JP2005517893A - Finned low profile heat exchanger - Google Patents

Abstract

SOLUTION: A plurality of elongated passages 50 having a first surface 40 and a second surface 42 facing each other, extending outward from the first surface and opened to face the second surface. A fin plate 5 including a plurality of spaced apart elongated fins 44 that define a fluid flow chamber 24 and a cover plate 18 and a shim plate 14 that are separated from each other and are sealed together. And a flat container having an inflow opening 28 and an outflow opening 30 in communication with the fluid circulation chamber 24 so that the fluid can enter, pass through and outflow into the fluid circulation chamber. The first surface 40 of the plate is attached to the shim plate 14 to allow heat transfer therebetween, and the second surface 42 of the fin plate is exposed, and the low profile heat exchange. Vessel 10.

Description

  The present invention relates to a finned low profile heat exchanger used for cooling a fluid.

Low profile heat exchangers are commonly used in applications where the height clearance of the heat exchanger is significantly lower, such as snowmobile waste oil box coolers and underbody mounted fuel coolers in automotive applications. One type of conventional low profile heat exchanger has a louver plate that is exposed to airflow, snow, and common foreign objects, to which a meandering tube is fixed, This tube reciprocates back and forth across the plate. The fluid to be cooled passes through this serpentine tube. Another type of conventional low profile heat exchanger runs laterally and is integrally extruded with the top and bottom walls, with the top and bottom walls facing side edges. Fins are defined to provide a fluid cooling vessel with cavities welded at opposite ends after extrusion by connecting together.
German utility model application publication No. 29722841 JP 07-280484 A European Patent Application Publication No. 0907061

  Conventional low profile heat exchangers are heavy and relatively expensive to manufacture. Accordingly, there is a need for a low profile heat exchanger that is relatively lightweight and relatively cost effective to manufacture. In addition, a low profile heat exchanger with improved fluid temperature drop due to its relative size is desirable.

  According to the present invention, a plurality of elongate passages having a first surface and a second surface facing each other, extending outward from the first surface, and opened to face the second surface. A fin plate that includes a plurality of spaced apart elongated fins, and has a separate cover plate and shim plate that are sealably coupled to the entire circumference of each outer peripheral edge and that define a fluid flow chamber; A low profile heat exchanger is provided that includes a low profile vessel having an inflow opening and an outflow opening in communication with the flow chamber. The first surface of the fin plate is attached to the shim plate to allow heat transfer between the low profile container and the fin plate, and the second surface of the fin plate is exposed.

  According to another aspect of the present invention, a plurality of first and second surfaces facing each other, extending outward from the second surface, and open on the opposite side of the second surface An extruded fin plate having a flat support wall including a plurality of spaced apart elongated fins defining an elongate passageway, and a substantially flat central portion spaced from the first surface of the support wall; A separately formed low profile in which a fluid flow chamber having an inflow opening and an outflow opening in communication is defined between the support walls to allow entry into, passage through, and outflow into the fluid flow chamber. A low profile heat exchanger is provided.

  Preferred embodiments of the invention are described by way of example with reference to the drawings.

  Referring to FIG. 1, there is shown an exploded view of a heat exchanger, generally designated by the reference numeral 10, in accordance with a preferred embodiment of the present invention. The heat exchanger 10 includes a fin plate 12, a shim plate 14, a turbulator plate 16, and a cover plate 18 at the bottom. In FIG. 1, these plates are shown arranged in the vertical direction, but this is for illustrative purposes only. This heat exchanger can take any desired direction.

  With reference to FIGS. 1 and 2, the cover plate 18 and shim plate 14 define a flat, low profile container having an internal fluid flow chamber 24. The cover plate 18 includes a central flat portion 20 that is generally rectangular in the illustrated embodiment. Side wall flanges 22 are provided on the outer peripheral edges of all four sides of the central flat portion 20. The side wall flange 22 extends toward the shim plate 14 and provides a continuous side wall all around the fluid flow chamber 24 defined between the cover plate 18 and the shim plate 14. An outwardly extending connecting flange 26 is preferably provided along the bottom edge of at least one pair of opposing wall portions of the side wall flange 22. Each connection flange 26 has a flat surface 27 that contacts and is fixed to the shim plate 14.

  A pair of fluid flow openings 28, 30 functioning as one fluid inlet and the other as a fluid outlet are provided through the central flat portion 20 in communication with the fluid flow chamber 24. In one embodiment, cylindrical fittings 32, 34 having fluid through passages are provided for openings 28, 30. The pipe joints 32, 34 may include an annular flange 36 for sealingly connecting to the cover plate 18.

  In a preferred embodiment, the cover plate 18 is a unitary structure, which is a roll-formed or stamped aluminum alloy clad with a brazing alloy.

  The shim plate 14 is simply a flat plate having a first flat surface facing the inside of the central flat portion 20 of the cover plate 18 and an opposing flat surface 37 connected facing the fin plate 12. The shim plate 14 is substantially rectangular in the illustrated embodiment and has a footprint that is approximately the same area as the footprint of the cover plate 18. In one preferred embodiment, the shim plate 14 comprises an aluminum or aluminum alloy sheet clad with a brazing alloy.

  In one preferred embodiment, the fin plate 12 is a monolithic structure made of extruded aluminum or aluminum alloy. The fin plate 12 includes a flat support wall 38 having a first flat surface 40 facing and secured to the shim plate 14 and an opposed surface 42 provided with a plurality of elongated parallel fins 44. . A mounting flange 46 through which a fixing opening 48 passes may be provided along the edge on the side facing the support wall 38 so that the heat exchanger can be mounted on the surface.

  2 and 3, each fin 44 extends substantially from the first end to the second end of the support wall 38, and a plurality of elongated passages 50 are defined between the fins. Has been. The opposite side of the fin plate 12 to the side facing the shim plate 14 is open and the alternately arranged fins 44 and the passages 50 are exposed, so that air passes through the passages 50 during use and on the fins 44. Can be exceeded. In some applications, other materials such as water, snow, and other foreign objects can collide with the exposed fins and passages. In the heat exchanger shown in FIGS. 1 to 3, the fins 44 extend from the flat surface 42 on the outer side of the fin support wall 38 at an equal angle at an angle perpendicular thereto, and from one end of the heat exchanger. A straight fin extending to the other end.

  A turbulator plate 16 is disposed in the fluid flow chamber 24 to increase the fluid flow rate, resulting in increased efficiency in removing heat from the fluid. Referring to FIGS. 4, 5, 6 and 7, in one preferred embodiment, the turbulator plate 16 is formed of a metal, specifically aluminum, which has been expanded by either a roll forming or stamping process. Has been. On the turbulator plate 16, there are provided rows of rotating portions 64 that are crossed alternately or offset. This swivel has a flat bottom and top 66 to obtain a good connection with the cover plate 18 and shim plate 14, but has a rounded top or a sinusoidal shape if desired. It can also be. A portion of one of the rows of the turn 64 is compressed, rolled, or crimped together to form transverse crimps 68 and 69 (where crimp refers to crimping, stamping, roll forming). Or any other method for sealing the rotation of the turbulator plate 16). The crimp portions 68 and 69 form a barrier 62 in order to reduce a short-circuit flow in the fluid flow chamber 24. In FIG. 7, the barrier 62 is shown using phantom lines and extends between the flow openings 28 and 30, so that fluid flowing from one of the openings 28 or 30 is simply within the fluid chamber 24. It is necessary to flow through a more distant path, instead of flowing straight through the revolving part 64 and flowing out from the other flow opening 30 or 28. In the illustrated example in which two flow openings 28, 30 are arranged near the common end 60, the barrier 62 is slightly separated from the opposite end 58 of the heat exchanger 10 from the vicinity of the common end 60. Since a substantial portion of the fluid flowing into the chamber 24 from the opening 28 flows out of the chamber 24 through the opening 30, it travels around the point 72 in the U-shaped channel. It must flow as shown at 74 (when opening 28 is the inlet of chamber 24 and opening 30 is the outlet of chamber 24). In one preferred embodiment, the cover plate 18 and shim plate 14 are made of aluminum clad with a brazing alloy, and the heat exchanger 10 is assembled by clamping the parts in the order shown in FIG. Since the assembled components are manufactured by heating in a brazing furnace, the side wall flange 22 of the cover plate is hermetically brazed to the shim plate 14 at the entire periphery of the lower end thereof, The burator plate 16 is sandwiched between the cover plate 18 and the shim plate 14, and the shim plate 14 is brazed to the support wall 38 of the fin plate 12. In some applications, soldering can be used instead of brazing to connect the components. In some embodiments, some or all of the heat exchanger components can be formed using other metallic materials, such as steel and non-metallic polymer materials. The polymer components can be bonded together using thermal bonding, ultrasonic bonding, or adhesives or other means.

  The heat exchanger 10 can be used as a low profile device for cooling the fluid flowing through the fluid flow vessel defined by the cover plate 18 and the shim plate 14, where heat from the fluid is removed from the fluid. Separated and guided to the exposed fins 44 and then cooled by the air flowing through it. In some applications, cooling of the exposed fins 44 is assisted by other materials, such as snow and water impinging on the exposed fins 44. The heat exchanger 10 can be used, for example, as a snowmobile engine coolant cooler or as an underbody-mounted fuel cooler for an automobile, but these are examples and are not limiting. .

  The heat exchanger 10 can be manufactured to different sizes relatively easily by using longer fin plates 12 and correspondingly rolling longer shim plates 14 and cover plates 18. . Although the cover plate 18 has been described above with an integrally formed side wall flange 22, in some embodiments, separate side walls may be used. Further, in some embodiments, the shim plate 14 may be omitted, and instead the upper side of the support wall 38 may be used as the bottom wall of the fluid flow chamber 24. Although the shape of the heat exchanger 10 has been described as rectangular, in some applications it may be other shapes, such as a circular disc shape.

  Various different types of turbulators or fluid flow increasing means may be used in the fluid flow chamber 24, and the turbulator plate 16 may not be present in some applications. Further, in some embodiments, a shorting barrier that is different from the crimped barrier 62 can be used. In this regard, FIGS. 8 and 9 show a further shim plate 78 that can be used in the heat exchanger 10 in place of the shim plate 14. The shim plate 78 includes a central elongated baffle wall 80 that extends upwardly toward the cover plate 18 (not shown in FIG. 8). The baffle wall 80 is positioned over the cover plate 18 between positions where the flow openings 28, 30 are provided (such positions are indicated by phantom lines 28 ', 30' in FIG. 8). Therefore, the baffle wall can cause the fluid in the chamber 24 to flow in a U-shaped flow path having a detour as indicated by an arrow 82. The baffle 80 is formed by a portion of a shim plate 78 punched along three side edges, and then the shim plate 78 leaving a rectangular opening 84 through the shim plate 78 hermetically sealed by the support wall 38. Preferably, it is formed by rotating upward with respect to the fourth side edge in a state of being connected to the remaining portion. Separate turbulator plates can be provided on opposite sides of the baffle wall 80.

  FIGS. 10 and 11 show a skeleton baffle plate 86 that can be used in place of the turbulator plate 16 between the shim plate 15 and the cover plate 18 in yet another embodiment of the heat exchanger 10. . The positions of the flow openings 28, 30 with respect to the skeleton baffle plate 86 are indicated by phantom lines 28 ', 30' in FIG. The skeletal baffle plate 86 includes an outer rectangular frame 88 dimensioned to fit snugly inside the sidewall flange 22 of the cover plate 18. The skeletal baffle plate 86 has a height H (see FIG. 11) that coincides with the height of the fluid chamber 24, and further includes other baffle walls 90, 92 that are substantially parallel. The baffle wall 90 extends from the first end wall 94 in the vicinity where the flow openings 28 and 30 are located to the vicinity of the opposed end wall 96. Since another baffle wall 92 extends from the opposed end wall 96 to the vicinity of the first end wall 94, the baffle walls 90, 92 are shown throughout the fluid chamber 24 by arrow 98 in FIG. 10. Thus, the flow paths meandering back and forth are collectively defined (assuming opening 28 is a higher pressure opening). In another embodiment, the baffle wall as provided by the skeletal baffle plate 86 can be replaced with embossed ribs formed on the shim plate 14 or the cover plate 18 or both, and in many applications. Ribs embossed on the cover plate and / or shim plate are preferred as separate baffle plates because they reduce the number of components that need to be assembled. A number of examples of embossed cover plate configurations suitable for use in the heat exchanger 10 are given below.

  In some applications, it is desirable to use a fin plate that is lighter than the extruded fin plate 12. Referring to FIGS. 12-14, a further embodiment of a low profile heat exchanger, indicated generally at 100, is shown as another preferred embodiment of the present invention. The heat exchanger 100 is similar to the heat exchanger 10 except for differences that will become apparent from the following description. The heat exchanger 100 has a substantially rectangular footprint, and is a laminate of a fin plate 102, a shim plate 104, and a cover plate 106 similar to the heat exchanger 10, as shown in the best example in FIG. In the illustrated embodiment, the cover plate 106 includes a rectangular central flat rib portion 108 that is rolled or stamped of aluminum or aluminum alloy clad with a brazing alloy. The side wall flange 110 continuously extends toward the shim plate 104 all around the outer periphery of the central flat portion 108, and in this case, an edge 112 turned to the outside of the side wall flange 110 having the flat portion is formed on the shim plate 104. Facing and sealingly connected. The shim plate 104 and the cover plate 106 of the heat exchanger 100 are interposed between the first flow opening 114 and the second flow opening 116 provided at opposite corners of the cover plate 106 on the diagonal line. Collectively defining a fluid flow chamber 113 including a flow path. One of the flow openings 114 and 116 is a fluid inlet into the fluid flow chamber 113, and the other is a fluid outlet. In the illustrated example, each opening 114, 116 is provided with a corresponding pipe joint 122 by brazing to the cover plate 106, and has a flow path parallel to the plane of the central portion 108.

  By alternately forming the embossed baffle ribs 118 and 120 in the central portion 108 of the cover plate 106, the flow path between the openings 114 and 116 is divided into a path meandering back and forth. In particular, spaced apart parallel ribs 118 extend from the first end 124 of the cover plate 106 to a position that is near the end 126 on the opposite side of the cover plate 106 but slightly spaced. The alternately arranged parallel ribs 120 extend from the end portion 126 to a position in the vicinity of the first end portion 124 but slightly apart. As shown in the best example in FIG. 13, each of the ribs 118, 120 includes a pair of opposing elongated side walls 128 that form a good bond with the shim plate 104. Are joined along respective end edges by a flat portion 130 having a flat surface.

  A bracket 132 is brazed to the cover plate 108 so that the heat exchanger 100 can be secured in place. Each of the brackets 132 shown in FIGS. 12 and 13 has a substantially rectangular central body that extends beyond the cover plate and has a portion through which the fixing hole 134 passes. The bracket central body 132 disposed on the cover plate 108 is dimensioned to be disposed between two adjacent ribs 120, 118, and preferably, the bracket 132 is positioned and positioned in place. Opposing positioning tabs 136 that extend into the ribs 120, 118 are included to assist in securing. In some applications, because of its light weight construction, no additional brackets are needed because the heat exchanger is well supported by connecting the inlet and outlet fittings together.

  The shim plate 112 is simply a flat rectangular plate made of aluminum or aluminum alloy clad with a brazing alloy. The fin plate 102 is fixed to the shim plate 112 facing the fluid chamber 113 to remove heat from the fluid chamber, is substantially rectangular, and substantially covers the entire shim plate. . The fin plate 102 includes one surface fixed to the shim plate 104 and an exposed facing surface. As shown in the cross-sectional view of FIG. 13 and the bottom view of FIG. 14, the fin plate 102 includes a plurality of spaced apart elongated fins 138 that extend from the shim plate 104. Projecting and extending over its entire length, each fin is formed by a generally U-shaped wall. The fins 138 define a plurality of open surface air passages 140 separated by closed surface passages 142 disposed within each fin 138. The side end portion of the fin plate 102 may be opened to open the opposite closed surface type passage 142. Each of the U-shaped fins 138 is connected to the adjacent fins 138 by a flat connection wall 144 fixed to the shim plate 104 by brazing. In practice, the U-shaped fins 138 and the connection walls 144 collectively form a corrugated corrugation. As shown in FIG. 14, the fins 138 have a uniform size, but are formed in a curving shape that gently undulates over their entire length, thereby assisting in blocking the boundary layer of all air passing through the interior. . The fin 138 is lightweight and is preferably formed by roll forming or stamping aluminum or an aluminum alloy. In the illustrated example, each of the alternately arranged open surface type channels 140 and closed surface type channels 142 have substantially the same cross-sectional area, but a relatively different area is used depending on the application. It is possible. Furthermore, different fin shapes can be used, for example V-shaped.

  FIG. 15 shows an example of a further fin plate structure 146 that can be used on the underside of the shim plates 14, 104 of the heat exchangers 10, 100. The fin plate 146 has a first surface 148 and a second exposed surface 150 that are brazed to the shim plate. A plurality of open-surface air passages 152 are disposed from the first end 154 to the second end of the fin plate 146 between the elongated fin structures that are alternately or transversely offset from the row of convolutions 158. To 156. The convolution has a flat top 160 to provide good coupling with the shim plates 14, 104, but may be rounded or sinusoidal if desired. In one preferred embodiment, the fin plate 146 is formed of a metal, specifically aluminum, that has been expanded by either roll forming or stamping.

  FIG. 17 shows a bottom view of yet another possible fin plate configuration. The fin plate 162 of FIG. 17 is similar to the fin plate 102 except that hollow U-shaped fins 164 (defining spaced apart open-faced passages 166) are arranged in a front and rear pattern. Are the same.

  In addition to the cover plates 18, 106 described above, many other flat cover plate configurations can be used. FIG. 18 illustrates a further usable cover plate 168 according to the present invention, which is the same as the cover plate 18 but with alternating embossed ribs 170, 172. The ribs 118 and 120 of the plate 106 extend in a direction perpendicular to the ribs 118 and 120, and each of the ribs 118 and 120 is formed in a curve that undulates along its length direction. A difference is that a meandering flow path in the lateral direction indicated by an arrow 174 is defined between the two. An embossed baffle rib can be formed on the shim plate instead of on the cover plate, in which case the shim plate has a plan view similar to that shown in FIG. There are no flow openings through the plate. Alternatively, it is possible to form embossed ribs on both the cover plate and the shim plate, the ribs sealingly contacting each other to form a flow path in the fluid chamber, in which case the cover plate and Both the plan view and the bottom view of the shim plate are similar to the plan view of FIG. 18 (the shim plate is not provided with a flow opening), and the embossed rib 170 between the cover plate and the shim plate, Each of 172 has a depth of about one half of the height of the fluid chamber. Many different patterns of embossed ribs and other types of embossed flow increasing means or barriers may be provided on the cover plate or shim plate.

  FIGS. 19 and 20 show a further heat exchanger 190 that is substantially identical to the heat exchanger 100 except that a plurality of dimples 194 have an embossed cover plate 192. Since the dimple 194 extends to and engages the shim plate 104, an increase in flow rate occurs in the fluid chamber 113.

  FIG. 21 shows an exploded view of yet another heat exchanger, indicated generally by the reference numeral 200. The heat exchanger 200 is substantially the same as the heat exchanger 100 except as is apparent from the drawings and described in the following description. The cover plate 202 of the heat exchanger 200 does not have embossed ribs for defining flow paths in the fluid chamber 113, but instead the cover plate 202 and shim plate 104 in the fluid chamber 113 A corrugated baffle plate 204 (made of another suitable material of aluminum) is secured between the two. Since the corrugated baffle plate 204 extends from one end 208 to the other end 210 of the fluid chamber 113, the corrugated baffle plate 204 includes a plurality of pairs of the first barrier wall 206A and the second barrier wall 206B that are substantially parallel to each other. The barrier walls 206A, 206B in each pair are joined by a flat wall that contacts and is fixed to the inside of the cover plate 202 along the upper first vertical edge thereof (as used herein, "upper" and " Directional terms such as “horizontal” are for illustrative purposes only because the heat exchanger can take any direction). The pair of barrier walls is joined by a further wall 214 that contacts and is fixed to the shim plate 104 along its lower edge, and in particular, one pair of barrier walls 206B is at its lower edge. , Connected to the lower edge of the barrier wall 206A of the adjacent pair of barrier walls. A side flow opening 216 is provided at the end of each barrier wall 206A near the end 208 of the heat exchanger, and each barrier wall 206B near the end 210 on the opposite side of the heat exchanger 200 is provided. A lateral flow opening 218 is provided at the end. Accordingly, alternating fluid paths are defined in the fluid chamber 113 by barrier walls 206A, 206B, where the barrier wall openings 216, 218 cause one flow opening 116 to flow to the other. In the passage extending into the opening 114 (or vice versa, depending on which is the high-pressure opening), there is a fluid flow before and after meandering.

  Referring to FIG. 21A, in one embodiment, the corrugated barrier plate 204 includes a flat horizontal portion 220 that forms a longitudinal edge on the outside thereof, which portion 220 is connected below the cover plate 202. It is sandwiched between the flange 26 and the shim plate 104.

  Next, the shapes of still another cover plate and shim plate for the heat exchanger 200 will be described with reference to FIGS. 22 to 23C. Referring first to FIGS. 22 and 23A, in one embodiment, the cover plate 230 is dish-shaped and defines an angle slightly greater than 90 ° with respect to the inner surface of the central flat portion 240 and is integral with the outer periphery. A central flat portion 240 having a flange 242 formed and extending downwardly. The shim plate 236 does not have openings 116 and 114 formed therethrough, and a flange 244 that extends below the shim plate 236 is nested within the flange 242 of the cover plate 240 to support it. Other than that, having a fluid chamber 113 defined between the flat central portion of the cover plate 240 and the shim plate 236 is similar. Fin plate 102 (illustrated with round corrugated fins rather than rectangular) is secured to the underside of the flat central portion of shim plate 244. The shim plate flange 244 may be truncated at the location just below the bottom edge of the cover plate flange 242 to minimize any adverse effects on airflow through the fin plate 102.

  FIG. 23B shows that the shim plate 238 extends in the opposite direction to the cover plate flange 242 and turns upward, and has an outer peripheral flange 246 that has an outer surface that is nested in and brazed to the inner surface of the cover plate flange 242. A similar configuration is shown except that The configuration shown in FIGS. 23A and 23B can be easily “turned over” with the fin plate disposed on the opposite side, as indicated by the phantom line 102 ′ in FIG. 23B. Further, in some embodiments, fin plates may be used on both sides of the heat exchanger.

  FIG. 23C shows a further configuration, in which case the cover plate 234 and the shim plate 248 are exactly the same (except that the shim plate is not provided with a flow opening), Contact flanges 250 and 252 are formed on the entire circumference of the central flat portion.

  FIG. 24 shows a further heat exchanger 260 identical to the heat exchanger 100 except for the differences described below. The cover plate 262 of the heat exchanger 260 includes a plurality of perforated air flow openings 264 therethrough. Each opening 264 is aligned with a corresponding opening 268 provided through the shim plate 266. Each cover plate air flow opening 264 is surrounded by a wall 265 around its outer periphery extending from the cover plate to the shim plate to hermetically close the air opening from the fluid chamber 113. The wall 265 is preferably protruded from the cover plate material when drilling the opening 264. Since the aligned openings 264, 268 are arranged in a range where the fin plate 102 does not contact the shim plate, the aligned openings are not completely blocked by the fin plate 102. In some embodiments, corresponding openings can be drilled through the fin plate 102. As shown in FIG. 26, in use, air can flow through the openings 268, 264, so that air can flow into the sealed compartment of the fluid container defined by the shim plate and the cover plate. become. As shown in FIG. 26, in some applications, the heat exchanger is angled with respect to the direction of movement (arrow 270) to improve performance by increasing the angle of attack at which air collides with the fin plate 102. May be attached.

  Although many components of the heat exchanger according to the present invention have been described as being made of aluminum or an aluminum alloy, other materials can be used as appropriate to form the component, and in some applications, for example, It is also possible to use non-metallic materials, such as polymers that are heat bondable, ultrasonically bondable and adhesively bondable. It will be apparent to those skilled in the art that many applications and variations in the practice of the present invention are possible without departing from the spirit or scope of the invention. Accordingly, the scope of the invention should be construed in accordance with the subject matter defined by the appended claims.

1 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention. It is sectional drawing along line II-II of FIG. It is a bottom view of the heat exchanger of FIG. It is an expansion perspective view which shows the turbulator plate of the heat exchanger of FIG. It is an enlarged scrap figure of the part of Drawing 4 shown by circle 5 in Drawing 4. It is a top view of the turbulator plate of FIG. It is a top view of the heat exchanger of FIG. It is a top view of the shim plate used in one embodiment of a heat exchanger. It is sectional drawing along line IX-IX of FIG. It is a top view of the frame | skeleton barrier plate used in one Embodiment of a heat exchanger. It is sectional drawing along line XI-XI of FIG. It is a top view of the heat exchanger by another embodiment of this invention. It is sectional drawing along XIII-XIII of FIG. It is a bottom view of the heat exchanger of FIG. It is a bottom view of another fin plate used with embodiment of the heat exchanger of this invention. It is a side view of the fin plate of FIG. It is a bottom view of another fin plate. It is a top view of another cover plate used with the heat exchanger of this invention. It is a top view of the further embodiment of the heat exchanger of the present invention. It is sectional drawing along line XX-XX of FIG. FIG. 21A is an exploded perspective view of another embodiment of a heat exchanger according to the present invention, and FIG. 21A is a partial cross-sectional view of the assembled portion of the heat exchanger along line XXIA-XXIA of FIG. . FIG. 6 is a front view of a further embodiment of a heat exchanger according to the present invention. FIG. 23 is a cross-sectional view taken along line XXIII-XXIII in FIG. 22, each showing a different usable cover plate and shim plate combination, according to an embodiment of the present invention. FIG. 23 is a cross-sectional view taken along line XXIII-XXIII in FIG. 22, each showing a different usable cover plate and shim plate combination, according to an embodiment of the present invention. FIG. 23 is a cross-sectional view taken along line XXIII-XXIII in FIG. 22, each showing a different usable cover plate and shim plate combination, according to an embodiment of the present invention. It is a top view of the further embodiment of the heat exchanger of the present invention. FIG. 25 is a cross-sectional view taken along line XXV-XXV in FIG. 24. It is a side surface enlarged view of the heat exchanger of FIG.

Claims (21)

A plurality of opposing first and second surfaces, extending outwardly from the first surface and defining a plurality of elongate passageways open facing the second surface A fin plate including elongated fins spaced apart;
The entire circumference of each peripheral edge is hermetically coupled, has a spaced apart cover plate and shim plate defining a fluid flow chamber, and has an inflow opening and an outflow opening in communication with the fluid flow chamber. A low profile container and
The first surface of the fin plate is attached to the shim plate to allow heat transfer between the low profile container and the fin plate, and the second surface of the fin plate is exposed. A low-profile heat exchanger.   The shim plate is in the form of a flat sheet, and the cover plate is connected to the substantially flat central portion and the shim plate so as to be hermetically sealed, and the entire circumference of the outer peripheral edge of the central portion. The heat exchanger according to claim 1, further comprising an integrally formed side wall flange provided on the heat exchanger.   The heat exchanger according to claim 2, wherein a side connection flange having a flat surface that is in contact with and connected to the shim plate is provided at an outer peripheral edge of the side wall flange.   The heat exchanger according to any one of claims 1 to 3, wherein a turbulator having a row of rotating parts for increasing the flow rate of fluid is disposed in the fluid flow chamber.   The heat exchanger according to claim 4, wherein a plurality of the rotating portions are crimped to provide a barrier for directing a fluid flow between the inflow opening and the outflow opening.   A skeletal frame having a plurality of barrier walls is disposed in the fluid circulation chamber in order to provide a meandering flow path passing through the fluid circulation chamber between the inflow opening and the outflow opening. The heat exchanger according to any one of claims 1 to 3.   A plurality of embossed ribs extend into the fluid flow chamber to provide a tortuous flow path through the fluid flow chamber between the inflow opening and the outflow opening, the cover plate and the shim The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger is formed on at least one of the plates.   The fin plate is a corrugated plate having elongate fins defining open-ended passages that are alternately disposed with the open-facing passages facing the shim plate. The heat exchanger according to any one of claims 1 to 7.   9. The heat exchanger according to claim 8, wherein the fin has a U-shaped cross section and is connected to the shim plate by a connection wall brazed or soldered.   The heat exchanger according to claim 9, wherein the fins are longitudinally curved in alternating directions to divide a boundary layer of air flow in the fins.   10. The heat exchanger according to claim 9, wherein the fins are bent in the longitudinal direction in alternate directions of a herringbone pattern to divide a boundary layer through which air flows in the fins. .   Each fin is a longitudinal row of generally U-shaped lateral turns provided on the fin plate, and in each row, at least some of the turns are in each row relative to other turns. The heat exchanger according to any one of claims 1 to 7, wherein the heat exchanger is offset laterally along the heat exchanger.   The heat exchanger according to any one of claims 1 to 12, wherein the inflow opening and the outflow opening are formed through the cover plate disposed to face the shim plate.   The fin plate includes a flat support wall defining the first surface from which the fins extend, the shim plate being partially separated from the rest of the shim plate and fluid in the fluid flow chamber. The heat exchanger according to any one of claims 1 to 3 and 13, further comprising a portion bent so as to protrude into the fluid circulation chamber so as to be circulated.   14. A plurality of dimples extend from the cover plate into the fluid circulation chamber to increase the flow rate of fluid in the fluid circulation chamber. Heat exchanger.   A corrugated baffle plate disposed in the fluid flow chamber and configured to circulate the flow in the chamber, wherein the baffle plate substantially extends from a first end to a second end of the fluid flow chamber. A plurality of parallel flow paths extending through the chamber and defining a plurality of parallel flow paths, and one flow opening for circulating fluid through the fluid flow chamber is provided in each baffle wall. The heat exchanger according to any one of claims 1 to 3 and 13.   Each of the cover plate and shim plate has a flat central portion surrounded by an integral side wall flange, and one of the cover plate and shim plate is nested in the other side wall flange. The heat exchanger according to claim 1, wherein the heat exchanger is connected in a sealable manner.   The cover plate and shim plate each have a flat central portion surrounded by an integral side wall flange that is surrounded by a lateral connection flange, the connection flange of the cover plate and shim plate being The heat exchanger according to claim 1, further comprising a contact flat surface connected in a sealable manner.   A plurality of air flow paths extending through the shim plate, the fluid flow chamber and the cover plate are provided through the low profile container, and each of the air flow paths extends from the fluid flow chamber. The heat exchanger according to any one of claims 1 to 18, wherein the heat exchanger is sealed.   The heat exchanger of claim 19, wherein the fin plate defines an air passage in fluid communication with the air flow path through the low profile vessel. A plurality of first and second surfaces facing each other, extending outward from the second surface, and defining a plurality of elongated passages open on the opposite side of the second surface An extruded fin plate having a flat support wall comprising spaced apart elongated fins;
Having a substantially flat central portion spaced from the first surface of the support wall, having an integral side wall flange all around its outer periphery, the side wall flange extending to the support wall; A lateral connection flange at its extended edge, the connection flange having a substantially flat surface sealably connected to the first surface of the support wall, and fluid is contained in the fluid flow chamber; A separately formed low profile cover plate defined between the support wall and a fluid flow chamber having communicating inflow and outflow openings for allowing inflow, passage and outflow. A low profile heat exchanger characterized by comprising.

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