JP2593879Y2 - Plate heat exchanger - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention generally relates to a plate type heat exchanger for an automobile.

[0002]

2. Description of the Related Art Heat exchangers used in automobiles, for example for air conditioners, are well known and are generally of the flat plate type. Plate heat exchangers (sometimes called evaporators) have alternating adjacent laterally extending fluid and air flow passages. The coolant fluid passage includes a plurality of fluid flow obstructions disposed therein and is formed by joining together a pair of elongated plates having depressions disposed therein. The plurality of fluid flow obstructions so formed form a tortuous flow path in the fluid flow passage, forming a turbulent flow, increasing the contact area between the walls of the passage and the refrigerant fluid, Increases the efficiency of heat transfer from the air to the fluid.

[0003] In one type of evaporator, the refrigerant fluid inlet and outlet are located adjacent the ends of the elongated plate. This is described, for example, in US Pat. No. 4,700,455 (S
acca) and US Patent No. 4,600,053 (Patel et al.)
Is shown in These ports are formed from raised portions, sometimes called bowls, located adjacent to the ends of each plate. The ridge is generally circular and has a lip at the bottom of the bowl, the edge of which defines an opening at the bottom of the bowl. When a pair of elongated plates are joined, the bowls of each plate of the pair align and form a fluid inflow or outflow passage therethrough. Fluid entering the inlets enters lateral fluid passages between the plates through inlets located in these opposing bowl portions.

An evaporator is assembled by joining a plurality of pairs of these joined plates. The pairs of plates are joined together around the lips at the bottom of the bowl and a secure seal is formed by brazing. In this way, a multi-plate assembly is made. The airflow passage is between adjacent pairs of plates. There, fins for increasing the surface area are provided in order to increase the heat exchange efficiency.

[0005] In other types of heat exchangers, an inlet and outlet tank, including a flow port, are adjacent to each other and located at one end of the heat exchanger. Examples are U.S. Pat. No. 4,696,342 (Yamauchi et al.) And U.S. Pat.
(hara et al.).

[0006]

A disadvantage of these heat exchangers is that they are inefficient because the entire front surface of the heat exchanger is not used. This is because the refrigerant inlet and outlet tank sections including the fluid passage are arranged over the entire width on both sides thereof. Fins cannot be provided in the area occupied by the tank portion, and the ratio of the fin area to the duct area becomes smaller than 1;
Typically, it is about 0.70 to 0.80.

Another disadvantage of these heat exchangers using bowl assemblies formed by the above-described drawing is that:
During assembly, a precise and precise control of the relative positioning of the two plates is required. This is because obtaining a good seal between the lips of adjacent bowls is important for proper operation of the heat exchanger. In addition, the high surface area and unsupported joints of these molds have low burst strengths,
upture). This will become increasingly important as air conditioners with chlorine, eg R-12, are replaced with environmentally safe substances. Some of these, such as R-134, have higher operating vapor pressures than current refrigerants, and therefore, heat exchangers using this alternative refrigerant are required to have greater burst strength. .

[0008] British Patent Specification A-1,305,464 (January 31, 1973)
2) shows a sheet metal radiator assembly for circulation of cooling oil of an electric transformer. The heat exchanger is comprised of a number of spaced, upstanding plate units, each plate unit being entirely comprised of a pair of thin sheet steel stamped. The assembly has top and bottom headers, which are formed by tubular extensions at the top and bottom of the plate, which are fitted and brazed together. In this known construction, there are no fins arranged between the pair of plates, and the space between the pair of plates is a shoulder provided near the base of the tubular interconnecting member used to form each header. Defined by

[0009] Conventional types of heat exchangers penetrate long, flat fin arrays and form many parallel paths through the fins, thereby enabling airflow to be formed throughout the front face. It has a small-diameter tube. A disadvantage of this type of heat exchanger is that the hot fluid contacts a relatively small surface area while flowing through the heat exchanger. This is due to the restriction that the fluid passes through the tube.

Another disadvantage of conventional air conditioner evaporators is that the refrigerant fluid residence time in each section of the heat exchanger.
s). It has been observed that the speed of the refrigerant flow in some parts of conventional heat exchangers is lower than in other parts, and dead zones or spots are formed. At operating conditions near the evaporator outlet, the refrigerant is subject to chemical breakdown and is liable to form strong acids such as hydrochloric acid and hydrofluoric acid. These acids are known to cause corrosion at brazed joints and pinholes in the dead zone.

[0011]

SUMMARY OF THE INVENTION The present invention provides a plate heat exchanger having fins formed entirely. In accordance with one aspect of the invention, a heat exchanger having fins formed therein has a plurality of coupled plate pairs, each plate of the pair having a substantially flat portion, and each pair having a substantially flat portion. The plates are sealably connected to each other, with the flat portions spaced apart from each other to enclose the longitudinal flow passage therebetween and to form a space defining a lateral air passage between adjacent pairs of plates. . The plates each have at least two openings through the plate at a location remote from the perimeter of the plate. Each opening in one plate is aligned with an opening in the other plate of the pair. The plate includes a tube surrounding each opening and extending transversely from the plate. A plurality of pairs of plates are stacked in spaced relation to each other, and each tube extending from each pair is aligned with a tube extending from an adjacent pair of plates to form a hermetic connection, wherein the connection is at least one of the tubes. And an overlap portion that overlaps with a part of. The tubes of each upper plate then project upwardly, and the tubes of each lower plate project in opposite transverse directions from the respective lower plate. Neither tube nor plate pair has spacing means in the region of the opening for positioning the tube of each upper plate relative to the tube of the lower plate connected to it in the axial direction of the tube. The connected tubes surround the substantially transverse flow passages, which are spaced apart from each other and are in communication with the transverse passages. In addition, means are provided for forming an inlet communicating with one of the transverse passages, and means for forming an outlet communicating with the other of the transverse passages. The transverse passage has an end and means for closing said end which is not in communication with the inlet and outlet. Fins are disposed in the lateral passages and have transverse fluid passages therethrough in thermal contact with and through the plate. The outer end regions of the fins are located laterally adjacent to the tube or longitudinally outside the tube. The lateral position of the outer edge section is in a direction perpendicular to the longitudinal edges of the plate.

According to another aspect of the invention, a plate heat exchanger has a plurality of coupled plate pairs, each pair comprising an upper plate and a lower plate, wherein each plate of the pair is substantially A flat portion, two longitudinal edges extending the length of the plate, and two edges connecting said longitudinal edges, each pair of plates being hermetically coupled; The flat portions surround the longitudinal flow passages that are spaced apart and extend therebetween, forming spaces that form lateral air passages between adjacent pairs of plates, each of which passes through it. Having at least two openings, spaced apart from the periphery of the plate, each opening of one plate being substantially aligned with an opening of the other plate of the pair of plates, the plate surrounding the periphery of each opening; A connection extending transversely thereto from
The plurality of plate pairs are stacked in spaced relation, each connection extending from the pair of plates being connected to a connection extending from an adjacent pair of plates to form a hermetic connection, wherein the connection is substantially transverse. Means for forming an inlet communicating with one of said transverse passages, said transverse passages being spaced apart from each other and communicating with said transverse passage; and Means for forming an outlet communicating with the other of the directional passages, said transverse passage comprising an end and means for closing said end not communicating with said inlet and outlet. A fin disposed in the lateral air passage, wherein the fin is in thermal contact with the plate and has a transverse fluid passage therethrough; the connection is a tube; The sealing connection overlaps at least one part of the tube. With a wrap, the tubes of each upper plate project upwardly from the respective upper plate, each lower plate extends in the opposite transverse direction from the respective lower plate, and the edges of the plates each extend from its flat portion. A transversely extending flange member, the flange member having a curved end, wherein the curved end overlaps a curved end of a pair of adjacent plate flange members, and an outer end area of the fin. Is located laterally adjacent to the tube or at a position longitudinally outward from the tube, and the lateral position of the outer end section is in a direction perpendicular to the longitudinal edge of the plate. Features.

[0013]

BRIEF DESCRIPTION OF THE DRAWINGS Preferred and alternative embodiments of the method of making the heat exchanger and its components are described below by way of example with reference to the drawings.

The structure and operation of the evaporator provided with the fins of the present invention will be described. Similar reference numerals are used to indicate similar parts of different embodiments of the heat exchanger.

Referring to FIGS. 1 and 2, an evaporator or heat exchanger provided with fins on the entire surface is indicated generally by the reference numeral 10 and includes a plurality of elongated plates 12. Plates 12 are arranged to form adjacent pairs 18. 18 pairs
Has an upper plate 14 and a lower plate 16 and is sealed so as to form a refrigerant flow passage 20 therebetween. Such plate pairs 18 are coupled together as described below to form the heat exchanger 10.
Is formed. Air passages 22 are located between adjacent plate pairs 18 and fins 24 are located within air passages 22 and fins 24 are in thermal contact with adjacent plate pairs 18 and fins 24 The surface area for heat exchange between the air and the air flowing through the air passage 22 is increased.

The heat exchanger 10 includes a refrigerant fluid inlet 26 and a refrigerant fluid outlet 28 projecting from the upper part of the heat exchanger 10. The ports 26 and 28 are provided inwardly from the end or edge 30 of the heat exchanger 10. Heat exchanger 10
Has an upper protective plate 32, and the openings 26 and 28 pass through the upper protective plate 32, for example. Plate 32 is provided adjacent the top pair of plates to protect top fin 24 from damage. The evaporator 10 further has a lower protection plate 34.
The lower protection plate 34 not only protects the lowermost fins 24 from damage, but also serves as a support structure when the evaporator 10 is installed.

FIG. 2 shows the heat exchanger 10 having a refrigerant fluid inlet passage 36 communicating with the inlet 26 and a fluid outlet passage 37 communicating with the outlet 28. The passages 36 and 37 are a pair of plates.
It extends transversely to the fins 8 and the fins 24 and extends through the interior of the heat exchanger 10.

FIG. 3 shows another embodiment of the heat exchanger. This heat exchanger is generally designated by the numeral 40 and is similar to the heat exchanger 10, but with an inlet 26 'and an outlet 28'.
Are provided on the same side of the heat exchanger 40, but adjacent to the lower and upper plates 34, 32, respectively. The extension tube 41 connects the outlet 28 'to the transverse passage 36'. Another extension tube 44 connects the inlet 26 'with the transverse flow passage 37'. Plugs 42 and 43 are provided in the inflow and outflow passages 37 'and 36'. The role of the plugs 42 and 43 will be described later.

The details of the construction and manufacturing of various embodiments of plate 12 and passages 36 and 37 will be described with reference to FIGS.

Referring to the exploded perspective view of FIG. 4, plate pair 18 includes an upper plate 14 and a lower plate 16. Plates 14 and 16 are identical. Therefore, the following description applies equally to both plates. The plates 14, 16 are the central flat part 5
6 having a plurality of recesses 58 evenly distributed in each plate. Each plate has a pair of spaced openings 60. The opening 60 is provided at a position closer to the inside from the peripheral edge 62 of the plate. Tubes 64 and 66 are integrally formed or joined to the periphery of each opening 60,
It extends transversely of the plate and in the opposite direction from the recess 58 from the plate. The plate has a raised edge 68 adjacent the periphery 62. This is best illustrated in the lower half of FIG. The recess 58 and the raised edge 68 are
From the same distance and in a direction transverse to the plate.

Preferably, tube 64 has a diameter D1 and tube 66 has a diameter D2, wherein D1 is greater than D2 and tube 66 is inserted into a corresponding tube 64 located on another plate. To facilitate this insertion, the small diameter tube 66 is bent radially inward at 70 (FIG. 6) and the tube 64 is
2 may be widened.

Referring to FIG. 7, the plates 14, 16 have a generally spherical protrusion 74 disposed near one end and extending in the same direction as the recess 58. A spherical receiver 78 is located near the other end of the plate and extends in a direction opposite to the protrusion 74. Protrusions 74 and receivers 78 are provided to prevent lateral movement of plates 14 and 16 during assembly of the heat exchanger. The protruding portions 74 are spaced from each other by a distance D
It extends for more than half of three and is received in the receptacle 78 when the plates are compressed together, thereby preventing lateral movement of the plates. Preferably,
The protrusions 74 and receivers 78 of each plate are located on the line connecting the tubes 64 and 66 and are located adjacent to each other to form additional flow obstructions in the flow passage between the plates.

The plate pairs 18 are assembled individually by compressing the plates. In this case, the raised edges 68 of each plate are aligned, and the protrusions 74 of one plate are aligned with the receiving portions 78 of the other plate.
Accepted to. When assembled, the pair of plates includes two pairs of concentrically aligned tubes. The concentric alignment is achieved as a result of the openings 60 in each plate being aligned with the openings 60 in the other pair of plates. Each pair of tubes attached to each plate
It is formed to have different diameters. Adjacent plate pairs are joined together by aligning the plates so that the larger diameter tube of one plate is aligned with the smaller diameter tube of the adjacent plate pair. The plate pair is then compressed and a small tube is inserted into the large tube, as shown in FIG.

FIG. 8 shows a pair of adjacent plates, for example, pair 1 of plates.
10 shows another example of a method of connecting tubes between the tubes 10 and 112. Tubes 114 and 116 have the same diameter,
And also its length is short enough so that the tubes do not overlap each other when the plates are assembled to form the core of the heat exchanger. In this connection method, tubes 116 and 114 are inserted into collars or retaining rings 118 when plate pairs 110 and 112 are assembled. When the entire heat exchanger is assembled and brazed, the color 1
A fluid tight joint is formed between 18 and tubes 116,114.

FIGS. 6 and 8 also show different examples of the arrangement of the plates. The peripheral edge of the plate includes transversely extending flange members 100,130. The flange member has curved ends 102,132. Plate pairs 90, 92, 11
When 0, 112 are joined together, each bent portion 102, 102 ', 132, 132' overlaps,
Holds the plate pair and prevents the formation of pointed edges. These overlapping flanges also form part of the limits of the air flow passage 22.

In another embodiment of the heat exchanger according to the invention, at the ends of the pair of plates, near the opening 60,
Directional ribs (not shown) are provided in place of the recesses 58 to allow the refrigerant to flow out of the ends.

It will be apparent to those skilled in the art that more than one tube 64 or 66 may be formed at each end of the plate to provide the heat exchanger with more than one fluid inlet or outlet passage.

FIG. 9 and FIG.
Two methods of forming 66 are shown. FIG. 9 shows a preferred manufacturing technique. This method involves drilling and pulling (st
(retch) method, in which a hole 162 (FIG. 9A) corresponding to a desired tube position of the plate 160 is perforated. Next, hole 16 in the board
2 is pulled to form a tube 164 having a diameter D1 (FIG. 9B). If necessary, the tube 164 can be stretched by ironing if the desired length is not obtained by the pulling process (FIG. 9).
(C)). The end of the small diameter tube is bent inward as shown at 166 in FIG. 9 (d). The end of the large diameter tube is widened outward (not shown).

The diameter of the tube 164 should be between 0.6 and 2 to maintain the heat exchanger flow rate at a sufficient value, thereby minimizing the possibility of creating low flow dead zones.
Preferably it is cm (1/4 to 3/4 inches).

FIG. 10 shows another method of forming a tube in the plate 180. In this method, a known drawing (drawin) is first performed.
g) to form a closed tube portion 182 (FIG. 10).
(A)) Then, an opening 184 is formed by perforation (FIG. 10 (b)). Next, the pipe portion 182 is straightened and stretched as shown in FIG. Tube 18
2 has an outer diameter of D1. Another small diameter D2 tube 192
Is formed in the same manner on the plate 180 (FIG. 10E).
And FIG. 10 (g)). The end of the large diameter tube is shown in FIG.
The small diameter tube end is bent radially inward as shown at 196 in FIG. 10 (g), as shown in FIG.

Several fin configurations may be employed to accommodate refrigerant fluid inflow and outflow conduits therethrough. Figures 11 to 13 show several such fin configurations. FIG. 11 shows a preferred embodiment. In this configuration, a fin 200 having essentially the same planar dimensions as the plate is provided with two rectangular openings 202 and 204 for flow passages 36 and 37. Openings 202 and 204
Can be formed by, for example, laser cutting, water jet processing, or electrochemical processing.

FIG. 12 shows another fin 210. In this fin, the openings 202 'and 204' are circular holes.

FIG. 13 shows another fin configuration. The fins 220 have three generally rectangular portions 222, 2
24 and 226. In the case of FIG. 13, a plurality of inlets and outlets can be provided. In the example shown, two inlets 240 and 242 and two outlets 244 and 246
Is provided.

FIG. 14 shows details of one embodiment of the connection of the fluid inlet and outlet to the heat exchanger in the present invention. Outer plate pair 240 includes an upper plate 242 having an opening 244 concentric with fluid inlet passage 246. Fitting (fitt
ings) 248 has a lip 250 configured to fit into opening 244. The fitting 248 includes a surface 252 that abuts the top plate 242. A protective retaining plate 254 is positioned adjacent to and spaced from the outermost plate pair 240 to form an outermost air passage 241 and the fins 24 (not shown) ) Are arranged in the passage 241. A similar structure is used at the bottom of the heat exchanger. An opening 256 is provided in the retaining plate 254, and a fixture 248 is inserted into the opening 256. During the brazing process of assembling the heat exchanger, the fixture 248
Is connected to the plate 242 by brazing. The attachment 248 is provided with a first internal shoulder 258 and a second internal shoulder 260. A standard female thread 262 is provided. The refrigerant fluid hose 264 is
6 and a thick portion 270. An O-ring 268 is fitted around the thin part. In the thick part 270,
A male screw 272 that matches the female screw 262 is provided. Hose 264 is threaded into fitting 248 until O-ring 268 is compressed by shoulder 258 to seal hose 264 and fitting 248. Similar hose and fitting assemblies can be used for other fluid port connections (not shown).

To assemble the heat exchanger of the present invention, first assemble a pair of individual plates and then sandwich the fins between adjacent pairs of plates. In the embodiment of FIG. 6 utilizing different sized tubes, expanding may be performed after adjacent pairs of plates have been assembled. In this flaring process, the inner tube is spread outwardly toward the outer tube, forming a close physical connection between them. If the tubes have the same diameter, a collar may be used as in the embodiment of FIG. The top and bottom retaining plates are in place, the entire evaporator is clamped, and the resulting assembly is placed in a brazing furnace and heated to the appropriate temperature for brazing. The plates are all made of braze-coated aluminum or similar furnace brazing material.

The operation of the heat exchanger in the embodiment shown in FIGS. 1 and 3 will be described. When refrigerant fluid inflow and outflow hoses (not shown) are connected to the inlet 26 and the outlet 28 of the evaporator, respectively, the refrigerant fluid flows into the inflow passage 3.
The evaporator 10 enters the evaporator 10 via 6 and reaches the outflow passage 37 through the passage 20 in a laterally non-linear path. At the same time, the air passes through the fins 24 in the air passage 22 and is cooled by heat transfer from the fins to the refrigerant fluid. By properly selecting the diameter of the tube, the flow rate of the outflow passage 37 can be kept above a predetermined threshold, thereby avoiding the problem of forming a dead zone.

In the evaporator of FIG. 1, the refrigerant fluid enters and exits the evaporator 10 via transverse passages 36 and 37, and flows between the passages 36 and 37 through the lateral flow passage 20.

In the alternative configuration shown in FIG. 3, fluid passes multiple times within evaporator 40 due to the presence of plugs 42 and 43 properly inserted into passages 36 'and 37'. Thus, fluid entering the passage 37 'through the inlet 26' flows to the plug 42 and from there laterally flows through the passage 20 'located in a pair of plates below the plug 42. , Reaches the passage 36 ′, flows upward to the plug 43, and laterally passes through the passage 2 below the plug 43.
0 'to flow passage 37' where fluid again flows upwards and laterally, passage 2 above plug 43.
It flows through 0 'and reaches outlet 28'.

The present invention has been described with respect to a preferred embodiment and other embodiments.
It will be understood that many modifications may be made without departing from the scope of the invention as set forth in the claims.

[0040]

Since the present invention is configured as described above, a large portion of the available area of the evaporator can be used for heat exchange.

[Brief description of the drawings]

FIG. 1 is an elevation view of a preferred embodiment of the heat exchanger of the present invention.

FIG. 2 is a perspective view and a sectional view of the heat exchanger of FIG.

FIG. 3 is a partially cut away elevation view of another embodiment of the heat exchanger of the present invention.

FIG. 4 is an exploded perspective view of a pair of plates constituting a pair of plates of the heat exchanger.

5 is an exploded perspective view showing a portion of another embodiment of a plate of a heat exchanger, similar to FIG.

FIG. 6 is an enlarged cross-sectional elevation view showing a part of a pair of plates.

FIG. 7 is an enlarged sectional view showing a part of a pair of plates showing details of the plate positioning means.

FIG. 8 illustrates another example of a method for joining pairs of tubes of adjacent plates.

9 (a) to 9 (d) are cross-sectional views showing steps of a method for forming a pipe by perforating a plate and performing a tensile process.

10 (a) to 10 (g) are cross-sectional views showing another method of forming a tube by squeezing and piercing.

FIG. 11 shows a preferred embodiment of a fin that can be used in a heat exchanger.

FIG. 12 shows a preferred embodiment of a fin that can be used in a heat exchanger.

FIG. 13 shows a preferred embodiment of a fin that can be used in a heat exchanger.

FIG. 14 shows details of the coupling connection between the fluid inflow and outflow passages and the associated hose coupling.

[Explanation of symbols]

14: upper plate, 16: lower plate, 18: plate pair, 20: flow passage, 22: lateral air passage, 24: fin, 26: inflow passage, 28: outflow passage, 32, 34: plate pair, 36,3
7: transverse passage, 56: flat, 60: opening, 6
4, 66: tube, 74: projecting portion, 78: receiving portion, 110:
Flange member, 118: collar, 130: flange member, 240, 242, 244, 246: opening.

Continuation of the front page (56) References JP-A-3-1093 (JP, A) JP-A-2-259391 (JP, A) JP-A-63-99496 (JP, A) JP-A-55-80687 (JP, A) , U) Japanese Patent Publication No. 2-40426 (JP, B2) Japanese Patent Publication No.4-16707 (JP, B2) (58) Fields investigated (Int. Cl. ⁶ , DB name) F28F 3/00-3/14 F25B 39/00-39/04 F28D 1/00-9/02

Claims (8)

(57) [Scope of request for utility model registration] A plurality of joined plate pairs (18), each pair comprising an upper plate (14) and a lower plate (16);
Each plate of the pair has a substantially flat portion (56), two longitudinal edges extending in the direction of the length of the plate, and two edges connecting the longitudinal edges; Each pair of plates is hermetically connected to each other, the flat portions being spaced apart and surrounding a longitudinal flow passage (20) extending therebetween, and a lateral air passage (22) between adjacent pairs of plates. Forming at least two openings (60) therethrough;
The opening is provided at a position away from the periphery of the plate,
Each opening of one plate is aligned with the other opening of the pair of plates; the plate surrounds the perimeter of each opening and includes a connection extending transversely from the plate; And each connection extending from a pair of plates is connected to a connection extending from an adjacent pair of plates to form a hermetic connection, the connection surrounding a generally transverse flow passage, and The flow passages are spaced apart from each other and communicate with the lateral flow passages, and further comprise means for forming an inlet (26) in communication with one of the transverse passages (36); (36) an outlet (28) in communication with another one;
Wherein said transverse passage (36, 37) has an end and means for closing said end which is not in communication with said inlet and outlet (26, 28); And a fin (24) disposed in the transverse air passage (22), the fin being in thermal contact with the plate and having a transverse fluid passage therethrough; The portion is a tube (64, 66), wherein the hermetic connection includes an overlapping portion overlapping at least a portion of at least one of the tubes, wherein the tubes of each top plate (14) project upwardly from the respective top plate; The tubes of the lower plates (16) protrude in opposite transverse directions from the respective lower plates, and the tubes (64, 6
6) Neither the plate pair has a spacing means for positioning the tube of each upper plate in the area of the opening with respect to the tube of the lower plate connected thereto in the axial direction of the tube, and The outer end area of (24) is at a location laterally adjacent to the tube or at a location longitudinally outside the tube;
Plate heat exchanger characterized in that the lateral position of the outer end section is perpendicular to the longitudinal edges of the plate. Wherein said sealing coupling comprises a collar (118), a plate-type heat according to claim 1 in which the end portion of the tube, characterized in that it is sealingly inserted in one end of each of the color Exchanger. 3. The tube (6) which is respectively connected to each plate.
4, 66) have first and second diameters, respectively, wherein the second diameter is smaller than the first diameter and the second diameter tube (66) is a tube of the first diameter. The plate heat exchanger according to claim 1, wherein the plate heat exchanger is hermetically received at (64) to form a hermetic connection. 4. The laminated structure of the pair of plates includes an outermost pair of plates (32, 34), and further comprising a retaining plate adjacent and spaced apart from the outermost pair of plates. Has,
The distance between the retaining plate and the outermost plate pair forms an outermost air passage (22), and fins (24) disposed in the outermost air passage are in thermal contact with the retaining plate. The plate type heat exchanger according to claim 1, wherein 5. The plate comprises plate positioning means each having at least one protrusion (74) and at least one receiving portion (78), wherein the protrusion of one plate (14) of the pair of plates is provided. It is received in the receiving part of the other plate (16) of the pair of plates, so that at least 2 between the plates of the pair of plates.
The plate heat exchanger according to claim 1, wherein two interlock connections are formed. 6. The plate has two pairs of openings (240, 242,
244, 246) and two pairs of tubes (64, 66), one of the pair of openings and tubes being spaced from one end of each plate, and the second pair of openings and tubes being connected to each plate. The plate-type heat exchanger according to claim 1, wherein the plate-type heat exchanger is located at a position separated from an opposite end of the heat exchanger. 7. When the pair of plates and the fins are assembled, the pair of plates is separated from each other by the fins.
4. The plate according to claim 1, wherein the distance between pairs of adjacent plates of the heat exchanger corresponds to the height of fins located between each pair of adjacent plates.
Type heat exchanger. 8. A plurality of joined plate pairs (18), each pair comprising an upper plate (14) and a lower plate (16);
Each pair of plates has a substantially flat portion (56), two longitudinal edges extending the length of the plates, and two edges connecting the longitudinal edges. A pair of plates are hermetically coupled, the flat portions being spaced apart from each other and surrounding a longitudinal flow passage (20) therebetween, and a lateral air passage (22) between adjacent pairs of plates. The plate defines at least two openings (6) therethrough.
0), wherein the openings are spaced from the perimeter of the plate, each opening of one plate being substantially aligned with an opening of the other plate of the pair of plates, the plate surrounding the periphery of each opening; Wherein the plurality of plates are stacked in spaced relation, and each connection is connected from a pair of plates to a connection extending from an adjacent pair of plates to form a hermetic connection. Wherein said connection surrounds a substantially transverse flow passage, said transverse flow passages being spaced apart from each other and in communication with said transverse flow passage, and further comprising one of said transverse passages (36). And means for forming an outlet (28) communicating with the other of said transverse passages (37), said means for forming an outlet (28) communicating with the other of said transverse passages (37). Closes the end and the end not communicating with the inlet and outlet (26, 28). Means for chaining, and further comprising fins (24) disposed in said lateral air passages (22), said fins being in thermal contact with the plate and having a transverse fluid passing therethrough. A passage, wherein said connection is a tube (64, 66), said sealing connection including an overlap portion overlapping at least a portion of said tube, wherein said tube of each upper plate (14) is a respective upper portion; Projecting upwardly from the plates, the tubes of each lower plate (16) extend in opposite transverse directions from the respective lower plates, the edges of the plates each comprising a flange member ( 100 , 130), the flange members being bent. And the bent end overlaps the bent end of a pair of flange members (100, 130) of an adjacent plate, and the outer end area of the fin (24) extends transversely to the tube. Adjacent to or longitudinally outside of the tube In position, the lateral position of the outer end zone plate type heat exchanger, characterized in that in the direction perpendicular to the longitudinal edge of the plate.