JP2004530092A5 - - Google Patents

Description

Heat exchanger, car air conditioner using the same, and vehicle equipped with heat exchanger

The present invention includes a heat exchanger for automobiles or industrial use, such as an evaporator, a condenser, an oil cooler, an intercooler, a heat exchanger used for a heater core, a car air conditioner using the heat exchanger, and a heat exchanger. About cars .

Conventionally, heat exchangers, in particular evaporators for car air-conditioning is often used commonly aluminum heat exchanger from the viewpoint of light weight and workability.

Currently, an evaporator for car air conditioning, laminate type (laminated type) evaporator has become the mainstream. This is because the fin-tube expansion method, which has been used so far, has been used in terms of performance and productivity in order to integrally braze and join the heat exchange fins for air and the tube portion where the refrigerant evaporates. This is because it is better than a heat exchanger. In terms of performance in particular, louver fins with high heat transfer performance can be used for the air-side fins, which have a high heat exchange capacity and low airflow resistance, which shows characteristics that overwhelm the fin-tube expansion method up to then. .

  Therefore, in response to market demands for miniaturization and weight reduction, there has been a shift to lighter and more compact heat exchangers. In particular, recently, a filter is often mounted on the front of the evaporator due to a problem in the vehicle interior, and a demand for a thinner heat exchanger has been increasing in order to secure a space for the filter.

  The conventional heat exchanger for an evaporator is, for example, as shown in FIG. 25, one side of a substantially rectangular aluminum plate (62), and is divided into front and rear by a vertically long partitioning projection (64). Adjacent plates are provided with a recess (66) for forming a coolant passage, and a recess (not shown) for forming a header portion that is continuous with the upper and lower ends of the recess (66) for forming the front and rear coolant passages and is deeper than these. (62) (62) are layered on top of each other with the recesses facing each other, and the opposing partitioning projections (64) (64) of both plates (62) (62), and the same peripheral edge. By joining the portions (63) and (63) to each other, a flat tube portion (61) having front and rear flat refrigerant flow passage portions (68) and upper and lower header portions (not shown) connected thereto is formed, A large number of these flat tube sections (61) are arranged in parallel via air-side fins to form a heat exchanger. Preparative (62) was made by press forming of the aluminum plate.

  However, the conventional heat exchanger for an evaporator has the following problems with respect to the market demand for a thinner heat exchanger.

  A. The plate (62) constituting the flat tube part (61) is made by drawing of an aluminum plate by pressing, so that the partitioning convex part (64) and the peripheral part (63) of the plate (62) become wider. Therefore, the joining portion of the two plates (62) (62), that is, the opposing partitioning projections (64) and (64) of the plates (62) and (62) and the peripheral portions (63) and (63) The area of the waste portion where the refrigerant does not pass is relatively increased, and as a result, the cross-sectional area of the refrigerant passage decreases at the same evaporator volume, so that the passage resistance of the refrigerant increases. , Resulting in performance degradation.

  In order to cope with such a problem, a method of increasing the height of the refrigerant passage and securing the cross-sectional area of the passage can be considered. In this case, the volume occupied by the air-side fins within the same volume is reduced. In other words, the heat transfer area of the fins is reduced, resulting in a decrease in performance. In addition, since the air passage is further reduced, the ventilation resistance increases, and an appropriate air volume cannot be obtained.

  B. On the other hand, in the air-side fin, since the joint between the peripheral portions (63) and (63) of the two plates (62) and (62) does not directly contact the fin, the heat transfer performance is poor, and By reducing the thickness of the heat exchanger while containing heat, the relative ratio of the area of the waste portion through which the refrigerant does not pass is increased, and the cooling performance is reduced.

  C. The recess for forming the header portion of the plate (62) is formed deeper than the recesses (66) and (66) for forming the refrigerant flow passages on both the front and rear sides of the partitioning protrusion (64) by drawing. The thickness becomes further thinner than that of the concave portion (66). For this reason, the flat tube portion (61), which accounts for a large proportion, has a margin in pressure resistance, but the header portion is weakest in pressure resistance. In the conventional heat exchanger, since the flat tube portion (61) and the header portion are formed of an integral plate material and are formed by press working, there is a limit in further reducing the thickness and weight of the heat exchanger.

  An object of the present invention is to solve the above-mentioned problems of the prior art, and to have a plate used for a heat exchanger having an uneven strip provided on one side by forging or cutting without using a conventional press-formed product. In addition, by forming the header forming member from a different material from the plate and forming the header portion, the width of the flat tube in the front-rear direction can be narrowed, and the flat tube can be thinned (thinned). Another object of the present invention is to provide a heat exchanger capable of increasing the heat transfer area, improving the heat transfer efficiency, and greatly improving the heat exchange performance.

  In order to achieve the above object, the heat exchanger according to the present invention firstly has a peripheral ridge that projects to one side at a peripheral portion, projects to the same side at the center of the width, and extends downward from the upper end. A central ridge extending to a position where a fluid return channel can be formed is provided by forging or cutting, respectively, and a fluid channel forming recess on both front and rear sides of the central ridge is provided inside the peripheral ridge. And a U-shaped fluid flow path forming recess formed by a fluid return flow path forming recess below the central ridge. A U-shaped fluid flow path forming recess is formed at one end of the U-shaped fluid flow path forming recess. One of the two through-holes is provided with the other through-hole at the other end of the concave portion, and the plate having the other surface being a flat surface is formed into a pair of two U-shaped fluid flow paths. Of the two plates are overlapped with the recesses facing each other. The tips of the peripheral ridges are joined to each other, and the tips of the central ridges are joined to form a flat tube having a U-shaped fluid flow path therein, and a plurality of flat tubes are arranged in parallel. In addition, between the upper ends of the adjacent flat tubes, a header forming member including a pair of front and rear fluid flow cylinders and a middle connecting portion between the front and rear fluid communication cylinders respectively communicating with the fluid inlet / outlet through holes of the plate is interposed, It is characterized in that front and rear headers communicating with the upper end of the flat tube are formed.

  Secondly, the heat exchanger of the present invention secondly has a left and right side edge portion and a lower edge portion projecting to one side, and a U-shaped edge ridge as a whole projects to the width center portion to the same one side and Central ridges extending from the bifurcated upper end to a position where a lower fluid return channel can be formed are provided by forging or cutting, respectively, and the central ridge is provided inside the U-shaped edge ridge. A U-shaped fluid flow path forming recess formed by the fluid flow path forming recesses on both front and rear sides of the ridge and the fluid return flow path forming recess below the central ridge is formed, and the other surface is flat. A pair of plates are superimposed on each other such that U-shaped fluid flow path forming recesses face each other, and a pair of opposed U-shaped edge projecting ridges of both plates. , And the tips of the central ridges including the forked upper end are joined to each other to form an upper end. A flat tube having a bifurcated opening and having a U-shaped fluid flow path formed therein is formed, and a flat tube upper end opening insertion hole is provided at a predetermined interval on each lower wall of a pair of front and rear header forming members formed of a square pipe. The flat tubes are arranged in parallel by connecting the bifurcated upper ends of the flat tubes into the insertion holes of the front and rear header forming members, respectively. It is characterized in that front and rear header portions communicating with the forked upper end portion are formed.

  In the heat exchanger having the above-described first and second features, a plurality of flow path dividing U-shaped ridges are provided in the U-shaped fluid flow path forming recess of each plate by forging or cutting, and the flat tube is provided. A plurality of U-shaped split fluid passages are formed in the internal U-shaped fluid flow passage, and there are several aspects of this.

  First, in the first aspect of the dividing ridge, a plurality of channel dividing U-shaped ridges are provided in the U-shaped fluid channel forming recess of each plate by forging or cutting, and a pair of two ridges is provided. In the superimposed state where the plates face the concave portions, the tips of the flow dividing U-shaped ridges facing each other are joined to each other, and a plurality of U-shaped divided fluids are formed in the U-shaped fluid flow path inside the flat tube. A passage is formed.

  Next, in the second aspect of the dividing ridge, the fluid flow path forming recess of each plate has a height twice as large as the depth of the recess and is located in the front and rear straight flow path forming portion of the recess. A plurality of front and rear flow path dividing ridges each consisting of a straight portion and a quarter arc portion connected to the lower end thereof and located at the folded portion of the recess are formed by a pair of two plates facing the recess. In the superimposed state, provided by forging or cutting so as to be alternately positioned in the superimposed state, in a superimposed state in which a pair of plates face the concave portions, the front end portions of the front and rear flow path dividing ridges are A plurality of U-shaped divided fluid passages are formed in the U-shaped fluid passage inside the flat tube by being joined to the flat surface of the bottom wall of the fluid passage forming concave portion of the plate facing these.

  A third aspect of the dividing ridge is that a U-shaped fluid flow channel forming concave portion of each pair of plates is provided with a U-shaped fluid channel dividing concave portion having a height twice the depth of the concave portion. The ridges are provided by forging or cutting so that these plates are alternately positioned in a superposed state in which the concave portions face each other. In the superimposed state of these two types of plates, The tip of the U-shaped ridge is joined to the flat surface of the bottom wall of the fluid passage forming recess of the plate facing the U-shaped ridge, and a plurality of U-shaped divided fluid passages are formed in the U-shaped fluid passage inside the flat tube. Is formed.

  A fourth aspect of the dividing ridge is that a plurality of channel dividing ridges having a height twice the depth of the concave portion are formed by forging or cutting in the latter half of the fluid channel forming concave portion of each plate. The bottom wall of the first half of the recess is formed as a flat surface having no channel dividing ridge, and in a superimposed state in which a pair of plates face the recess, The tips of the channel dividing ridges are joined to the flat surface of the bottom wall of the fluid channel forming concave portion of the plate facing them, and a plurality of U-shaped divided fluids are formed in the U-shaped fluid channel inside the flat tube. A passage is formed.

  Next, in the heat exchanger having the first feature of the present invention, one of the pair of plates may be replaced with a flat plate.

  That is, in this case, the peripheral ridge that protrudes to one side at the peripheral portion, the central ridge that protrudes to the same side at the center of the width, and extends from the upper end to a position where a lower fluid return channel can be formed. The ridges are provided by forging or cutting, respectively, and the inside of the peripheral ridge is formed with a fluid passage forming recess on both the front and rear sides of the central ridge and the bottom of the central ridge is formed with a fluid turn-back channel. And a U-shaped fluid flow passage forming recess formed by: and one of the through-holes for the fluid inlet / outlet is formed at one end of the U-shaped fluid flow passage forming recess at the other end of the recess. A plate with a ridge provided with the other through-hole and a flat surface on the other surface; a plate having the same shape and the same outer shape as the plate; Laminated flat plate with holes And the tip of the ridge is joined to the periphery of the flat plate, and the tip of the ridge at the center of the plate is a flat surface at the corresponding center of the flat plate. To form a flat tube having a U-shaped fluid flow path therein, a plurality of flat tubes arranged in parallel, and a fluid inlet / outlet of a plate between upper ends of adjacent flat tubes. A header forming member including a pair of front and rear fluid communication cylinders respectively communicating with the through-holes and a middle connecting portion therebetween is formed to form a front and rear header communicating with the upper end of the flat tube.

  In the heat exchanger having the second feature of the present invention, one of the pair of plates may be replaced with a flat plate.

  That is, in this case, the left and right side edge portions and the lower edge portion protrude to one side, and the U-shaped edge ridge as a whole projects from the upper end portion protruding to the same side at the center of the width and formed into a forked shape. A central ridge extending to a position where a lower fluid return channel can be formed is provided by forging or cutting, respectively, and a fluid channel on both the front and rear sides of the central ridge is provided inside the U-shaped edge ridge. A U-shaped fluid flow path forming recess formed by a forming recess and a fluid folded flow path forming recess below the central convex ridge is formed, and a plate with a convex strip having a flat surface on the other surface. And the flat plate having the same shape and the same outer shape as the plate are overlapped, and the peripheral edge of the ridged plate is joined with the tip of the ridge, and the ridged plate is The tip of the central ridge including the bifurcated upper end Parts are joined to the flat surface of the corresponding central part of the flat plate to form a flat tube having a bifurcated upper end and a U-shaped fluid flow passage therein, and a pair of front and rear square pipes At the lower wall of each of the header forming members, the flat tube upper opening opening insertion holes are provided at predetermined intervals, and the bifurcated upper ends of the flat tubes are respectively connected to the insertion holes of the front and rear header forming members. By doing so, the flat tubes are arranged in parallel, and the front and rear header portions communicating with the bifurcated upper end portions of the flat tubes are formed.

  In the heat exchanger using these flat plates, a plurality of U-shaped ridges for dividing the flow path are provided in the U-shaped fluid flow path forming recesses of the ridged plate by forging or cutting. In the superposed state of the plate and the flat plate, the tip of the U-shaped ridge for channel division of the ridged plate is joined to the flat surface of the corresponding portion of the flat plate, and the U-shaped fluid passage inside the flat tube is formed. A plurality of U-shaped split fluid passages are formed.

  Thirdly, in the heat exchanger of the present invention, a peripheral ridge protruding to one surface side at a peripheral portion, and a central convex ridge protruding to the same surface side at the width center portion and extending in the vertical direction, respectively, It is provided by forging or cutting, and the inner and outer peripheral ridges are formed with fluid passage forming recesses on both front and rear sides of the central ridge, and penetrate the upper and lower ends of both front and rear fluid passage forming recesses. Plates provided with holes and having flat surfaces on the other side are superposed on each other in a state where the front and rear fluid flow path forming recesses are opposed to each other, one pair at a time. The tip portions of the convex portions are joined together, and the tip portions of the central convex portion are joined to form a flat tube having both front and rear fluid channels therein, and a plurality of flat tubes are arranged in parallel, Upper and lower ends of adjacent flat tubes The upper and lower header forming members formed of a pair of front and rear fluid communication cylinders respectively connected to the through holes of the plate and an intermediate connection between them are interposed therebetween, and communicate with the upper end portions and the lower end portions of the flat tubes. It is characterized in that upper and lower header portions are respectively formed.

  Fourth, the heat exchanger of the present invention has, at the left and right side edges, side edge protrusions protruding to one side, and upper and lower end portions that are bifurcated at the center of the width and protrude to the same side. The central ridges are provided by forging or cutting, respectively, and inside and outside the left and right side edge ridges, the fluid channel forming recesses on both front and rear sides of the central ridge are formed, and the other surface is flat. And a pair of plates are superimposed on each other such that the front and rear fluid flow path forming recesses face each other, and the leading end portions of the left and right side edge ridges of the two plates facing each other, and The tips of the central ridges including the forked upper and lower ends are joined together to form a flat tube having upper and lower ends open in a forked shape and having front and rear fluid flow paths therein, and are formed of a square pipe. On the upper wall or lower wall of a pair of front and rear and one pair of upper and lower header forming members, Flat tube upper end opening insertion holes are provided at predetermined intervals, and the forked upper end or lower end of the flat tube is connected to the insertion hole of the header forming member, respectively, so that the flat tube is inserted. It is characterized in that a pair of front and rear and a pair of upper and lower headers are formed in parallel with each other and communicate with the bifurcated upper and lower ends of the flat tube.

  In the heat exchanger having the above-described third and fourth features, a plurality of flow path dividing ridges are provided by forging or cutting in the front and rear fluid flow path forming recesses of each plate, and the front and rear inside of the flat tube are formed. A plurality of divided fluid passages are formed in the fluid flow path, and there are several aspects of this.

  First, in the first mode of the dividing ridge, a plurality of channel dividing ridges are provided by forging or cutting in the front and rear fluid channel forming recesses of each plate. In the superposed state in which the concave portions are opposed to each other, the distal ends of the flow dividing ridges facing each other are joined to form a plurality of divided fluid passages in the front and rear fluid flow passages inside the flat tube.

  Next, in a second aspect of the dividing ridge, the front and rear fluid channel forming recesses of each plate are provided with a plurality of front and rear channel dividing ridges having a height twice the depth of the recess. A pair of plates are provided by forging or cutting so that they are alternately positioned in a superposed state in which the concave portions are opposed to each other. The portions are joined to the flat surface of the bottom wall of the fluid flow passage forming concave portion of the plate opposed thereto, and a plurality of divided fluid passages are formed in the front and rear fluid flow passages inside the flat tube.

  Further, in the third aspect of the dividing ridge, the channel dividing ridge having a height twice the depth of the concave portion is provided in each of the front and rear fluid channel forming concave portions of the pair of plates, These plates are provided by forging or cutting so as to be located alternately in a superposed state. In a superimposed state in which these two types of plates are opposed to each other in the concave portions, the front and rear flow path dividing ridges of each plate are provided. Is joined to the flat surface of the bottom wall of the concave portion for forming the front and rear fluid flow passages of the plate opposed thereto, and a plurality of divided fluid passages are formed in the front and rear fluid passages inside the flat tube.

  Further, the fourth aspect of the divisional ridge is that a plurality of flow path divisional ridges having a height twice as large as the depth of the concave part are provided in one of the front and rear fluid flow path forming concave parts of each plate. Are provided by forging or cutting, and the bottom wall of the other one of the front and rear fluid flow path forming recesses is a flat surface having no flow path dividing ridge, and a pair of two sheets is provided. In a superposed state in which the concave portions of the plates are opposed to each other, the distal end portions of the flow path dividing ridges are joined to the flat surface of the bottom wall of the fluid flow path forming concave portion of the plate facing the flow path, and the flat tube is formed. A plurality of divided fluid passages are formed in the internal front and rear fluid passages.

  In the heat exchanger having the third feature of the present invention, one of the pair of plates may be replaced with a flat plate.

  That is, a peripheral ridge protruding to one surface side at the peripheral portion, a central ridge protruding to the same surface side at the center of the width and extending vertically is provided by forging or cutting, respectively. Fluid flow path forming recesses on both front and rear sides of the central convex ridge are formed inside the ridge, and through holes are respectively provided at upper and lower ends of the front and rear fluid flow path forming recesses, and the other surface is a flat surface. The plate with the ridge and the flat plate having the same shape and the same outer shape as the plate and having a through-hole for fluid entrance and exit corresponding to the through-hole for fluid entrance and exit are overlapped, and the projection is formed. The tip of the ridge on the peripheral edge of the striped plate is joined to the edge of the flat plate, and the tip of the ridge on the center of the ridged plate is joined to the flat surface of the corresponding central part of the flat plate. A flat tube having both front and rear fluid flow paths therein is formed, a plurality of flat tubes are arranged in parallel, and a plate penetrates between upper ends and lower ends of adjacent flat tubes. Upper and lower header forming members each including a pair of front and rear fluid communication tubular portions communicating with the holes and an intermediate connecting portion therebetween are interposed, and upper and lower header portions communicating with the upper end portions and the lower end portions of the flat tubes are respectively formed. ing.

  Here, an intermediate connecting portion of any one of the upper and lower header forming members interposed between the upper end portions and the lower end portions of the adjacent flat tubes is used for the front and rear fluid distribution of the header forming member. There may be a case where a communication passage connecting the cylindrical portions is provided.

  In the heat exchanger having the fourth feature of the present invention, one of the pair of plates may be replaced with a flat plate.

  That is, the left and right side edges have side edge protrusions projecting to one surface side, and the center portion protrusions projecting to the same surface side at the width center and having bifurcated upper and lower ends are forged or cut, respectively. Provided by processing, while a concave portion for forming a fluid flow path on both the front and rear sides of the central ridge is formed inside the left and right side edge ridges, and a ridged plate with the other surface being a flat surface, The plate and a flat plate having the same shape and the same outer shape are overlapped, and the right and left side edges of the ridged plate are joined to the left and right side edges of the flat plate, and the ridges are provided. The tip of the central ridge including the bifurcated upper and lower ends of the plate is joined to the flat surface of the corresponding central part of the flat plate, the upper and lower ends are bifurcated, and the front and rear fluid flow paths are inside. A flat pipe having a square pipe is formed. A flat tube upper opening opening insertion hole is provided at predetermined intervals on the upper wall or lower wall of each of a pair of front and rear and upper and lower header forming members, and the flat tube bifurcation is inserted into the insertion hole of the header forming member. The upper end or lower end of the flat tube is connected in the form of a plug, so that the flat tubes are arranged in parallel, and a pair of front and rear and a pair of upper and lower portions respectively communicating with the upper and lower ends of the flat tube are forked. Header portions are respectively formed.

  In the heat exchanger using these flat plates, a plurality of channel dividing ridges are provided by forging or cutting in the front and rear fluid channel forming recesses of the ridged plate, and the ridged plate and the flat plate are provided. In the superimposed state, the leading end of the channel dividing ridge of the ridged plate is joined to the flat surface of the corresponding portion of the flat plate, and a plurality of divided fluid passages are formed in the front and rear fluid channels inside the flat tube. Have been.

  In the heat exchanger having the first and third features, the right and left end surfaces of the front and rear fluid flow tube portions of the header forming member interposed between the ends of the adjacent flat tubes are flattened to face these. It is joined to the other flat part of the tube plate. In these cases, it is preferable that a temporary fixing protrusion for temporarily fixing the header forming member is provided at each edge of the fluid inlet / outlet through hole at each plate end.

  In the heat exchanger according to the present invention, a plurality of notches are provided in the channel dividing ridge of each plate, and adjacent divided fluid passages inside the flat tube are communicated with each other at the notched portion. Is preferred.

  Further, in all the heat exchangers of the present invention, fins are interposed between the flat tubes adjacent to each other in the flat tubes arranged in parallel, and the right and left side edges of the fins are flattened on the flat tube plate. It is joined to the other surface part.

A car air conditioner according to the present invention uses the above heat exchanger.
An automobile according to the present invention includes the above-described heat exchanger.

  According to the heat exchanger of the present invention, in any of the above cases, the plate used for the heat exchanger, without using a conventional press-formed product, has irregularities provided by forging or cutting on one surface. In addition, the header forming member is formed of a different material from the plate, and the header portion is formed to reduce the width of the flat tube in the front-rear direction, thereby achieving the thinning (thinning) of the flat tube. As a result, the heat transfer area can be increased, the heat transfer efficiency can be improved, and the heat exchange performance can be greatly improved.

  Next, embodiments of the present invention will be described with reference to the drawings.

  In this specification, front and rear, left and right, and up and down are based on FIG. 2, the front is the left side of FIG. 2, the rear is the same right side, and the left is the front side of the drawing sheet and the right is the right side. The upper side means the upper side in the figure, and the lower side means the lower side.

  The drawings show a case where the heat exchanger according to the present invention is applied to an evaporator for a car air conditioner.

  1 to 6 show a first embodiment according to the present invention. The heat exchanger (1) used for the evaporator is made of aluminum (including aluminum alloy).

  First, a substantially rectangular plate (2) made of an aluminum plate is provided with a peripheral ridge (3) protruding on one side at the peripheral portion, and a refrigerant protruding on the same side at the center of the width and extending downward from the upper end. A central ridge (4) extending to a position where a folded flow path can be formed is provided, and a linear refrigerant flow path is formed inside the peripheral ridge (3) on both the front and rear sides of the central ridge (4). U-shaped refrigerant flow path forming recesses (6), each of which is formed by a concave part (6a) (6b) for use and a concave part (6c) for forming a refrigerant return flow path below the central ridge (4). .

  In the first embodiment, a U-shaped notch (14) as viewed from the front is provided at the center of the width of the upper end of the plate (2), and the upper end of the central ridge (4) is The lower end of the U-shaped cut portion (14) is continuous with the peripheral ridge (3).

  At one end of the U-shaped refrigerant flow passage forming recess (6) of the plate (2), one of the through-holes (10) for the refrigerant inlet / outlet (10) is provided with another through-hole (10). The other through-hole (10) is provided at the end, and a plurality of U-shaped ridges (5) for dividing the flow channel extending substantially over the entire length of the concave portion (6) are provided in the concave portion (6) for forming the U-shaped refrigerant flow channel. Is provided.

  Due to the presence of the U-shaped notch (14) in the center of the width of the upper end of the plate (2), the coolant inlet / outlet through holes (10) (10) are separated from each other by the gap of the U-shaped notch (14). However, this prevents unnecessary heat exchange between the low-temperature inlet refrigerant and the high-temperature outlet refrigerant, and the refrigerant introduced into the later-described inlet-side header portion is short-circuited to the outlet-side header portion and migrates. This is to prevent the user from doing so.

  In addition, in order to improve the heat exchange performance of the U-shaped refrigerant flow channel forming concave portion (6), a short arc-shaped ridge ( 9) is provided.

  Here, each plate (2) is made by forging or cutting. Then, the plates (2) are superposed on each other in a state where the U-shaped refrigerant flow passage forming recesses (6) and (6) are opposed to each other by one set of two plates, and the two plates (2) and (2) are The tips of the peripheral ridges (3) and (3) facing each other, the tips of the central ridges (4) and (4) and the tips of the U-shaped ridges for channel division (5) and (5) The flat tubes (12) having the U-shaped refrigerant passages (8) are joined to each other, and a plurality of U-shaped divided refrigerant passages (7) are formed in the refrigerant passages (8) inside the flat tubes (12). ) Is formed.

  These components can be easily joined by using a clad material in which a brazing material is preliminarily bonded to one surface of each plate (2), desirably both inner and outer surfaces.

  In the evaporator (1) of the present invention, so-called header portions (23) and (23) connecting the flat tubes (12) and (12) forming the refrigerant circuit are formed as follows.

  That is, a plurality of the flat tubes (12) are arranged in parallel, and between the upper end portions of the adjacent flat tubes (12) (12), the through-holes (10) for the refrigerant inlet / outlet of the plate (2). A so-called eyeglass-shaped header forming member (20) composed of a pair of front and rear refrigerant circulation tubular portions (21) (21) and a middle connecting portion (22) thereof respectively communicating with the (10) is interposed, and the header forming member ( The left and right end surfaces of the front and rear refrigerant flow tube portions (21) and (21) of (20) are joined to the other flat flat surface portions of the flat tubes (12) and the flat tubes (12) opposed thereto. The front and rear header portions (23) (23) communicating with the upper end portion of the pipe (12) are formed. And, between the flat tubes (12) (12) adjacent to each other below the front and rear header portions (23) (23), a corrugated louver fin (24) for performing heat exchange with air is interposed, and a corrugated louver fin (24) The left and right side edges of the flat tube (12) are joined to other flat flat surfaces of the plates (2) and (2).

  Note that the corrugated louver fin (24) that performs heat exchange with air is formed by forming a louver that improves heat transfer simultaneously with bending.

  In addition, the depth of the gap in the U-shaped notch (14) provided at the center of the width of the upper end of each plate (2) is set to a spectacle type in order to discharge condensed water accumulated in the gap. It is necessary that the header forming member (20) be located below the intermediate connecting portion (22).

  Temporary fixing projections (13) (13) for temporarily fixing the header forming member (20) are provided at the lower edge of the central part of the through-holes (10) (10) for the refrigerant inlet / outlet at the upper end of each plate (2). It is possible to prevent the header forming member (20) from being moved by these temporary fixing projections (13) (13) during brazing.

  As shown in FIGS. 1 and 4, a pair of side plates (25) and (25) are disposed at both left and right ends of the evaporator (1). A block (27) for the entrance and exit pipe connection is joined and integrated to the part, a pair of front and rear through holes (26) (26) opened at the upper end of the side plate (25), and a block for the entrance and exit pipe connection The pair of front and rear through holes (28) and (28) opened in (27) are connected to each other, and the eyeglass-shaped header is formed through the through holes (26) and (26) at the upper end of the side plate (25). The front and rear refrigerant flow tube portions (21) and (21) of the member (20) can be communicated with each other.

  The side plate (25) becomes unnecessary when the entrance / exit pipe connection block (27) is directly attached to the left and right outer end plates (2) of the evaporator (1). In addition, the entrance / exit pipe connection block (27) may be attached to an intermediate portion of the height of the side plate (25). In addition, the entrance / exit pipe connection block (27) is attached to the longitudinal center of the evaporator (1), or the entrance / exit pipe connection block and exit are arranged so that the entrance / exit is located at the left and right separate ends. The pipe connection block on the side may be separately attached to the left and right ends of the evaporator (1).

  After the above evaporator components are combined, they are integrally joined by brazing to form a basic part of the evaporator (1).

  In the above, the brazing is performed by a vacuum brazing method performed in a vacuum or an in-furnace brazing method using a fluorine-based flux.

  Here, it is desirable to use a relatively high-strength material for the header forming member (20) and the side plate (25) in view of pressure, and it is particularly preferable to use an aluminum alloy material to which magnesium is added. preferable.

  Also, in the joining using a fluorine-based flux, it is preferable to use a material made of an aluminum alloy having a magnesium content of 0.4% or less, since the joining property and strength can be improved.

  Since the joint surface between the plate (2) and the corrugated fin (24) is almost flat, the corrugated fin (24) and the flat tube (12) are in a nearly 100% joined state, and the flat tube (12) The heat exchange from the inside of the circuit to the corrugated fin (24) becomes highly efficient.

  The header forming member (20) constituting the header portions (23) and (23) has a roughly glasses-shaped cross section having two refrigerant passages, one of which is an inlet refrigerant, and the other is an outlet refrigerant. Have the function of collecting or distributing

  When the heat exchanger of the present invention is used as an evaporator (1), a refrigerant is introduced into each flat tube (12) in a mixed state of liquid and gas. At this time, the liquid refrigerant has a higher density than the gas, and is more susceptible to the inertia of the flow. It can be said that the flow of the liquid refrigerant has higher straightness than the gas. For this reason, the liquid refrigerant tends to collect a large amount of the refrigerant at the header end far from the inlet header portion. The drift of the liquid refrigerant causes an imbalance in the latent heat of evaporation of each part, which is a major cause of performance degradation. As a method of preventing this, it is effective to project the flat tube (12) into the header portion (23) and to reduce the straightness of the liquid refrigerant as a so-called baffle plate.

  In the present invention, the height (b1) of the through hole (10) on the inlet side of the flat tube (12) is made smaller than the inner diameter (b2) of the refrigerant flow tube (21) of the header forming member (20). The structure of the baffle can be easily taken. Alternatively, at one or more locations, the cross-sectional area of the front and rear refrigerant flow cylinders (21) and (21) of the glasses-type header forming member (20) may be reduced to change the cross-sectional area of the flow, as a baffle plate. Has the effect of

  By these operations, the liquid refrigerant reduces the straightness in the header portions (23) and (23), and the branching to each flat tube (12) becomes uniform, so that a high heat exchange performance can be obtained. It is.

In the evaporator (1) according to the present invention, the projecting ratio of the flat tube (12) in the header portion (23),
When defined as (b2-b1) / b2,
(Where b1: the height of the through-hole (10) on the inlet side of the flat tube (12), b2: the inner diameter of the refrigerant flow tube (21) of the header forming member (20))
The pop-out ratio is preferably in the range of 10 to 60%. Here, if the pop-out ratio is less than 10%, the effect as a baffle plate is lost, and drift is likely to occur. If the pop-out ratio exceeds 60%, the flow resistance in the header portion (23) increases, On the contrary, the performance decreases.

  By the way, as shown in detail in FIG. 5, a tapered surface is provided on the inner surface of the peripheral ridges (3) (3) of the pair of plates (2) (2) of each flat tube (12), and A tapered surface is provided on the inner surface of the ridges (4) and (4), and a tapered surface is provided on the inner surface of each of the U-shaped ridges (5) and (5) for dividing the flow passage, and the inside of the flat tube (12) is formed. It is particularly preferable that the cross section of the plurality of U-shaped divided refrigerant passages (7) formed in the refrigerant passage (8) is substantially hexagonal. This is because it is advantageous in terms of heat transfer to thinly extend the liquid refrigerant to the surface inside the refrigerant passage (8) of the flat tube (12).

  Among the plurality of U-shaped divided refrigerant passages (7) formed in the refrigerant passage (8) inside the flat tube (12), the peripheral ridge (3) and the U-shaped ridge (5) The cross-section of the divided refrigerant passage (7a) is a wide hexagon, and the cross-section of the divided refrigerant passage (7b) between the U-shaped ridges (5) (5) for dividing the flow path is It is a narrow hexagon.

  On the other hand, as shown in FIG. 7, for example, when the cross section of the plurality of U-shaped divided refrigerant passages (7) formed in the refrigerant passages (8) inside the flat tubes (12) is square, When the circuit width is reduced to increase the surface area on the refrigerant side, the liquid refrigerant tends to collect at the corners of the wall surface of the flat tube (12). The reason for this is that the liquid refrigerant having a low flow velocity is pushed to the end of the passage with respect to the gas flowing at a high velocity. As a result of the liquid refrigerant required for evaporation being pushed to the end, the peripheral ridges (3) and (3), the central ridges (4) and (4) in the flat tube (12), and the U The liquid refrigerant does not adhere to the inner wall surfaces of the ridges (5) and (5), and effective heat transfer cannot be obtained, so that the desired performance cannot be achieved.

  As shown in FIG. 5, since the cross-section of the U-shaped divided refrigerant passage (7) has a substantially hexagonal shape, the liquid refrigerant is most likely to collect in the concave portion in the middle of each refrigerant passage (7). , A flat tube (12), a pair of plates (2), (2), a tapered surface of a ridge (3), (3) at the peripheral edge, a tapered surface of a ridge (4), (4) at the center, and each channel The liquid refrigerant adheres to the tapered surfaces of the U-shaped ridges (5) and (5) to obtain effective heat transfer, and these ridges effectively act as internal fins, improving heat transfer performance. As a result, the effective portion of the heat transfer section inside the refrigerant passage (7) is increased, and the air is comfortably cooled.

  However, the evaporator (1) of the present invention may be any of the embodiments shown in FIGS. This is because the entire width of the passage through which the refrigerant flows and the width of contact with the corrugated fin (24) are the same, so that a higher heat exchange rate can be obtained as compared with a conventional heat exchanger.

  In the first embodiment of the present invention, the width of the plate (2) is, for example, 10 to 40 mm, and the thickness of the plate (2) is, for example, 0.25 to 1.0 mm.

  The thickness of the peripheral ridge (3) of the plate (2) is, for example, 0.25 to 1.0 mm, and the width thereof is, for example, 0.5 to 2.0 mm. The thickness of the central ridge (4) of the plate (2) is, for example, 0.25 to 1.0 mm, and the width is, for example, 0.5 to 2.0 mm. The thickness of each U-shaped ridge (5) for dividing the flow channel of the plate (2) is, for example, 0.25 to 1.0 mm, and the width thereof is, for example, 0.25 to 1.0 mm.

  In the evaporator (1), the refrigerant introduced into the front header portion (23) from the one inlet side through hole (28) opened in the entrance / exit pipe connection block (27) passes through each flat tube (12). From one end of the U-shaped refrigerant passage (8), it flows into the U-shaped divided refrigerant passage (7) in a U-shape, reaches the other end of the U-shaped refrigerant passage (8), and further has a rear header ( From 23), it is discharged to the outside through the other exit side through hole (28) of the entrance / exit pipe connection block (27).

  On the other hand, the air flows from the front to the rear, and the waveform between the adjacent flat tubes (2) and (2) of the evaporator (1) and between the flat tubes (12) and the end plate (25). The air and the refrigerant can efficiently exchange heat through the gap where the louver fins (24) are present and through the wall surface of the flat tube (12), the end plate (25), and the corrugated louver fins (24). .

  According to the evaporator (1) of the first embodiment, the plate (2) used for the evaporator (1) can be provided with an uneven strip provided on one side by forging or cutting without using a conventional press-formed product. The header forming member is formed of a different material from the plate, and by forming the front and rear header portions (23) and (23), the width of the flat tube (12) in the front-rear direction is reduced, and the flat tube is formed. (12) can be made thinner (thinner), the heat transfer area can be increased, the heat transfer efficiency can be improved, and the heat exchange performance can be greatly improved.

  As shown in FIG. 8, for example, in order to improve the heat transfer of the refrigerant in the flat tube (12), a plurality of notches (15) are formed in the U-shaped ridge (5) for dividing the flow passage of each plate (2). ) Are provided at predetermined intervals and in a staggered arrangement with mutually adjacent ones, and the adjacent U-shaped divided refrigerant passages (7) (7) inside the flat tube (12) are notched ( 15) It is preferred that the parts communicate with each other.

  Alternatively, in the flat tube (12), as shown in, for example, FIGS. 9 and 10, a turbulent flow is caused in the flow of the refrigerant, and a turbulence promoting body (projection) (16) is staggered to improve heat transfer. It is good to provide in the shape arrangement.

  11 and 12 show a second embodiment of the present invention. Here, the difference from the case of the first embodiment is that a pair of front and rear header forming members (41) and (42) made of a square pipe are used.

  That is, a substantially rectangular plate (2) made of an aluminum plate of the evaporator (1) is provided on one side with left and right side edges and a lower edge, and a U-shaped edge ridge (33) is provided as a whole, A central ridge (34) is provided at the center of the width and extends from the upper end (34a), which protrudes to the same side, and extends from the upper end (34a), which is formed into a forked shape, to a position where a refrigerant return flow path can be formed. Inside the ridges (33), the recesses (36a) and (36b) on both sides of the center ridges (34) before and after the center ridges (34) and the coolant return channels below the center ridges. A concave portion (36) for forming a U-shaped refrigerant flow path formed of a concave portion (36c) is formed, and a plurality of flow path divisions extending over substantially the entire length of the concave portion (36) are formed in the concave portion (36) for forming a U-shaped refrigerant flow path. A U-shaped ridge (35) is provided.

  In addition, in order to improve the heat exchange performance at the portion of the U-shaped refrigerant flow channel forming concave portion (36), at the corner of the refrigerant return flow channel forming concave portion (36c), a short arc-shaped ridge ( 39) is provided.

  In the second embodiment, a U-shaped notch (37) as viewed from the front is provided at the center of the width of the upper end of the plate (2), and the upper end (34a) of the central ridge (34) is provided. Are forked.

  Here, each plate (2) is made by forging or cutting. Then, the plates (2) are superposed on each other such that the U-shaped refrigerant flow path forming recesses (36) (36) are opposed to each other, one set of two plates. The tips of the U-shaped edge ridges (33) and (33) facing each other, the tips of the central ridges (34) and (34) including the forked upper ends (34a) and (34a), and the flow path The distal ends of the U-shaped ridges (35) (35) for division are joined to each other to form a flat tube (32) whose upper end portions (32a) and (32a) open in a bifurcated manner. 32), a plurality of U-shaped divided refrigerant passages are formed.

  On the other hand, the pair of front and rear header forming members (41) and (42) are each formed of a square pipe having a lower wall (43), a front wall (45), a rear wall (46), and an upper wall (47). There are flat tube upper end opening insertion holes (44) and (44) at predetermined intervals on the lower walls (43) and (43) of the front and rear header forming members (41) and (42), respectively. The forked upper ends (32a) and (32a) of the flat tubes (32) are connected to the insertion holes (44) and (44) of the disposed front and rear header forming members (41) and (42), respectively. Thus, the flat tubes (32) are arranged in parallel in the left-right direction, and the front and rear header portions communicating with the forked upper ends (32a) (32a) of the flat tubes (32) are formed. At this time, the rear wall of the parallel front and rear header forming members (41) and (42) are inserted into the U-shaped cut portions (37) and (37) at the upper ends of the left and right plates (2) and (2) of each flat tube (32). (46) and the front wall (45) are fitted in a superposed state.

  Corrugated fins (24) are interposed between adjacent flat tubes (32) (32) below the front and rear headers, and the left and right side edges of the corrugated fins (24) are plates (2) of flat tubes (32). It is joined to the flat other surface part of (2).

  In the evaporator (1) according to the second embodiment, the brazing is performed in a vacuum brazing method performed in a vacuum or an in-furnace brazing method using a fluorine-based flux. Since the configuration is the same as that of the first embodiment, the same components are denoted by the same reference numerals in the drawings.

  Although not shown, in the evaporator (1) according to the second embodiment of the present invention, instead of the pair of front and rear header forming members (41) and (42) formed of a square pipe, a central portion is formed by a partition wall. Using one extruded aluminum member having two partitioned refrigerant passages having a substantially rectangular cross section, flat tube upper end opening insertion holes (44) (44) are provided at predetermined intervals in the lower wall of each refrigerant passage. These flattened tubes are arranged in parallel by connecting the forked upper ends (32a) and (32a) of the flat tubes (32) to these insertion holes (44) and (44), respectively. The front and rear header portions communicating with the forked upper end portions (32a) and (32a) of the pipe (32) may be formed.

  13 to 17 show a third embodiment of the present invention. Here, the difference from the first embodiment is that header portions (57) and (58) are provided on the upper and lower sides of the evaporator (1).

  Referring to the figure, a substantially rectangular plate (2) made of an aluminum plate is provided with a peripheral ridge (3) protruding to one side at a peripheral portion thereof, and protruding to the same side at a central portion of the width and vertically. The central ridge (4) is provided, and the refrigerant channel forming recesses (6a) and (6b) on both the front and rear sides of the central ridge (4) are formed inside the peripheral ridge (3). In addition, through holes (10) and (10) are provided at the upper and lower ends of both the front and rear refrigerant flow path forming recesses (6a) and (6b), and the front and rear refrigerant flow path forming recesses (6a) and (6b) are provided. A linear channel dividing ridge (5) extending substantially over the entire length of the concave portions (6a) (6b) is provided therein.

  Here, each plate (2) is made by forging or cutting. Then, the plates (2) are superposed on each other such that the front and rear recesses (6a) and (6b) for the refrigerant flow channel formation are opposed to each other, one set of two plates, and the plates (2) and (2) are The tips of the opposing peripheral ridges (3) and (3), the tips of the central ridges (4) and (4), and the tips of the channel dividing ridges (5) and (5) are joined. Thus, a flat tube (12) is formed, and a parallel divided refrigerant passage (7) is formed inside the flat tube (12) (see FIG. 7 of the first embodiment).

  The required number of flat tubes (12) are arranged in parallel, and between the upper ends and the lower ends of the adjacent flat tubes (12) (12), the through holes (10) ( A so-called eyeglass-shaped upper and lower header forming member (51) comprising a pair of front and rear refrigerant flow cylinders (53) (53) (54) (54) and a middle connecting portion (55) (56) communicating with the front and rear, respectively. ) (52) are interposed.

  As shown in detail in FIG. 14, of the pair of front and rear through holes (10) provided at the upper and lower ends of the plate (2), a pair of front and rear through holes (10a) (10a) ( 10a) each have a long oval in the horizontal direction, and corresponding to these, before and after the upper header forming member (51) interposed between the upper ends of the flat tubes (12) and (12). The two refrigerant distribution cylinders (53), (53) similarly have an oblong cross section that is long in the horizontal direction. On the other hand, the pair of front and rear through holes (10b) (10b) at the lower end of the plate (2) have oblong shapes inclined forward and downward, and corresponding to these, the flat tube (12 Both the front and rear refrigerant flow cylinders (54) and (54) of the lower header forming member (52) interposed between the lower ends of the (12) are oval similarly inclined forward and downward. .

  As shown in FIGS. 16 and 17, the left and right end surfaces of the front and rear refrigerant flow tube portions (53), (53), (54), and (54) of the upper and lower header forming members (51) and (52) are flat. Upper and lower header portions (57) (58) which are joined to the flat other surface portion of the plate of the tubes (12) (12) and communicate with the upper end portions and the lower end portions of the flat tubes (12) (12) respectively. Is formed.

  A wavy louver fin (24) for exchanging heat with air is interposed between flat tubes (12) (12) adjacent to each other in the middle between the upper and lower header portions (57) (58), and a wavy louver fin (24) The left and right side edges are joined to the other flat surface of the plates (2) and (2) of the flat tubes (12) and (12).

  Further, in the evaporator (1) of the third embodiment, the upper and lower header forming members (51) (52) interposed between the upper ends and the lower ends of the adjacent flat tubes (12) (12). Of these, communication passages (59) for connecting the front and rear refrigerant flow cylinders (54) (54) of the header forming member (52) to the left and right sides of the intermediate connecting portion (56) of the lower header forming member (52). ) (59).

  In the evaporator (1) of the third embodiment, the front upper header portion (57) of each upper header forming member (51) is inserted through one of the entrance side through holes (28) opened in the entrance / exit pipe connection block (27). The refrigerant introduced into the front-side refrigerant flow tube portion (53) constituting the front-end portion (57) flows from the header portion (57) into the front upper end portion of the refrigerant passage (8) of each flat tube (12), and further flows straight. The front refrigerant flows down the divided refrigerant passage (7), reaches the front lower end of the refrigerant passage (8), and forms the front lower header part (58) of each lower header forming member (52) from there. Once flowing into the distribution cylinder (54), there passes through the communication passages (59) (59) in the lower header forming member (52) and forms a rear lower header (58) for rear refrigerant circulation. It flows into the cylindrical portion (54). Then, the refrigerant flows into the rear lower end portion of the refrigerant passage (8) of each flat tube (12), and further rises in the linear divided refrigerant passage (7), and then flows after the refrigerant passage (8). To the upper end of the side, passing through the rear refrigerant flow tube (53) constituting the rear upper header (57) of each upper header forming member (51), and passing through the other end of the inlet / outlet pipe connection block (27). Is discharged to the outside through the outlet side through hole (28).

  In the evaporator (1) of the third embodiment, both the front and rear refrigerant flow cylinders (54) of the lower header forming member (52) interposed between the lower ends of the flat tubes (12) (12). ) (54) has an oblong cross section inclined forward and backward downward because the condensed water (condensed water) formed on the outer surface of the evaporator (1) when the evaporator (1) is used. ) Is taken into consideration so that the discharge can be performed smoothly.

  Although not shown, in the evaporator (1) of the third embodiment, a plurality of notches (5) are formed in the channel dividing ridges (5) of each plate as in the modification of FIG. 15) may be provided, and the adjacent divided refrigerant passages (7) (7) inside the flat tube (12) may be connected to each other at the notch (15).

  Also, in the evaporator (1) of the third embodiment, contrary to the case shown in the drawing, the upper and lower header forming members ( Of the 51) and (52), the left and right refrigerant flow cylinders (53) and (53) of the header forming member (51) are provided on the left and right sides of the intermediate connecting portion (55) of the upper header forming member (51). Communication passages (59) (59) for communication are provided, and the refrigerant may flow in the opposite direction to that shown in the drawings.

  In other respects, the evaporator (1) of the third embodiment is the same as that of the first embodiment, and therefore, the same components are denoted by the same reference numerals in the drawings.

  FIGS. 18 and 19 show a second mode of the channel dividing ridges (5) of the plate (2) used in the evaporator (1) of the first embodiment of the present invention. The shape and arrangement of the flow path dividing ridges (5a) and (5b) provided in the refrigerant flow path forming recess (6) are the flow paths shown in FIGS. 2, 3 and 5 of the first embodiment. Unlike the U-shaped ridges for division (5), the leading ends of the ridges (5a) and (5b) for dividing the flow path of each plate (2) are used for forming the refrigerant flow path of the plate (2) opposed thereto. The difference is that it is joined to the flat surface of the bottom wall of the recess (6).

  Referring to the figure, a peripheral ridge (3) protruding on one side is provided on the peripheral edge of each plate (2) of the evaporator (1), and a protruding edge on the same side at the center of the width and from the upper end. A central ridge (4) is provided extending to a position where a lower refrigerant return flow path can be formed, and the depth of the concave portion (6) is provided in the refrigerant flow path forming concave portion (6) of each plate (2). A large number of ridges (5a) and (5b) for dividing the front and rear flow passages having a double height have a U-shape of the flat tube portion (12) when the pair of plates (2a) and (2b) are overlapped. Are formed so as to form independent parallel U-shaped divided refrigerant passages (7) in the refrigerant passage (8).

  That is, referring to FIG. 18, the front and rear flow path dividing ridges (5a) and (5b) are provided in the front and rear straight flow path forming portions (6a) and (6b) of the refrigerant flow path forming recess (6). The U-shaped portion consisting of the straight portions (5a1) (5b1) and the quarter-arc portions (5a2) (5b2) connected to them and provided in the folded portion (6c) of the recess (6). It has the shape of The straight portions (5a1) and (5b1) and the quarter-arc portions (5a2) and (5b2) of these channel dividing ridges (5a) and (5b) are composed of a pair of plates (2a) and (2b). ) Are arranged alternately at predetermined intervals in a superposed state in which the concave portions (6) and (6) face each other.

  Then, in the superposed state of these two plates (2a) and (2b), the central ridges (4) and (4) facing each other and the peripheral ridges (3) and (3) of the same plate abut each other. While being joined together, the tip of the linear portion (5a1) (5b1) and the tip of the quarter-arc portion (5a2) (5b2) of the two channel dividing ridges (5a) (5b) are A flat tube portion (12) having a U-shaped refrigerant flow path (8) is formed by being joined to the flat surface of the bottom wall of the refrigerant flow path forming concave portion (6) of the plate (2a) (2b) opposed thereto. Then, in the U-shaped refrigerant flow path (8) of the flat tube portion (12), the ridges (5a) for splitting the front flow path of the front plate (2a) of one of the two plates (2a) and (2b). ) And the rear channel dividing ridge (5b) of the other plate (2b) are connected in a U-shape to form a parallel U-shaped divided refrigerant channel (7). The folded portion of each divided refrigerant flow path (7) has a semicircular arc shape.

  In addition, the U-shaped refrigerant flow path forming concave portion (6) has short arc-shaped portions at both front and rear corners of the refrigerant return flow path forming concave portion (6c) in order to improve the heat exchange performance in this portion. The convex ridges (9a) and (9b) are provided, however, these short arc-shaped convex ridges (9a) and (9b) on both front and rear sides are such that a pair of plates (2a) and (2b) 6) They are arranged so as to be alternately positioned at predetermined intervals in a superposed state where (6) is opposed to each other.

  In the above, other points such as each plate (2) being made by forging or cutting are the same as in the case of the first embodiment. The sign was attached.

  According to the evaporator (1), the ridges (5a) and (5b) for dividing the front and rear passages of the pair of plates (2a) and (2b) are combined with the linear portions (5a1) and (5b1). It has a shape that is just half of a U-shape consisting of a series of quarter-arc portions (5a2) and (5b2), and these channel dividing ridges (5a) and (5b) are a pair of plates (2a ) (2b) are arranged so that they are alternately positioned at predetermined intervals in the superposed state where the recesses (6) and (6) face each other, so that each plate (2a) (2b) is forged or cut. The number of the channel dividing ridges (5a) (5b) formed by processing or the like can be reduced, and between the channel dividing ridges (5a) (5b) of each plate (2a) (2b). The gap is wide, and the shape of each channel dividing ridge (5a) (5b) is only half the size of the U-shape, and therefore the advantage that the plates (2a) (2b) can be easily manufactured is provided. is there.

  FIG. 20 and FIG. 21 show a third mode of the channel dividing ridges (5) of the plate (2) used in the evaporator (1) of the first embodiment of the present invention. Using two types of plates (2a) and (2b) having different arrangements of the U-shaped ridges (5a) and (5b) for channel division provided in the concave portions (6) and (6), and both plates (2a) The leading ends of the flow path dividing ridges (5a) and (5b) of (2b) are joined to the flat surfaces of the bottom walls of the refrigerant flow path forming recesses (6) of the plates (2a) and (2b) opposed thereto. Is different from the case of the first embodiment.

  Referring to the figure, the depth of the recesses (6) and (6) is twice the depth of the recesses (6) and (6), respectively, in the U-shaped coolant passage forming recesses (6) and (6) of the pair of plates (2a) and (2b). U-shaped ridges (5a) (5b) for channel division having a height of are provided such that these plates (2a) (2b) are alternately positioned at predetermined intervals in a superimposed state. .

  Then, in the superposed state of these two plates (2a) and (2b), the central ridges (4) and (4) facing each other and the peripheral ridges (3) and (3) of the same plate abut each other. The ends of the U-shaped ridges (5a) (5b) for dividing the flow path of both plates (2a) and (2b) are connected to the refrigerant flow paths of the plates (2a) and (2b) opposed to these. It is joined to the flat surface of the bottom wall of the forming recesses (6) and (6), and is formed in the U-shaped refrigerant flow path (8) by the parallel divisions divided by the flow dividing ridges (5a) and (5b). A flat tube portion (12) having a U-shaped divided refrigerant passage (7) is formed.

  In addition, the U-shaped refrigerant flow path forming recesses (6), (6) in the front and rear corners of the refrigerant return flow path forming recessed part (6c), in order to improve the heat exchange performance in this part, respectively, Short arc-shaped ridges (9a) and (9b) are provided, and these short arc-shaped ridges (9a) and (9b) on both front and rear sides are paired with a pair of plates (2a) and (2b). Are provided alternately at predetermined intervals in the superimposed state.

  In the above, other points such as each plate (2) being made by forging or cutting are the same as in the case of the first embodiment. The sign was attached.

  According to the evaporator (1) using the two types of plates (2a) and (2b), the U-shaped ridges (5a) and (5b) for dividing the flow path of both plates (2a) and (2b) (2a) (2b) Since they are provided so as to be alternately positioned at predetermined intervals in the superimposed state of each other, U for channel dividing formed by forging or cutting on each plate (2a) (2b) The number of the convex ridges (5a) and (5b) can be reduced, and the distance between the U-shaped convex ridges (5a) and (5b) of each plate (2a) and (2b) is wide, so that the plates (2a) and There is an advantage that the production of 2b) is easy.

  FIGS. 22 and 23 show a fourth mode of the channel dividing ridges (5) of the plate (2) used in the evaporator (1) of the first embodiment of the present invention. A large number of flow dividing ridges (5) are provided only in the second half of the refrigerant flow passage forming concave portion (6), and the flow dividing ridge (5) is provided in the first half of the concave portion (6). It is not provided at all, it has a flat surface, and the channel dividing ridge (5) has a shape that is exactly half of the U-shape. The difference from the first embodiment is that the tip of the ridge (5) is joined to the flat surface of the bottom wall of the refrigerant flow passage forming recess (6) of the plate (2) facing the ridge (5). ing.

  Referring to the figure, a peripheral ridge (3) protruding on one side is provided on the peripheral edge of each plate (2) of the evaporator (1), and a protruding edge on the same side at the center of the width and from the upper end. A central ridge (4) is provided extending to a position where a lower refrigerant return channel can be formed, and a concave portion (6) is provided at the rear half of the refrigerant channel forming concave portion (6) of each plate (2). A large number of channel dividing ridges (5b) having a height twice the depth are provided, and the bottom wall of the first half of the concave portion (6) is completely covered with the channel dividing ridge (5). It has a flat surface that it does not have.

  That is, referring to FIG. 22, the channel dividing ridges (5b) provided in the rear half of the refrigerant flow path forming recess (6) of each plate (2) are ), A straight portion (5b1) provided in the rear straight flow path constituting portion (6b), and a quarter-arc portion (5c1) connected to the straight portion (5b1) and provided in the folded portion (6c) of the recess (6). 5b2).

  In the superposed state of the pair of plates (2a) and (2b), the central ridges (4) and (4) opposed to each other and the peripheral ridges (3) and (3) of the plate Are abutted to each other and joined, and the leading end of the channel dividing ridges (5) and (5) are opposed to the plates (2a) and (2b). A flat tube portion (12) having a U-shaped refrigerant flow path (8) is formed by being joined to the flat surface of the bottom wall of (6), and the front side of one of the plates (2a) and (2b) (2a) is formed. The parallel U-shaped divided refrigerant flow path divided by the flow dividing ridge (5a) and the rear flow dividing ridge (5b) of the other plate (2b) being continuous in a U shape ( 7) are formed in the U-shaped refrigerant flow path (8) of the flat tube portion (12). The folded portion of each divided refrigerant flow path (7) has a semicircular arc shape.

  In addition, a short arc-shaped portion is provided at the rear corner portion of the U-shaped refrigerant flow channel forming concave portion (6) on the rear side of the refrigerant folded flow channel forming concave portion (6c) in order to improve heat exchange performance at the portion. A ridge (9) is provided.

  In the above-mentioned evaporator (1), other points such as each plate (2) being made by forging or cutting are the same as in the case of the first embodiment. Those are given the same reference numerals.

  Further, according to the evaporator (1), the ridges (5) for dividing the flow passage of each plate (2) are formed in a U-shape composed of straight portions (5b1) and quarter-arc portions (5b2) connected to the straight portions (5b1). And the bottom wall of the front half of the recess (6) for forming the coolant flow passage of each plate (2) has a flat surface having no ridges (5) for dividing the flow passage at all. Therefore, the size of the channel dividing ridges (5) formed on each plate (2) by forging or cutting, etc., is half the size, so that the plates (2a) and (2b) can be easily manufactured. There is an advantage that there is.

  FIG. 24 shows a case where one of a pair of plates is replaced with a flat plate in the evaporator (1) of the first embodiment of the present invention.

  Referring to FIG. 2, a plate (2b) composed of the plate with ridges (2) of the first embodiment has a peripheral ridge protruding to one surface side on its peripheral edge, as is apparent from FIG. (3) is provided, and a central ridge (4) is provided at the center of the width, protruding to the same side, and extending from the upper end to a position where a lower refrigerant return flow path can be formed. Inside the strip (3), the recesses (6a) and (6b) for forming the linear refrigerant flow path on both front and rear sides of the central ridge (4) and the refrigerant return flow path below the central ridge (4) A U-shaped refrigerant flow path forming concave portion (6) formed of the concave portion (6c) is formed. A plurality of U-shaped ridges (5) for dividing the flow passage are provided in the U-shaped refrigerant flow passage forming recess (6) over substantially the entire length of the recess (6). At the center of the width of the upper end of the plate (2b), a U-shaped notch (14) is provided as viewed from the front, and the upper end of the central ridge (4) is formed by the U-shaped notch (14). ) Is continuous with the peripheral ridge (3) at the lower end. At one end of the U-shaped refrigerant flow passage forming recess (6) of the plate (2b), one of the through-holes (10) for the refrigerant inlet / outlet is provided with one of the through-holes (10). The other through hole (10) is provided at the end.

  On the other hand, the flat plate (2a) is not provided with a U-shaped refrigerant flow passage forming concave portion or a U-shaped ridge for dividing the flow channel, and is a flat surface, but the flat plate (2b) has a flat surface. The flat plate (2a) has the same outer shape, and is provided with a U-shaped notch at the center of the width of the upper end of the flat plate (2a) when viewed from the front. Further, through holes for refrigerant inlet / outlet are provided on both front and rear sides of the upper end of the flat plate (2a) (not shown).

  Then, the flat plate (2a) and the ridged plate (2b) are overlapped one by one in an opposing manner, and the periphery of the ridged plate (2b) and the tip of the ridge (3) are flat plate. The tip of the central ridge (4) is on the flat surface of the central portion of the flat plate (2a), and the tip of the U-shaped ridge (5) Are joined to corresponding flat surfaces of the flat plate (2a) to form a flat tube (12) having a U-shaped refrigerant passage (8), and a refrigerant passage (8) inside the flat tube (12). ), A plurality of U-shaped divided refrigerant passages (7) are formed.

  Note that, in the evaporator (1) using the flat plate (2a), other points such as that the ridged plate (2b) is formed by forging or cutting, etc. are the same as those of the first embodiment. Therefore, the same components are denoted by the same reference numerals in the drawings.

  According to the evaporator (1), the same applies to the ridged plate (2b) having the peripheral ridge (3), the central ridge (4), and the U-shaped ridge for channel division (5). Since the flat plate (2a) having the outer shape is used, the number of use of the ridged plate (2b) formed by forging or cutting can be halved, and therefore, it is easy to manufacture the evaporator (1). There are advantages.

  In the evaporator (1) using the pair of front and rear header forming members (41) and (42) made of the square pipe of the second embodiment shown in FIGS. Is raised.

  First, similarly to the case shown in FIGS. 18 and 19, the first modified example has linear portions (5a1) and (5b1) in the concave portions (6) for forming the refrigerant passages of each plate (2). A large number of ridges for dividing the front and rear flow passages having a shape that is just half the U-shape composed of a series of quarter-arc portions (5a2) and (5b2) and having a height that is twice the depth of the recess (6). 5a and 5b are independent parallel U-shaped divided refrigerants in the U-shaped refrigerant passageway 8 of the flat tube portion 12 when the pair of plates 2a and 2b are superimposed. A plate (2) provided so as to form the flow path (7) can be used.In this case, the leading end of the flow path dividing ridge (5a) (5b) of each plate (2) can be used. Are joined to the flat surface of the bottom wall of the concave portion (6) for forming the coolant flow path of the plate (2) facing these.

  Next, similarly to the case shown in FIGS. 20 and 21, the second modified example is provided in the coolant flow path forming recesses (6) and (6) and has a depth of each of the recesses (6) and (6). It is possible to use two types of plates (2a) and (2b) having different arrangements of the U-shaped ridges (5a) and (5b) for dividing the flow channel having a height twice as large as the above. 2a) (2b) the flat ends of the bottom walls of the refrigerant flow passage forming recesses (6) of the plates (2a) and (2b) facing the front ends of the flow dividing ridges (5a) (5b). Is joined to.

  Further, in the third modified example, similarly to the case shown in FIGS. 22 and 23, a large number of flow dividing ridges (5) are provided only in the rear half of the concave part (6) for forming the refrigerant flow path. In the first half of the recess (6), there is no flow dividing ridge (5) at all, and the flat surface is formed, and the flow dividing ridge (5) is just half of the U-shape. A plate (2) having a shape can be used, and in this case, the leading end of the channel dividing ridge (5) of each plate (2) has the tip of the plate (2) opposed thereto. It is joined to the flat surface of the bottom wall of the recess (6) for forming a coolant flow path.

  Further, in the fourth modified example, similarly to the case shown in FIG. 24, a flat plate having the same outer shape as the plate with a ridge (2b) formed of the plate (2) of the second embodiment shown in FIG. A plate (2a) can be used.In this case, the tip of the peripheral ridge (3) of the ridged plate (2b) is convex on the flat surface of the peripheral edge of the flat plate (2a). The tip of the ridge (4) is on the flat surface at the center of the flat plate (2a), and the tip of the U-shaped ridge for channel splitting (5) is on the flat surface of the corresponding portion of the flat plate (2a). A flat tube (12) having a U-shaped refrigerant passage (8) is formed by joining, and a plurality of U-shaped divided refrigerant passages (7) are formed in the refrigerant passage (8) inside the flat tube (12). Is formed.

  Although not shown, in the evaporator (1) in which the header portions (57) and (58) are provided on the upper and lower sides of the third embodiment of the present invention, the so-called glasses-type upper and lower portions shown in FIGS. Instead of the header forming members (51) and (52), a pair of front and rear header forming members (41) and (42) made of a so-called square pipe shown in FIGS. 11 and 12 may be used.

  If this case is referred to as a fourth embodiment of the present invention, the evaporator (1) of the fourth embodiment of the present invention will be described with reference to FIGS. A central portion convex ridge (34) having upper and lower ends (34a) (34a) which are protruded on the same surface side at the width central portion and have a bifurcated shape is formed at the central portion of the width. Each is provided by forging or cutting, and inside the left and right side edge ridges (33) and (33), the linear refrigerant flow path forming recesses (36a) on both front and rear sides of the central ridge (34) (36a) ( 36b) are formed, and the plate (2) having a flat surface on the other side is overlapped with each other such that the front and rear refrigerant flow path forming recesses (36a) and (36b) face each other. Including the front and rear ends of the linear left and right side edge ridges (33) and (33) facing each other of the plates (2) and (2), and the bifurcated upper and lower ends (34a) and (34a) Same as the tip of the central ridge (34) (34) A flat tube (32) having upper and lower ends open in a forked shape and having linear front and rear refrigerant flow paths (38) and (38) is formed therein, and a pair of front and rear square pipes are formed. A flat tube upper end opening insertion hole (44) (44) is provided in the upper wall (47) (47) or the lower wall (43) (43) of the upper and lower set of header forming members (41) (42), respectively. Provided at intervals, the forked upper end or lower end of the flat tube (32) is inserted into the insertion holes (44, 44) of the header forming members (41, 42) respectively. Thereby, the flat tubes (32) are arranged in parallel in the left-right direction, and a pair of front and rear and a pair of upper and lower headers respectively communicating with the forked upper and lower ends of the flat tubes (32) are respectively formed. ing. At this time, the rear wall of the parallel front and rear header forming members (41) and (42) are inserted into the U-shaped cut portions (37) and (37) at the upper ends of the left and right plates (2) and (2) of each flat tube (32). (46) and the front wall (45) are fitted in a superposed state.

  Then, the evaporator (1) according to the third embodiment of the present invention in which the header portions (57) and (58) are provided on both upper and lower sides by the glasses-type upper and lower header forming members (51) and (52), and In the evaporator (1) according to the fourth embodiment of the present invention in which header portions are provided on both upper and lower sides by a pair of front and rear header forming members (41) and (42) formed of a mold pipe, the following modified examples are given. Can be

  First, in the first modified example, similarly to the case shown in FIGS. 18 and 19, the recesses (6a) and (6b) are formed in the recesses (6a) and (6b) for forming the front and rear refrigerant passages of each plate (2). A large number of straight front and rear flow path dividing ridges (5a) and (5b) having a height twice the depth of the flat pipes in a state where two plates (2a) and (2b) are superimposed. Plates (2) (2a) (2b) provided to form independent parallel divided refrigerant flow paths (7) in the refrigerant passages (8) of the portion (12) can be used, In this case, the leading ends of the flow path dividing ridges (5a) (5b) of the plates (2a) (2b) are opposed to the plates (2a) (2b). 6a) and (6b) are joined to the flat surface of the bottom wall.

  Next, similarly to the case shown in FIGS. 20 and 21, the second modified example is provided in the coolant flow path forming recesses (6) and (6) and has a depth of each of the recesses (6) and (6). It is possible to use two types of plates (2a) and (2b) having different arrangements of the linear channel dividing ridges (5a) and (5b) having a height twice as large as the above. (2a) (2b) The linear flow path dividing convex ridges (5a) (5b) have the leading ends thereof opposed to the refrigerant flow path forming concave parts (6) (6) (6) of the plates (2a) (2b). ) Is joined to the flat surface of the bottom wall.

  Further, in the third modified example, as in the case shown in FIGS. 22 and 23, a large number of linear channel dividing ridges (5) are provided only in the rear half of the refrigerant channel forming concave portion (6). A plate (2) having a flat surface without any linear flow dividing ridges (5) in the first half of the concave portion (6) can be used. Of the plate (2), the leading end of the linear channel dividing ridge (5) is opposed to the flat surface of the bottom wall of the refrigerant channel forming recess (6) of the plate (2). Is joined to.

  Further, in the fourth modification, a flat plate (2a) having the same outer shape can be used for the ridged plate (2b) as in the case shown in FIG. The tip of the side ridge (3) (33) of the ridge with plate (2b) is on the flat surface of the side edge of the flat plate (2a), and the tip of the center ridge (4) (34) Are joined to the flat surface at the center of the flat plate (2a), and the tip of the straight channel dividing ridge (5) is joined to the flat surface of the corresponding portion of the flat plate (2a). The flat tubes (12) and (32) having the refrigerant passages (8) and (38) are formed, and a plurality of divided refrigerant passages are formed in the refrigerant passages (8) and (38) inside the flat tubes (12) and (32). (7) is formed.

  In the above embodiment, the case where the heat exchanger (1) according to the present invention is applied to an evaporator for a car air conditioner has been described.However, the present invention relates to a heat exchanger for automobiles or industrial use, for example, an evaporator, It is applicable to condensers, oil coolers, intercoolers, heater cores, and the like.

  For example, when the heat exchanger (1) of the present invention is used as a heat exchanger for a heater of a heating device, since the entire width of the passage through which the fluid flows and the contact width with the radiating fin (24) are the same. And efficient heat exchange can be obtained. In addition, the internal fluid can be made to flow in a direction opposite to the air, so that the temperature efficiency is increased, so that a high heat exchange rate is obtained and downsizing is achieved.

It is a perspective view of a heat exchanger showing a 1st embodiment of the present invention. It is an enlarged front view of the plate of the heat exchanger of FIG. It is a partial expansion perspective view of the same plate. FIG. 2 is an enlarged exploded perspective view of a main part of the heat exchanger of FIG. 1. It is an expanded cross-sectional view of the flat tube part of the same heat exchanger. FIG. 3 is an enlarged perspective view of a main part of the heat exchanger, which is partially cut away. FIG. 4 is a partially enlarged cross-sectional view showing a modification of the dividing ridge of the plate of the heat exchanger of FIG. 1. It is an enlarged front view which shows the modification of the plate of the heat exchanger. It is a partial expansion perspective view which shows another modification of the plate of the heat exchanger. FIG. 10 is an enlarged cross-sectional view of a flat tube portion of the heat exchanger using the plate of FIG. 9. It is a principal part expanded exploded perspective view of the heat exchanger which shows 2nd Embodiment of this invention. FIG. 12 is a partially enlarged front view of the plate of the heat exchanger of FIG. 11, with a header portion also shown. It is a perspective view of a heat exchanger which shows a 3rd embodiment of the present invention. It is an enlarged front view of the plate of the heat exchanger of FIG. It is a partial expansion perspective view of the plate of the heat exchanger. It is an expansion disassembled perspective view of the upper end part of the same heat exchanger. It is an expansion exploded perspective view of the lower end part of the heat exchanger. FIG. 4 is an enlarged front view of a plate used in the heat exchanger of FIG. 1, showing a second mode of the dividing ridge. FIG. 19 is an enlarged cross-sectional view of a flat tube portion of the heat exchanger using the plate of FIG. 18. FIG. 3 is an enlarged front view of a plate used in the heat exchanger of FIG. 1, illustrating a third mode of the dividing ridge, and illustrating one of a pair of plates. It is an enlarged front view of the other plate. FIG. 4 is an enlarged front view of a plate used for the heat exchanger in FIG. 1, showing a fourth embodiment of the dividing ridge. FIG. 23 is an enlarged cross-sectional view of a flat tube portion of the heat exchanger using the plate of FIG. 22. It is an expanded cross-sectional view of the flat tube part of the heat exchanger which shows the modification which replaced one of the pair of plates with the flat plate in the heat exchanger of this invention. It is an expanded cross-sectional view of the flat tube part which shows the example of the conventional heat exchanger.

Explanation of reference numerals

1: Evaporator (heat exchanger)
2: Plate 2a: Flat surface 3: Peripheral ridge 4: Central ridge 5: U-shaped ridge 6 for dividing the flow path: Recess for forming a refrigerant flow path (recess for forming a fluid flow path)
7: U-shaped split refrigerant passage (U-shaped split fluid passage)
8: Refrigerant passage (fluid passage)
10: Through-hole 12: Flat tube 15: Notch 20: Header forming member 21: Refrigerant flow tube (fluid flow tube)
22: connecting portion 23: header portion 24: corrugated fin 32: flat tube 33: U-shaped edge ridge 34: central ridge 35: U-shaped ridge 36 for dividing a flow channel: concave portion for forming a refrigerant flow channel ( Fluid flow path forming recess)
38: refrigerant passage (fluid passage)
41: Front header forming member made of a square pipe 42: Rear header forming member 43 made of a square pipe 43: Lower wall 44: Flat tube upper opening opening insertion hole 51: Upper header forming member 52: Lower header forming member 53 : Refrigerant distribution tube (fluid distribution tube)
54: Refrigerant distribution tube (fluid distribution tube)
55: connecting portion 56: connecting portion 57: upper header portion 58: lower header portion 59: communication passage

Claims (25)

  A peripheral ridge protruding on one side at the peripheral portion, a central protruding ridge protruding from the upper end to a position where a fluid return flow path below can be formed at the center of the width, and protruding from the upper surface to the same side, is forged or A U-shape which is provided by cutting and has a concave portion for forming a fluid flow path on both sides of a central ridge and a concave portion for forming a fluid return channel below the central ridge inside a peripheral ridge. A recess for forming a fluid flow path is formed, and one of the through holes for fluid inlet / outlet is provided at one end of the recess for forming a U-shaped fluid flow path, and the other through hole is provided at the other end of the recess. And a pair of flat plates having the other surface overlapped with each other in a state where the U-shaped fluid flow path forming recesses are opposed to each other, and a pair of opposed peripheral edge protrusions of both plates are provided. The tips of the strips and the tips of the central ridges are joined. A flat tube having a U-shaped fluid flow path therein is formed, a plurality of flat tubes are arranged in parallel, and a through hole for a fluid inlet / outlet of a plate is provided between upper ends of adjacent flat tubes. A heat exchanger in which a front and rear header portion communicating with an upper end portion of a flat tube is formed by interposing a header forming member including a pair of front and rear fluid communication cylinder portions respectively connected to the flat tube and an intermediate connection portion therebetween.   A left-right edge and a lower edge protrude to one side and a generally U-shaped edge ridge protrudes to the same side at the center of the width, and is a fluid return flow path below the upper end formed as a bifurcated shape. Are formed by forging or cutting, respectively, and the inside of the U-shaped edge ridge is provided with a fluid channel forming recess and a central portion on both front and rear sides of the center ridge. A U-shaped fluid flow path forming recess formed by the fluid return flow path forming recess below the convex ridge is formed, and two plates each having a flat surface are formed in a U-shape. Of the U-shaped edge ridges of the two plates facing each other, and the tip of the central ridge including the bifurcated upper end. Parts are joined together, the upper end is open in a bifurcated shape, and a U-shaped fluid is A flat tube having a passage is formed, and flat tube upper end opening insertion holes are provided at predetermined intervals on the lower walls of a pair of front and rear header forming members each formed of a square pipe, and are inserted into the insertion holes of the front and rear header forming members. By connecting the forked upper ends of the flat tubes in a plug-in manner, the flat tubes are arranged in parallel, and the front and rear header portions communicating with the forked upper ends of the flat tubes are formed. Have a heat exchanger.   In the U-shaped fluid flow passage forming recess of each plate, a plurality of flow dividing U-shaped ridges are provided by forging or cutting, and in a superimposed state in which a pair of plates face the recess, 3. The plurality of U-shaped divided fluid passages are formed in the U-shaped fluid passage inside the flat tube by joining the tips of the flow dividing U-shaped ridges facing each other. Heat exchanger.   In the concave portion for forming the fluid flow path of each plate, a linear portion having a height twice the depth of the concave portion and located in the front and rear linear flow path constituting portion of the concave portion, Forging or cutting such that a plurality of ridges for dividing the front and rear passages each having a quarter-arc portion located at the folded portion are alternately positioned in a superposed state in which a pair of plates face each other with the concave portions facing each other. In a superimposed state in which a pair of plates face each other with the concave portions facing each other, the front ends of the front and rear channel dividing ridges are formed at the bottoms of the fluid channel forming concave portions of the plates facing each other. The heat exchanger according to claim 1 or 2, wherein a plurality of U-shaped divided fluid passages are formed in the U-shaped fluid flow path inside the flat tube by being joined to a flat surface of the wall.   In each of the U-shaped fluid flow channel forming recesses of the pair of plates, a U-shaped flow channel dividing ridge having a height twice the depth of the recess is provided. Are provided by forging or cutting so as to be alternately positioned in the superposed state. In the superimposed state of these two types of plates, the leading end of the U-shaped ridge for channel division of each plate faces the same. 3. The heat-generating device according to claim 1, wherein a plurality of U-shaped divided fluid passages are formed in the U-shaped fluid passage inside the flat tube by being joined to a flat surface of a bottom wall of the recess for forming a fluid passage of the plate. Exchanger.   A plurality of flow path dividing ridges having a height twice the depth of the concave portion are provided by forging or cutting in a latter half of the fluid flow channel forming concave portion of each plate, and a bottom portion of a front half portion of the concave portion is provided. The wall is formed as a flat surface having no channel dividing ridge, and in a superimposed state in which a pair of plates face the concave portions, the tip of the channel dividing ridge is A plurality of U-shaped divided fluid passages are formed in the U-shaped fluid passage inside the flat tube by being joined to the flat surface of the bottom wall of the fluid passage forming concave portion of the plate facing these. 2. The heat exchanger according to 2.   A peripheral ridge protruding on one side at the peripheral portion, a central protruding ridge protruding from the upper end to a position where a fluid return flow path below can be formed at the center of the width, and protruding from the upper surface to the same side, is forged or A U-shape which is provided by cutting and has a concave portion for forming a fluid flow path on both sides of a central ridge and a concave portion for forming a fluid return channel below the central ridge inside a peripheral ridge. A recess for forming a fluid flow path is formed, and one of the through holes for fluid inlet / outlet is provided at one end of the recess for forming a U-shaped fluid flow path, and the other through hole is provided at the other end of the recess. A plate with a ridge having a flat surface on the other side, and having the same shape and size as the plate, and a through-hole for a fluid port corresponding to the through-hole for a fluid port. The flat plate is superimposed on the flat plate. The tip of the ridge on the peripheral edge of the flat plate is joined to the periphery of the flat plate, and the tip of the ridge on the center of the plate with the ridge is joined to the flat surface of the corresponding central portion of the flat plate. A flat tube having a U-shaped fluid flow path is formed, a plurality of flat tubes are arranged in parallel, and the upper and lower ends of adjacent flat tubes communicate with the through-holes for fluid inlet / outlet of the plate. A heat exchanger in which a front and rear header portion communicating with an upper end portion of a flat tube is formed with a header forming member including a pair of front and rear fluid circulation cylinder portions and an intermediate connection portion therebetween.   A left-right edge and a lower edge protrude to one side and a generally U-shaped edge ridge protrudes to the same side at the center of the width, and is a fluid return flow path below the upper end formed as a bifurcated shape. Are formed by forging or cutting, respectively, and the inside of the U-shaped edge ridge is provided with a fluid channel forming recess and a central portion on both front and rear sides of the center ridge. A U-shaped fluid flow path forming recess formed by a fluid return flow path forming recess below the protruding strip is formed, and a plate with a convex strip having another flat surface is provided. A flat plate having the same shape and outer shape is overlapped, and the peripheral edge of the ridged plate is joined to the edge of the flat plate, and the forked upper end of the ridged plate is joined to the flat plate. The tip of the central ridge is flat plate A flat tube having a bifurcated upper end and a U-shaped fluid flow passage formed therein is formed, which is joined to the flat surface of the corresponding central portion, and a pair of front and rear header forming members formed of a square pipe are formed. On each lower wall, flat tube upper opening opening insertion holes are provided at predetermined intervals, and the bifurcated upper ends of the flat tubes are connected to the insertion holes of the front and rear header forming members, respectively, by inserting. A heat exchanger in which flat tubes are arranged in parallel, and front and rear header portions communicating with a bifurcated upper end of the flat tubes are formed.   A plurality of U-shaped ridges for channel division are provided in the U-shaped fluid channel forming concave portion of the ridged plate by forging or cutting processing. A plurality of U-shaped divided fluid passages are formed in the U-shaped fluid passage inside the flat tube by joining the tip of the U-shaped ridge for channel division of the plate to the flat surface of the corresponding portion of the flat plate. The heat exchanger according to claim 7.   A peripheral ridge protruding to one side at the peripheral portion, a central ridge protruding to the same side at the center of the width and extending vertically is provided by forging or cutting, respectively. Fluid flow path forming recesses on both front and rear sides of the central ridge are formed on the inside, and through holes are respectively provided at upper and lower ends of the front and rear fluid flow path forming recesses, and the other surface is made flat. Plates are superimposed on each other in such a manner that the front and rear fluid channel forming recesses are opposed to each other, and the leading edge portions of the peripheral edge projections of the two plates facing each other, and the center The tips are joined together to form a flat tube having both front and rear fluid flow paths therein, and a plurality of flat tubes are arranged in parallel, and between the upper end portions and the lower end portions of adjacent flat tubes. To the through holes in the plate An upper and lower header forming member consisting of a pair of front and rear fluid communication cylinders and a middle connecting portion therebetween is interposed, and upper and lower headers communicating with upper end portions and lower end portions of the flat tubes are respectively formed. Heat exchanger.   The left and right edges have side edges protruding on one side, the center protruding on the width center has both upper and lower ends protruding on the one side and bifurcated, respectively, by forging or cutting. The plate is provided with fluid flow path forming recesses on the front and rear sides of the central ridge on the inside of the left and right side edge ridges, and the other surface is a flat plate. The front and rear fluid flow path forming recesses are overlapped with each other in a state where they face each other, the leading ends of the left and right side edge ridges facing each other of both plates, and the central ridge including the bifurcated upper and lower ends. The front ends are joined to form a flat tube whose upper and lower ends are bifurcated and have front and rear fluid passages therein. The upper or lower wall has an insertion hole at the upper end of the flat tube. The flat tubes are arranged in parallel with each other by connecting the bifurcated upper ends or lower ends of the flat tubes in the insertion holes of the header forming member at intervals, respectively. A heat exchanger, wherein a pair of front and rear and a pair of upper and lower headers respectively communicating with upper and lower ends of a bifurcated shape of a tube are respectively formed.   A plurality of channel dividing ridges are provided by forging or cutting in the front and rear fluid channel forming recesses of each plate, and a pair of two plates oppose each other in a superposed state in which the recesses face each other. The heat exchanger according to claim 10 or 11, wherein a plurality of divided fluid passages are formed in the front and rear fluid passages inside the flat tube by joining the tips of the divided flow dividing ridges.   A plurality of ridges for dividing the front and rear flow channels having a height twice as large as the depth of the concave portions are superimposed on the concave portions for forming the front and rear fluid flow channels of each plate. It is provided by forging or cutting so as to be alternately positioned in the state, and in the superimposed state of the two types of plates, the front end portions of the front and rear flow path dividing ridges are formed for the fluid flow path formation of the plate opposed thereto. The heat exchanger according to claim 10, wherein a plurality of divided fluid passages are formed in the front and rear fluid flow paths inside the flat tube by being joined to a flat surface of a bottom wall of the concave portion.   In each of the pair of plates, the front and rear fluid flow path forming recesses are provided with flow path dividing ridges having a height twice as high as the depth of the recesses, which are alternately positioned in a state where these plates are overlapped. In the superimposed state in which the two types of plates are provided with the concave portions facing each other, the leading ends of the front and rear flow path dividing ridges of the respective plates are formed by forging or cutting. The heat exchanger according to claim 10 or 11, wherein a plurality of divided fluid passages are formed in the front and rear fluid passages inside the flat tube by being joined to a flat surface of a bottom wall of the flow passage forming recess.   In one of the front and rear fluid passage forming recesses of each plate, a plurality of passage dividing ridges having a height twice the depth of the recess are provided by forging or cutting, and the front and rear fluid flow passages are provided. The bottom wall of the other concave portion of the channel forming concave portion is formed as a flat surface having no channel dividing convex ridge, and in a superimposed state in which a pair of plates face the concave portion. The tip of the channel dividing ridge is joined to the flat surface of the bottom wall of the fluid channel forming concave portion of the plate facing these, and a plurality of divided fluid passages are formed in the front and rear fluid channels inside the flat tube. The heat exchanger according to claim 10, wherein the heat exchanger is formed.   A peripheral ridge protruding to one side at the peripheral portion, a central ridge protruding to the same side at the center of the width and extending vertically is provided by forging or cutting, respectively. Fluid flow path forming recesses on both front and rear sides of the central ridge are formed on the inside, and through holes are respectively provided at upper and lower ends of the front and rear fluid flow path forming recesses, and the other surface is made flat. The plate with the convex stripes and the flat plate having the same shape and the same outer shape as the plate and having a through-hole for the fluid entrance corresponding to the through-hole for the fluid entrance are overlapped, and The tip of the peripheral ridge of the plate is joined to the peripheral edge of the flat plate, and the tip of the central ridge of the plate with the ridge is joined to the flat surface of the corresponding central portion of the flat plate. A flat tube having both front and rear fluid flow paths is formed, a plurality of flat tubes are arranged in parallel, and the upper and lower ends of adjacent flat tubes communicate with the through holes of the plate. An upper and lower header forming member composed of a pair of front and rear fluid communication cylinders and an intermediate connecting portion therebetween is interposed, and upper and lower headers communicating with upper ends and lower ends of the flat tubes are formed, respectively. Exchanger.   At the intermediate connecting portion of any one of the upper and lower header forming members interposed between the upper end portions and the lower end portions of the adjacent flat tubes, the front and rear fluid circulation cylinder portions of the header forming member are connected to each other. The heat exchanger according to claim 16, wherein a communication passage communicating with the heat exchanger is provided.   The left and right edges have side edges protruding on one side, the center protruding on the width center has both upper and lower ends protruding on the one side and bifurcated, respectively, by forging or cutting. A ridged plate having fluid flow path forming recesses on both front and rear sides of a central ridge formed inside the left and right side edge ridges, and a flat surface on the other surface; The flat plate having the same shape and the same size as the flat plate is overlapped, and the left and right side edge portions of the ridged plate are joined to the left and right side edge portions of the flat plate. The tips of the central ridges including the bifurcated upper and lower ends are joined to the flat surface of the corresponding central part of the flat plate, the upper and lower ends are bifurcated and have front and rear fluid flow paths inside. Before a flat tube is formed and a square pipe is formed A flat tube upper end opening insertion hole is provided at predetermined intervals on the upper wall or lower wall of each of the pair of upper and lower header forming members, and the bifurcated upper end of the flat tube is inserted into the insertion hole of the header forming member. The flat tube is arranged in parallel by connecting the lower portion or the lower portion respectively, and a pair of front and rear and a pair of upper and lower headers respectively communicating with the upper and lower ends of the bifurcated shape of the flat tube are formed. Each formed heat exchanger.   A plurality of channel dividing ridges are provided by forging or cutting in the front and rear fluid channel forming recesses of the ridged plate, and when the ridged plate and the flat plate are overlapped, the flow of the ridged plate is reduced. 19. The heat according to claim 16 or 18, wherein a plurality of divided fluid passages are formed in the front and rear fluid flow paths inside the flat tube by joining a front end portion of the channel dividing ridge to a flat surface of a corresponding portion of the flat plate. Exchanger.   The left and right end surfaces of the front and rear fluid flow tube portions of the header forming member interposed between the ends of the adjacent flat tubes are joined to the other flat surface portions of the flat tube plates facing these. The heat exchanger according to any one of claims 1, 7, 10, and 16.   17. A temporary fixing protrusion for temporarily fixing a header forming member is provided at an edge of each of the fluid inlet / outlet through holes at an end of each plate. A heat exchanger according to claim 1.   A plurality of notches are provided in the channel dividing ridge of each plate, and adjacent divided fluid passages inside the flat tube are connected to each other at the notched portions. 20. The heat exchanger according to any one of claims 15 to 19.   The fin is interposed between the flat tubes adjacent to each other of the flat tubes arranged in parallel, and the left and right side edges of the fin are joined to the other flat surface of the plate of the flat tube. The heat exchanger according to any one of claims 2, 7, 8, 10, 11, 16, and 18. A car air conditioner using the heat exchanger according to any one of claims 1 to 23. An automobile comprising the heat exchanger according to any one of claims 1 to 23.