KR20010083957A - Radial flow annular heat exchanges - Google Patents

Abstract

A heat exchanger is disclosed using a plurality of stacked plate pairs (30) consisting of face-to-face, mating, ringlike plates (32), each plate having an outer peripheral flange (34), an annular inner boss (36) located in a common plane with the peripheral flange (34), and an offset intermediate area (39) located between the peripheral flange (34) and the inner boss (36). The peripheral flanges (34) and inner bosses (36) in the mating plates (32) are joined together. The intermediate areas (39) have outwardly disposed joined intermediate bosses (46) having aligned inlet and outlet openings (48, 50) forming manifolds (52, 54) for the flow of the first heat exchange fluid circumferentially through the plate pairs (30) from the inlet manifold (52) to the outlet manifold (54). The heat exchanger also has a header (70, 76, 82) enclosing either the inner bosses (36) or the outer peripheral flanges (34) to cause all of a second heat exchange fluid to pass between the plate pairs transversely relative to the flow of the first heat exchange fluid.

Description

Radial-flow annular heat exchanger {RADIAL FLOW ANNULAR HEAT EXCHANGES}

Oil coolers have been manufactured from a plurality of laminate treatments in the past located in housings or canisters. The septic tank normally has fittings for the flow of the engine cooling medium entering and exiting the septic tank as it circulates around the plate treatment. The plate treatment itself has an inlet and outlet, which is usually designed to form a manifold so that the oil passes through all the plate treatments at the same time. This manifold is connected to the return line located outside of the oil supply and the sump. One example of such an oil cooler is given in Japanese Utility Model Publication No. 63023579, published February 16, 1988.

Where an oil cooler is used with an oil filter, the plate treatment is usually annular and the conduit is located at the top or bottom of the oil cooler and passes through the torus center, which transfers the oil to or from the filter connected to the conduit. The oil passes through the filter and then through the oil cooler or vice versa. Examples of such oil coolers are Thomas E. No. 4,967,835 and Charles M., assigned to Thomas E. Leferger. No. 5,406,910 to Charles M. Wallin.

However, the difficulty with such prior art oil cooling is that it is not particularly efficient. They are also often disadvantageous due to the large pressure drop on the oil side of the cooler.

The present invention relates to a so-called "donus" type oil cooler, which can be used separately or in combination with oil filters in automobiles and other engines and transmission chillers.

Embodiments of the present invention will now be described by way of example with reference to the accompanying drawings, the contents of which are as follows:

1 is a vertical sectional view of a first embodiment of a heat exchanger and an oil filter coupling using one embodiment of a heat exchanger according to the present invention;

FIG. 2 is an enlarged perspective view of a partial cut away of the heat exchanger of the embodiment shown in FIG. 1; FIG. 3 is an enlarged perspective view similar to FIG. 2 but showing the bottom of the heat exchanger of FIG.

4 is an enlarged perspective view showing an inner surface of one of the plates used to form the plate treatment of the heat exchanger embodiment shown in FIGS. 2 and 3;

5 is a plan view of the plate shown in FIG. 4;

6 is an enlarged cross-sectional view taken along line 6-6 of FIG. 5 and showing an additional laminated plate above and below the plates of FIGS. 4 and 5;

FIG. 7 shows another embodiment in which a vertical cross section similar to FIG. 6 or a plate header is formed around the outside of the plate treatment;

8 shows another embodiment of a heat exchanger according to the invention in an enlarged sectional view of the lower left corner of FIG. 1;

9 shows a perspective view similar to that of FIG. 4 but another embodiment of a plate used to make a heat exchanger according to the invention;

10 is a plan view of the plate shown in FIG. 9;

FIG. 11 shows another embodiment of a heat exchanger and oil filter combination using a vertical cross-sectional view similar to FIG. 1 or another embodiment of a heat exchanger according to the present invention; FIG.

FIG. 12 is a partially cutaway perspective view of the heat exchanger used in the embodiment shown in FIG. 11; FIG.

FIG. 13 shows a plate similar to that of FIG. 4 but used to make the heat exchanger embodiment shown in FIG. 2;

FIG. 14 shows a further cross section along line 14-14 of FIG. 13, showing further plates stacked above and below the plate of FIG. 13;

15 is a plan view of another embodiment of a heat exchanger substrate such as a ring to make a heat exchanger according to the present invention;

FIG. 16 is a plan view of a top or bottom plate used to make a heat exchanger using the plate shown in FIG. 15; FIG.

FIG. 17 shows another embodiment of a plate similar to FIGS. 4 and 9 but in combination with a turbine such as used to make a heat exchanger according to the invention;

18 shows another embodiment of a heat exchanger as used in conjunction with a general purpose oil filter to make a vertical cross-sectional schematic or combination of a heat exchanger and a filter, similar to FIGS. 1 and 11;

FIG. 19 is a partially cutaway perspective view of the heat exchanger shown in FIG. 8; FIG.

20 is a plan view of another embodiment of a plate used to make a heat exchanger according to the invention;

FIG. 21 is a top view of an alternative spacer that may be used with the plate of FIG. 20; FIG.

22 is a perspective view of the inside of another embodiment of a plate used to make a heat exchanger according to the invention;

FIG. 23 is a plan view of the plate shown in FIG. 14;

24 is a plan view of another embodiment of a plate used to make a heat exchanger according to the invention,

25 is a plan view of another embodiment of a plate used to make a heat exchanger according to the invention.

It is an object of the present invention to obviate the disadvantages of the prior art.

The heat exchanger of the present invention is very efficient even at relatively low pressure drops. The primary heat exchange fluid moves circumferentially through a plate treatment such as a ring, and both secondary heat exchange fluids flow between the plate treatments transversely to the primary heat exchange oil.

According to one aspect of the invention there is provided a heat exchanger comprising a plurality of laminate treatments consisting of opposed ring-like plates. Each plate has an outer periphery flange, an annular inner boss with its periphery flange and a portion thereof located on the common surface, and an intermediate region located between the peripheral flange and the inner boss. The peripheral flange and the inner boss are connected together in a mating plate. The intermediate region has spaced apart portions to form inner fluid passages between the plates. The intermediate region plate has a spaced apart intermediate boss located between the outer peripheral flange and the inner boss extending from the intermediate region in the opposite direction to the peripheral flange and the inner boss. The intermediate boss defines the range of the inlet and outlet and for the flow of the primary heat exchange fluid along the circumferential direction through the inner fluid passage from the inlet manifold to the outlet manifold, which is connected to the intermediate boss at the back plate Daewoo. Determine the range of the entry and exit manifolds. Back Daehan's adjoining middle area defines the range of flow paths in Isaiah. The header also surrounds either the inner boss or the outer periphery flange. The header includes a fluid outlet for the flow of the secondary heat exchange fluid to allow the secondary heat exchange fluid to flow in the transverse direction through the outer fluid passage.

According to another aspect of the present invention, there is provided a method for transferring thermal energy between a lubricating fluid and an engine refrigerant. The method includes providing a closely spaced laminated plate treatment, such as a plurality of rings, with an outer fluid passageway between the inner fluid passageway and the plate Daewoo. Any one of the fluid and the refrigerant passes through the plate treatment in the circumferential direction, and all of the other fluid and the refrigerant passes through the plate treatment in the transverse direction.

The object of the invention is achieved by the combination of the features of the independent claim. The subclaims set forth further advantageous embodiments of the invention.

The summary of the invention does not necessarily disclose all important features for defining the invention, the invention may be potential for subcombination of the disclosed features and may be defined by the independent claims or the dependent claims.

Referring first to FIG. 1, one embodiment of a heat exchanger and oil filter combination according to the present invention is indicated generally by the reference numeral 10. However, any fluid that is not necessarily oil may be used in the present invention, so the term "oil" should be taken to mean any heat exchanger fluid for the purposes of the present disclosure. The coupling unit 10 comprises a housing 12 comprising an oil filter 14 and one embodiment of a heat exchanger according to the invention indicated by reference numeral 16. The oil filter 14 is universal and is not in itself considered part of the present invention. The oil filter 4 has an annular shape and in FIG. 1, the oil flows from the inside of the housing to the central shaft chamber 15 through the filter wall and passes downward through the pipe or the conduit 18. From) Nevertheless, the flow direction of oil passes through the conduit 18 and passes through the filter 12 radially outward into the housing 12. In the embodiment shown in FIG. 1, the oil preferably flows out of the housing through the filter and outflows through conduit 18. The heat exchanger 18 will be described in more detail below, but before leaving FIG. 1, the heat exchanger 18 passes through it to the heat exchanger 16 depending on how the housing 12 wishes to have oil flow through the filter 14. It will be noted that for the oil passage there is a base plate 19 comprising a hole 20 therein. Conduits 22 and 24 are attached to the base plate 19 for entering and exiting the heat exchanger 16 of the refrigerant entering and exiting the heat exchanger 16,

Referring to FIGS. 2 to 6, the heat exchanger 6 is formed of a plurality of laminated plate treatments 30 which are formed in pairs of opposite annular or ring-like plates 32. As best seen in FIGS. 4 to 6, each plate 32 has an annular inner boss 36 having an outer peripheral flange 34, an outer peripheral flange 34 and a portion 37 located on a shared surface. It has an intermediate region 39 located between the peripheral flange 34 and the inner boss 36. A plurality of intersecting ribs and grooves 38 and 40 are formed in the intermediate region 39 and extend between the inner boss 36 and the peripheral flange 34. The ribs and grooves 38 and 40 are flow increasing means. Loves and grooves in the plate, which are arranged at an angle and in the form of a spiral or involute curve, for forming the plate treatment 30, are corrugated between the plates of the plate treatment 30. Intersect while forming an inner flow passage. Similarly, adjacent ribs and grooves 38 and 40 of the back-to-back plate treatment intersect, forming a corrugated outer flow passage 44 between the plate treatment 30. The outer flange 34 includes an alternative arrangement notch 45 to assist in the proper arrangement of the plates 32 during assembly of the heat exchanger 16. Such an arrangement notch may be used in all embodiments of the present invention as needed.

The plate 32 is located between the outer periphery flange 34 and the inner boss 36 and spaced apart in space extending in one direction from the intermediate region 39 in the opposite direction to the peripheral flange 34 and the inner boss 36. It has an intermediate boss 46. The middle boss 46 defines the range of the inlet and outlet holes 48 and 50. The middle boss 46 has the inlet and outlet holes 48 and 50 connected thereto in the plate treatment back to the inner side along the circumferential direction. Or an outlet inlet manifold (52, 54) (FIG. 3) for the flow of primary heat exchange fluid such as engine refrigerant through the inner flow passage from the inlet manifold (52) to the outlet manifold (54). Deciding. The neighboring intermediate region 39 of the back plate treatment 30 delimits the outer flow passage 44 therebetween. The heat exchanger 16 has upper and lower carver plates 56 and 58. The lower cover plate 58 has holes 62 and 64 that coincide with the entry and exit manifolds 52 and 54 thereto. Conduits 22 and 24 (see FIG. 1) pass through the housing base plate 19 and are connected to the holes 62 and 64.

The ribs 38 and grooves 40 have a predetermined height and the intermediate boss 46 is preferably ribs 38 having a height or depth shown in FIG. 4, ie at least the same height as the ribs 38. The rib 38 is in contact with each other, as the outer surface of the intermediate boss 46, as the outer surface of the intermediate boss 46, when the plate treatment is located back to back as shown in Figure 6 . However, as shown in FIG. 6, the height of the inner annular boss 36 and the outer periphery flange 34 is greater than the height of the ribs and the grooves. Away. This reduces the water-side pressure drop of the refrigerant flowing through the plate treatment 30.

The intermediate boss 46 is located adjacent to each other so that the radial rib 66 (see FIGS. 4 and 5) extends between the intermediate boss 46 from the inner boss 36 to the outer periphery flange 34. The radial ribs 66 are in the same plane or have the same height as the inner boss 36 and the outer periphery flange 34 so that the two ribs join together to form the plate treatment 30. Are bitten together to prevent bypass flow from the inner hole 48 to the outer hole 50. The radial ribs 66 also form radial grooves on the outside or oil side of the plate treatment. This radial groove improves the radial or transverse flow between the intermediate repair 46 and the surrounding plate treatment.

The inner periphery flange 68 is formed in the annular inner boss 36 and has the middle boss 46 and the Daewoo flange portion 69 located on the common surface so that the inner periphery flange 68 of the plate Daewoo back is connected together. Form the inner boss 36 and the header 70 (see FIG. 6) along the transverse or radial direction through the outer flow passage 44 between the treated plates 30 back to the inlet 71. To flow,

The inner boss 36 includes a plurality of holes 72 that are spaced around the inner boss 36. When the plate treatments 30 are stacked together, the holes 72 are arranged or scared to form flow ports for supplying fluid to the header 70.

Next, referring to FIG. 7, which is similar to FIG. 6 but shows another embodiment of the heat exchanger 79 according to the present invention, it has a laminated treatment plate similar to the embodiment of FIGS. 1 to 6, but here the inside of FIG. The header 70 is deleted.

The primary reference numerals are used in FIGS. 7 to 25 to indicate the correction parts of the embodiment shown in FIGS. 1 to 6. The inner boss 36 'is cut off leaving the annular groove 80 for entering and exiting the flow passage 44 between the plate treatment of the fluid flow. The outer end flange 74 in this embodiment forms a header surrounding the outer periphery flange 34 'to allow the heat exchange fluid for all to pass through the transverse or radial direction in the plate-wool. This embodiment also shows that the inner annular boss 36 'and the outer periphery flange 34' have the same height as the height of the ribs and grooves, so that the adjacent ribs 38 of the inner flow passage 42 'are shown in FIGS. It is not spaced apart as in the embodiment shown in. However, adjacent ribs 38 of the inner flow passage 42 'may be spatially spaced apart as in FIG. 6 or the FIG. 6 embodiment may not be spatially separated as in FIG. 7 with ribs 38 as needed. will be.

8 shows another embodiment of a heat exchanger 801 wherein the header 82 is formed by an annular space defined by upper and lower cover plates 56 and 58 and the conduit 18 is airtight therein. As much as possible. The inner boss 36 'and the outer periphery flange 34 also do not have additional flanges formed thereon to form the header. The lower cover plate 58 includes a flow port 84 for the flow of fluid into or out of the header 82.

Figures 9 and 10 Another embodiment of a ring-like plate 85 is shown with reference to the following, which is similar to the plate 32 of Figures 4 and 5, but instead of ribs 38 and grooves 40 as intermediate means of flow increase. It has a plurality of spatially separated dimples 87 and 89 formed in the area 39. The dimples 87 extend into the outer flow passage 44 and the grooves 89 extend into the inner flow passage 42. The dimples 87 and 89 have a set height that is preferably equal to the height of the intermediate boss 46 in the case of the dimple 87.

However, some or all of the dimples 87 may have a height smaller than that of the intermediate boss 46.

If necessary, the plate 85 may be formed of an outer end flange, such as the flange 74 of the embodiment shown in FIG. 7, in addition to or in addition to the inner periphery flange 68 and header 70 as shown in FIG. 6. Instead, the header 76 may be defined around the outside of the plate.

The dimples 87 and 89 are arranged in rows along the circumferential direction and at regular equidistant intervals, but they can be compromised in different directions and spacings and can achieve special flow effects between and within the plate treatment.

FIG. 11 shows another embodiment of a heat exchanger and filter 91 similar to the coupling unit 10 of FIG. 1 but using a heat exchanger 28 as detailed in FIGS. 12 to 14. The top plate 56 ′ of the heat exchanger 28 is the bottom wall of the housing 12 ′ including the strainer 14 and the removable lid 93 allows for replacement of the strainer 14.

With particular reference to FIGS. 12-14, the heat exchanger 28 may be considered a modification to the heat exchanger of FIGS. 2 to 6. In the heat exchanger 28, the plate 32 'has an outer circumferential flange 34' extending radially and the outer end flange 74 has an outer circumferential flange 34 'having a Daewoo flange port 75. Is formed. The Daewoo flange portion 75 is located on the shared surface with the middle boss 46, and the end flange 74 of the plate Daewoo 30 'is turned back to form the outer peripheral flange 34' and the header 76. . Holes 77 are formed in the outer periphery flange 34 'and are arranged in the laminate treatment to receive the fluid flowing between the treatments back to form the flow ports. However, it will be appreciated that a reversal of the flow direction is possible to supply fluid such that the header 76 flows inward in the radial direction towards the center of the heat exchanger 28.

As best seen in FIG. 12, the upper cover plate 56 ′ is formed of a plurality of holes 78 that communicate with the holes 77, form a header 76 portion, and communicate with the interior of the housing 12 ′. It will also be understood that the heat exchanger 28 has two headers 70 and 76 with array holes forming the flow ports of these headers.

FIG. 15 shows a plate 95 that is a modification of the plate 32 'such that the plate 95 is rectangular or planar. The outer periphery flange 34 "is also rectangular and the inner boss 36 is shown in a circular or annular shape, but the inner boss 36 may be quadrangular if necessary. For the purposes of this specification, the plate 95 is provided. Is also considered to be within the scope of terms such as annular or ring and the flow from inlet 48 to outlet 50 is also considered circumferential and the flow from inner hole 72 to outer hole 77 is also into the plate treatment. It is considered radial or transverse for flow along the circumference.

16 shows quartz top plate 56 ′ for use with plate 95. The top plate 56 'has a periphery hole 97 whose size is variable and obtains a uniform flow distribution along the radial or transverse direction. It will be noted that the corner holes 97 are particularly large and the flow increases at the corners of the heat exchanger made of this plate. Alternatively, uniformly sized holes 7 may be closely spaced or further apart to provide a desired flow distribution instead of holes 7 of different sizes. This hole size or shape difference may also be used in connection with the hole 77 in the core plate 95 of FIG.

FIG. 17 has another type of flow increase instead of ribs and grooves as shown in FIGS. 1-6, or dimples shown in FIGS. 9 and 10, such as plates 85 shown in FIGS. . In the FIG. 17 embodiment, the steel mesh turbine 101 is used as the flow increasing means. Of course, the turbineizer 101 may be formed of a material different from steel, such as plastic mesh. 17 is a view of the plate 99 viewed from the oil side or the outside of the plate treatment. The intermediate region 39 is located under the turbineizer 101 and is spaced apart to form an inner flow passage into the plate treatment. The turbo riser 101 can be of any type of turbine riser and if the flow resistance varies in a particular direction, the holes 72 and 77 are adapted to the turbo riser so as to flow in radial or transverse directions between the plate Daewoo. You can arrange them differently or change their size to keep them uniform. The turbo riser 101 may be used either in the plane of the inner flow passage or instead of the outer flow passage as shown in FIG. 17,

18 and 19 illustrate a heat exchanger 28 ′, which is one modification of the heat exchanger 28 shown in FIGS. 11 and 12. In the heat exchanger 28 ′, an annular filter seat 103 is provided on the upper copper plate 56 to accommodate a universal spin-on filter 107 screwed to the conduit 18. The filter seat 103 has an inner hole to allow fluid to flow out of the header 76 or the hole 78 so as to be delivered to the filtering hole 109.

FIG. 20 shows the inner or water side of the plate 32 'and the inner annular boss 36' and outer peripheral flange 34 'with ribs for both intermediate boss 46 and inner peripheral flange 68. FIG. It is the same height as the height of the grooves 38 and 40. In this embodiment, to reduce the pressure drop in the plate treatment, a spacer 86 as shown in FIG. 21 can be used between the plates of the plate treatment. The spacer 86 has an outer annular portion 88 located between the inner annular portion 90 located between the outer peripheral flange 34 'and the inner annular boss 36'. The inner annular portion 90 has a plurality of holes 92 therein and coincides with the holes 72 in the inner boss 36 '. The rotation of the space 86 relative to the plate 32 'acts as a valve to act as a valve to set or regulate the pre-flow rate through the hole 72 during the manufacture of the heat exchanger using this type of plate. .

22 and 23 show a plate 94 similar to the plate 32 ′ of FIG. 20 but with a peripheral bypass groove 96 located inside the plate right side adjacent to the outer periphery flange 34 ′. The bypass groove 96 has a first end portion 98 which is located adjacent to any one of the intermediate bosses 46 and extends to the second end portion 100 just over a half distance around the plate 4. When the two plates 94 are arranged, the ends 100 facing each other overlap and the bypass groove 96 extends all around the plate treatment from one intermediate boss 46 to the other boss. Form a groove of height 2. Bypass groove 96 is used to reduce the pressure drop in the plate treatment if necessary.

FIG. 24 shows a plate 102 similar to the plate 4 of FIG. 23 but with at least one bypass groove 104 extending between the intermediate bosses 46. In fact, the grooves between the intermediate bosses 46 overlap and intersect with each other so that several half-high bypass channels extend between the intermediate bosses 46. Again this bypass channel is provided to reduce the pressure drop in the plate Daewoo. If necessary, the bypass groove 104 can be used in place of the peripheral bypass groove 96.

FIG. 25 is a modification of the plate 102 of FIG. 24. In the plate 102 ', the bypass groove 104 is formed as a concave groove 106 for restricting the flow rate so as to control or set a set amount of bypass flow between the intermediate bosses 46.

In describing the embodiments of the present invention, it will be understood that various modifications may be made in the above structure. For example, an intermediate boss comprising an outlet opening may be smaller so that the inner annular boss 36 has a hole 72 that allows the same width across all of these circumferences so that it can extend over the entire circumference of this boss. Various heat exchangers can be made using any number of plate counters, and various plate treatment embodiments can be compromised to adapt to meet special requirements. The upper and lower cover plates can be omitted in some applications, where plates Other means are used to close the various flow manifolds formed by the holes in. For example, the end plates may be used to make plate treatments similar to the plates used, in which case the various openings and openings of these end plates will not be punched. Ribs, grooves and other shapes for dimples and turbo risers are also needed. You will be able to use it in the city.

Although embodiments are specified for use as oil coolers, the heat exchanger of the present invention may be used to cool or heat other engine fluids such as fuel, transmission oil, hydraulic control oil, refrigerant and even engine refrigerant itself. You will also understand the point. The fluid may pass through the plate treatment or plate treatment and the heat exchanger of the present invention may be used for heating as well as for cooling the fluid. In addition, the heat exchanger of the present invention can be used for other applications than the automobile industry.

Various alternatives and modifications are possible in the practice of the present invention without departing from the spirit or scope thereof as apparent to those skilled in the art in view of the above disclosure. The above description has been given by way of example only and is not intended to limit the scope of the invention.

Claims (27)

Heat exchangers include: Each plate with outer circumferential flanges of the ring-like plates facing each other, an annular inner ring with a peripheral flange and shared surface and a portion located thereon, and an intermediate region located between the peripheral flange and the inner boss, connected together A plurality of laminated plates composed of intermediate regions having spaced apart portions to form an inner flow passage between the peripheral flange of the treated plate and the inner boss and the plate; The middle plate area is spaced between the outer periphery flange and the annular inner boss and extends from the middle area in the opposite direction to the surrounding flange and the inner boss. The middle boss defines the outflow hole and the middle boss Connected to and through the inlet and outlet through which the outlet inlet manifold for the primary heat exchange flows in the circumferential direction through the inner flow passage from the inlet manifold to the outlet manifold, the adjacent intermediate region of the plate Daewoo from behind Define an outer flow path therebetween; The header surrounds either one of the inner boss and the outer periphery flange, and the header includes a flow port for the flow of the secondary heat exchange fluid therethrough to cause the secondary heat exchange to flow transversely through the outer flow passage. Heat exchanger. The heat exchanger of claim 1, further comprising a flow increasing means located in either of the inner flow passage and the outer flow passage. 3. The flow increasing apparatus according to claim 2, wherein the flow increasing means includes an intermediate region consisting of a plurality of intersecting ribs and grooves extending between the inner boss and the outer circumferential flange, wherein the ribs and the grooves are formed between the plates in the treatment plate. A heat exchanger that intersects and forms a corrugated inner flow passage, and the ribs and grooves of the plate Daewoo adjacent to each other intersect while forming a corrugated outer flow passage in the plate Daewoo. 3. The heat exchanger of claim 2, wherein the flow increasing means comprises an intermediate region formed of a plurality of spatially spaced dimples extending into at least one of the inner flow passage and the outer flow passage. 3. The heat exchanger according to claim 2, wherein the flow increasing means comprises a turbo riser located in at least one of the inner flow passage and the outer flow passage. 4. The heat exchanger of claim 3, wherein the ribs and the grooves have a preset height, wherein the intermediate boss has at least the same height as the height of the preset ribs and the grooves. The heat exchanger according to claim 6, wherein the inner boss and the outer peripheral flange boss of each plate have the same height as the height of the ribs and the grooves. The heat exchanger according to claim 6, wherein the inner boss and outer peripheral flange of each plate have a height greater than the height of the ribs and the grooves. 8. The heat exchanger of claim 7, further comprising a spacer positioned between the plates of each plate treatment, the spacer having an outer portion located between the inner portion located between the outer periphery flange and the inner boss. The heat exchanger of claim 1, wherein the intermediate bosses are positioned adjacent to each other. 11. The heat exchanger of claim 10, further comprising radial ribs extending between intermediate bosses from the inner boss to the outer periphery flange, wherein the rub is on the shared surface. 12. The heat exchanger of claim 11, further defining a peripheral bypass groove located in the plate treatment adjacent to the outer periphery flange and extending over a distance just one half of the periphery of each plate. 11. The heat exchanger of claim 10 further comprising at least one bypass rib and a groove extending between said intermediate bosses. The heat exchanger according to claim 13, wherein the bypass lip and the groove are pre-set and are formed by flow restriction cutting to generate a bypass flow. 5. The heat exchanger of claim 4, wherein the dimples extend in both inner and outer flow passages. The heat exchanger of claim 15, wherein the dimple has a predetermined height and the intermediate boss has a height that is at least equal to the dimple height. 6. The heat exchanger of claim 5, wherein the turbineizer is located in the outer flow passage. 18. The heat exchanger of claim 17, wherein the turbo riser has a predetermined height, wherein the intermediate boss has a height equal to one-half the height of the turbo riser. 19. The inner periphery flange of claim 6, 16 or 18, further comprising an inner periphery flange formed on the inner boss and having a Daewoo flange portion located on the co-planar surface with the intermediate boss, wherein the inner periphery flange of the backside Daewoo is connected to the inner boss and the inner boss. And a port formed by an inner boss defining a hole arranged therein. 20. The outer circumferential flange according to claim 6, 16 or 19, further comprising an end flange formed in the outer circumferential flange and having a middle boss and a Daewoo flange portion located on a shared surface, and the outer end flange of the back-side plate Daewoo is connected to the outer circumferential flange. And the header, wherein the port is defined by an outer periphery flange defining a hole arranged therein. 21. The filter according to claim 1, 19 or 20, further comprising a housing that surrounds the lamination treatment, the oil filter is embedded in the housing and has an inlet and outlet, the conduit passes through the housing and communicates with any one of the filter inlet and outlet. The other communicates with the interior of the housing, the housing defining an oil port in communication with the header port such that oil passes between the oil port and the interior of the housing. 21. The heat exchanger of claim 19 or 20, further comprising a filter having a hollowing defining an inlet and outlet, wherein the filter is attached to the laminate treatment with any of the filter inlets and outlets communicating with the port. 22. The conduit of claim 21 wherein the conduit passes along the laminate treatment along the axial direction and includes a top and bottom cover plate attached to the top and bottom of the laminate treatment and bites with the conduit therethrough to maintain airtightness, the carver plate and the conduit passing through the header. And the flow port is formed in the lower cover plate. The heat exchanger of claim 2, wherein the plate is in the shape of a rectangle. The following steps between the lubricating oil and the engine refrigerant: providing a plurality of ring-shaped closely spaced laminate treatments having an outer flow passage between the inner flow passage and the plate Daewoo; A method of circumferentially passing through any one of the liquid and the refrigerant through the plate treatment and passing the heat energy through the other and all of the liquid along the transverse direction between the plate treatment. 26. The method of claim 25, wherein a fluid or refrigerant is passed transversely between the plate treatments by providing headers that communicate with all outer flow passages between the plate treatments, wherein the headers are located at either of the centers and on the outer periphery of the laminate treatment. A method of transferring heat energy through which all of the fluid or the refrigerant passes through the plate treatment in the transverse direction. 26. The method of claim 25, wherein the refrigerant passes circumferentially through the plate treatment and the fluid passes transversely between the plate treatments.