧ (2Lp−1.4) (1.33La ³ −300La ² + 17100La) / 10 ⁵ −5Lp + 4.9 + (2Lp−1.4) {0.1085 (2Fp−2.9) ² +0.32 (2Fp -2.9)} (1)
It may be set so as to satisfy the relationship.

  This is based on the simulation results shown below. The inventors set a plurality of levels for each factor of the fin pitch Fp, the louver inclination angle La, and the louver pitch Lp, combine them, change the flat part length Lf in each combination, perform flow analysis, and perform the core part 20. The flat part length Lf in which the flow direction of the air flowing out from the gas becomes the direction perpendicular to the downstream side surface of the core part 20 (the deflection angle of the outflow air flow becomes 0 °) was obtained. For example, as shown in FIG. 5, the fin part pitch Lp is 1.45 mm, the louver inclination angle La is 25 °, the louver pitch Lp is 0.7 mm, the flat part length Lf is changed, and the flow part analysis is performed to obtain the flat part length Lf. Was 1.4 mm or more, the deflection angle of the outflow air flow was determined to be 0 °.

  FIG. 6 shows the analysis results thus obtained, and shows the minimum value of Lf at which the deflection angle of the outflow air flow becomes 0 ° with the louver inclination angle La as the horizontal axis and the flat portion length Lf as the vertical axis. Yes. FIG. 7 shows the minimum value of Lf at which the deflection angle of the outflow air flow is 0 °, with the louver pitch Lp as the horizontal axis and the flat portion length Lf as the vertical axis. FIG. 8 shows the minimum value of Lf at which the deflection angle of the outflow air flow is 0 °, with the fin pitch Fp as the horizontal axis and the flat portion length Lf as the vertical axis. In any graph, the deflection angle of the outflow air flow from the core portion 20 is set to 0 ° by setting the flat portion length Lf on the line connecting the points indicating the analysis results or a value above the line. Can do.

  When an approximate expression that approximates the values of these analysis results is calculated, the relationship of the above-described expression (1) is obtained. When the flow analysis is performed, the plate thickness of the fin 40 is 0.07 mm, and the wind speed is 2.88 m / s. In addition, the length W of the fin 40 in the air flow direction AA changes the flat portion length Lf, and thus W-Lf is set to 35 mm. Note that the wind speed is also analyzed for speeds other than 2.88 m / s, and the analysis result is affected up to a wind speed of 100 m / s, which is much higher than the general maximum wind speed of the air passing through the evaporator 4. Make sure not to give.

  The length Lf of the flat portion 44 is preferably 25% or less of the length W of the fin 40 in the air flow direction AA. This is because if the flat portion length Lf is longer than ¼ of the fin length W (width W of the so-called corrugated fin 40), the formation region of the louver 43 cannot be sufficiently secured, and the heat exchange performance of the evaporator 4 This is because cannot be fully exhibited.

  According to the above-described configuration, the fin 40 of the evaporator 4 has a flat portion that extends from the flat surface portion 41 in the air flow direction AA at the most downstream portion in the air flow direction AA and has a predetermined length Lf in the air flow direction AA. 44 and an upstream side of the air flow direction AA of the flat portion 44, and is cut and raised from the flat surface portion 41 in the same direction so as to be inclined at a predetermined inclination angle La with respect to the air flow direction AA. A plurality of louvers 43 parallel to the air flow direction AA at Lp are provided, the flat portion 44 is adjacent to the formation region of the plurality of louvers 43, and the fin pitch Fp is 1 mm ≦ Fp ≦ 2.5 mm. Yes, when the louver inclination angle La is 25 ° ≦ La ≦ 40 ° and the louver pitch Lp is 0.7 mm ≦ Lp ≦ 1.2 mm, the predetermined length Lf of the flat portion 44 is set to the fin 4 The length is set to 25% or less of the length W in the air flow direction AA of 0, and the relationship of the above-described formula (1) is satisfied.

  Accordingly, the predetermined length Lf of the flat portion 44 is set to 25% or less of the length W of the fin 40 in the air circulation direction AA, and the base 41 region in which the louver is formed is secured in the fin 40 to thereby heat the evaporator 4. While ensuring the replacement performance, the flow direction of the air deflected by flowing along the louver 43 is rectified by the flat portion 44 on the downstream side of the louver 43 and is orthogonal to the downstream side surface of the core portion 20 (of the tube 30). Air can flow out of the core portion 20 in a direction perpendicular to the arrangement plane. In this way, it is possible to suppress the deflection of the outflowing air.

  As described above, by suppressing the deflection of the air flowing out from the core portion 20, in the vehicle air conditioner shown in FIG. 1, the arrangement direction of the first opening 8 and the second opening 9 is the tube of the evaporator 4. Even in the extending direction BB, it is easy to distribute the cold air that has passed through the evaporator 4 evenly to the first opening 8 and the second opening 9, and the opening ratio between the two openings 8 and 9 of the air mix door 7. The temperature control control by is very easy.

  When the evaporator 904 to which the present invention is not applied is adopted, the air outflow direction from the evaporator 904 is deflected in any one of the tube extending directions BB due to the influence of the inclination of the louver at the most downstream portion of the fin. Therefore, for example, as shown in FIG. 9 (a), the cold air that has passed through the evaporator 904 is distributed to the second opening 9 larger than the first opening 8, or as shown in FIG. 9 (b). The cold air that has passed through 904 is distributed more largely to the first opening 8 than to the second opening 9, and temperature control control based on the ratio of the openings 8 and 9 of the air mix door 7 becomes relatively difficult. .

  The fins 40 of the evaporator 4 are so-called corrugated fins having a corrugated shape. Therefore, since it is easy to make the flat part 41 of the fin 40 parallel to the extending direction BB of the tube 30 with the fin pitch Fp, the manufacturing process of the evaporator 4 can be simplified.

  When the evaporator 4 is manufactured, even if the orientation of the corrugated fins 40, specifically, the inclined direction of the louver 43 at the most downstream portion of the flat surface portion 41 is randomly assembled, the air that flows out between the tubes 30 Therefore, it is possible to suppress the deflection of the air flowing out as the entire core portion 20.

  On the other hand, in the case of an evaporator to which the present invention is not applied, when corrugated fins are assembled at random, outflow from the core portion depends on the ratio of the louver in the most downstream portion of the flat portion of the corrugated fin. The deflection direction and the deflection angle of air change for each evaporator and are not constant, and temperature control control for each vehicle air conditioner becomes extremely difficult.

  In the evaporator 4 of the above embodiment, the fin pitch Fp is set to 1 mm ≦ Fp ≦ 2.5 mm. However, the fin pitch Fp is set to 1 mm ≦ Fp ≦ 2 mm to ensure a large heat transfer area of the fin 40 and heat exchange performance. The present invention is also extremely effective when applied to the evaporator 4 with improved characteristics.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In the above embodiment, the arrangement direction of the first opening 8 and the second opening 9 of the vehicle air conditioner is the tube extending direction BB of the evaporator 4 and suppresses the deflection of the air flowing out from the core portion 20. Thus, the cold air that has passed through the evaporator 4 is easily distributed evenly to the first opening 8 and the second opening 9, but is not limited thereto.

  In another heat exchanger, a first opening and a second opening through which the external fluid flows are provided on the downstream side in the flow direction of the external fluid, and the first opening and the second opening are provided. The heat exchanger may be arranged side by side in the tube extending direction (longitudinal direction) of the heat exchanger. According to this, the flow direction of the external fluid that flows along the louver and is deflected in the arrangement direction of the first opening and the second opening is rectified by the flat portion on the downstream side of the louver, and the external fluid is arranged in the tube arrangement. It can be made to flow out of the heat exchanger in a direction perpendicular to the plane. Therefore, it is possible to facilitate the control of distributing and supplying the external fluid that has passed through the heat exchanger to the first opening and the second opening.

  For example, when the present invention is applied to a heater core of a vehicle air conditioner and a plurality of outlet openings provided on the downstream side of the heater core are arranged in the tube extending direction of the heater core, the air distribution to each outlet opening Control can be facilitated.

  Moreover, in the said embodiment, the arrangement direction of the 1st opening part 8 of the vehicle air conditioner and the 2nd opening part 9 is the tube extension direction BB of the evaporator 4, and deflection | deviation of the air which flows out from the core part 20 is carried out. Although the cold air that has passed through the evaporator 4 is easily distributed evenly to the first opening 8 and the second opening 9 by suppressing, the arrangement of the first opening 8 and the second opening 9 is facilitated. The direction may not be the tube extending direction BB of the evaporator 4. For example, the arrangement direction of the first opening 8 and the second opening 9 may be the stacking direction of the tubes stacked at intervals (a direction perpendicular to the tube extending direction). According to this, the flow rate distribution of the external fluid flowing into the opening can be made uniform at each opening.

  In addition, the present invention is effective when applied to a single opening on the downstream side of the heat exchanger. For example, the present invention may be applied to an evaporator of a reheat type vehicle air conditioner. When all the air that has passed through the core of the evaporator is supplied to the heater core, the flow distribution of the cold air flowing into the core of the heater core can be made uniform, and temperature control control can be facilitated by efficient reheating. .

  Moreover, in the said embodiment, although the fin 40 was a corrugated fin, it is not limited to this. For example, plate fins in which the flat portions are continuous in the tube stacking direction may be employed so that the flat portions are arranged in parallel in the tube extending direction at a predetermined fin pitch Fp.

  Moreover, in the said embodiment, although the louver 43 was cut and raised from the plane part 41 which is a base, it is not limited to this, In the direction which cross | intersects air flow direction AA from the plane part 41 What protrudes may be sufficient.

  Moreover, in the said embodiment, although the evaporator 4 was comprised by the end part of the flat tube 30 being fitted and brazed to the tube hole provided in the header tank 60, the structure of an evaporator is set to this. It is not limited. For example, a drone cup type or serpentine type evaporator may be used.

  Moreover, in the said embodiment, although the heat exchanger was the evaporator 4, it is not limited to this, The present invention is widely applicable and effective even if it is another heat exchanger.

4 Evaporator (heat exchanger, heat exchanger for cooling)
5 Heater core (heating means)
8 First opening (heating inlet)
9 Second opening (bypass inlet)
20 Core part (Heat exchange part)
30 tube 40 fin (heat exchange promoting means)
41 Flat part (base)
43 louver (louver part)
44 Flat part AA Air flow direction (flow direction of external fluid)
BB Extension direction of tube (longitudinal direction of tube)
Fp Fin pitch La Louver inclination angle Lf Flat part length Lp Louver pitch W Fin air flow direction length (corrugated fin width)

Claims (5)

A plurality of tubes (30) through which the first fluid flows are arranged in parallel,
A heat exchanger provided between adjacent tubes (30) is provided with heat exchange promoting means (40) for promoting heat exchange between the first fluid and the second fluid flowing outside the tube (30). And
The heat exchange promoting means (40)
A base (41) extending in a flat plate shape in the flow direction (AA) of the second fluid;
A louver part (43) protruding from the base part (41) in a direction crossing the flow direction (AA);
Provided on the most downstream side in the flow direction in the second fluid of the base (41), rectify the second fluid and blow out toward the direction along the flow direction (AA) on the wake side It has a flat part (44) extended in the said distribution direction (AA) from the base (41), The heat exchanger characterized by the above-mentioned. The heat exchange facilitating means (40) is thermally applied to the tube (30) so that the base (41) is juxtaposed in the extending direction (BB) of the tube (30) at a base pitch Fp that is a predetermined interval. A fin (40) connected to
The flat portion (44) has a predetermined length Lf in the flow direction (AA),
The louver portion (43) is provided upstream of the flow direction (AA) of the flat portion (44), and is inclined in the same direction so as to be inclined at a predetermined inclination angle La with respect to the flow direction (AA). A plurality of louvers (43) that are cut and raised and parallel to the flow direction (AA) at a predetermined louver pitch Lp;
The flat portion (44) and the formation region of the plurality of louvers (43) are adjacent to each other,
The base pitch Fp is 1 mm ≦ Fp ≦ 2.5 mm, the inclination angle La is 25 ° ≦ La ≦ 40 °, and the louver pitch Lp is 0.7 mm ≦ Lp ≦ 1.2 mm,
The predetermined length Lf of the flat portion (44) is
And not more than 25% of the length of the fin (40) in the flow direction (AA),
Lf ≧ (2Lp−1.4) (1.33La ³ −300La ² + 17100La) / 10 ⁵ −5Lp + 4.9 + (2Lp−1.4) {0.1085 (2Fp−2.9) ² +0.32 (2Fp -2.9)}
The heat exchanger according to claim 1, wherein the relationship is satisfied.   The heat exchanger according to claim 2, wherein the base pitch Fp is 1 mm ≦ Fp ≦ 2 mm.   The heat exchanger according to claim 2 or 3, wherein the fin (40) has a corrugated shape. A cooling heat exchanger for performing heat transfer from the second fluid to the first fluid to cool the second fluid;
On the downstream side of the flow direction (AA), a heating inlet (8) for guiding the second fluid to the heating means (5) and a second fluid for guiding the second fluid so as to bypass the heating means (5). The heat exchanger according to any one of claims 1 to 4, wherein a bypass introduction port (9) is arranged side by side in the extending direction (BB).

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