EP0415584B1 - Stack type evaporator - Google Patents
Stack type evaporator Download PDFInfo
- Publication number
- EP0415584B1 EP0415584B1 EP19900308796 EP90308796A EP0415584B1 EP 0415584 B1 EP0415584 B1 EP 0415584B1 EP 19900308796 EP19900308796 EP 19900308796 EP 90308796 A EP90308796 A EP 90308796A EP 0415584 B1 EP0415584 B1 EP 0415584B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- coolant
- stack type
- ribs
- type evaporator
- evaporator according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
- F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0085—Evaporators
Description
- The present invention relates to a stack type evaporator for use in the car cooling system or the like, and more particularly to a stack type evaporator which comprises a plurality of plate-shaped tubular elements each having inner paths for coolant, wherein a plurality of air paths are defined through and by a fin member interposed between one tubular element and the next.
- In general stack type evaporators for the uses mentioned above comprise tubular elements whose inner paths for coolant are in fluid communication with each other in such a state that a coolant circuit is formed between an inlet and an outlet of the coolant. A mist of coolant enters the inlet and flows through the circuit so that heat exchange takes place between the coolant and the air passing through the air paths. The coolant is thus gradually evaporated to become a gas which then flows out of the evaporator through the outlet.
- Fig. 12 shows one of the known tubular elements (such as disclosed in Japanese Utility Model Publication Sho. 53-32375) which has one end portion formed with a
delivery header 10a and areturn header 10b. A coolant stream circuit is formed such that coolant flows through thedelivery header 10a into the inside of the tubular member, advances toward the other end portion thereof where it makes a U-turn and then flows back to thereturn header 10b. Such a coolant stream within the circuit is made turbulent by the existence of many protrudinginner ribs 70 possessed by each of dish-shaped core plates 60 which are secured to each other at their peripheries so as to form a space for the coolant circuit therebetween, theribs 70 being disposed within the space. Theribs 70 are oblique with respect to the flow direction of coolant stream, and as shown by solid lines and broken lines in Fig. 12, eachrib 70 of onecore plate 60 and eachcorresponding rib 70 of the other core plate firmly coupled with the one core plate intersect one another. However, the U-turn of the coolant stream within the circuit of the tubular element is likely to cause a "channel" or uneven flow of coolant in the circuit, thereby bringing about a substantial decrease in the effective heat transfer surface. - It is further to be noted that the
mutually intersection ribs 70 disposed oblique to the direction of coolant flow are disadvantageous in that pressure loss of coolant increases unfavourably in the tubular elements near an outlet port of the evaporator, in spite of lowered efficiency of heat transfer due to the increasing ratio of gas in the coolant which is getting near the outlet. Such a disadvantage depreciates the value of an expected advantage, that is an improved heat transfer efficiency, which will be obtained owing to violent turbulence of coolant in the tubular elements disposed near an inlet port of the evaporator. - A stack type evaporator with fin members interposed between a plurality of stacked plate-shaped tubular elements with inlet and outlet header portions is disclosed in DE-A-3 536 325. Additionally an evaporator having tubular elements with coolant paths formed by alternating ribs at the core plates is disclosed in US-A-4 371 034.
- An object of the present invention, which was made in view of the problems in the known evaporators, is to provide a stack type evaporator which is low in its pressure loss of coolant but high in its heat transfer efficiency.
- According to the present invention a stack type evaporator comprises a plurality of plate-shaped tubular elements of a predetermined thickness, the tubular elements being stacked side by side in a direction of the thickness with a fin member interposed between two of such tubular elements and being composed respectively of a pair of dish-shaped core plates which are provided with a plurality of ribs protruding from a flat body and are fixed to each other at their peripheries so as to form coolant paths, in the pair of core plates facing each other with their ribs arranged inwardly, characterized in that each tubular element comprises an inlet header portion disposed at an end and an outlet header portion disposed at another end, the ribs of each core plate extending parallel with a flow direction of the coolant and arranged at regular intervals of distance to form a row in a direction perpendicular to the flow direction and each rib protruding from one of the paired core plates being disposed intermediate between two ribs protruding from the other core plate in the pair so that end surfaces of the ribs of one core plate are alternately bonded to the flat body of the other core plate in the pair whereby the coolant paths are formed parallel with each other and straight from the inlet header portion toward the outlet header portion, the ribs having outer surfaces formed on the side surfaces of the tubular elements, the rib outer surfaces respectively forming a plurality of open-top groove-like drain ducts extending from one end of the tubular elements toward the other end, whereby water condensed on the side surface of each of tubular element flows through the drain ducts to be discharged at the other end to thereby effectively prevent any water-drop-flying action from occurring.
- The coolant which flows through the tubular elements each provided with the inlet header portion at one end and with the outlet header portion at the other end need not to make any U-turn. Thus any uneven flow of the coolant does not occur in the evaporator of the invention, thereby eliminating the problem that the effective heat transfer surface is decreased and the pressure loss is increased due to the U-turn of coolant in the known apparatuses.
- The coolant can flow through the coolant circuit of evaporator smoothly without being disturbed by the ribs which are formed parallel with the flow direction so that heat transfer takes place uniform throughout the circuit extending from an inlet pipe to an outlet pipe for the coolant, with a decreased pressure loss and with an improved overall efficiency or heat transfer.
- Further, such an alternate position of the ribs of the coupled core plates as employed in the invention wherein the end surface of each rib of one core plate bears against the facing flat body of the other core plate will not only improve heat transfer efficiency but also will secure the core plates more rigidly to each other, thereby improving the pressure resistance of the evaporator. in order to improve heat exchange efficiency, it is desirable to employ a smaller "equivalent diameter" for the coolant paths, the equivalent diameter being such a value as obtained by dividing by an internal periphery length of coolant path a product of cross-sectional area thereof multipled by "4". According to the invention, the equivalent diameter can be made sufficiently small through a rib pitch (i.e. distance between two adjacent ribs) of the core plates is high. In other words, such a high rib pitch in the invention does not significantly reduce the equivalent diameter of coolant paths but makes easier the manufacture of the core plates in the invention. It is also advantageous that the outer flat surfaces of the core plates are so broad that the area of contact with the corrugated fins is increased to further improve the heat exchange efficiency.
- An amount of water which is condensed in the air flow passages defined between adjacent tubular elements can smoothly flow down along draining recesses defined between the ribs. Therefore, the so-called "water-drop-flying" phenomenon is prevented from taking place in the evaporator provided in the invention. In an embodiment wherein a side plate is attached to the outermost fin member, inner grooves or channels formed thereon to extend in a vertical direction may help the condensed water flow down smoothly to avoid the flying of water drops even if a significant amount of water is condensed or flows in between the outer-most tubular element and the side plate.
- The invention will now be described further, by way of example, with reference to the accompanying drawings, in which:-
- Fig. 1 is a side elevation of a core plate, seen from the side of coolant paths, of a first embodiment;
- Fig. 2 is an enlarged cross section on the line 2 - 2 of Fig. 1;
- Fig. 3 is a perspective view showing two core plates constituting one tubular element as well as a corrugated fin member which are in a separated state;
- Fig. 4 is a front elevation showing the assembled state of the evaporator;
- Fig. 5 is a perspective view showing a side plate, corrugated fin members and tubular elements, in their separated state of an alternative embodiment;
- Fig. 6 is a front elevation corresponding to Fig. 5;
- Fig. 7 is a plan view corresponding to Fig. 5;
- Fig. 8 is a side elevation of the tubular element;
- Fig. 9 is a side elevation of a core plate:
- Fig. 10 is a cross section on the line 10 - 10 of Fig. 6;
- Fig. 11 is an enlarged partial front elevation of the evaporator; and
- Fig. 12 is a side elevation of a core plate, seen from the side of coolant paths, of a prior art apparatus.
- Embodiments of the invention which are applied to stack type, evaportors made of aluminum or its alloys for use in the car cooling system will now be described in detail.
- Figs. 1 to 4 illustrate a stack type evaporator manufactured according to a first embodiment of the invention.
- This evaporator comprises a plurality of plate-shaped tubular elements 1 which are disposed upright and stacked side by side in a horizontal direction. The evaporator also comprises
corrugated fin members 2, most of them being interposed respectively between two adjacent tubular elements 1 and remaining one of them disposed outside of the outer-most tubular element. Eachcorrugated fin member 2 is fixed integral with the tubular elements. - Each of the tubular elements 1 is, as shown in Figs. 1 to 4, provided with upper and
lower header portions Coolant paths 1c extending longitudinally of the element 1 are formed intermediate between and in fluid connection with theheader portions coolant paths 1c as a whole thereby assuming a flat path for coolant. - The adjacent tubular elements 1 are tightly combined one another at their
header portions openings 1d. As shown in Fig. 4, theupper header portion 1a of the right-hand (in the drawings) outermost tubular element 1 is connected to a coolant inlet pipe 3, on the other hand theupper header portion 1a of the left-hand (in the drawings) outermost tubular element 1 is connected to a coolant outlet pipe 4. Small blind plates (not shown) are mounted between theupper header portions 1a of the second and third tubular elements near the coolant inlet, between those of the eighth and ninth ones and between the fourteenth and fifteenth ones near the coolant outlet so as to close the coolant-flowingopenings 1d. Similarly, the small blind plates (not shown) are also interposed between thelower header portions 1b of the fifth and sixth tubular elements and between those of the eleventh and twelfth ones so as to close the coolant-flowingopenings 1d. Such blind plates cause the coolant flowing into the evaporator through the inlet pipe 3 to advance in zigzag patterns changing its flow direction at every boundary between adjacent groups of the tubular elements. Heat exchange is effected between the coolant flowing in this way and air streams passing through air paths which are formed between the adjacent tubular elements and through thefin members 2, before the coolant leaves the evaporator through the outlet pipe 4. A side plate 5 (Fig.4) is disposed outside of the outermostcorrugated fin member 2. - The tubular elements 1 are each made by arranging two dish-
shaped core plates 6 into an inside-to-inside relation and by subsequently soldering them at theirperlpheries 6a to be integral with each other. Thecore plates 6 are manufactured by the pressing of any appropriate metal, preferably by the pressing of a brazing sheet. The brazing sheet comprises an aluminum-based alloy core sheet having its front and back surfaces covered with a brazing metal which is applied by the cladding technique. End portions of eachcore plate 6 protrude outwardly to form expandedportions 9. A coolant-flowingopening 1d is formed through a ridge of each expanded portion, in a transverse direction of the core plate extends. Aflange 9a protrudes from a semicircular edge of theelliptical opening 1d. - Formed on inner surface of the
core plate 6 areribs 7 which contribute to the improvement of heat transfer efficiency in the evaporator described above. Theribs 7 run parallel with a flow direction of coolant, i.e. longitudinally of the core plate and extend almost all over the entire length thereof. Theribs 7 are located at regular intervals in the transverse direction although they are slightly offset as a whole toward one side edge of thecore plate 6. - Two
core plates 6 each havingribs 7 are brought into close contact so as to be soldered at theirperlpheries 6a. As seen in Fig. 1 and 2, therib 7 of onecore plate 6 is shown by solid lines and that of the other core plate is shown by broken lines alternate with each other. End surfaces of theribs 7 of onecore plate 6 tightly engage with and are soldered to a flat body 8 between twoadjacent ribs 7 of the other core plate whereby the plurality ofcoolant paths 1c are defined straight from thedelivery header 1a to thereturn header 1b within tubular element 1. - Such
straight coolant paths 1c enhance smoothness of coolant flow by preventing uneven flow or violent agitation of the coolant from taking place in the tubular element 1. Further, the coolant flows so uniformly through all the paths that heat transfer is efficiently effected improving the heat transfer capacity of the evaporator. - In addition, any excessively high accuracy is not required in manufacturing this evaporator since the end surfaces of the
ribs 7 in one core plate need not be strictly aligned with each other but may merely be placed on and soldered to the relatively wide flat body 8 of theother core plate 6, in a state such that as already described the ribs of two core plates alternate in a direction perpendicular to the flow direction of coolant. This structure is also advantageous in that the twocore plates 6 can be easily and securely soldered to enhance the mechanical strength and pressure resistance of the tubular elements 1 in the evaporator. Furthermore, such a structure is also effective to increase the heat transfer surface and to raise the heat transfer efficiency. - Another important feature of this embodiment resides in the shape of the
ribs 7 which are wider at their ends so that thecoolant paths 1c are constricted at their portions near the inlet and outlet. This enables the coolant to flow more uniformly between the paths, preventing any inadvertent decrease in the effective surface of heat transfer. - In order to make the coolant path cross section as large as possible, it is preferable to design the width W1 of
ribs 7 so as to fall within a range from two to four times the thickness "t" of the plate, as illustrated in Fig. 2. -
- A second embodiment of the invention will now be described with reference to Figs. 5 to 11.
- Although the fundamental features of an evaporator in the second embodiment are the same as those in the first embodiment. there are some minor differences for instance in the header portions of tubular elements, in the structure of side plates or other members.
- The evaporator in the second embodiment is also provided with the
tubular elements 101 which have at their longitudinal ends anupper header portion 101a and alower header portion 101b of a bulky shape. The plate-liketubular elements 101 are disposed upright and stacked side by side withcorrugated fin member 102 interposed between two of such elements. Onecorrugated fin member 102 is located outside of the outermosttubular element 101 and is covered with aside plate 105. - Fluid communication passages formed through coolant-flowing
openings 101d is closed between theupper header portions 101a of the fifth and sixth tubular elements near a coolant inlet, and between those of the fourteenth and fifteenth ones near a coolant outlet. Similarly, the passages through theopenings 101d are closed between thelower header portions 101b of the tenth and eleventh tubular elements. such a local closing of the passages causes the coolant flowing into the evaporator through aninlet pipe 103 via aninlet header 103a to advance zigzag changing its flow direction at every boundary between adjacent groups of the tubular elements, before it flows out of the evaporator through anoutlet pipe 104 via anoutlet header 104a. - The
tubular element 101 are constructed, as is in the first embodiment, by facing two dish-like core plates 106 to each other and by soldering them integral with each other.Ribs 107 protruding from the inner surfaces of thecore plates 106 and arranged at regular intervals longitudinally of the plates formcoolant paths 101c which extend straight within eachtubular element 101, from anupper header portion 101a to alower header portion 101b. - Upper and lower expanded
portions 109 of thecore plates 106 are of an elliptical shape, as shown in Figs. 5, 8 and 9, which allows three rows of coolant-flowingopenings 101d to be formed therethrough. There are formedrecesses 109a above and between the coolant-flowingopenings 101d of the upper expandedportions 109 and also below and between theopenings 101d of the lower expandedportions 109.Lugs 109b which are formed corresponding to therecesses 109a are engaged therewith to provide additional soldered surfaces which will improve the pressure resistance of the upper andlower header portions -
Protrusions 106b on the surfaces of thecore plates 106 are used to place thecorrugated fin members 102 in position. Theprotrusions 106b are located adjacent to but more inwardly than the expandedportions 109 and are arranged between theribs 107 as well as outside of theoutermost rib 107 in such a state as forming rows. The upper and lower rows of theprotrusions 106b support as shown in Fig. 11 the upper and lower ends of thecorrugated fin members 102, respectively, when thetubular elements 101 and thefin members 102 are temporarily assembled to alternate with each other before they are soldered. Thus, there will be provided gaps of a predetermined distance between the top surfaces of the fin members and theupper header portions 101a, as well as between the bottom surfaces of the fin members and thelower header portions 101b. Such gaps will function as draininggaps 125 after all the integral parts of the evaporator are bonded to each other in one and single operation by, for example, the soldering method. - As is shown in Fig. 9, the inner width of the expanded
portions 109 is preferably made substantially the same as that of aflat pipe portion 108.Side walls 121 which cover theportions flat pipe portion 108 towards the upper andlower header portions coolant paths 101c including the outermost one are straight fluid connection with theheader portions - As will be seen in Figs. 5 and 6, the
side plates 105 have a plurality ofinner channels 128 which are formed by, for instance, the pressing of metal sheet to extend vertically and parallel with each other. Suchinner channels 128 providevertical drain ducts 129 between theside plate 105 and thecorrugated fin member 102. - In operation of the above described evaporator, heat transfer takes place between the stream of coolant and the stream of air, the former entering the evaporator through the
inlet pipe 103 to flow through the evaporator and leave it through theoutlet pipe 104, while the latter is flowing through air paths defined in thecorrugated fin members 102 disposed between twotubular elements 101 or between onetubular element 101 and theside plate 105. As a result of such heat transfer, the heat of the air stream is absorbed by the evaporator so that a considerable amount of condensed water will be produced in the air paths between twotubular elements 101 or between the outermosttubular element 101 and theside plate 105, or such condensed water will enter the air paths. - The amount of condensed water in the air paths between the two
tubular elements 101 will flow downwards through drain ducts 126 (Fig. 10) which are defined between the outer surface of tubular elements and thecorrugated fin members 102 due to recesses formed by theribs 107. Then, the condensed water will be discharged to the outer bottom surface and thelower header portions 101b. - On the other hand, another amount of condensed water in the air paths between the outermost
tubular element 101 and theside plate 105 will flow downwards likewise throughdrain ducts 126 defined by theribs 107 between the outermosttubular element 101 and thecorrugated fin member 102. in addition, another amount of condensed water will also flow downwards through thedrain ducts 129 formed between theside plate 105 and thecorrugated fin member 102 due to theinner channels 128. Thus, drainage is improved for those air paths in a region mentioned here whereby the water-drop-flying is prevented which has been inevitably caused by the air flow through the known evaporators. - Depth "D2" of the
inner channels 128 is designed such that the amount of condensed water can smoothly flow, and may preferably be set at 0.5 mm or more. - The
inner channels 128 are formed by corrugation of theside plates 105 so that rigidity thereof is increased. Therefore, load can be uniformly imparted to the entire width of a temporary assembly consisting of theside plates 105 and pairs of the alternatingtubular elements 101 andfin members 102, the pairs being interposed between theside plates 105 in "banding" state before the soldering process. - The increased rigidity can make thinner the
side plates 105 to about 0.5 mm, whose thickness has been about 1.6 mm in the known evaporators. - As shown in Figs. 5, 6 and 11, the lowermost portions of the
side plates 105 are pressed to beheader supporting tongues 130 which abut the end surfaces of thelower header portions 101b. Theinner channels 128 extend across thetongues 130, continuously from the main portions of the side plates. This structure of the end plates not only ensures the drainage of condensed water but also increases the mechanical strength at the outer surfaces oflower header portions 101b of the outermosttubular elements 101, to whichportions 101b neither theheader 103a nor the header 103b is attached after all of the evaporator parts are made rigidly integral with each other.
Claims (12)
- A stack type evaporator comprising a plurality of plate-shaped tubular elements (1) of a predetermined thickness, the tubular elements being stacked side by side in a direction of the thickness with a fin member (2) interposed between two of such tubular elements and being composed respectively of a pair of dish-shaped core plates (6) which are provided with a plurality of ribs (7) protruding from a flat body (8) and are fixed to each other at their peripheries so as to form coolant paths, the pair of core plates (6) facing each other with their ribs (7) arranged inwardly, characterized in that each tubular element (1) comprises an inlet header portion (1a) disposed at an end and an outlet header portion (1b) disposed at another end, the ribs (7) of each core plate (6) extending parallel with a flow direction of the coolant and arranged at regular intervals of distance to form a row in a direction perpendicular to the flow direction and each rib (7) protruding from one of the paired core plates (6) being disposed intermediate between two ribs (7) protruding from the other core plate (6) in the pair so that end surfaces of the ribs (7) of one core plate (6) are alternately bonded to the flat body (8) of the other core plate (6) in the pair whereby the coolant paths are formed parallel with each other and straight from the inlet header portion (1a) toward the outlet header portion (1b), the ribs (7) having outer surfaces formed on the side surfaces of the tubular elements, the rib outer surfaces respectively forming a plurality of open-top groove-like drain ducts (126) extending from one end of the tubular elements toward the other end, whereby water condensed on the side surface of each of tubular element flows through the drain ducts to be discharged at the other end to thereby effectively prevent any water-drop-flying action from occurring.
- A stack type evaporator according to claim 1,
characterized in that the tubular elements (1) are disposed vertically and stacked side by side in a horizontal direction. - A stack type evaporator according to claim 1,
characterized in that the core plates (6) are formed by pressing a brazing sheet which comprises a core material of aluminum alloy having front and back surfaces covered with a brazing agent which is applied by a cladding method. - A stack type evaporator according to claim 1,
characterized in that the core plates (6) are formed at their ends with elliptical expanded portions (9) having ridge portions through which a row of coolant-flowing openings are formed. - A stack type evaporator according to claim 4,
characterized in that the expanded portion (9) of one core plate (6) is formed at its outer surface with recesses which are disposed between the coolant-flowing openings, the recesses mating and bonded to corresponding lugs of the other core plate. - A stack type evaporator according to claim 1,
characterized in that the core plates (6) comprise protrusions adapted to determine the positions of upper and lower end surfaces of the corrugated fin members. - A stack type evaporator according to claim 4,
characterized in that the core plates (6) are formed to have substantially the same inner width of the expanded portions as an inner width of flat pipe portions whereby all of the coolant paths including an outermost coolant path extend straight into fluid communication with the inside of the header portions (1a, 1b). - A stack type evaporator according to claim 1,
characterized in that the ribs (7) are wider at their ends than at their intermediate portions whereby the coolant paths are narrowed down near the inlet (1a) and the outlet (1b) header portions. - A stack type evaporator according to claim 1,
characterized in that the ribs (7) are of a width falling within a range of two times to four times a thickness of the core plates. - A stack type evaporator according to claim 1,
characterized in that one of the fin members (102) is disposed on the outside of each outermost tubular element (101) and a side plate (105) having inner vertical channels is disposed on the outside of one fin member (102) whereby drain ducts (129) are provided along the inner channels (128) between the side plate (105) and one fin member (102). - A stack type evaporator according to claim 10,
characterized in that the inner channels (128) run parallel with each other. - A stack type evaporator according to claim 10 or 11,
characterized in that the inner channels (128) have a depth of 0.5 mm or more.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1223685A JP2533197B2 (en) | 1989-08-30 | 1989-08-30 | Multilayer evaporator for air conditioner |
JP223685/89 | 1989-08-30 | ||
JP10429190A JPH043861A (en) | 1990-04-18 | 1990-04-18 | Layered type evaporator |
JP104291/90 | 1990-04-18 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0415584A2 EP0415584A2 (en) | 1991-03-06 |
EP0415584A3 EP0415584A3 (en) | 1991-12-18 |
EP0415584B1 true EP0415584B1 (en) | 1994-03-30 |
Family
ID=26444796
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900308796 Expired - Lifetime EP0415584B1 (en) | 1989-08-30 | 1990-08-09 | Stack type evaporator |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0415584B1 (en) |
DE (1) | DE69007709T2 (en) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5800673A (en) * | 1989-08-30 | 1998-09-01 | Showa Aluminum Corporation | Stack type evaporator |
US5470431A (en) * | 1990-08-20 | 1995-11-28 | Showa Aluminum Corp. | Stack type evaporator |
US5514248A (en) * | 1990-08-20 | 1996-05-07 | Showa Aluminum Corporation | Stack type evaporator |
US5125453A (en) * | 1991-12-23 | 1992-06-30 | Ford Motor Company | Heat exchanger structure |
CA2075686C (en) * | 1992-04-03 | 2003-02-11 | Nobuyuki Okuda | Stack type evaporator |
KR0143540B1 (en) * | 1992-08-27 | 1998-08-01 | 코오노 미찌아끼 | Stacked heat exchanger and method of manufacturing the same |
AU668403B2 (en) * | 1992-08-31 | 1996-05-02 | Mitsubishi Jukogyo Kabushiki Kaisha | Stacked heat exchanger |
KR100353020B1 (en) * | 1993-12-28 | 2003-01-10 | 쇼와 덴코 가부시키가이샤 | Multilayer Heat Exchanger |
JPH08136086A (en) * | 1994-11-01 | 1996-05-31 | Nippondenso Co Ltd | Refrigerant evaporator |
JPH08200977A (en) * | 1995-01-27 | 1996-08-09 | Zexel Corp | Flat tube for heat exchanger and manufacture thereof |
FR2755217B1 (en) * | 1996-10-28 | 1999-01-08 | Valeo Climatisation | IMPROVED STACKED PLATE EVAPORATOR FOR AIR CONDITIONING INSTALLATION, ESPECIALLY A MOTOR VEHICLE |
EP0935115B1 (en) * | 1998-02-05 | 2003-07-09 | Denso Corporation | Heat exchanger constructed by plural heat conductive plates |
CN106610151B (en) * | 2015-10-22 | 2019-05-07 | 丹佛斯微通道换热器(嘉兴)有限公司 | A kind of heat exchanger |
JP2018066534A (en) * | 2016-10-21 | 2018-04-26 | パナソニックIpマネジメント株式会社 | Heat exchanger and refrigeration system |
CN107014230A (en) * | 2017-03-30 | 2017-08-04 | 贵州永红航空机械有限责任公司 | A kind of internal deflector type multipaths plate fin type radiator |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4371034A (en) * | 1979-08-03 | 1983-02-01 | Hisaka Works, Limited | Plate type evaporator |
JPS5623700A (en) * | 1979-08-03 | 1981-03-06 | Fuji Heavy Ind Ltd | Heat exchanger |
US4712612A (en) * | 1984-10-12 | 1987-12-15 | Showa Aluminum Kabushiki Kaisha | Horizontal stack type evaporator |
JP2646580B2 (en) * | 1986-12-11 | 1997-08-27 | 株式会社デンソー | Refrigerant evaporator |
-
1990
- 1990-08-09 EP EP19900308796 patent/EP0415584B1/en not_active Expired - Lifetime
- 1990-08-09 DE DE1990607709 patent/DE69007709T2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
EP0415584A3 (en) | 1991-12-18 |
DE69007709T2 (en) | 1994-07-14 |
DE69007709D1 (en) | 1994-05-05 |
EP0415584A2 (en) | 1991-03-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5152337A (en) | Stack type evaporator | |
EP0234942B1 (en) | Plate type heat exchanger | |
EP0415584B1 (en) | Stack type evaporator | |
AU668403B2 (en) | Stacked heat exchanger | |
US6273183B1 (en) | Heat exchanger turbulizers with interrupted convolutions | |
CA1313183C (en) | Embossed plate heat exchanger | |
CA1064902A (en) | Heat exchange device | |
US5125453A (en) | Heat exchanger structure | |
US3783938A (en) | Disturbing device and heat exchanger embodying the same | |
US4804041A (en) | Heat-exchanger of plate fin type | |
US4756362A (en) | Heat exchanger | |
US4958681A (en) | Heat exchanger with bypass channel louvered fins | |
US4699209A (en) | Heat exchanger design for cryogenic reboiler or condenser service | |
KR100414852B1 (en) | Refrigerant distributor for heat exchanger | |
JPH07167578A (en) | Lamination type heat exchanger | |
EP0678721A1 (en) | Laminated heat exchanger | |
EP0448183A2 (en) | A condenser | |
KR20030072601A (en) | Inner fin for heat exchanger flat tubes and evaporator | |
JPS63271099A (en) | Heat exchanger | |
US4330035A (en) | Heat exchanger | |
EP1007893B1 (en) | Heat exchanger turbulizers with interrupted convolutions | |
EP0203458A1 (en) | Heat-exchanger of plate fin type | |
US1993872A (en) | Radiator core | |
EP0769669A1 (en) | Heat exchanger | |
JP2602788Y2 (en) | Stacked evaporator elements |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): DE FR GB |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): DE FR GB |
|
17P | Request for examination filed |
Effective date: 19920305 |
|
17Q | First examination report despatched |
Effective date: 19921016 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REF | Corresponds to: |
Ref document number: 69007709 Country of ref document: DE Date of ref document: 19940505 |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TQ |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20080821 Year of fee payment: 19 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20080818 Year of fee payment: 19 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20080820 Year of fee payment: 19 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20090809 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20100430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100302 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090809 |