JP6514996B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger that can exchange heat with a refrigerant by circulating the refrigerant inside and passing the air outside to perform heat exchange with the air.

  2. Description of the Related Art Conventionally, in a vehicle air conditioner used in a vehicle such as a car, a heat exchanger such as an evaporator that cools air passing by circulating a refrigerant inside is used.

  For example, as shown in Patent Document 1, this heat exchanger includes a set of headers, a plurality of tubes connected between the headers, and a plurality of fins provided between the tubes. The tubes are provided at predetermined intervals so as to form two rows along the flow direction of air in the heat exchanger. This tube is a drainage promoting member for draining water so that the condensed water does not stay in the heat exchanger because the moisture in the air is cooled and attached as condensed water when the air passes through the heat exchanger Is provided. The drainage promoting member is formed in a hollow shape and is fixed between one tube and the other tube.

  Then, the condensed water adhering to the tube or fin is drained downward along the tube in the direction of gravity and at the same time led to the side of the drainage promoting member by the capillary effect, and then downward along the drainage promoting member Drained.

Patent No. 4774295 gazette

  However, in the above-described heat exchanger, since the drainage promoting member for draining the condensed water is provided for each tube, there is a problem that the number of parts and the manufacturing cost increase, and the assembly man-hour increases.

  On the other hand, it is also conceivable to enhance drainage by arranging so that the gap between the upstream tube and the downstream tube in the air flow direction becomes smaller without providing the above-mentioned drainage promoting member. . However, in this case, by bringing the tubes close to each other, it is necessary to thin the partition plate which is provided in the connected header of the tubes and which divides the inside of the header into two, so that it is maintained by the partition plate The strength of the header will be reduced.

  The present invention has been made in consideration of the above-described problems, and it is an object of the present invention to provide a heat exchanger capable of enhancing the drainage of condensed water while maintaining the strength of the tank with a simple configuration. Do.

In order to achieve the above object, the present invention is directed to a set of tanks spaced from each other, a plurality of tubes each having a longitudinal end connected to the tanks, and an adjacent tube. And a plurality of fins provided between them, the partition plate divides the inside of the tank into upstream and downstream flow directions of air passing through the fins, and the tubes are provided in parallel along the flow direction In the heat exchanger,
The end portion of the tube has an insertion portion formed at least at the side of the partition plate in the flow direction so as to be narrow, and is connected to the tank via the insertion portion, and the plate thickness of the partition plate is equal to or greater than the tank thickness Among the plurality of flow paths which are set in the inside of the tube and through which the refrigerant flows, the hole size of the flow path closest to the partition plate is smaller than the throttling allowance in the width direction of the insertion portion of the tube in the flow direction The cross-sectional area of the flow path which is set large and closest to the partition plate is smaller than the cross-sectional area of the adjacent flow path in the insertion portion, and the stepped portion formed by the throttle does not contact the tank. Do.

  According to the present invention, in the heat exchanger, the end portion of the plurality of tubes is provided with the insertion portion formed in a narrow shape at least on the side of the partition plate in the flow direction of the air passing through the fins. And the tube, and the plate thickness of the partition plate for dividing the inside of the tank is set to be equal to or more than the plate thickness of the tank, and of the plurality of flow paths formed inside the tube, The hole size of the flow path is set to be larger than the widthwise throttling margin of the insertion portion in the tube in the flow direction.

  Therefore, the tube provided on the upstream side in the air flow direction and the downstream side in the air flow direction are provided in a state in which the plate thickness of the partition plate is secured equal to or greater than the plate thickness of the tank without thinning. It is possible to arrange with a small gap with the tube.

  As a result, when the moisture in the air passing through the heat exchanger adheres to the tube etc. as condensed water while securing the strength of the tank by the partition plate with a simple configuration in which the insertion portion is provided at the end of the tube In the gaps between the tubes arranged in parallel and in close proximity to each other, it is possible to suitably drain the condensed water attracted to each other by the capillary effect downward in the direction of gravity.

  Further, it is preferable to divide the flow path in the width direction of the tube and provide a plurality of flow paths.

  Furthermore, it is possible to arrange one tube and the other tube closer to each other and reduce the gap by forming a recess in the partition plate in which a part of the tubes arranged in parallel is inserted respectively It becomes.

  Furthermore, by forming the recess so that the end of the tube abuts, positioning along the longitudinal direction of the tube is facilitated.

  In addition, the insertion portion is formed in a narrow shape in the width direction outer side opposite to the partition plate side, and the hole dimension of the flow passage most separated from the partition plate is set larger than the width direction throttling margin of the insertion portion By doing this, it is possible to further miniaturize the tank to which the tube is connected.

  According to the present invention, the following effects can be obtained.

  That is, in the heat exchanger, the end of the plurality of tubes is provided with the insertion portion formed at least at the side of the partition plate narrow in the flow direction of the air passing through the fins, and the tank and the tubes While connecting, the plate thickness of the partition plate for dividing the inside of the tank is set to be equal to or more than the plate thickness of the tank, and of the plurality of flow passages formed inside the tube, By setting the hole size to be larger than the throttling allowance in the width direction of the insertion portion in the flow direction, the thickness of the partition plate can be made equal to or greater than the thickness of the tank without thinning. Since the strength can be secured, and the gap between the tubes arranged in parallel can be set small, the condensed water adhering to the tubes is directed downward through the gap by the capillary effect. It becomes possible to suitably and drainage.

It is an appearance perspective view of a heat exchanger concerning a 1st embodiment of the present invention. It is sectional drawing along the II-II line of FIG. It is an expanded sectional view which shows the tube end part vicinity in FIG. It is sectional drawing along the IV-IV line of FIG. It is whole sectional drawing of the heat exchanger which concerns on the 2nd Embodiment of this invention. 6A is a partially omitted sectional view taken along the line VIA-VIA of FIG. 5, and FIG. 6B is a partially omitted sectional view taken along the line VIB-VIB of FIG.

  The heat exchanger according to the present invention will be described by way of preferred embodiments with reference to the attached drawings. In FIG. 1, reference numeral 10 denotes a heat exchanger according to a first embodiment of the present invention.

  As shown in FIGS. 1 and 2, the heat exchanger 10 is used, for example, as an evaporator through which a refrigerant flows, and includes a pair of first and second headers (tanks) 12 and 14; A plurality of tubes 16 for connecting between the first header 12 and the second header 14; and a plurality of fins 18 provided between the tubes 16 and bent in an undulating manner, the first and second headers Heat exchange with the refrigerant is performed by the passage of air in the thickness direction (the direction of the arrow A1) of the heat exchanger 10 orthogonal to the width direction of the sheets 12 and 14.

  The first header 12 is provided at one end thereof with an inlet pipe 20 and an outlet pipe 22 for supplying and discharging a refrigerant, and a thickness direction (arrow A1) in which the inside is orthogonal to the width direction (arrows B1 and B2 direction) , A2 direction) is divided into two by the first partition plate 24. That is, in the inside of the first header 12, the first and second space portions 26 and 28 divided into two, which are the back side and the front side, are formed by the first partition plate 24 provided at the center in the thickness direction. The first space portion 26 is provided on the downstream side (the arrow A1 direction) in the air flow direction, and the second space portion 28 is provided on the upstream side (the arrow A2 direction) in the air flow direction.

  On the other hand, the second header 14 is divided into two in the thickness direction (directions of arrows A1 and A2) by the second partition plate 30 provided at the center in the thickness direction like the first header 12 and the back surface thereof Third and fourth spaces 32, 34 are formed on the side and the surface side. The third space portion 32 is provided on the downstream side (the arrow A1 direction) in the air flow direction, and the fourth space portion 34 is provided on the upstream side (the arrow A2 direction) in the air flow direction.

  A plurality of communication ports 35 are formed in the second partition plate 30, and the third space portion 32 and the fourth space portion 34 divided by the second partition plate 30 communicate with each other.

  As shown in FIG. 2, the plate thickness t1 of the first and second partition plates 24 and 30 is set to be substantially equal to or larger than the plate thickness t2 of the plate material constituting the first and second headers 12 and 14. (T1 ≧ t2).

  Further, by providing the first and second partition plates 24 and 30 at the thickness centers of the first and second headers 12 and 14, the strength of the first and second headers 12 and 14 formed in a hollow shape can be increased. I am improving.

  The tube 16 is formed in, for example, a flat shape in cross section made of an aluminum material and is formed in a straight line having a predetermined length, as shown in FIGS. The tubes 16 extend in a substantially vertical direction (directions of arrows C1 and C2 in FIG. 1), and are equally spaced from each other along the width direction (directions of arrows B1 and B2) of the first and second headers 12 and 14. The first and second headers 12 and 14 are provided in two rows spaced apart by a predetermined distance so as to form a pair in the thickness direction (flow direction of air) of the first and second headers 12 and 14.

  Further, as shown in FIG. 3 and FIG. 4, a plurality of (for example, seven) flow channels 36 through which the refrigerant flows are formed in the inside of the tube 16 along the longitudinal direction (the directions of arrows C1 and C2). Ru. The flow path 36 is, for example, formed in a rectangular shape in cross section and is formed to be spaced apart from each other at equal intervals along the width direction (direction of arrows A1 and A2) of the tube 16, and one end to the other end of the tube 16 It has penetrated.

  Further, at one end and the other end of the tube 16, a pair of narrow insertion portions 38a and 38b narrowed by a predetermined width in the width direction (arrows A1 and A2 directions) are formed.

  The insertion portions 38a and 38b are formed, for example, by crushing one end portion and the other end portion of the tube 16 toward the center in the width direction of the width direction, and other portions than the one end portion and the other end portion On the other hand, they are respectively crushed and formed in the width direction (directions of arrows A1 and A2) with a crushing margin (diaphragm allowance) F (see FIG. 3). Therefore, in the tube 16, the insertion portions 38 a and 38 b have a narrow width with respect to the other flow channels 36 by crushing the flow channel 36 a provided on the outermost side in the width direction among the plurality of flow channels 36. It has become.

  In other words, as shown in FIG. 3, the hole dimension G along the width direction of the flow passage 36 a in the tube 16 is formed to be larger than the crushing margin F in the width direction of the insertion portions 38 a and 38 b Therefore, the flow path 36a is not blocked from penetrating from one end to the other end of the tube 16 so that the refrigerant can flow.

  In addition, the insertion portions 38a and 38b are formed to have predetermined lengths from the one end portion and the other end portion of the tube 16 in the central direction, respectively.

  The insertion portions 38a and 38b are fixed by brazing or the like in a state in which the insertion portions 38a and 38b are inserted by a predetermined length through the insertion holes 40 opened in the bottom wall portions of the first and second headers 12 and 14, respectively. . As a result, one end of a pair of tubes 16 arranged in parallel along the air flow direction (arrow A1 direction) is connected to the first and second space portions 26 and 28 in the first header 12, and the other The ends are connected to the third and fourth space portions 32 and 34 in the second header 14, and the first header 12 and the second header 14 communicate with each other through the flow path 36 of the tube 16.

  Under the present circumstances, since the tube 16 has the insertion parts 38a and 38b where the one end part and the other end part become narrow shape, the 1st and 2nd partition plate 24 of the 1st and 2nd headers 12 and 14 is carried out. , 30 and can be made close to the gap D and connected without contact (see FIG. 2).

  The fins 18 are bent in a wave shape in cross section, for example, by forming a thin plate of an aluminum material or the like, and two tubes disposed adjacent to each other in the width direction (arrows B1 and B2) of the first and second headers 12 and 14 They are arranged to contact alternately with 16 and are formed to extend in a wave-like cross-sectional shape along the thickness direction (directions of arrows A1 and A2) of the heat exchanger 10 by a predetermined width.

  The heat exchanger 10 according to the first embodiment of the present invention is basically configured as described above, and next, its operation and effects will be described.

  First, the refrigerant introduced from the introduction pipe 20 through a pipe (not shown) is supplied to the first space portion 26 of the first header 12 as shown in FIG. 1 and FIG. After flowing downward (in the direction of arrow C1), it is introduced into the third space portion 32 of the second header 14.

  Next, the refrigerant supplied to the third space portion 32 flows to the fourth space portion 34 side in the second header 14 through the plurality of communication ports 35 opened in the second partition plate 30, and then, is upstream It flows upward (in the direction of the arrow C 2) through the plurality of tubes 16 arranged on the side, and reaches the second space portion 28 of the first header 12.

  Then, the refrigerant returned to the first header 12 is discharged from the outlet pipe 22. Thus, heat is exchanged between the refrigerant circulating in the plurality of tubes 16 between the first header 12 and the second header 14 and the air passing through the fins 18, and the air is cooled to the downstream side ( While supplied in the direction of arrow A1), the refrigerant is warmed and drawn out from the outlet pipe 22 and circulated to an apparatus (not shown).

  At this time, when air passes through the heat exchanger 10 for heat exchange, the moisture contained in the air is cooled by the refrigerant to be condensed water and adhere to the surfaces of the fins 18 and the tube 16. In this heat exchanger 10, the gap D (see FIGS. 2 to 4) of the pair of tubes 16 arranged adjacent to each other in two rows along the air flow direction (arrow A1 direction) is set small. . Therefore, in the gap D, the condensed water attached to one tube 16 and the condensed water attached to the other tube 16 mutually attract each other by the capillary effect, thereby increasing the volume and the gravity, and the gravity via the gap D It flows in the downward direction (arrow C1 direction) and is drained. As a result, the condensed water adhering to the fins 18 and the tubes 16 can be suitably drained downward in the direction of gravity (in the direction of the arrow C1) along the adjacent tubes 16.

  As described above, in the first embodiment, in the plurality of tubes 16 constituting the heat exchanger 10, the air flows to one end and the other end connected to the first and second headers 12 and 14. The first and second tubes 16 arranged in parallel in the air flow direction (the direction of the arrow A1) are formed by forming the insertion portions 38a and 38b formed in a narrow shape along the direction. It is possible to arrange the first and second partition plates 24 and 30 in the headers 12 and 14 closer to one another while maintaining the predetermined thickness t1 without thinning the first and second partition plates 24 and 30.

  As a result, by maintaining the plate thickness t1 of the first and second partition plates 24 and 30, the gaps D between the two rows of tubes 16 while securing the strength of the hollow first and second headers 12 and 14. Can be drained by guiding the condensed water adhering to the tubes 16 to the lower side in the direction of gravity (the direction of the arrow C 1) suitably using the gap D between the tubes 16.

  Further, the insertion portions 38a and 38b are not limited to the case where the insertion portions 38a and 38b are formed by being crushed by the crushing margin F equally from both sides along the width direction of the tube 16. For example, the first and second partition plates You may form so that only one side (1st and 2nd partition plate 24 and 30 side) which faces 24 and 30 may be crushed.

  Next, a heat exchanger 100 according to a second embodiment is shown in FIGS. 5 to 6B. In addition, the same referential mark is attached to the same component as the heat exchanger 10 which concerns on 1st Embodiment mentioned above, and the detailed description is abbreviate | omitted.

  In the heat exchanger 100 according to the second embodiment, the concave portions 108a and 108b into which a part of each tube 106 is inserted in the first and second partition plates 102 and 104 in the first and second headers 12 and 14, respectively. In the heat exchanger 10 according to the first embodiment.

  The concave portions 108 a and 108 b are respectively formed on both side surfaces of the first and second partition plates 102 and 104 facing the tube 106 so as to be semicircular in cross section, and the same number as the number of the tubes 106 is provided. The recesses 108a and 108b are formed to be spaced apart from each other at equal intervals along the extending direction (the arrow H direction) of the first and second partition plates 102 and 104. That is, the recess 108a provided on one side (the direction of arrow A2) of the first and second partition plates 102 and 104 and the recess 108b provided on the other side (the direction of arrow A1) It arrange | positions so that it may become linear in orthogonal direction (arrow A1 and A2 direction) (refer FIG. 6A and 6B).

  In addition, the concave portions 108a and 108b are simultaneously formed when, for example, the first and second partition plates 102 and 104 are formed by pressing, and in the first and second partition plates 102 and 104, the first and second partition plates are formed. It forms in the height according to the insertion allowance of the tube 106 inserted with respect to the bottom face of the headers 12 and 14 (refer FIG. 5).

  In other words, the concave portions 108a and 108b in the first partition plate 102 are provided in the vicinity of the end portion which is on the second partition plate 104 side (arrow C1 direction), while the concave portions 108a and 108b in the second partition plate 104 are And an end portion near the first partition plate 102 (in the direction of the arrow C2).

  Then, the end portions of the insertion portions 110a and 110b of the respective tubes 106 in the first and second headers 12 and 14 are inserted into the recess portions 108a and 108b, and the end portions are in contact with the end walls 112 of the recess portions 108a and 108b. By being in contact, it is fixed in a state of being positioned along the longitudinal direction (the directions of arrows C1 and C2).

  At the same time, each tube 106 is positioned at a position along the extension direction of the first and second partition plates 102 and 104 (the direction of arrow H in FIGS. 6A and 6B) by the recesses 108 a and 108 b The gap D 'between the tubes 106 along the flow direction (the direction of the arrow A1) is maintained at a predetermined interval. That is, as compared with the heat exchanger 10 according to the first embodiment, the tubes 106 arranged in parallel along the air flow direction may be arranged closer to each other by the amount of the concave portions 108a and 108b. Yes (D> D ').

  Thereby, the plurality of tubes 106 are fixed in a state of being accurately positioned to the predetermined position via the concave portions 108 a and 108 b of the first and second partition plates 102 and 104.

  As described above, in the second embodiment, a part of the tube 106 is inserted and held in the first and second partition plates 102 and 104 provided inside the first and second headers 12 and 14. By providing the recesses 108a and 108b, the pair of tubes 106 arranged in parallel in the air flow direction (the direction of the arrow A1) can be divided into the first and second partition plates 102 in the first and second headers 12 and 14, respectively. As compared with the heat exchanger 10 according to the above-described first embodiment, it is possible to further arrange the tubes 106 closer to each other without thinning 104.

  As a result, it is possible to arrange the gaps D 'of the two rows of tubes 106 further smaller, and accordingly, the condensed water adhering to the tubes 106 is further suitably used by utilizing the gaps D' between the tubes 106. It can be led downward (in the direction of arrow C1) to drain water.

  Further, by arranging the tubes 106 arranged in parallel in the air flow direction close to each other, it is possible to adopt a wider tube 106 as compared to the heat exchanger 10 according to the first embodiment. Therefore, the flow resistance of the refrigerant flowing inside can be reduced, and the flow amount of the refrigerant can be increased, so that the heat exchange performance can be improved.

  Furthermore, by assembling the respective tubes 106 to the first and second partition plates 102 and 104 using the recesses 108 a and 108 b, the respective tubes 106 can be accurately positioned with respect to the first and second headers 12 and 14. As it is possible to assemble, it is possible to improve the assembling accuracy of the heat exchanger 100 and to further improve the quality.

  Furthermore, since the recesses 108a and 108b can be formed simultaneously when the first and second partition plates 102 and 104 are press-formed, they can be formed without increasing the number of manufacturing steps of the heat exchanger 100. And is preferred.

  The heat exchanger according to the present invention is, of course, not limited to the above-described embodiment, and various configurations can be adopted without departing from the scope of the present invention.

DESCRIPTION OF SYMBOLS 10, 100 ... Heat exchanger 12 ... 1st header 14 ... 2nd header 16, 106 ... Tube 24, 102 ... 1st partition plate 30, 104 ... 2nd partition plate 36, 36a ... Flow path 38a, 38b, 110a, 110b ... insertion part 108a, 108b ... recessed part

Claims (5)

It has a set of tanks spaced apart from one another, a plurality of tubes whose longitudinal ends are respectively connected to the tank, and a plurality of fins provided between the adjacent tubes. In the heat exchanger, the inside of the tank is divided into the flow direction upstream and the downstream of the air passing through the fins by the partition plate, and the tubes are provided in parallel in the flow direction.
The end portion of the tube has an insertion portion formed at least at the side of the partition plate narrow in the flow direction, and is connected to the tank via the insertion portion, and the plate thickness of the partition plate In the flow direction, the hole size of the flow passage which is most adjacent to the partition plate among the plurality of flow passages formed inside the tube and through which the refrigerant flows is set to the plate thickness of the tank or more. wherein the said insert portion greater than the width direction aperture margin of the tube, is smaller than the cross-sectional area of the flow path adjacent to each other in most the partition plate side becomes the flow path is the insertion cross-sectional area of, A heat exchanger characterized in that a step formed by the throttle does not abut the tank . In the heat exchanger according to claim 1,
The heat exchanger is characterized in that a plurality of the flow paths are divided in the width direction of the tube. In the heat exchanger according to claim 1 or 2,
A heat exchanger characterized in that the partition plate is formed with a recess into which a part of the tubes arranged in parallel is respectively inserted. In the heat exchanger according to claim 3,
The heat exchanger according to claim 1, wherein the recess is formed to abut the end of the tube. In the heat exchanger according to any one of claims 1 to 4,
The insertion portion is formed such that the width direction outer side opposite to the side of the partition plate is narrow, and the hole dimension of the flow passage most separated from the partition plate is smaller than the widthwise throttling margin of the insertion portion A heat exchanger characterized in that it is also set large.

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