EP0097612A2 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP0097612A2
EP0097612A2 EP83730057A EP83730057A EP0097612A2 EP 0097612 A2 EP0097612 A2 EP 0097612A2 EP 83730057 A EP83730057 A EP 83730057A EP 83730057 A EP83730057 A EP 83730057A EP 0097612 A2 EP0097612 A2 EP 0097612A2
Authority
EP
European Patent Office
Prior art keywords
fins
portions
heat exchanger
needle
flat
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.)
Granted
Application number
EP83730057A
Other languages
English (en)
French (fr)
Other versions
EP0097612A3 (en
EP0097612B1 (de
Inventor
Ryomyo Takasago Technical Institute Hamanaka
Michio Takasago Technical Institute Fujimoto
Yoshiaki Nagoya Technical Institute Aoki
Yoshinori Nagoya Technical Institute Watanabe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from JP9146582U external-priority patent/JPS58194384U/ja
Priority claimed from JP15901782U external-priority patent/JPS5965275U/ja
Priority claimed from JP17331282U external-priority patent/JPS5976885U/ja
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP0097612A2 publication Critical patent/EP0097612A2/de
Publication of EP0097612A3 publication Critical patent/EP0097612A3/en
Application granted granted Critical
Publication of EP0097612B1 publication Critical patent/EP0097612B1/de
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
    • 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
    • F28D1/04—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 tubular conduits
    • F28D1/047—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 tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—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 tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings

Definitions

  • the present invention relates to a heat exchanger.
  • the heat exchanger is a device for transmitting heat energy from a high-temperature fluid to a low-temperature fluid through a partition wall in order to accomplish heating or cooling. If the heat exchangers are classified structurally, there will be found a pipe type heat exchanger having fins. When a gas is caused to flow outside a heat transfer pipe, a heat transfer rate between the heat transfer pipe and the gas is small, therefore the pipe type heat exchanger having fins is employed in which the fins are fixed on the surfaces of the heat transfer pipe to increase heat fluxes.
  • This suggested heat exchanger equipped with the needle fins is excellent as a condenser in an air conditioner for a car and a house, an evaporator or the like, and its structure is, for example, as shown in FIGS. 1 to 3 attached hereto. That is to say, as a heat transfer pipe, there is used an extruded flat pipe 1 having chambers therein defined by a plurality of partition walls la; flat surfaces lb of the flat pipe 1 are confronted with each other at an interval and disposed in parallel; and a needle fin group 2, which is formed by corrugating a strip metal plate, is disposed between the confronted flat surfaces lb of the flat pipe 1 in a manner normal to the lengthwise direction of the flat pipe 1.
  • a heat exchange medium is fed into the flat pipe 1 through union joints 3 at opposite ends thereof, and a fluid such as air is caused to flow thereinto from outside in a direction normal to the lengthwise direction of the flat pipe 1 (i.e., in a direction along straight portions of the corrugate needle fins 2) in order to carry out heat exchange.
  • the needle fin group 2 can be prepared by forming numerous rectangular punched portions 2b in the strip metal plate (plate width h), slightly leaving opposite width direction end portions 2a thereof, so that the plate is shaped into a ladder-like form.
  • the thus formed needle fin group 2 is corrugated by causing it to meander along the lengthwise direction of the flat pipe at a meander width w, and the opposite width direction end portions of the needle fin group are brazed or caused to adhere to the confronted flat surfaces lb of the flat pipe 1 by use of a brazing material or an adhesive previously applied on the flat surfaces lb.
  • the needle fin group 2 having numerous needle fins 2c is arranged so that each fin pitch parallel to the flow direction of air 4 may be P L and each fin pitch normal to the flow direction of the air 4 may be P T .
  • An object of the present invention is to provide a heat exchanger which can eliminate conventional drawbacks described above, and can improve yield of a fin material, rigidity of fins and performance of heat transfer and is hard to become a reject article.
  • a heat exchanger comprising a flat pipe for allowing a heat exchange medium to pass therethrough, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, characterized in that the fins take the configuration of a needle fin group which is prepared by punching out the strip metal plate in the portions corresponding to curved portions of the corrugated plate, leaving its opposite width direction end portions; forming numerous width direction notches in portions corresponding to straight portions of the corrugated plate in order to provide fins therebetween; and causing the respective adjacent fins to alternately oppositely project.
  • Another object of the present invention is to provide a heat exchanger which can overcome the aforementioned conventional drawbacks and has less pressure loss and high heat transfer performance.
  • a heat exchanger comprising a flat pipe for allowing a heat exchange medium to pass therethrough, flat surface of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, characterized in that the fins take the configuration of a ladder-like fin group which is formed by punching out the strip metal plate in the portions corresponding to curved portions of the corrugated plate, leaving its opposite width direction end portions; and punching out the strip metal plate in the portions corresponding to straight portions of the corrugated plate in order to form numerous slits therein.
  • Still another object is to provide a heat exchanger adapted to have great heat transfer rate and to generate less noise.
  • a heat exchanger comprising a flat pipe for allowing a heat exchange medium to pass therethrough, flat surfaces of the flat pipe being confronted with each other at an interval and being disposed in parallel, and fins formed by corrugating a strip material plate, the fins being arranged between the confronted flat surfaces above and along their lengthwise direction, characterized in that the fins are removed partially to form portions for allowing a fluid to pass therethrough, and outer peripheral surfaces of the fins are made in the state of a smooth curvy surface.
  • a further object is to provide a heat exchanger which can further improve an air-side heat transfer rate.
  • a heat exchanger comprising a flat pipe, in cross section, meanderingly arranged so that its flat surfaces may be parallel to each other at a predetermined interval, and a ladder-like needle corrugate fin meanderingly arranged in a space defined by the flat surfaces above so as to be parallel to each other in the width direction of the flat pipe, characterized in that the needle portions of the corrugate fin are shaped into a circular form in cross section, and the respective adjacent needle portions are caused to alternately oppositely project from a standard plane.
  • FIGS. 1 (a) and 1 (b) to FIGS. 3 (a) and 3 (b) show a heat exchanger having conventional needle fins
  • FIG. 1 (a) is a front elevational view
  • FIG. 1 (b) is a cross-sectional view
  • FIG. 2 is a partial perspective view
  • FIG. 3 (a) is a partial cross-sectional view
  • FIG. 3 (b) is a partial cross-sectional view of the needle fins
  • FIGS. 4 (a), (b) and (c) and FIG. 5 show a first embodiment of the heat exchanger according to the present invention
  • FIG. 4 (a) is a partial cross-sectional view
  • FIG. 4 (b) is a partial cross-sectional view of the needle fins
  • FIG. 4 (c) is a partial front elevational view
  • FIG. 5 is an enlarged perspective view of the needle fins
  • FIG. 6 (a) and (b) and FIG. 7 show a second embodiment of the heat exchanger according to the present invention
  • FIG. 6 (a) and (b) are partial cross-sectional views, respectively
  • FIG. 7 is an enlarged perspective view of the fin portions
  • FIG. 8 (a), (b) and (c) show a third embodiment of the heat exchanger according to the present invention
  • FIG. 8 (a) is a partial cross-sectional view
  • FIG. 8 (b) is a partial cross-sectional view of the needle fins
  • FIG. 8 (c) is an enlarged perspective view of the needle fins
  • FIG. 9 (a) and (b) and FIG. 10 show a fourth embodiment of the heat exchanger according to the present invention
  • FIG. 9 (a) is a partial cross-sectional view of the needle fins
  • FIG. 9 (b) is an enlarged perspective view of the needle fins
  • FIG. 10 is a diagram showing an air-side heat transfer rate according to the heat exchanger illustrated in FIG. 9 for comparison with that of the heat exchanger in FIG. 8.
  • the needle fin group 20 can be formed from the strip metal plate as follows: The strip metal plate having a wall thickness of T and a width of h is employed; the strip metal plate is punched out in the portions corresponding to curved portions R of the corrugated plate, slightly leaving opposite width direction end portions 20a thereof, in order to form punched portions 20b; the strip metal plate is formed with width direction notches in the portions corresponding to straight portions L of the corrugated plate at an interval substantially equal to the wall thickness T in order to form needle fins 20c between the respective notches; and the adjacent needle fins 20c are caused to alternately project in order to obtain a needle fin group 20 as shown enlargedly in FIG. 5.
  • the thus formed needle fin group 20 is corrugated so that a corrugation width and a fin pitch of the straight portions L may be w and P T , respectively, and the corrugated needle fin group 20 is inserted between the flat surfaces lb of the flat pipe 1. Then, the fin group is secured on the flat surfaces lb by the aid of the brazing material or adhesive which is previously affixed on the flat surfaces lb.
  • a fin pitch parallel to the flow direction of air 4 is P L
  • a fin pitch, normal to the flow direction of the air 4, of the straight portions L of the corrugated plate is P T
  • a fin pitch between the needle fins 20c on the straight line L is Pt
  • a height of the fins (plate width) is h
  • a wave height of the fins (meander width) is w.
  • the portions 20b corresponding to the curved portions after completion of corrugation are only punched out in forming the needle fin group 20, therefore the yield of the used material can be improved to a great degree.
  • the notches are provided and the respective adjacent needle fins 20c are caused to alternately project, therefore the fin rigidity can be improved noticeably. As a result, even if a pressure is applied at the time of securing the needle fin group on the flat surfaces lb, it will not be deformed. This makes it possible to obtain a stable heat exchanger without any deformation.
  • the needle fin group of the present invention can increase the fins by the number corresponding to the punched portions. In consequence, a heat transfer area can be enlarged and a heat transfer performance can thus be enhanced. Additionally, when it is attempted to obtain the same performance as in the conventional one, the heat exchanger according to the present invention can be miniaturized. Moreover, since the needle fins are arranged so as to project alternately oppositely, the development of boundary layers can be restrained and the heat transfer performance can thus be improved.
  • FIGS. 6 and 7 attached hereto show a second embodiment of the present invention.
  • an extruded flat pipe 1 in which partition walls la (which may be disposed along a longer axis, in cross section, of the pipe, though FIG. 1 (b) shows its arrangement along a shorter axis) are installed therein in its lengthwise direction as in the case of the conventional one.
  • the one flat pipe 1 may be caused to meander so that its flat surfaces lb may be confronted with each other at an interval and disposed in parallel, as shown in FIG. 1, alternatively many flat pipes 1 may be connected to each other with the interposition of headers.
  • a needle fin group 30 in a securing manner by use of the brazing material or adhesive, the needle fin group 30 being formed by corrugating a strip metal plate and being disposed there in a style normal to the lengthwise direction of the flat pipe 1 or in an inclined style.
  • the needle fin group 30 of this embodiment is formed as follows:
  • the strip metal thin plate which is a fin material is extensively punched out in the portions corresponding to the curved portions R of the corrugated plate, slightly leaving opposite width direction end portions 30a thereof, in order to form punched portions 30b; and the portions, of the strip metal plate, corresponding to the straight portions L of the corrugated plate are formed with numerous rectangular slits 30c, slightly leaving the opposite width direction end portions 30a thereof, in order to leave ladder-like needle fins 30d which constitute the needle fin group 30.
  • the thus formed group 30 is corrugated by meandering it along the lengthwise direction of the flat surfaces lb of the flat pipe 1.
  • securing the needle fin group 30 on the flat surfaces lb of the flat pipe 1 as a heat transfer pipe can be carried out by brazing or bonding the opposite width direction end portions of the corrugated needle fin group 30 to the flat surfaces lb with the aid of the brazing material or adhesive which is previously applied on the flat surfaces, but at this securing operation, the straight portions L of the corrugated plate may be arranged so as to be parallel to the width direction of the flat pipe 1 or to be inclined as much as an angle 6.
  • the curved portions R of the corrugated plate have no needle fins 30d, therefore the inflow and outflow of the air 4 can smoothly and uniformly carried out without any obstruction.
  • the flow velocity vector 4a of the air 4 at the curved portions R is equal to the flow velocity vector 4b of the air 4 at the straight portions L, and thus the pressure loss of the air is reduced and the heat transfer rate is improved. Therefore, when it is contemplated to obtain the same performance as in the conventional one, the heat exchanger according to the present invention can be miniaturized.
  • FIG. 8 shows a third embodiment of the present invention, and a heat exchanger of this embodiment, as illustrated in FIGS. 8 (a), (b) and (c), comprises a flat pipe 1, in cross section, which is caused to meander so that its flat surfaces lb may be parallel to each other at an interval, and a corrugate fin 40 meanderingly arranged in a space defined between the flat surfaces 16.
  • the corrugate fin 40 has needle portions 40b between its opposite end portions 40a, 40a, and each needle portion 40b is shaped into a circular form in cross section.
  • the corrugate fins 40 are arranged in parallel to each other in the width direction of the flat surfaces 16 of the flat pipe 1, and the respective needle portions 40b are in-line arranged (i.e., arranged in a straight line) at a fin pitch P TI in parallel with the width direction of the flat surfaces 16 (i.e., the inflow and outflow direction of the air flow 4), as illustrated in FIG. 8 (b).
  • the sectional shape of the needles is circular, but it may be elliptic. Furthermore, if edge portions of the needle fin, in addition to the needle portions thereof, are shaped into an elliptic form in cross section, or are finished in the form of smooth curved surface, the pressure loss will be small. Moreover, it is to be noted that a fluid referred to here means a gas or a liquid.
  • the fin portions near which the fluid passes have their outer peripheral surfaces finished in the form of a smooth curved surface, therefore the pressure loss of the fluid which runs along the members having an increased heat transfer area is small. As a result, the generation of noise is also small and the heat transfer rate between the fluid and the members having the increased heat transfer area is great.
  • FIG. 9 shows a fourth embodiment of the present invention, and it is directed to a further improved heat exchanger of the third embodiment illustrated in FIG. 8.
  • This heat exchanger as shown in FIG. 9 (a), comprises a flat pipe in cross section and a corrugate fin 50 meanderingly arranged in a space defined by the flat surfaces lb of the flat pipe 1.
  • needle portions 50b are formed in a ladder-like form between opposite end portions 50a, 50a, and the respective needle portions 50b are shaped into a substantially circular form in cross section.
  • openings 50c there are formed openings 50c, and at the curved portions 50a' of the end portions 50a, there are formed fin-free portions 50d in order to facilitate the inflow and outflow of the air flow 4.
  • bending portions 50e are formed between the needle portions 50b and the opposite end portions 50a, 50a so that the respective adjacent needle portions 50b, 50b may be caused to alternately oppositely project by a predetermined distance from a plane comprising the opposite end portions 50a, 50a.
  • corrugate fins 50 are arranged so that they may be in parallel with each other in the width direction of the flat surfaces lb of the flat pipe 1, and the fin pitch of the needle portions 50b is PTS.
  • the needle portions 50b are caused to alternately project from the plane of the opposite end portions 50a, therefore the downstream needle portions 50b can efficiently be heat exchanged with the air flow 4, which improves the air-side heat transfer rate.
  • P TS 2P TI
  • an effect on the improvement in ⁇ a kcal/m.°C.hr air-side heat transfer rate has been investigated, and obtained results are set forth in FIG. 10.
  • an abscissa axis represents an air flow velocity (Fv ⁇ m/sec) and an ordinate axis represents an improvement ratio of the air-side heat transfer rate of the heat exchanger regarding this embodiment with respect to that of the heat exchanger shown in FIG. 8.
  • the heat exchanger of this embodiment is better in the a a than the one shown in FIG. 8. Further, the improvement ratio of the a tends to decrease with the increase a in the air flow velocity, but within the range usually employed (Fv ⁇ 3 m/sec) , it improves as much as 35% or more
  • the aforesaid heat exchanger can be miniaturized and lightened, if it is attempted to have the same performance as in the conventional one. Therefore, when this heat exchanger is applied as an air conditioner for a car, effects such as saving of a car fuel and expansion of a car space can be obtained.
  • the ladder-like needle corrugate fin 50 can be formed by in-line punching and circularization in cross section, and its punching pitch is a fin pitch for permitting acquisition of a maximum air-side heat transfer rate a al .
  • the'maximum value of the air-side heat transfer rate ⁇ at can be obtained-at a position where the fin pitch P TS is narrower than 2P TI . For this reason, the fin pitch P TS is to be narrowed, which serves to improve the yield of a used material.
  • the heat exchanger having such needle portions can obtain noticeable effects of improvement in the air-side heat transfer rate, miniaturization and lightening of the heat exchanger body, betterment in the yield of the material, and the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP19830730057 1982-06-21 1983-06-21 Wärmetauscher Expired EP0097612B1 (de)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP91465/82 1982-06-21
JP9146582U JPS58194384U (ja) 1982-06-21 1982-06-21 熱交換器
JP159017/82 1982-10-22
JP15901782U JPS5965275U (ja) 1982-10-22 1982-10-22 熱交換器
JP17331282U JPS5976885U (ja) 1982-11-16 1982-11-16 熱交換器
JP173312/82 1982-11-16

Publications (3)

Publication Number Publication Date
EP0097612A2 true EP0097612A2 (de) 1984-01-04
EP0097612A3 EP0097612A3 (en) 1985-01-23
EP0097612B1 EP0097612B1 (de) 1988-08-10

Family

ID=27306751

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830730057 Expired EP0097612B1 (de) 1982-06-21 1983-06-21 Wärmetauscher

Country Status (4)

Country Link
EP (1) EP0097612B1 (de)
AU (1) AU1599483A (de)
CA (1) CA1230872A (de)
DE (1) DE3377666D1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0325261A1 (de) * 1988-01-21 1989-07-26 Sanden Corporation Wärmeaustauscher
US8177932B2 (en) 2009-02-27 2012-05-15 International Mezzo Technologies, Inc. Method for manufacturing a micro tube heat exchanger
DE102017217568A1 (de) * 2017-10-04 2019-04-04 Mahle International Gmbh Wärmeübertrager

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH219262A (de) * 1939-08-28 1942-01-31 Ungarische Radiatoren Fabriks Lamellen-Wärmeaustauschvorrichtung.
FR1119126A (fr) * 1954-02-20 1956-06-15 Escher Wyss Ag Faisceau de tubes pour échangeurs de chaleur et procédé pour sa fabrication
GB1218635A (en) * 1967-04-14 1971-01-06 Chausson Usines Sa Improvements in or relating to heat dissipating surfaces for radiators
US3776015A (en) * 1970-12-01 1973-12-04 Chausson Usines Sa Process for manufacturing expanded and corrugated heat exchanger cores from metal strip material
EP0074122A1 (de) * 1981-09-09 1983-03-16 D. Mulock-Bentley And Associates (Proprietary) Limited Wärmetauscher

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH219262A (de) * 1939-08-28 1942-01-31 Ungarische Radiatoren Fabriks Lamellen-Wärmeaustauschvorrichtung.
FR1119126A (fr) * 1954-02-20 1956-06-15 Escher Wyss Ag Faisceau de tubes pour échangeurs de chaleur et procédé pour sa fabrication
GB1218635A (en) * 1967-04-14 1971-01-06 Chausson Usines Sa Improvements in or relating to heat dissipating surfaces for radiators
US3776015A (en) * 1970-12-01 1973-12-04 Chausson Usines Sa Process for manufacturing expanded and corrugated heat exchanger cores from metal strip material
EP0074122A1 (de) * 1981-09-09 1983-03-16 D. Mulock-Bentley And Associates (Proprietary) Limited Wärmetauscher

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0325261A1 (de) * 1988-01-21 1989-07-26 Sanden Corporation Wärmeaustauscher
US8177932B2 (en) 2009-02-27 2012-05-15 International Mezzo Technologies, Inc. Method for manufacturing a micro tube heat exchanger
DE102017217568A1 (de) * 2017-10-04 2019-04-04 Mahle International Gmbh Wärmeübertrager

Also Published As

Publication number Publication date
EP0097612A3 (en) 1985-01-23
DE3377666T2 (de) 1988-09-15
DE3377666D1 (en) 1988-09-15
AU1599483A (en) 1984-01-05
EP0097612B1 (de) 1988-08-10
CA1230872A (en) 1987-12-29

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